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WO2010046952A1 - Hydraulic pressure generation device - Google Patents

Hydraulic pressure generation device Download PDF

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Publication number
WO2010046952A1
WO2010046952A1 PCT/JP2008/003014 JP2008003014W WO2010046952A1 WO 2010046952 A1 WO2010046952 A1 WO 2010046952A1 JP 2008003014 W JP2008003014 W JP 2008003014W WO 2010046952 A1 WO2010046952 A1 WO 2010046952A1
Authority
WO
WIPO (PCT)
Prior art keywords
plunger
hydraulic pressure
cam
pressure generating
recess
Prior art date
Application number
PCT/JP2008/003014
Other languages
French (fr)
Japanese (ja)
Inventor
北浦一郎
宗近隆幸
Original Assignee
パスカルエンジニアリング株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by パスカルエンジニアリング株式会社 filed Critical パスカルエンジニアリング株式会社
Priority to PCT/JP2008/003014 priority Critical patent/WO2010046952A1/en
Publication of WO2010046952A1 publication Critical patent/WO2010046952A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports

Definitions

  • the present invention relates to a hydraulic pressure generating device, and more particularly to a hydraulic pressure generating device suitable for intermittently supplying hydraulic pressure to two hydraulic pressure supply systems connected to various hydraulic actuators such as machine tools and construction machines.
  • a hydraulic pressure generating device including one electric motor and a plunger pump driven by the electric motor has been put to practical use.
  • the hydraulic pressure discharged from the pump is supplied to a hydraulic actuator such as a hydraulic cylinder via an oil passage.
  • a hydraulic actuator such as a hydraulic cylinder
  • an on-off valve or a direction switching valve is provided in the middle of the oil passage. Normally, it is normal to operate the electric motor continuously after startup.
  • the oil passage is branched, and a pressure reducing valve or the like is interposed in one oil passage to obtain a low pressure oil pressure.
  • a hydraulic pressure generating device comprising a swash plate type hydraulic pump provided with a plurality of plungers is also in practical use.
  • the pump includes a swash plate fixed to the pump casing, a cylinder block fixed to the drive shaft of the electric motor and having a plurality of plunger holes formed therein, and a tip end portion attached to the plunger holes. And a plurality of small plungers.
  • the tandem type swash plate type hydraulic pump of Patent Document 1 includes one electric motor and two swash plate type hydraulic pumps of the same structure driven by the electric motor. Although the discharge amount of the hydraulic pressure is approximately doubled, the discharge pressure is common. JP-A-8-121328
  • the hydraulic pressure is usually supplied by continuous operation.
  • the pump can not follow even if the electric motor is turned on and off, so intermittent discharge can be performed by controlling the on-off valve and direction switching valve provided in the oil passage. Let me do it. This complicates the hydraulic circuit and increases the power consumption.
  • the object of the present invention is to provide a hydraulic pressure generating device suitable for intermittent discharge of hydraulic pressure and capable of reducing power consumption, and to provide a hydraulic pressure generating device having a simple configuration and capable of easily setting two types of discharge pressure and discharge amount. Providing a hydraulic pressure generating device capable of easily changing the characteristics of the discharge pressure and the discharge amount.
  • the hydraulic pressure generating apparatus is a hydraulic pressure generating apparatus for supplying hydraulic pressure to two hydraulic pressure supply systems, comprising: a main body case; and a pair of vertical openings each having an outlet at the lower end thereof.
  • a driven roller rotatably mounted on the upper end of the plunger member of the plunger pump by a horizontal support pin, and the cam mechanisms mounted on the drive shaft and mounted on the upper end of the outer peripheral surface of the driven roller
  • a cam member having an outer peripheral cam surface which abuts, and the pair of cam mechanisms differ by 90 ° or more in timing of top dead center of the two plunger members in the rotational angle of the drive shaft It is characterized in that configured so that.
  • the hydraulic pressure generator drives the pair of plunger pumps by the electric motor via the pair of cam mechanisms, so that one electric motor can control the hydraulic pressure to the two hydraulic pressure supply systems.
  • Supply becomes possible.
  • By changing the shape of the cam member of a pair of cam mechanisms it is possible to generate two systems of hydraulic pressure of different discharge pressure and discharge amount, so that hydraulic pressure to be supplied to various hydraulic actuators can be generated. Excellent.
  • the pair of cam mechanisms is configured to make the timing of the top dead center of the two plunger members different by 90 ° or more in the rotational angle of the drive shaft, so that the load acting on the drive shaft can be leveled. Thus, the size of the electric motor can be reduced.
  • the present invention may adopt the following configuration in addition to the above configuration.
  • the electric motor is a short-time rated high torque motor that exhibits high torque as compared to a continuous rated motor of the same capacity, and starts the electric motor every time the tool of the spindle of the machine tool is replaced
  • a control means is provided for controlling the electric motor such that the operation of the automatic tool changer arm of the changer and the rotational movement of the cam member of each cam mechanism are synchronized.
  • a rotation restricting mechanism is provided which restricts the plunger members from rotating about their vertical axes.
  • each cam member Of the outer peripheral cam surfaces of each cam member, the oil pressure generating cam surface portion extending from the first recess to the second recess in the direction opposite to the rotation direction of the cam member is opposite to the rotation direction of the cam member It is formed longer in direction than the return cam surface portion from the second recess to the first recess.
  • the cam member is formed such that the lowering time for moving each plunger member from the top dead center to the bottom dead center is longer than the rising time for moving from the bottom dead center to the top dead center.
  • a plunger is formed at a lower end portion of each of the plunger members, and a plunger hole into which the plunger is inserted is formed at a lower end portion of each of the plunger pumps.
  • An oil storage chamber for storing oil for supplying each of the plunger pumps was formed at a portion corresponding to the lower outer peripheral portion of the pump.
  • a tapered portion is formed on the outer periphery of the lower end portion of each plunger member at the lower end, and the plunger hole and the oil are formed on the outer peripheral side of the tapered portion when each plunger member is at top dead center.
  • a communication gap communicating the storage chamber was formed.
  • the plunger of each of the plunger members is formed with a recessed hole having an open lower end, and a compression coil spring for elastically urging the plunger member upward is attached to the recessed hole and the plunger hole.
  • An oil replenishment recess having a predetermined size in plan view is formed in the upper end portion of the main body case, and a fluid passage connecting the oil replenishment recess and the upper end of the oil storage chamber is formed in the main body case. It was done.
  • the accumulator connected to the discharge port which discharges an oil pressure from each said plunger hole was provided.
  • FIG. 1 is a cross-sectional view of a spindle unit of a machining center to which a hydraulic pressure generating device according to an embodiment of the present invention is connected. It is a longitudinal cross-sectional view of a hydraulic pressure generating device.
  • FIG. 3 is a cross-sectional view taken along line III-III of FIG.
  • FIG. 4 is a cross-sectional view taken along line IV-IV of FIG.
  • FIG. 5 is a cross-sectional view taken along line VV of FIG. 2;
  • FIG. 6 is a cross-sectional view taken along line VI-VI of FIG. It is a top view of a hydraulic pressure generating device. It is explanatory drawing of a cam member.
  • the hydraulic pressure generating device 30 specific to the present invention is an unclamping hydraulic cylinder 20 for unclamping a clamping mechanism 15 for clamping a tool to the spindle 2 of the spindle unit 1 of a machining center (machine tool). It is applied to a machining center to supply and discharge hydraulic pressure.
  • the spindle unit 1 of the vertical machining center, the clamp mechanism 15, the hydraulic cylinder 20 for unclamping, and the like will be described.
  • the tip end side portion of the spindle 2 of the spindle unit 1 is rotatably supported by the spindle case 5 of the spindle unit 1 via a plurality of bearings 4 a.
  • the upper portion of the spindle 2 is rotatably supported by the spindle case 5 via a bearing 4b.
  • a through hole 6 having a substantially full length is formed in the central portion of the main shaft 2, and a draw bar 7 is movably mounted in the through hole 6 in the axial direction.
  • a coolant supply passage 9 for supplying a coolant to the tool holder 8 is formed at the center of the draw bar 7.
  • An annular spring mounting hole 11 is formed on the outside of the draw bar 7 inside the through hole 6 in the central portion of the main spindle 2, and the disc spring laminate 12 in which a plurality of disc springs are stacked is elastically compressed in the spring mounting hole 11.
  • the draw bar 7 is strongly urged upward by the disc spring laminate 12.
  • a main part of a clamp mechanism 15 for fixing the tool holder 8 mounted in the tapered hole 3 a of the spindle main body 3 to the spindle 2 is provided at the tip of the draw bar 7 inside the tip of the spindle 2.
  • the clamp mechanism 15 clamps the pull stud 8 a at the tip of the tool holder 8 by the elastic force of the disc spring laminate 12 and the plurality of collets 16, but the clamp mechanism 15 is not limited to this clamp mechanism 15.
  • a ball lock type clamp mechanism or other clamp mechanism may be used.
  • a small diameter cylindrical portion 7 a is integrally formed at the upper end portion of the draw bar 7.
  • An annular pressing member 14 is externally fitted and fixed to the small diameter cylindrical portion 7 a in the middle step portion of the spindle 2 so that the pressing member 14 and the draw bar 7 move up and down integrally with the spindle main body 3. .
  • a cylindrical member 18 extending downward is fixedly fitted on the tip of the output shaft 17 a of the electric motor 17 erected above the main shaft 2.
  • the upper end portion of the draw bar 7 is inserted into the lower end portion of the cylindrical member 18.
  • the cylindrical member 18 is connected to the upper end portion of the main spindle body 3 via the pressing member 14, and transmits the rotational driving force of the electric motor 17 to the main spindle 2.
  • a coolant supply passage 19 formed on an output shaft 17 a of the electric motor 17 is connected to the coolant supply passage 9 inside the draw bar 7.
  • the unclamping hydraulic cylinder 20 includes a cylinder main body 21 fixed to the main shaft case 5, an annular piston member 22, and a hydraulic operating chamber 24 provided with hydraulic pressure for releasing the clamp formed on the upper side of the piston member 22.
  • a hydraulic pressure chamber 25 is provided under the piston member 22 and is supplied with hydraulic pressure for returning movement, a hydraulic pressure supply port 26a, 26b, and a hydraulic pressure generating device 30 described later, which hydraulic pressure supply port 26a, 26b.
  • the hydraulic hoses 28a and 28b (corresponding to two hydraulic pressure supply systems) connected to the discharge ports 33A and 33B are provided.
  • the hydraulic pressure generating device 30 includes a main body case 31, plunger pumps 50A and 50B incorporated in the main body case 31 in an upright posture, accumulators 59A and 59B, and driven rollers 61A,
  • the cam mechanisms 60A and 60B respectively including 61B and cam members 63A and 63B, a pair of rotation restricting mechanisms 86 for the plunger members 51A and 51B of the plunger pumps 50A and 50B, and the plungers via the cam mechanisms 60A and 60B
  • the main body case 31 is constituted by a lower end case 32, a plunger case 35, a cylindrical case 38, an intermediate case 42, an upper case 45 and the like.
  • the lower end case 32 is fixed to the plunger case 35 by a plurality of bolts, and the plunger case 35, the pair of middle case 42 and the upper case 45 are fixed by a plurality of positioning pins and a plurality of bolts.
  • a discharge port 33A and an oil passage 34A of the plunger pump 50A are formed in the right side portion of the lower end case 32, and an accumulator 59A for storing an extra hydraulic pressure is connected to the oil passage 34A.
  • a discharge port 33B of the plunger pump 50B and an oil passage 34B are formed on the left side portion of the lower end case 32, and an accumulator 59B for storing an extra hydraulic pressure is connected to the oil passage 34B.
  • a vertically oriented rod hole 36A and a plunger hole 37A connected to the lower end of the rod hole 36A are formed concentrically and in communication.
  • the lower end of the plunger hole 37A communicates with the discharge port 33A.
  • a vertically oriented rod hole 36B and a plunger hole 37B connected to the lower end of the rod hole 36B are formed concentrically and in communication.
  • the lower end of the plunger hole 37B communicates with the discharge port 33B.
  • the cylindrical case 38 is externally fitted to the lower portion of the plunger case 35, and the oil case 40 located on the outer peripheral side of the plunger pumps 50A and 50B by the plunger case 35 and the cylindrical case 38. Is formed.
  • the oil storage chamber 40 stores oil supplied to the plunger pumps 50A and 50B.
  • the annular oil storage chamber 40 is sealed by a plurality of seal members.
  • the pair of middle stage cases 42 respectively have an annular plate portion 42 a and a cylinder portion 42 b, and the middle stage case 42 is mounted so as to be sandwiched between the plunger case 35 and the upper case 45.
  • a seal member 42c is mounted on the outer peripheral portion of the cylindrical portion 42b.
  • the plunger pump 50A includes a rod hole 36A and a plunger hole 37A, a plunger member 51A movably attached to the rod hole 36A and the plunger hole 37A, and a lower end portion of the plunger member 51A.
  • the plunger 52 is inserted into the formed plunger hole 37A, and the rod portion 53 integrally formed with the plunger 52 is provided on the top of the plunger member 51A.
  • the plunger member 51A is driven to move up and down by a reduction gear electric motor 90 via the cam mechanism 60A, and the plunger 52A is driven to move back and forth in the plunger hole 37A to generate hydraulic pressure, and the hydraulic pressure is discharged from the discharge port 33A.
  • the lower end portion of the rod hole 36A communicates with the oil storage chamber 40 through the annular recess 55a and the hole 55b.
  • a tapered portion 52a is formed on the outer periphery of the lower end portion of the plunger 52 so as to decrease in diameter toward the lower side.
  • a tapered surface 37a is formed at the upper end portion of the plunger hole 37A to increase in diameter upward.
  • a lower end open recess 52b is formed in the plunger 52, and a compression coil spring 57 for elastically biasing the plunger member 51 upward is attached to the recess 52b and the plunger hole 37A.
  • a seal member 37b is attached to the plunger hole 37A below the tapered surface 37a.
  • a wear ring 36a and two-stage seal members 36b and 36c are attached to the wall of the rod hole 36A.
  • the cam mechanism 60A has a driven roller 61A rotatably mounted on the upper end portion of the plunger member 51A by a horizontal support pin 62, and an outer peripheral surface of the driven roller 61A.
  • the cam member 63A has an outer peripheral cam surface 64 in contact with the upper end of the support shaft 71, which is fixed to the cam member 63A in a penetrating manner.
  • the cam member 63A is rotationally driven by rotationally driving the support shaft 71 by the electric motor 90 with a reduction gear.
  • the driven roller 61A protrudes upward from the regulation hole 53a at the upper end of the rod portion 53 of the plunger member 51A, and the position of the follower roller 61A is regulated by the regulation hole 53a.
  • a support shaft 71 supporting the cam member 63A is an output shaft of the reduction motor-equipped electric motor 90.
  • the electric motor 90 with a reduction gear is fixed to the upper case 45 by fitting the fitting portion 91a of the reduction gear case to the fitting hole 45a of the upper case 45 via a ring 91b.
  • the tip end of the support shaft 71 is supported by the bearing 72 on the upper case 45.
  • the cam members 63A and 63B are rotationally restrained by the key with respect to the support shaft 71, and their axial positions are restricted by the annular spacers 74a and 74b.
  • the spacer 74 a is regulated by the bearing 72, and the bearing 72 is regulated by the sealing member 76.
  • the fitting cylindrical portion 76a of the sealing member 76 is fitted in the hole 45b of the upper case 45 and sealed by the sealing member 76b.
  • An oil seal 77 is mounted between the support shaft 71 and the fitting cylinder 76a.
  • a disc member 79 for controlling the electric motor 90 is attached to an outer end of the support shaft 71 outside the sealing member 76, and a plurality of proximity switches 81 for detecting the disc member 79 is an upper case. It is provided at 45.
  • the cam members 63A and 63B shown in FIG. 8 when the driven rollers 61A and 61B respectively abut on the point A, the plunger members 51A and 51B become the top dead center (upper limit position) and the driven rollers 61A and 61B are respectively at the point B When in contact, the plunger members 51A and 51B are at the bottom dead center (lower limit position).
  • the electric motor 90 when stopping the cam members 63A, 63B at the top dead center, the electric motor 90 is turned off when the first points C of the cam members 63A, 63B abut against the driven rollers 61A, 61B, respectively. Do. Further, when stopping the cam members 63A, 63B at the bottom dead center, the electric motor 90 is turned off when the second points D of the cam members 63A, 63B respectively abut the driven rollers 61A, 61B.
  • a cover member 83 for closing the outer side of the disk member 79 is provided, and the cover member 83 is fixed to the upper case 45 by a plurality of bolts.
  • the cam storage chamber 85 in which the cam mechanisms 60A and 60B in the upper case 45 are stored communicates with the gear storage chamber in the reduction gear case 91 of the reduction motor-equipped electric motor 90, and the cam storage chamber 85 and the gear storage chamber Is filled with lubricating oil.
  • the outer peripheral surfaces of the rod portions 53A, 53B of the plunger members 51A, 51B are also lubricated with the above-described lubricating oil.
  • the plunger case 35 is formed with a lubricant oil release passage 35a for discharging a part of the lubricant oil.
  • cam members 63A and 63B will be described, but since the cam members 63A and 63B have the same configuration, only the cam member 63A will be described.
  • the cam members 63A and 63B are configured to make the timing of the top dead center of the plunger members 51A and 51B different by 180 ° at the rotation angle of the drive shaft 71.
  • an upper end portion of the driven roller 61A engages with a portion of the outer peripheral cam surface 64 of the cam member 63A that engages with the driven roller 61A when the plunger member 51A reaches the top dead center.
  • a recess 65 is formed.
  • a second concave portion 66 with which the upper end portion of the driven roller 61A is engaged is formed in a portion of the outer peripheral cam surface 64 of the cam member 63A which engages with the driven roller 61A when the plunger member 51A reaches the bottom dead center. ing.
  • the first recess 65 is recessed in a partial arc toward the center point of the cam member 63A
  • the second recess 66 is recessed in a partial arc toward the center point of the cam member 63A.
  • both side portions of the point A have an overall flat shape, but the radius from the axial center P of the cam member 63A is minimized at the position of the point A in the first recess 65 .
  • both side portions of the point B have a curved shape as a whole, but the radius from the axial center P of the cam member 63A is minimized at the position of the point B in the second recess 66.
  • the spring 57 which urges the plunger member 51A upward is a spring 57 which exerts a strong elastic force
  • the plunger member 51A becomes a top dead center.
  • the rotation of the cam member 63A is stopped.
  • the rotation of the cam member 63A stops at the point B where the plunger member 51A is at the bottom dead center.
  • the oil pressure generating cam surface portion 67 extending from the first recess 65 to the second recess 66 in the direction opposite to the rotational direction (arrow direction of FIG. 8) of the cam member 63A It is formed longer than the return cam surface portion 68 from the second recess 66 to the first recess 65 in the direction opposite to the rotational direction of the member 63. That is, the cam member 63A is formed such that the lowering time for the plunger member 51A to move from the top dead center to the bottom dead center is longer than the rising time for moving from the bottom dead center to the top dead center.
  • the hydraulic pressure generating cam surface portion 67 is formed in a circumferential range of about 210 degrees with respect to the axial center P, and the return cam surface portion 68 is circumferential direction of about 150 degrees with respect to the axial center P. It is formed in the range. Since the hydraulic pressure generating cam surface portion 67 is formed to be long in the circumferential direction, the radius increase slope of the hydraulic pressure generating cam surface portion 67 can be reduced to miniaturize the electric motor 90.
  • the outer peripheral surface 61a of the driven rollers 61A, 61B is a cylindrical surface, and the outer peripheral cam surface 64 of the cam members 63A, 63B is in contact with the outer peripheral surfaces 61a of the driven rollers 61A, 61B. It is desirable that the axial center 62a of the support pin 62 and the axial center 71a of the support shaft 71 be always in parallel in order to be formed.
  • pin support portions 53b for supporting both end portions of the support pins 62 are formed at the upper end portions of the plunger members 51A and 51B, and the width (the width in the direction orthogonal to the support pins 62) of the pin support portions 53b is a plunger member It is formed in about half the width of the diameter of the upper end part of 51A, 51B.
  • a cross-shaped cross-shaped hole 87 is formed in the cylinder portion 42b of the middle case 42 in plan view, and the vertical wall surfaces of the cross-shaped hole 87 make surface contact with the pin support portion 53b and the plunger members 51A and 51B.
  • a pair of rotation restricting surfaces 88 are formed to restrict rotation of the Even when the plunger members 51A and 51B are at the lower limit position, the rotation restricting surface 88 restricts the rotation.
  • the cross hole 87 and the rotation restricting surface 88 correspond to the rotation restricting mechanism 86.
  • the electric motor 90 with a reduction gear is a reduction gear 92 fixedly provided on the upper case 45, and an electric motor for inputting rotational driving force to the input shaft of this reduction gear.
  • a motor 93 is a short-time rated high torque motor that exhibits high torque as compared to a continuous rated motor of the same capacity.
  • the electric motor 93 is a four-phase three-phase induction motor with 0.4 kW, 200 V, 50/60 Hz, 1500/1800 rpm, rated for 20 seconds.
  • an oil replenishment recess 95 having a predetermined size in a plan view is formed.
  • An oil supply port 97 and a cap 98 capable of opening and closing the oil supply port 97 are provided on a lid member 96 for covering the oil supply recess 95.
  • the upper case 45, the middle case 42, and the plunger case 35 are formed with two fluid passages 99a and 99b that communicate the upper end of the oil replenishment recess 95 and the upper end of the oil storage chamber 40.
  • the control unit 100 for controlling the machining center includes an operation panel 101, a spindle drive control system 102, an X axis drive control system 103, a Y axis drive control system 104, a Z axis drive control system 105, an ATC 106, and the like.
  • the hydraulic pressure generator 30 and the like are connected.
  • the control unit 100 includes an ATC control unit 108 that controls an ATC (automatic tool changer) (not shown), and an electric motor control unit 109 with a reduction gear that controls the reduction motor and electric motor 90 of the hydraulic pressure generation device 30.
  • ATC control unit 108 that controls an ATC (automatic tool changer) (not shown)
  • an electric motor control unit 109 with a reduction gear that controls the reduction motor and electric motor 90 of the hydraulic pressure generation device 30.
  • a signal is transmitted and received between the ATC control unit 108 and the electric motor control unit 109, and the ATC 106 and the electric motor 90 with a reduction gear are controlled to cooperate with each other. That is, the electric motor 90 is controlled so that the operation of the automatic tool change arm and the rotational movement of the cam members 63A and 63B are synchronized while the electric motor 90 is started every time the tool is replaced.
  • the rotation operation of the cam member 63A is an operation for releasing the clamp
  • the rotation operation of the cam member 63B is an operation for clamping.
  • FIG. 10 is a diagram showing the relationship between the rotation angle of the cam member 63A and the stroke of the plunger member 51A of the plunger pump 50A.
  • FIG. 11 is a graph showing the rotation angle of the cam member 63A and the piston stroke of the unclamping hydraulic cylinder 20. It is a diagram which shows a relation. Since the rotation angle of the cam member 63B at this time is different from that of the cam member 63A by 180 °, the relationship between the cam member 63B and the stroke of the plunger member 51B is 180 in FIG. 10 compared with that of the cam member 63A. It will be off-set.
  • FIG. 12 is a diagram showing the relationship between the rotation angle (horizontal axis) of the cam shaft of the cam mechanism that pivots the ATC arm of the ATC around the vertical axis and raises and lowers it, and the turning angle (vertical axis) of the ATC arm;
  • FIG. 13 is a diagram showing the relationship between the rotation angle (horizontal axis) of the cam shaft and the elevation stroke of the ATC arm.
  • the "positive" value of the up-and-down stroke of the ATC arm indicates a downward stroke. Since the operation of the ATC arm and the operation of the unclamping hydraulic cylinder 20 are linked, the cycle time of 0 to 360 ° in the horizontal axis of FIGS. 10 and 11 and 0 of the horizontal axis in FIGS. 12 and 13. The cycle time of ⁇ 360 ° is set at the same time.
  • the on / off control of the electric motor 90 is controlled based on the synchronization signal from the ATC control unit 108 and detection signals from a plurality of proximity switches 81 linked to the disk member 79 attached to the support shaft 71.
  • the clamp mechanism 15 in the main spindle 2 is held in the clamp state, the electric motor 90 is stopped, the plunger member 51B is at the bottom dead center, and driven by the second recess 66 of the cam member 63B.
  • the roller 61B is engaged, and the plunger member 51A is at a position slightly lowered from the top dead center, and the driven roller 61A is in contact with the point slightly moved in the rotational direction from the first recess 65 of the cam member 63A. 51B holds the initial position.
  • the control unit 100 drives and controls the ATC 106 and the electric motor 90 so as to form the time chart as described above via the ATC control unit 108 and the electric motor control unit 109 with a reduction gear. .
  • the hydraulic pressure generated in the hydraulic pressure generating device 30 is supplied to the hydraulic pressure operating chamber 24 of the unclamping hydraulic cylinder 20 at a predetermined timing, the hydraulic pressure in the hydraulic pressure operating chamber 25 is discharged, and the clamp mechanism 15 is unclamped.
  • the electric motor 90 is stopped for a predetermined time. At this time, the plunger member 51A is held at the bottom dead center for a short time with the second recess 66 of the cam member 63A engaged with the driven roller 61A.
  • the cam member 63A rotates to supply the hydraulic pressure to the hydraulic operation chamber 24 for replacing the tool holder 8
  • the cam member 63B also rotates, and the plunger member 51B passes through the first recess 65. Therefore, the hydraulic pressure of the hydraulic actuation chamber 25 can be discharged from the communication gap.
  • the excess hydraulic pressure until discharged is stored in the accumulator 59B.
  • the driven roller 61B is in contact with a point slightly moved in the rotational direction from the first concave portion 65 of the cam member 63B, and is held at a position slightly lowered from the top dead center.
  • the electric motor 90 is released from the stop to raise the plunger member 51A, remove the hydraulic pressure from the hydraulic operation chamber 24 of the unclamping hydraulic cylinder 20, and lower the plunger member 51B.
  • the hydraulic pressure is supplied to the hydraulic operation chamber 25 so that the second concave portion 66 of the cam member 63B is engaged with the driven roller 61B (initial position) to hold the plunger member 51B at the bottom dead center.
  • the plunger member 51A passes through the first recess 65 as the cam member 63A rotates, so that the hydraulic pressure of the hydraulic actuation chamber 24 can be discharged from the communication gap.
  • the excess hydraulic pressure until discharged is stored in the accumulator 59A.
  • the plunger member 51A is in a state in which the driven roller 61A is in contact with a position slightly beyond the first concave portion 65 of the cam member 63A, and is held at a position slightly lowered from the top dead center.
  • the hydraulic pressure generation device 30 drives the pair of plunger pumps 50A and 50B by the electric motor 90 via the pair of cam mechanisms 60A and 60B, two systems of one electric motor 90 are used. Hydraulic pressure can be supplied to the hydraulic pressure supply system. Further, when the unclamping operation and the clamping operation are alternately performed, intermittent discharge can be easily performed by the on / off control of the electric motor 90 through the cam mechanisms 60A and 60B having high followability. Therefore, when intermittently discharging, the power consumption of the electric motor 90 can be reduced.
  • the plunger members 51A and 51B are not stopped when reaching the top dead center, but the electric motor 90 may be stopped and stopped at the top dead center.
  • the first concave portions 65 formed on the outer peripheral cam surfaces 64 of the cam members 63A and 63B are engaged with the driven rollers 61A and 61B, whereby the plunger members 51A and 51B of the plunger pumps 50A and 50B are at the top dead center.
  • the cam members 63A and 63B can be accurately stopped when reaching the
  • the electric motor 90 is a short time rated high torque motor, it can be a small motor as compared with the continuous rated motor, and the manufacturing cost is also low.
  • the oil pressure generating cam surface portion 67 extending from the first recess 65 to the second recess 66 in the direction opposite to the rotational direction of the cam members 63A and 63B is a return cam surface portion extending from the second recess 66 to the first recess 65 Since it is formed to be longer than 68, it is possible to miniaturize the electric motor 93 by reducing the radius increasing slope of the hydraulic pressure generating cam surface portion 67.
  • the oil storage chamber 40 for storing oil for supplying the plunger pumps 50A, 50B is formed in a portion corresponding to the outer peripheral side portion of the lower portion of the plunger pumps 50A, 50B, oil is supplied to the plunger pumps 50A, 50B.
  • Structure is simplified.
  • a tapered portion 52a is formed on the outer periphery of the lower end portion of each plunger 52 so as to decrease in diameter toward the lower side, and when the plunger members 51A and 51B are at top dead center, the plunger hole 37 and the oil accommodating chamber 40 are formed on the outer peripheral side of the tapered portion 52a. Since the communication gap communicating is formed, the oil can be reliably supplied from the oil storage chamber 40 to the plunger holes 37A and 37B by a simple structure, and the check valve etc. can be omitted. The oil can be returned from the unclamping hydraulic cylinder 20 to the oil storage chamber 40 when the clamping operation is performed.
  • a lower end open recessed hole 52b is formed in each plunger 52 of the plunger members 51A and 51B, and a compression coil spring which elastically biases the plunger members 51A and 51B upward to the recessed hole 52b and the plunger holes 37A and 37B. Since 57 is mounted, the structure of the plunger members 51A, 51B is not complicated.
  • An oil replenishing recess 95 having a predetermined size in plan view is formed in the upper end portion of the main body case 31, and at least two fluids connecting the oil replenishing recess 95 and the upper end of the oil storage chamber 40 to the main body case 31. Since the passages 99a and 99b are formed, when the oil storage chamber 40 is refilled with oil, the inflow of oil and the exhaust of air in the oil storage chamber 40 become smooth.
  • the accumulators 59A, 59B connected to the discharge ports 33A, 33B for discharging the hydraulic pressure from the plunger holes 37A, 37B are provided, the excess hydraulic pressure remaining without being filled in the unclamping hydraulic cylinder 20 is accumulated when unclamping. 59A, 59B, and when the clamp member 15 is moved up when the clamp mechanism 15 is operated, the hydraulic pressure absorbed by the accumulators 59A, 59B can be recovered in the plunger holes 37A, 33B. it can.
  • the tool replacement time is shortest. Can be done quickly. Since the hydraulic pressure generating device 30 includes the accumulators 59A and 59B connected to the discharge ports 33A and 33B, the volume of the hydraulic pressure generating device 30 is equal to the volume of the hydraulic operating chambers 24 and 25 of the unclamping hydraulic cylinder 20. Because the hydraulic pressure generating device 30 can be used by connecting to various sizes of unclamping hydraulic cylinders 22, it is excellent in versatility.
  • the hydraulic pressure generation device 30 drives the pair of plunger pumps 50A and 50B by the electric motor 90 via the pair of cam mechanisms 60A and 60B, so that hydraulic supply to two systems by one electric motor 90 is possible. It will be possible.
  • By changing the shape of the cam members 63A and 63B of the pair of cam mechanisms 60A and 60B it is possible to generate two systems of hydraulic pressure of different discharge pressure and discharge amount, so generate hydraulic pressure supplied to various hydraulic actuators. It is excellent in versatility because it can Moreover, since it is not necessary to adopt a directional switching valve or a pressure reducing valve in the oil passage, the manufacturing cost can be reduced. Since the discharge pressure and the discharge amount can be easily changed by replacing the cam members 63A and 63B of the cam mechanisms 60A and 60B, the versatility in manufacturing the hydraulic pressure generating device is excellent.
  • the cam mechanisms 60A and 60B are configured to make the timing of the top dead center of each of the plunger members 51A and 51B different by 180 degrees in the rotation angle of the drive shaft, so balancing of the load acting on the drive shaft is achieved.
  • the size of the electric motor can be reduced.
  • first and second recesses 65 and 66 are not limited to those shown in the drawings, and may be recesses of various shapes engageable with the tops of the driven rollers 61A and 61B.
  • the cam mechanisms 60A and 60B may be configured to make the timing of the top dead center of the two plunger members 51A and 51B different by 90 ° or more at the rotation angle of the drive shaft.
  • the electric motor 17 that rotationally drives the spindle 2 may be a built-in electric motor incorporated in the spindle case 5.
  • This hydraulic pressure generating device is suitable for intermittently supplying hydraulic pressure to two hydraulic pressure supply systems connected to various hydraulic actuators such as machine tools and construction machines, and can reduce power consumption.
  • Two types of discharge pressure and discharge amount can be easily set and have a simple configuration. The characteristics of the discharge pressure and the discharge amount can be easily changed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

A hydraulic pressure generation device (30) has a body case (31), a pair of plunger pumps (50A, 50B) vertically mounted in the body case and respectively having discharge openings at the lower ends of the plunger pumps, a common drive shaft (71) for driving the pair of plunger pumps, an electric motor (90) provided with a reduction gear and rotationally driving the drive shaft, and a pair of cam mechanisms (60A, 60B) connected to the drive shaft and driving the pair of plunger pumps. The pair of cam mechanisms has follower rollers (61A, 61B) rotatably mounted on the upper ends of plunger members (51A, 51B) of the plunger pumps by means of horizontal support pins, and also has cam members (63A, 63B) mounted on the drive shaft and having outer peripheral cam surfaces making contact with the upper ends of the outer peripheral surfaces of the follower rollers. The pair of cam mechanisms is adapted such that the timings of the top dead centers of the two plunger members are different by 90 degrees or more in terms of the angle of rotation of the drive shaft.

Description

油圧発生装置Hydraulic pressure generator
　本発明は、油圧発生装置に関し、特に工作機械や建設機械等の種々の油圧アクチュエータに接続される２系統の油圧供給系に油圧を間欠的に供給するのに好適の油圧発生装置に関する。 The present invention relates to a hydraulic pressure generating device, and more particularly to a hydraulic pressure generating device suitable for intermittently supplying hydraulic pressure to two hydraulic pressure supply systems connected to various hydraulic actuators such as machine tools and construction machines.
　従来、１台の電動モータとこの電動モータで駆動されるプランジャポンプからなる油圧発生装置が実用化されている。このポンプから吐出される油圧は、油路を介して油圧シリンダなどの油圧アクチュエータに供給される。油路への油圧の供給をオン、オフする場合は、油路の途中部に開閉弁や方向切換弁が設けられる。通常、起動後は電動モータを連続運転するのが普通である。また、圧力の異なる２種類の油圧が必要である場合には、油路を分岐し、その一方の油路に減圧弁等を介装して、低圧の油圧にする。 Conventionally, a hydraulic pressure generating device including one electric motor and a plunger pump driven by the electric motor has been put to practical use. The hydraulic pressure discharged from the pump is supplied to a hydraulic actuator such as a hydraulic cylinder via an oil passage. When the supply of hydraulic pressure to the oil passage is turned on or off, an on-off valve or a direction switching valve is provided in the middle of the oil passage. Normally, it is normal to operate the electric motor continuously after startup. In addition, when two types of oil pressure different in pressure are required, the oil passage is branched, and a pressure reducing valve or the like is interposed in one oil passage to obtain a low pressure oil pressure.
　複数のプランジャを備えた斜板式油圧ポンプからなる油圧発生装置も実用に供されている。このポンプは、ポンプケーシングに固定された斜板と、電動モータの駆動軸に固定され複数のプランジャ孔が形成されたシリンダブロックと、これらプランジャ孔に装着され先端部が斜板に当接された複数の小型プランジャとを有している。
　特許文献１のタンデム型斜板式油圧ポンプでは、１台の電動モータと、この電動モータで駆動される２台の同構造の斜板式油圧ポンプとを有する。油圧の吐出量は約２倍になるが、吐出圧は共通である。
特開平８- １２１３２８号公報 A hydraulic pressure generating device comprising a swash plate type hydraulic pump provided with a plurality of plungers is also in practical use. The pump includes a swash plate fixed to the pump casing, a cylinder block fixed to the drive shaft of the electric motor and having a plurality of plunger holes formed therein, and a tip end portion attached to the plunger holes. And a plurality of small plungers.
The tandem type swash plate type hydraulic pump of Patent Document 1 includes one electric motor and two swash plate type hydraulic pumps of the same structure driven by the electric motor. Although the discharge amount of the hydraulic pressure is approximately doubled, the discharge pressure is common.
JP-A-8-121328
　従来の上記の油圧発生装置では、通常、連続運転により油圧を供給するものである。しかし、ポンプから油圧を短時間だけ間欠吐出させるような場合、電動モータをオン・オフ制御してもポンプが追従できないため、油路に設けた開閉弁や方向切換弁を制御することにより間欠吐出を行わせる。このため、油圧回路が複雑化し、電力消費量が多くなる。 In the above-mentioned conventional hydraulic pressure generating device, the hydraulic pressure is usually supplied by continuous operation. However, when the hydraulic pressure is intermittently discharged from the pump for a short time, the pump can not follow even if the electric motor is turned on and off, so intermittent discharge can be performed by controlling the on-off valve and direction switching valve provided in the oil passage. Let me do it. This complicates the hydraulic circuit and increases the power consumption.
　異なる圧力の油圧を発生させる為には、減圧弁を設ける必要があるから、油圧回路が複雑化する。吐出圧や吐出量（油圧発生特性）を変更するには、ポンプ数を変更したり、減圧弁を設けたりする必要があるので、容易に対応できない。 In order to generate hydraulic pressure of different pressure, it is necessary to provide a pressure reducing valve, which complicates the hydraulic circuit. In order to change the discharge pressure or the discharge amount (hydraulic pressure generation characteristic), it is necessary to change the number of pumps or to provide a pressure reducing valve, which can not be easily coped with.
　本発明の目的は、油圧の間欠吐出に好適で電力消費量を節減できる油圧発生装置を提供すること、２種類の吐出圧・吐出量を容易に設定でき且つ簡単な構成の油圧発生装置を提供すること、吐出圧・吐出量の特性を容易に変更できる油圧発生装置を提供すること、などである。 The object of the present invention is to provide a hydraulic pressure generating device suitable for intermittent discharge of hydraulic pressure and capable of reducing power consumption, and to provide a hydraulic pressure generating device having a simple configuration and capable of easily setting two types of discharge pressure and discharge amount. Providing a hydraulic pressure generating device capable of easily changing the characteristics of the discharge pressure and the discharge amount.
　本発明の油圧発生装置は、２系統の油圧供給系に油圧を供給するための油圧発生装置において、本体ケースと、この本体ケースに夫々立向きに組み込まれ下端に吐出口を夫々有する１対のプランジャポンプと、これらプランジャポンプを駆動する共通の駆動軸及びこの駆動軸を回転駆動する為の減速機付き電動モータと、前記駆動軸に連結されて１対のプランジャポンプを駆動する１対のカム機構とを備え、前記各カム機構は、プランジャポンプのプランジャ部材の上端に水平な支持ピンにて回転自在に装着された従動ローラと、前記駆動軸に装着されて従動ローラの外周面の上端に当接する外周カム面を有するカム部材とを有し、１対のカム機構は、２つのプランジャ部材の上死点のタイミングを駆動軸の回転角度にて９０°以上異ならせるように構成されたことを特徴としている。 The hydraulic pressure generating apparatus according to the present invention is a hydraulic pressure generating apparatus for supplying hydraulic pressure to two hydraulic pressure supply systems, comprising: a main body case; and a pair of vertical openings each having an outlet at the lower end thereof. A plunger pump, a common drive shaft for driving the plunger pumps, an electric motor with a reduction gear for rotationally driving the drive shaft, and a pair of cams connected to the drive shaft to drive a pair of plunger pumps A driven roller rotatably mounted on the upper end of the plunger member of the plunger pump by a horizontal support pin, and the cam mechanisms mounted on the drive shaft and mounted on the upper end of the outer peripheral surface of the driven roller And a cam member having an outer peripheral cam surface which abuts, and the pair of cam mechanisms differ by 90 ° or more in timing of top dead center of the two plunger members in the rotational angle of the drive shaft It is characterized in that configured so that.
　本発明によれば、この油圧発生装置は、電動モータにより１対のカム機構を介して１対のプランジャポンプを夫々駆動するので、１台の電動モータで２系統の油圧供給系への油圧の供給が可能になる。１対のカム機構のカム部材の形状を異ならせることにより、異なる吐出圧・吐出量の２系統の油圧を発生できるため、種々の油圧アクチュエータへ供給する油圧を発生させることができるから、汎用性に優れる。しかも、油路に方向切換弁や減圧弁を採用する必要がないので、製作コストを節減することができる。カム機構のカム部材を交換することで、吐出圧・吐出量を容易に変更することができるから、油圧発生装置を製作する際の汎用性に優れる。 According to the present invention, the hydraulic pressure generator drives the pair of plunger pumps by the electric motor via the pair of cam mechanisms, so that one electric motor can control the hydraulic pressure to the two hydraulic pressure supply systems. Supply becomes possible. By changing the shape of the cam member of a pair of cam mechanisms, it is possible to generate two systems of hydraulic pressure of different discharge pressure and discharge amount, so that hydraulic pressure to be supplied to various hydraulic actuators can be generated. Excellent. Moreover, since it is not necessary to adopt a directional switching valve or a pressure reducing valve in the oil passage, the manufacturing cost can be reduced. Since the discharge pressure and the discharge amount can be easily changed by replacing the cam member of the cam mechanism, the versatility in manufacturing the hydraulic pressure generating device is excellent.
　１対のカム機構を介してプランジャポンプを駆動させるため、電動モータのオン・オフ制御に対する追従性が高くなり、電動モータのオン・オフ制御により容易に間欠吐出が可能となる。従って、間欠吐出させる場合に、電動モータの電力消費量を節減できる。
　１対のカム機構は、２つのプランジャ部材の上死点のタイミングを駆動軸の回転角度にて９０°以上異ならせるように構成したので、駆動軸に作用する負荷の平準化を図ることができるから、電動モータの小型化を図ることができる。 Since the plunger pump is driven through the pair of cam mechanisms, the followability to the on / off control of the electric motor is enhanced, and intermittent discharge can be easily performed by the on / off control of the electric motor. Therefore, when intermittently discharging, the power consumption of the electric motor can be reduced.
The pair of cam mechanisms is configured to make the timing of the top dead center of the two plunger members different by 90 ° or more in the rotational angle of the drive shaft, so that the load acting on the drive shaft can be leveled. Thus, the size of the electric motor can be reduced.
　本発明は、前記構成に加えて次のような構成を採用してもよい。
（１）前記各カム機構のカム部材の外周カム面に、プランジャ部材が上死点に達した時に前記従動ローラに係合する第１凹部と、プランジャ部材が下死点に達した時に前記従動ローラに係合する第２凹部とを形成した。このため、カム部材の外周カム面に形成した第２凹部を従動ローラに係合させることで、プランジャ部材が下死点に達した時にカム部材を精度よく停止させることができる。従って、ブレーキ機構やサーボ機構のない電動モータを採用することが可能となるため、製作コストを節減できる。しかも、自動工具交換の高速化を図ることも可能になる。 The present invention may adopt the following configuration in addition to the above configuration.
(1) The outer peripheral cam surface of the cam member of each cam mechanism, the first concave portion engaged with the driven roller when the plunger member reaches the top dead center, and the follower when the plunger member reaches the bottom dead center And a second recess engaged with the roller. Therefore, by engaging the second concave portion formed on the outer peripheral cam surface of the cam member with the driven roller, the cam member can be accurately stopped when the plunger member reaches the bottom dead center. Therefore, since it becomes possible to employ an electric motor without a brake mechanism or a servo mechanism, the manufacturing cost can be reduced. Moreover, it also becomes possible to speed up automatic tool change.
（２）前記電動モータは、同容量の連続定格モータに比較して高トルクを発揮する短時間定格高トルクモータであり、工作機械の主軸の工具の交換毎に電動モータを起動すると共に自動工具交換装置の自動工具交換アームの動作と前記各カム機構のカム部材の回転動作が同期するように電動モータを制御する制御手段を設けた。
（３）前記各プランジャ部材がその鉛直軸心回りに回転しないように規制する回転規制機構を設けた。 (2) The electric motor is a short-time rated high torque motor that exhibits high torque as compared to a continuous rated motor of the same capacity, and starts the electric motor every time the tool of the spindle of the machine tool is replaced A control means is provided for controlling the electric motor such that the operation of the automatic tool changer arm of the changer and the rotational movement of the cam member of each cam mechanism are synchronized.
(3) A rotation restricting mechanism is provided which restricts the plunger members from rotating about their vertical axes.
（４）前記各カム部材の外周カム面のうちの、前記カム部材の回転方向と反対向きに第１凹部から第２凹部に至る油圧生成用カム面部分は、前記カム部材の回転方向と反対向きに第２凹部から第１凹部に至る復帰用カム面部分よりも長く形成された。
（５）前記各プランジャ部材が上死点から下死点に移動する下降時間は、下死点から上死点に移動する上昇時間よりも長くなるように前記カム部材が形成されている。 (4) Of the outer peripheral cam surfaces of each cam member, the oil pressure generating cam surface portion extending from the first recess to the second recess in the direction opposite to the rotation direction of the cam member is opposite to the rotation direction of the cam member It is formed longer in direction than the return cam surface portion from the second recess to the first recess.
(5) The cam member is formed such that the lowering time for moving each plunger member from the top dead center to the bottom dead center is longer than the rising time for moving from the bottom dead center to the top dead center.
（６）前記各プランジャ部材の下端部分にはプランジャが形成されると共に、前記各プランジャポンプの下端部分には、前記プランジャが挿入されるプランジャ孔が形成され、前記本体ケースのうち、前記各プランジャポンプの下部の外周側部分に対応する部分には、前記各プランジャポンプに供給する為の油を収容する油収容室が形成された。
（７）前記各プランジャ部材のプランジャの下端部の外周には下方程小径化するテーパ部が形成され、前記各プランジャ部材が上死点のとき、前記テーパ部の外周側に前記プランジャ孔と油収容室を連通する連通隙間が形成された。 (6) A plunger is formed at a lower end portion of each of the plunger members, and a plunger hole into which the plunger is inserted is formed at a lower end portion of each of the plunger pumps. An oil storage chamber for storing oil for supplying each of the plunger pumps was formed at a portion corresponding to the lower outer peripheral portion of the pump.
(7) A tapered portion is formed on the outer periphery of the lower end portion of each plunger member at the lower end, and the plunger hole and the oil are formed on the outer peripheral side of the tapered portion when each plunger member is at top dead center. A communication gap communicating the storage chamber was formed.
（８）前記各プランジャ部材のプランジャには下端開放状の凹入穴が形成され、この凹入穴とプランジャ孔にプランジャ部材を上方へ弾性付勢する圧縮コイルスプリングが装着された。
（９）前記本体ケースの上端部分に、平面視にて所定の大きさの油補給用凹部が形成され、前記本体ケースに、油補給用凹部と油収容室の上端を連通する流体通路が形成された。
（１０）前記各プランジャ孔から油圧を吐出する吐出口に接続されたアキュムレータを設けた。 (8) The plunger of each of the plunger members is formed with a recessed hole having an open lower end, and a compression coil spring for elastically urging the plunger member upward is attached to the recessed hole and the plunger hole.
(9) An oil replenishment recess having a predetermined size in plan view is formed in the upper end portion of the main body case, and a fluid passage connecting the oil replenishment recess and the upper end of the oil storage chamber is formed in the main body case. It was done.
(10) The accumulator connected to the discharge port which discharges an oil pressure from each said plunger hole was provided.
本発明の実施例に係る油圧発生装置が接続されたマシニングセンタの主軸ユニットの断面図である。1 is a cross-sectional view of a spindle unit of a machining center to which a hydraulic pressure generating device according to an embodiment of the present invention is connected. 油圧発生装置の縦断面図である。It is a longitudinal cross-sectional view of a hydraulic pressure generating device. 図２のIII －III 線断面図である。FIG. 3 is a cross-sectional view taken along line III-III of FIG. 図２のIV－IV線断面図である。FIG. 4 is a cross-sectional view taken along line IV-IV of FIG. 図２のV－V線断面図である。FIG. 5 is a cross-sectional view taken along line VV of FIG. 2; 図２のVI－VI線断面図である。FIG. 6 is a cross-sectional view taken along line VI-VI of FIG. 油圧発生装置の平面図である。It is a top view of a hydraulic pressure generating device. カム部材の説明図である。It is explanatory drawing of a cam member. マシニングセンタと油圧発生装置の制御系のブロック図である。It is a block diagram of a control system of a machining center and a hydraulic pressure generating device. プランジャ部材ストロークのタイムチャートである。It is a time chart of plunger member stroke. 油圧発生装置のピストンストロークのタイムチャートである。It is a time chart of a piston stroke of an oil pressure generation device. ＡＣＴアーム旋回角のタイムチャートである。It is a time chart of ACT arm turning angle. ＡＣＴアームストロークのタイムチャートである。It is a time chart of ACT arm stroke.
符号の説明Explanation of sign
１            主軸ユニット
２            主軸
１５          クランプ機構
２０          油圧シリンダ
３０          油圧発生装置
３１          本体ケース
３３Ａ，３３Ｂ       吐出口
３５          プランジャケース
３７Ａ，３７Ｂ       プランジャ孔
４０          油収容室
５０Ａ，５０Ｂ       プランジャポンプ
５１Ａ，５１Ｂ       プランジャ部材
５２          プランジャ
５２ａ        テーパ部
５２ｂ        凹入穴
５７          圧縮コイルスプリング
５９Ａ，５９Ｂ       アキュムレータ
６０Ａ，６０Ｂ       カム機構
６１Ａ，６１Ｂ       従動ローラ
６２          支持ピン
６３Ａ，６３Ｂ       カム部材
６４          外周カム面
６５          第１凹部
６６          第２凹部
６７          油圧生成用カム面部分
６８          復帰用カム面部分
７１          支持軸
８６          回転規制機構
９０          減速機付き電動モータ
９５          油補給用凹部
９９ａ，９９ｂ       ２本の流体通路圧
１００        制御ユニット Reference Signs List 1 spindle unit 2 spindle 15 clamp mechanism 20 hydraulic cylinder 30 hydraulic pressure generator 31 main body case 33A, 33B discharge port 35 plunger case 37A, 37B plunger hole 40 oil storage chamber 50A, 50B plunger pump 51A, 51B plunger member 52 plunger 52a tapered portion 52b recessed hole 57 compression coil spring 59A, 59B accumulator 60A, 60B cam mechanism 61A, 61B driven roller 62 support pin 63A, 63B cam member 64 outer peripheral cam surface 65 first concave portion 66 second concave portion 67 hydraulic pressure generating cam surface portion 68 Cam surface portion for return 71 Support shaft 86 Rotation regulation machine Structure 90 Electric motor 95 with reduction gear Recess for oil supply 99a, 99b Two fluid passage pressure 100 Control unit
　以下、本発明を実施するための最良の形態について実施例に基づいて説明する。 Hereinafter, the best mode for carrying out the present invention will be described based on examples.
　図１～図８に示すように、本願特有の油圧発生装置３０は、マシニングセンタ（工作機械）の主軸ユニット１の主軸２に工具をクランプするクランプ機構１５をクランプ解除するアンクランプ用油圧シリンダ２０に油圧を供給・排出する為にマシニングセンタに適用したものである。 As shown in FIGS. 1 to 8, the hydraulic pressure generating device 30 specific to the present invention is an unclamping hydraulic cylinder 20 for unclamping a clamping mechanism 15 for clamping a tool to the spindle 2 of the spindle unit 1 of a machining center (machine tool). It is applied to a machining center to supply and discharge hydraulic pressure.
　最初に、縦型マシニングセンタの主軸ユニット１、クランプ機構１５、アンクランプ用油圧シリンダ２０等について説明する。
　図１に示すように、主軸ユニット１の主軸２の先端側部分は複数の軸受４ａを介して主軸ユニット１の主軸ケース５に回転自在に支持されている。主軸２の上部は軸受４ｂを介して主軸ケース５に回転自在に支持されている。主軸２の中心部にはほぼ全長に亙る貫通孔６が形成され、この貫通孔６にはドローバー７が軸心方向へ可動に装着されている。ドローバー７の中心部には、工具ホルダ８へクーラントを供給するクーラント供給路９が形成されている。 First, the spindle unit 1 of the vertical machining center, the clamp mechanism 15, the hydraulic cylinder 20 for unclamping, and the like will be described.
As shown in FIG. 1, the tip end side portion of the spindle 2 of the spindle unit 1 is rotatably supported by the spindle case 5 of the spindle unit 1 via a plurality of bearings 4 a. The upper portion of the spindle 2 is rotatably supported by the spindle case 5 via a bearing 4b. A through hole 6 having a substantially full length is formed in the central portion of the main shaft 2, and a draw bar 7 is movably mounted in the through hole 6 in the axial direction. A coolant supply passage 9 for supplying a coolant to the tool holder 8 is formed at the center of the draw bar 7.
　主軸２の中心部分の貫通孔６の内部において、ドローバー７の外側に環状のバネ装着穴１１が形成され、複数の皿バネを積層した皿バネ積層体１２がバネ装着穴１１に弾性圧縮状態に装着され、この皿バネ積層体１２によりドローバー７が上方へ強力に弾性付勢されている。 An annular spring mounting hole 11 is formed on the outside of the draw bar 7 inside the through hole 6 in the central portion of the main spindle 2, and the disc spring laminate 12 in which a plurality of disc springs are stacked is elastically compressed in the spring mounting hole 11. The draw bar 7 is strongly urged upward by the disc spring laminate 12.
　主軸２の先端部の内部においてドローバー７の先端部に、主軸本体３のテーパ穴３ａに装着された工具ホルダ８を主軸２に固定するクランプ機構１５の主要部が設けられている。このクランプ機構１５は、皿バネ積層体１２の弾性力と複数のコレット１６により工具ホルダ８の先端のプルスタッド８ａをクランプする形式のものであるが、このクランプ機構１５に限定されるものではなく、ボールロック式のクランプ機構やその他のクランプ機構でもよい。 A main part of a clamp mechanism 15 for fixing the tool holder 8 mounted in the tapered hole 3 a of the spindle main body 3 to the spindle 2 is provided at the tip of the draw bar 7 inside the tip of the spindle 2. The clamp mechanism 15 clamps the pull stud 8 a at the tip of the tool holder 8 by the elastic force of the disc spring laminate 12 and the plurality of collets 16, but the clamp mechanism 15 is not limited to this clamp mechanism 15. A ball lock type clamp mechanism or other clamp mechanism may be used.
　前記クランプ機構１５において、皿バネ積層体１２の弾性力によりドローバー７を上方へ引き付けると、複数のコレット１６の先端部分が閉じた状態になってプルスタッド８ａに係合し、プルスタッド８ａを上方へ引き付けて工具ホルダ８をクランプする。アンクランプの際に、ドローバー７を下方へ押動すると、複数のコレット１６の先端部分が開いた状態になってアンクランプ状態となり、工具ホルダ８を取り外し可能になる。 When the draw bar 7 is pulled upward by the elastic force of the disc spring laminate 12 in the clamp mechanism 15, the tips of the plurality of collets 16 are closed and engage with the pull stud 8a, and the pull stud 8a is moved upward. Pull it to clamp the tool holder 8. In unclamping, when the draw bar 7 is pushed downward, the tip portions of the plurality of collets 16 are in an open state to be unclamped, and the tool holder 8 can be removed.
　ドローバー７の上端部には、小径筒部７ａが一体的に形成されている。主軸２の中段部において、環状の押圧部材１４が小径筒部７ａに外嵌固定され、主軸本体３に対して相対的に押圧部材１４とドローバー７とが一体的に昇降するようになっている。 A small diameter cylindrical portion 7 a is integrally formed at the upper end portion of the draw bar 7. An annular pressing member 14 is externally fitted and fixed to the small diameter cylindrical portion 7 a in the middle step portion of the spindle 2 so that the pressing member 14 and the draw bar 7 move up and down integrally with the spindle main body 3. .
　主軸２の上方に立設された電動モータ１７の出力軸１７ａの先端部に下方へ延びる筒状部材１８が外嵌固定されている。この筒状部材１８の下端部分に、ドローバー７の上端部が挿入されている。この筒状部材１８は、押圧部材１４を介して主軸本体３の上端部分と連結され、電動モータ１７の回転駆動力を主軸２に伝達するようになっている。電動モータ１７の出力軸１７ａに形成されたクーラント供給路１９がドローバー７の内部のクーラント供給路９に接続されている。 A cylindrical member 18 extending downward is fixedly fitted on the tip of the output shaft 17 a of the electric motor 17 erected above the main shaft 2. The upper end portion of the draw bar 7 is inserted into the lower end portion of the cylindrical member 18. The cylindrical member 18 is connected to the upper end portion of the main spindle body 3 via the pressing member 14, and transmits the rotational driving force of the electric motor 17 to the main spindle 2. A coolant supply passage 19 formed on an output shaft 17 a of the electric motor 17 is connected to the coolant supply passage 9 inside the draw bar 7.
　次に、アンクランプ用油圧シリンダ２０について説明する。
　アンクランプ用油圧シリンダ２０は、主軸ケース５に固定されたシリンダ本体２１と、環状のピストン部材２２と、ピストン部材２２の上側に形成されたクランプ解除の為に油圧が供給される油圧作動室２４と、ピストン部材２２の下側に形成された復帰移動する為に油圧が供給される油圧作動室２５と、油圧供給ポート２６ａ，２６ｂと、この油圧供給ポート２６ａ，２６ｂを後述する油圧発生装置３０の吐出口３３Ａ，３３Ｂに接続する油圧ホース２８ａ，２８ｂ（２系統の油圧供給系に相当する）とを備えている。 Next, the unclamping hydraulic cylinder 20 will be described.
The unclamping hydraulic cylinder 20 includes a cylinder main body 21 fixed to the main shaft case 5, an annular piston member 22, and a hydraulic operating chamber 24 provided with hydraulic pressure for releasing the clamp formed on the upper side of the piston member 22. A hydraulic pressure chamber 25 is provided under the piston member 22 and is supplied with hydraulic pressure for returning movement, a hydraulic pressure supply port 26a, 26b, and a hydraulic pressure generating device 30 described later, which hydraulic pressure supply port 26a, 26b. The hydraulic hoses 28a and 28b (corresponding to two hydraulic pressure supply systems) connected to the discharge ports 33A and 33B are provided.
　環状のピストン部材２２が上限位置にあるとき、ピストン部材２２の下端と押圧部材１４の上面との間に僅かな隙間が形成されている。クランプ機構１５により工具ホルダ８をクランプしている状態では、油圧作動室２４の油圧が排出され、油圧作動室２５に油圧が供給されることで、ピストン部材２２が上方に付勢され上限位置に移動する。工具付きの工具ホルダ８の交換の為に、クランプ機構１５をアンクランプする際には、油圧ホース２８ａを介して油圧作動室２４に油圧を供給し、油圧ホース２８ｂを介して油圧作動室２５の油圧を排出すると、ピストン部材２２が押圧部材１４に当接し、押圧部材１４を下方へ変位させ、ドローバー７を下方へ変位させてアンクランプ状態にする。 When the annular piston member 22 is at the upper limit position, a slight gap is formed between the lower end of the piston member 22 and the upper surface of the pressing member 14. In a state where the tool holder 8 is clamped by the clamp mechanism 15, the hydraulic pressure of the hydraulic operating chamber 24 is discharged, and the hydraulic pressure is supplied to the hydraulic operating chamber 25, whereby the piston member 22 is urged upward to the upper limit position. Moving. When unclamping the clamp mechanism 15 for replacement of the tool holder 8 with a tool, the hydraulic pressure is supplied to the hydraulic working chamber 24 through the hydraulic hose 28a, and the hydraulic working chamber 25 of the hydraulic working chamber 25 through the hydraulic hose 28b. When the hydraulic pressure is discharged, the piston member 22 abuts on the pressing member 14 and displaces the pressing member 14 downward, displacing the draw bar 7 downward to bring it into an unclamped state.
　次に、油圧発生装置３０について説明する。
　図１～図７に示すように、油圧発生装置３０は、本体ケース３１と、この本体ケース３１に立向き姿勢に組み込まれたプランジャポンプ５０Ａ，５０Ｂと、アキュムレータ５９Ａ，５９Ｂと、従動ローラ６１Ａ，６１Ｂとカム部材６３Ａ，６３Ｂとを夫々含むカム機構６０Ａ，６０Ｂと、プランジャポンプ５０Ａ，５０Ｂのプランジャ部材５１Ａ，５１Ｂの為の１対の回転規制機構８６と、カム機構６０Ａ，６０Ｂを介してプランジャポンプ５０Ａ、５０Ｂを駆動する減速機付き電動モータ９０と、この電動モータ９０を駆動制御する制御ユニット１００と、本体ケース３１に形成された油収容室４０及び油補給用凹部９５及び２本の流体通路９９ａ，９９ｂなどを有する。 Next, the hydraulic pressure generating device 30 will be described.
As shown in FIGS. 1 to 7, the hydraulic pressure generating device 30 includes a main body case 31, plunger pumps 50A and 50B incorporated in the main body case 31 in an upright posture, accumulators 59A and 59B, and driven rollers 61A, The cam mechanisms 60A and 60B respectively including 61B and cam members 63A and 63B, a pair of rotation restricting mechanisms 86 for the plunger members 51A and 51B of the plunger pumps 50A and 50B, and the plungers via the cam mechanisms 60A and 60B An electric motor 90 with a reduction gear for driving the pumps 50A, 50B, a control unit 100 for driving and controlling the electric motor 90, an oil storage chamber 40 formed in the main body case 31, an oil replenishment recess 95 and two fluids It has passage 99a, 99b etc.
　次に、前記本体ケース３１について説明する。
　図２～図５に示すように、前記本体ケース３１は、下端ケース３２と、プランジャケース３５と、円筒ケース３８と、中段ケース４２と、上部ケース４５などで構成されている。下端ケース３２は複数のボルトによりプランジャケース３５に固定され、プランジャケース３５と１対の中段ケース４２と上部ケース４５は複数の位置決めピンや複数のボルトにより固定されている。尚、図２の上下左右を上下左右として説明する。 Next, the main body case 31 will be described.
As shown in FIGS. 2 to 5, the main body case 31 is constituted by a lower end case 32, a plunger case 35, a cylindrical case 38, an intermediate case 42, an upper case 45 and the like. The lower end case 32 is fixed to the plunger case 35 by a plurality of bolts, and the plunger case 35, the pair of middle case 42 and the upper case 45 are fixed by a plurality of positioning pins and a plurality of bolts. In addition, the upper and lower sides and right and left of FIG.
　図２に示すように、下端ケース３２の右側部分には、プランジャポンプ５０Ａの吐出口３３Ａと油路３４Ａが形成され、油路３４Ａには余分の油圧を貯留するアキュムレータ５９Ａが接続されている。下端ケース３２の左側部分には、プランジャポンプ５０Ｂの吐出口３３Ｂと油路３４Ｂが形成され、油路３４Ｂには余分の油圧を貯留するアキュムレータ５９Ｂが接続されている。 As shown in FIG. 2, a discharge port 33A and an oil passage 34A of the plunger pump 50A are formed in the right side portion of the lower end case 32, and an accumulator 59A for storing an extra hydraulic pressure is connected to the oil passage 34A. A discharge port 33B of the plunger pump 50B and an oil passage 34B are formed on the left side portion of the lower end case 32, and an accumulator 59B for storing an extra hydraulic pressure is connected to the oil passage 34B.
　プランジャケース３５の右側部分には、鉛直向きのロッド孔３６Ａと、このロッド孔３６Ａの下端に連なるプランジャ孔３７Ａとが同心状に且つ連通状に形成されている。プランジャ孔３７Ａの下端が吐出口３３Ａに連通している。プランジャケース３５の左側部分には、鉛直向きのロッド孔３６Ｂと、このロッド孔３６Ｂの下端に連なるプランジャ孔３７Ｂとが同心状に且つ連通状に形成されている。プランジャ孔３７Ｂの下端が吐出口３３Ｂに連通している。 In the right side portion of the plunger case 35, a vertically oriented rod hole 36A and a plunger hole 37A connected to the lower end of the rod hole 36A are formed concentrically and in communication. The lower end of the plunger hole 37A communicates with the discharge port 33A. In the left side portion of the plunger case 35, a vertically oriented rod hole 36B and a plunger hole 37B connected to the lower end of the rod hole 36B are formed concentrically and in communication. The lower end of the plunger hole 37B communicates with the discharge port 33B.
　図２～図４に示すように、プランジャケース３５の下部には円筒ケース３８が外嵌され、プランジャケース３５と円筒ケース３８とで、プランジャポンプ５０Ａ，５０Ｂの外周側に位置する油収容室４０が形成されている。この油収容室４０にはプランジャポンプ５０Ａ，５０Ｂに供給する油が収容されている。環状の油収容室４０は、複数のシール部材によりシールされている。１対の中段ケース４２は環状板部４２ａと筒部４２ｂとを夫々有し、中段ケース４２はプランジャケース３５と上部ケース４５の間に夫々挟み込んだ状態に装着されている。筒部４２ｂの外周部にはシール部材４２ｃが装着されている。 As shown in FIGS. 2 to 4, the cylindrical case 38 is externally fitted to the lower portion of the plunger case 35, and the oil case 40 located on the outer peripheral side of the plunger pumps 50A and 50B by the plunger case 35 and the cylindrical case 38. Is formed. The oil storage chamber 40 stores oil supplied to the plunger pumps 50A and 50B. The annular oil storage chamber 40 is sealed by a plurality of seal members. The pair of middle stage cases 42 respectively have an annular plate portion 42 a and a cylinder portion 42 b, and the middle stage case 42 is mounted so as to be sandwiched between the plunger case 35 and the upper case 45. A seal member 42c is mounted on the outer peripheral portion of the cylindrical portion 42b.
　次に、プランジャポンプ５０Ａ，５０Ｂについて説明するが、プランジャポンプ５０Ａ，５０Ｂは同じ構成を有するので、プランジャポンプ５０Ａについてのみ説明する。
　図２と図３に示すように、プランジャポンプ５０Ａは、ロッド孔３６Ａ及びプランジャ孔３７Ａと、ロッド孔３６Ａ及びプランジャ孔３７Ａに可動に装着されたプランジャ部材５１Ａと、このプランジャ部材５１Ａの下端部分に形成されたプランジャ孔３７Ａに挿入されるプランジャ５２と、プランジャ部材５１Ａの上部にプランジャ５２と一体形成されたロッド部５３を備えている。 Next, although plunger pump 50A, 50B is demonstrated, since plunger pump 50A, 50B has the same structure, only plunger pump 50A is demonstrated.
As shown in FIGS. 2 and 3, the plunger pump 50A includes a rod hole 36A and a plunger hole 37A, a plunger member 51A movably attached to the rod hole 36A and the plunger hole 37A, and a lower end portion of the plunger member 51A. The plunger 52 is inserted into the formed plunger hole 37A, and the rod portion 53 integrally formed with the plunger 52 is provided on the top of the plunger member 51A.
　プランジャ部材５１Ａは、減速機付き電動モータ９０によりカム機構６０Ａを介して昇降駆動され、プランジャ５２Ａがプランジャ孔３７Ａに進退駆動されて油圧が発生し、その油圧を吐出口３３Ａから吐出する。ロッド孔３６Ａの下端部は環状凹部５５ａと穴５５ｂを介して油収容室４０に連通されている。 The plunger member 51A is driven to move up and down by a reduction gear electric motor 90 via the cam mechanism 60A, and the plunger 52A is driven to move back and forth in the plunger hole 37A to generate hydraulic pressure, and the hydraulic pressure is discharged from the discharge port 33A. The lower end portion of the rod hole 36A communicates with the oil storage chamber 40 through the annular recess 55a and the hole 55b.
　プランジャ５２の下端部の外周には下方程小径化するテーパ部５２ａが形成されている。プランジャ孔３７Ａの上端部にも上方に向かって大径化するテーパ面３７ａが形成されている。プランジャ部材５１Ａが上死点のとき、テーパ部５２ａの外周側にプランジャ孔３７Ａと油収容室４０を連通する連通隙間が形成される。連通隙間を通って油に発生した気泡が油収容室４０へ浮上し、油収容室４０からプランジャ孔３７Ａへ油が補充される。 A tapered portion 52a is formed on the outer periphery of the lower end portion of the plunger 52 so as to decrease in diameter toward the lower side. A tapered surface 37a is formed at the upper end portion of the plunger hole 37A to increase in diameter upward. When the plunger member 51A is at the top dead center, a communication gap for communicating the plunger hole 37A with the oil storage chamber 40 is formed on the outer peripheral side of the tapered portion 52a. Air bubbles generated in the oil rise to the oil storage chamber 40 through the communication gap, and oil is replenished from the oil storage chamber 40 to the plunger hole 37A.
　プランジャ５２には下端開放状の凹入穴５２ｂが形成され、この凹入穴５２ｂとプランジャ孔３７Ａにプランジャ部材５１を上方へ弾性付勢する圧縮コイルスプリング５７が装着されている。テーパ面３７ａより下側においてプランジャ孔３７Ａにはシール部材３７ｂが装着されている。ロッド孔３６Ａの壁部にはウェアリング３６ａと、２段のシール部材３６ｂ，３６ｃが装着されている。 A lower end open recess 52b is formed in the plunger 52, and a compression coil spring 57 for elastically biasing the plunger member 51 upward is attached to the recess 52b and the plunger hole 37A. A seal member 37b is attached to the plunger hole 37A below the tapered surface 37a. A wear ring 36a and two- stage seal members 36b and 36c are attached to the wall of the rod hole 36A.
　次に、カム機構６０Ａ，６０Ｂについて説明するが、カム機構６０Ａ，６０Ｂは同じ構成を有するので、カム機構６０Ａについてのみ説明する。
　図２，図３，図６に示すように、カム機構６０Ａは、プランジャ部材５１Ａの上端部に水平な支持ピン６２にて回転自在に装着された従動ローラ６１Ａと、この従動ローラ６１Ａの外周面の上端に当接する外周カム面６４を有するカム部材６３Ａと、カム部材６３Ａに貫通固定された支持軸７１とを備えている。カム部材６３Ａは、減速機付き電動モータ９０によって支持軸７１を回転駆動することにより回転駆動される。 Next, the cam mechanisms 60A and 60B will be described, but since the cam mechanisms 60A and 60B have the same configuration, only the cam mechanism 60A will be described.
As shown in FIGS. 2, 3 and 6, the cam mechanism 60A has a driven roller 61A rotatably mounted on the upper end portion of the plunger member 51A by a horizontal support pin 62, and an outer peripheral surface of the driven roller 61A. The cam member 63A has an outer peripheral cam surface 64 in contact with the upper end of the support shaft 71, which is fixed to the cam member 63A in a penetrating manner. The cam member 63A is rotationally driven by rotationally driving the support shaft 71 by the electric motor 90 with a reduction gear.
　従動ローラ６１Ａは、プランジャ部材５１Ａのロッド部５３の上端の規制穴５３ａから上方へ突出し、規制穴５３ａにより位置規制されている。カム部材６３Ａを支持する支持軸７１は減速機付き電動モータ９０の出力軸である。減速機付き電動モータ９０は、減速機ケースの嵌合部９１ａを上部ケース４５の嵌合穴４５ａにリング９１ｂを介して嵌合することで、上部ケース４５に固定されている。 The driven roller 61A protrudes upward from the regulation hole 53a at the upper end of the rod portion 53 of the plunger member 51A, and the position of the follower roller 61A is regulated by the regulation hole 53a. A support shaft 71 supporting the cam member 63A is an output shaft of the reduction motor-equipped electric motor 90. The electric motor 90 with a reduction gear is fixed to the upper case 45 by fitting the fitting portion 91a of the reduction gear case to the fitting hole 45a of the upper case 45 via a ring 91b.
　支持軸７１の先端部は、ベアリング７２により上部ケース４５に支持されている。カム部材６３Ａ，６３Ｂはキーにより支持軸７１に対して回転拘束され、環状のスペーサ７４ａ，７４ｂにより軸方向の位置が規制されている。スペーサ７４ａはベアリング７２により位置規制され、ベアリング７２は封鎖部材７６により位置規制されている。封鎖部材７６の嵌合筒部７６ａが上部ケース４５の穴４５ｂに嵌合され、シール部材７６ｂでシールされている。支持軸７１と嵌合筒部７６ａの間にはオイルシール７７が装着されている。 The tip end of the support shaft 71 is supported by the bearing 72 on the upper case 45. The cam members 63A and 63B are rotationally restrained by the key with respect to the support shaft 71, and their axial positions are restricted by the annular spacers 74a and 74b. The spacer 74 a is regulated by the bearing 72, and the bearing 72 is regulated by the sealing member 76. The fitting cylindrical portion 76a of the sealing member 76 is fitted in the hole 45b of the upper case 45 and sealed by the sealing member 76b. An oil seal 77 is mounted between the support shaft 71 and the fitting cylinder 76a.
　封鎖部材７６よりも外側において、支持軸７１の外側の先端部には電動モータ９０を制御する為のディスク部材７９が装着され、このディスク部材７９を検出する為の複数の近接スイッチ８１が上部ケース４５に設けられている。図８に示すカム部材６３Ａ，６３Ｂにおいて、点Ａに従動ローラ６１Ａ，６１Ｂが夫々当接するときプランジャ部材５１Ａ，５１Ｂが上死点（上限位置）になり、点Ｂに従動ローラ６１Ａ，６１Ｂが夫々当接するときプランジャ部材５１Ａ，５１Ｂが下死点（下限位置）になる。 A disc member 79 for controlling the electric motor 90 is attached to an outer end of the support shaft 71 outside the sealing member 76, and a plurality of proximity switches 81 for detecting the disc member 79 is an upper case. It is provided at 45. In the cam members 63A and 63B shown in FIG. 8, when the driven rollers 61A and 61B respectively abut on the point A, the plunger members 51A and 51B become the top dead center (upper limit position) and the driven rollers 61A and 61B are respectively at the point B When in contact, the plunger members 51A and 51B are at the bottom dead center (lower limit position).
　前記ディスク部材７９と複数の近接スイッチ８１により、プランジャ部材５１Ａ，５１Ｂの上死点に対応する点Ａと、下死点に対応する点Ｂと、上死点の手前の第１点Ｃ（点Ａからカム部材６３Ａ，６３Ｂの回転方向へ例えば１０°の位置）と、下死点の手前の第２点Ｄ（点Ｂからカム部材６３Ａ，６３Ｂの回転方向へ例えば１０°の位置）とを検出するように構成されている。後述するように、カム部材６３Ａ，６３Ｂを上死点に停止させる際には、カム部材６３Ａ，６３Ｂの第１点Ｃが従動ローラ６１Ａ，６１Ｂに夫々当接した時に、電動モータ９０をオフにする。また、カム部材６３Ａ，６３Ｂを下死点に停止させる際には、カム部材６３Ａ，６３Ｂの第２点Ｄが従動ローラ６１Ａ，６１Ｂに夫々当接した時に、電動モータ９０をオフする。 A point A corresponding to the top dead center of the plunger members 51A and 51B, a point B corresponding to the bottom dead center, and a first point C before the top dead center by the disc member 79 and the plurality of proximity switches 81 A from the point A to the rotational direction of the cam members 63A and 63B, for example, and a second point D before the bottom dead center (the point from the point B to the rotational direction of the cam members 63A and 63B, for example, 10 °) It is configured to detect. As described later, when stopping the cam members 63A, 63B at the top dead center, the electric motor 90 is turned off when the first points C of the cam members 63A, 63B abut against the driven rollers 61A, 61B, respectively. Do. Further, when stopping the cam members 63A, 63B at the bottom dead center, the electric motor 90 is turned off when the second points D of the cam members 63A, 63B respectively abut the driven rollers 61A, 61B.
　ディスク部材７９の外側を塞ぐカバー部材８３が設けられ、カバー部材８３は複数のボルトで上部ケース４５に固定されている。上部ケース４５内のカム機構６０Ａ，６０Ｂが収容されたカム収容室８５は、減速機付き電動モータ９０の減速機ケース９１内のギヤ収容室と連通しており、カム収容室８５とギヤ収容室は潤滑油で満たされている。プランジャ部材５１Ａ，５１Ｂのロッド部５３Ａ，５３Ｂの外周面も、上記の潤滑油で潤滑される。尚、プランジャケース３５には上記の潤滑油の一部を排出する潤滑油逃し路３５ａが形成されている。 A cover member 83 for closing the outer side of the disk member 79 is provided, and the cover member 83 is fixed to the upper case 45 by a plurality of bolts. The cam storage chamber 85 in which the cam mechanisms 60A and 60B in the upper case 45 are stored communicates with the gear storage chamber in the reduction gear case 91 of the reduction motor-equipped electric motor 90, and the cam storage chamber 85 and the gear storage chamber Is filled with lubricating oil. The outer peripheral surfaces of the rod portions 53A, 53B of the plunger members 51A, 51B are also lubricated with the above-described lubricating oil. The plunger case 35 is formed with a lubricant oil release passage 35a for discharging a part of the lubricant oil.
　ここで、カム部材６３Ａ，６３Ｂについて説明するが、これらカム部材６３Ａ，６３Ｂは同じ構成を有するので、カム部材６３Ａについてのみ説明する。尚、カム部材６３Ａ，６３Ｂは、プランジャ部材５１Ａ，５１Ｂの上死点のタイミングを駆動軸７１の回転角度にて１８０°異ならせるように構成されている。 Here, the cam members 63A and 63B will be described, but since the cam members 63A and 63B have the same configuration, only the cam member 63A will be described. The cam members 63A and 63B are configured to make the timing of the top dead center of the plunger members 51A and 51B different by 180 ° at the rotation angle of the drive shaft 71.
　図８に示すように、カム部材６３Ａの外周カム面６４のうちプランジャ部材５１Ａが上死点に達した時に従動ローラ６１Ａに係合する部分には、従動ローラ６１Ａの上端部が係合する第１凹部６５が形成されている。また、カム部材６３Ａの外周カム面６４のうちプランジャ部材５１Ａが下死点に達した時に従動ローラ６１Ａに係合する部分には従動ローラ６１Ａの上端部が係合する第２凹部６６が形成されている。 As shown in FIG. 8, an upper end portion of the driven roller 61A engages with a portion of the outer peripheral cam surface 64 of the cam member 63A that engages with the driven roller 61A when the plunger member 51A reaches the top dead center. A recess 65 is formed. In addition, a second concave portion 66 with which the upper end portion of the driven roller 61A is engaged is formed in a portion of the outer peripheral cam surface 64 of the cam member 63A which engages with the driven roller 61A when the plunger member 51A reaches the bottom dead center. ing.
　第１凹部６５は、カム部材６３Ａの中心点に向けて部分円弧状に凹設され、第２凹部６６は、カム部材６３Ａの中心点に向けて部分円弧状に凹設されている。カム部材６３Ａの外周カム面６４のうち、点Ａの両側部分は全体として平坦な形状であるが、第１凹部６５における点Ａの位置でカム部材６３Ａの軸心Ｐからの半径が最小になる。カム部材６３Ａの外周カム面６４のうち、点Ｂの両側部分は全体として湾曲形状であるが、第２凹部６６における点Ｂの位置でカム部材６３Ａの軸心Ｐからの半径が最小になる。 The first recess 65 is recessed in a partial arc toward the center point of the cam member 63A, and the second recess 66 is recessed in a partial arc toward the center point of the cam member 63A. Of the outer peripheral cam surface 64 of the cam member 63A, both side portions of the point A have an overall flat shape, but the radius from the axial center P of the cam member 63A is minimized at the position of the point A in the first recess 65 . Of the outer peripheral cam surface 64 of the cam member 63A, both side portions of the point B have a curved shape as a whole, but the radius from the axial center P of the cam member 63A is minimized at the position of the point B in the second recess 66.
　プランジャ部材５１Ａを上方へ付勢するスプリング５７は強い弾性力を発揮するスプリング５７であるので、点Ｃが従動ローラ６１Ａに接する時に電動モータ９０をオフにすると、プランジャ部材５１Ａが上死点になる点Ａの位置でカム部材６３Ａの回転が停止する。同様、点Ｄが従動ローラ６１Ａに接する時に電動モータ９０をオフにすると、プランジャ部材５１Ａが下死点になる点Ｂの位置でカム部材６３Ａの回転が停止する。 Since the spring 57 which urges the plunger member 51A upward is a spring 57 which exerts a strong elastic force, when the electric motor 90 is turned off when the point C contacts the driven roller 61A, the plunger member 51A becomes a top dead center. At the point A, the rotation of the cam member 63A is stopped. Similarly, when the electric motor 90 is turned off when the point D contacts the driven roller 61A, the rotation of the cam member 63A stops at the point B where the plunger member 51A is at the bottom dead center.
　カム部材６３Ａの外周カム面６４のうちの、カム部材６３Ａの回転方向（図８の矢印方向）と反対向きに第１凹部６５から第２凹部６６に至る油圧生成用カム面部分６７は、カム部材６３の回転方向と反対向きに第２凹部６６から第１凹部６５に至る復帰用カム面部分６８よりも長く形成されている。つまり、プランジャ部材５１Ａが上死点から下死点に移動する下降時間は、下死点から上死点に移動する上昇時間よりも長くなるようにカム部材６３Ａが形成されている。 Of the outer peripheral cam surfaces 64 of the cam member 63A, the oil pressure generating cam surface portion 67 extending from the first recess 65 to the second recess 66 in the direction opposite to the rotational direction (arrow direction of FIG. 8) of the cam member 63A It is formed longer than the return cam surface portion 68 from the second recess 66 to the first recess 65 in the direction opposite to the rotational direction of the member 63. That is, the cam member 63A is formed such that the lowering time for the plunger member 51A to move from the top dead center to the bottom dead center is longer than the rising time for moving from the bottom dead center to the top dead center.
　本実施例の場合、油圧生成用カム面部分６７は軸心Ｐに対して約２１０度の周方向範囲に形成され、復帰用カム面部分６８は軸心Ｐに対して約１５０度の周方向範囲に形成されている。この油圧生成用カム面部分６７を周方向へ長く形成するため、油圧生成用カム面部分６７の半径増加勾配を小さくして電動モータ９０の小型化を図ることができる。 In the case of this embodiment, the hydraulic pressure generating cam surface portion 67 is formed in a circumferential range of about 210 degrees with respect to the axial center P, and the return cam surface portion 68 is circumferential direction of about 150 degrees with respect to the axial center P. It is formed in the range. Since the hydraulic pressure generating cam surface portion 67 is formed to be long in the circumferential direction, the radius increase slope of the hydraulic pressure generating cam surface portion 67 can be reduced to miniaturize the electric motor 90.
　次に、プランジャ部材５１Ａ，５１Ｂがその鉛直軸心回りに回転しないように規制する１対の回転規制機構８６について説明する。
　図２と図６に示すように、従動ローラ６１Ａ，６１Ｂの外周面６１ａは円筒面であり、カム部材６３Ａ，６３Ｂの外周カム面６４は従動ローラ６１Ａ，６１Ｂの各外周面６１ａに接触するように形成される関係上、支持ピン６２の軸心６２ａと支持軸７１の軸心７１ａとが常時平行になっていることが望ましい。そこで、プランジャ部材５１Ａ，５１Ｂの上端部には、支持ピン６２の両端部を支持するピン支持部５３ｂが形成され、このピン支持部５３ｂの幅（支持ピン６２と直交方向の幅）がプランジャ部材５１Ａ，５１Ｂの上端部の直径の約半分の幅に形成されている。 Next, a pair of rotation restricting mechanisms 86 for restricting the plunger members 51A and 51B from rotating about their vertical axes will be described.
As shown in FIGS. 2 and 6, the outer peripheral surface 61a of the driven rollers 61A, 61B is a cylindrical surface, and the outer peripheral cam surface 64 of the cam members 63A, 63B is in contact with the outer peripheral surfaces 61a of the driven rollers 61A, 61B. It is desirable that the axial center 62a of the support pin 62 and the axial center 71a of the support shaft 71 be always in parallel in order to be formed. Therefore, pin support portions 53b for supporting both end portions of the support pins 62 are formed at the upper end portions of the plunger members 51A and 51B, and the width (the width in the direction orthogonal to the support pins 62) of the pin support portions 53b is a plunger member It is formed in about half the width of the diameter of the upper end part of 51A, 51B.
　中段ケース４２の筒部４２ｂには平面視にて十文字形状の十文字穴８７が形成され、この十文字穴８７の鉛直な４つの壁面には、ピン支持部５３ｂに面接触してプランジャ部材５１Ａ，５１Ｂが回転しないように規制する１対の回転規制面８８が形成されている。プランジャ部材５１Ａ，５１Ｂが下限位置になった状態でも、回転規制面８８により回転規制される。この十文字穴８７と回転規制面８８が回転規制機構８６に相当する。 A cross-shaped cross-shaped hole 87 is formed in the cylinder portion 42b of the middle case 42 in plan view, and the vertical wall surfaces of the cross-shaped hole 87 make surface contact with the pin support portion 53b and the plunger members 51A and 51B. A pair of rotation restricting surfaces 88 are formed to restrict rotation of the Even when the plunger members 51A and 51B are at the lower limit position, the rotation restricting surface 88 restricts the rotation. The cross hole 87 and the rotation restricting surface 88 correspond to the rotation restricting mechanism 86.
　次に、減速機付き電動モータ９０について説明する。
　図１，図２，図７に示すように、減速機付き電動モータ９０は、上部ケース４５に固定的に設けられた減速機９２と、この減速機の入力軸に回転駆動力を入力する電動モータ９３とを有する。電動モータ９３は、同容量の連続定格モータに比較して高トルクを発揮する短時間定格高トルクモータである。例えば、電動モータ９３は、０．４ｋＷ、２００Ｖ、５０／６０Ｈｚ、１５００／１８００ｒｐｍ、定格２０秒、４極の三相誘導電動機である。 Next, the electric motor 90 with a reduction gear will be described.
As shown in FIG. 1, FIG. 2 and FIG. 7, the electric motor 90 with a reduction gear is a reduction gear 92 fixedly provided on the upper case 45, and an electric motor for inputting rotational driving force to the input shaft of this reduction gear. And a motor 93. The electric motor 93 is a short-time rated high torque motor that exhibits high torque as compared to a continuous rated motor of the same capacity. For example, the electric motor 93 is a four-phase three-phase induction motor with 0.4 kW, 200 V, 50/60 Hz, 1500/1800 rpm, rated for 20 seconds.
　上部ケース４５の上端部分に、平面視にて所定の大きさの油補給用凹部９５が形成されている。油補給用凹部９５を蓋する蓋部材９６には、油補給口９７と、この油補給口９７を開閉可能なキャップ９８が設けられている。上部ケース４５と中段ケース４２とプランジャケース３５に、油補給用凹部９５と油収容室４０の上端を連通する２つの流体通路９９ａ，９９ｂが形成されている。油収容室４０に油を補給する際、キャップ９８を開けて油を補給すると、一方の流体通路９９ａを通って油が油収容室４０へ流れ落ち、他方の流体通路９９ｂを通って油収容室４０内の気相部の空気が油補給用凹部９５へ流れる。そのため、迅速に油を補給することができる。 In the upper end portion of the upper case 45, an oil replenishment recess 95 having a predetermined size in a plan view is formed. An oil supply port 97 and a cap 98 capable of opening and closing the oil supply port 97 are provided on a lid member 96 for covering the oil supply recess 95. The upper case 45, the middle case 42, and the plunger case 35 are formed with two fluid passages 99a and 99b that communicate the upper end of the oil replenishment recess 95 and the upper end of the oil storage chamber 40. When the oil storage chamber 40 is refilled with oil, when the cap 98 is opened and oil is refilled, the oil flows down to the oil storage chamber 40 through one fluid passage 99a and the oil storage chamber 40 through the other fluid passage 99b. The air in the gas phase inside flows into the oil replenishment recess 95. Therefore, oil can be replenished quickly.
　次に、油圧発生装置３０の制御系について簡単に説明する。
　図９に示すように、マシニングセンタを制御する制御ユニット１００には、操作パネル１０１、主軸駆動制御系１０２、Ｘ軸駆動制御系１０３、Ｙ軸駆動制御系１０４、Ｚ軸駆動制御系１０５、ＡＴＣ１０６、油圧発生装置３０などが接続されている。この制御ユニット１００は、ＡＴＣ（自動工具交換装置）（図示略）を制御するＡＴＣ制御部１０８と、油圧発生装置３０の減速機付き電動モータ９０を制御する減速機付き電動モータ制御部１０９とを有する。ＡＴＣ制御部１０８と電動モータ制御部１０９との間で信号が授受され、ＡＴＣ１０６と減速機付き電動モータ９０とが連係動作するように制御される。つまり、工具の交換毎に電動モータ９０を起動すると共に自動工具交換アームの動作とカム部材６３Ａ，６３Ｂの回転動作が同期するように電動モータ９０が制御される。尚、ここでは、カム部材６３Ａの回転動作がクランプ解除の為の動作となり、カム部材６３Ｂの回転動作がクランプの為の動作となる。 Next, a control system of the hydraulic pressure generating device 30 will be briefly described.
As shown in FIG. 9, the control unit 100 for controlling the machining center includes an operation panel 101, a spindle drive control system 102, an X axis drive control system 103, a Y axis drive control system 104, a Z axis drive control system 105, an ATC 106, and the like. The hydraulic pressure generator 30 and the like are connected. The control unit 100 includes an ATC control unit 108 that controls an ATC (automatic tool changer) (not shown), and an electric motor control unit 109 with a reduction gear that controls the reduction motor and electric motor 90 of the hydraulic pressure generation device 30. Have. A signal is transmitted and received between the ATC control unit 108 and the electric motor control unit 109, and the ATC 106 and the electric motor 90 with a reduction gear are controlled to cooperate with each other. That is, the electric motor 90 is controlled so that the operation of the automatic tool change arm and the rotational movement of the cam members 63A and 63B are synchronized while the electric motor 90 is started every time the tool is replaced. Here, the rotation operation of the cam member 63A is an operation for releasing the clamp, and the rotation operation of the cam member 63B is an operation for clamping.
　次に、マシニングセンタに装備されたＡＴＣ（自動工具交換装置）の工具交換アームの動作と、油圧発生装置３０の動作についてのタイムチャート等について簡単に説明する。
　図１０は、カム部材６３Ａの回転角度とプランジャポンプ５０Ａのプランジャ部材５１Ａのストロークの関係を示す線図であり、図１１は、カム部材６３Ａの回転角度とアンクランプ用油圧シリンダ２０のピストンストロークの関係を示す線図である。尚、このときのカム部材６３Ｂの回転角度はカム部材６３Ａとは１８０°異なる為に、カム部材６３Ｂとプランジャ部材５１Ｂのストロークとの関係は、図１０ではカム部材６３Ａのものと比較して１８０°ずれたものになる。 Next, the operation of the tool change arm of ATC (automatic tool changer) equipped in the machining center and the time chart etc. for the operation of the hydraulic pressure generator 30 will be briefly described.
FIG. 10 is a diagram showing the relationship between the rotation angle of the cam member 63A and the stroke of the plunger member 51A of the plunger pump 50A. FIG. 11 is a graph showing the rotation angle of the cam member 63A and the piston stroke of the unclamping hydraulic cylinder 20. It is a diagram which shows a relation. Since the rotation angle of the cam member 63B at this time is different from that of the cam member 63A by 180 °, the relationship between the cam member 63B and the stroke of the plunger member 51B is 180 in FIG. 10 compared with that of the cam member 63A. It will be off-set.
　図１２は、ＡＴＣのＡＴＣアームを鉛直軸回りに旋回させ且つ昇降させるカム機構のカム軸の回転角度（横軸）と、ＡＴＣアームの旋回角度（縦軸）の関係を示す線図であり、図１３は、上記カム軸の回転角度（横軸）と、ＡＴＣアームの昇降ストロークの関係を示す線図である。尚、ＡＴＣアームの昇降ストロークの「正」の値は下方へのストロークを示す。ＡＴＣアームの動作と、アンクランプ用油圧シリンダ２０の動作とを連動させているため、図１０，図１１の横軸の０～３６０°のサイクル時間と、図１２，図１３の横軸の０～３６０°のサイクル時間とは同時間に設定される。 FIG. 12 is a diagram showing the relationship between the rotation angle (horizontal axis) of the cam shaft of the cam mechanism that pivots the ATC arm of the ATC around the vertical axis and raises and lowers it, and the turning angle (vertical axis) of the ATC arm; FIG. 13 is a diagram showing the relationship between the rotation angle (horizontal axis) of the cam shaft and the elevation stroke of the ATC arm. The "positive" value of the up-and-down stroke of the ATC arm indicates a downward stroke. Since the operation of the ATC arm and the operation of the unclamping hydraulic cylinder 20 are linked, the cycle time of 0 to 360 ° in the horizontal axis of FIGS. 10 and 11 and 0 of the horizontal axis in FIGS. 12 and 13. The cycle time of ~ 360 ° is set at the same time.
　これは、電動モータ９０の回転速度を、減速機９２の減速比と、ＡＴＣアームの旋回用モータの回転速度及びその減速機の減速比とを加味して適切に設定しておくことで達成できる。ＡＴＣ制御部１０８からの同期信号と、支持軸７１に付設したディスク部材７９に連係する複数の近接スイッチ８１からの検出信号に基づいて、電動モータ９０のオンとオフを制御する。 This can be achieved by appropriately setting the rotational speed of the electric motor 90 in consideration of the reduction gear ratio of the reduction gear 92, the rotational speed of the swing motor of the ATC arm and the reduction gear ratio of the reduction gear . The on / off control of the electric motor 90 is controlled based on the synchronization signal from the ATC control unit 108 and detection signals from a plurality of proximity switches 81 linked to the disk member 79 attached to the support shaft 71.
　次に、油圧発生装置３０の作用、効果について説明する。
　マシニングセンタで切削加工中には、主軸２内のクランプ機構１５はクランプ状態に保持され、電動モータ９０は停止して、プランジャ部材５１Ｂが下死点にあり、カム部材６３Ｂの第２凹部６６に従動ローラ６１Ｂが係合し、プランジャ部材５１Ａが上死点から少し下降した位置にあり、カム部材６３Ａの第１凹部６５から回転方向に少し移動した点に従動ローラ６１Ａが当接し、プランジャ部材５１Ａ，５１Ｂが初期位置を保持している。 Next, the operation and effects of the hydraulic pressure generation device 30 will be described.
During cutting at the machining center, the clamp mechanism 15 in the main spindle 2 is held in the clamp state, the electric motor 90 is stopped, the plunger member 51B is at the bottom dead center, and driven by the second recess 66 of the cam member 63B. The roller 61B is engaged, and the plunger member 51A is at a position slightly lowered from the top dead center, and the driven roller 61A is in contact with the point slightly moved in the rotational direction from the first recess 65 of the cam member 63A. 51B holds the initial position.
　工具ホルダ８を交換する際には、制御ユニット１００は、ＡＴＣ制御部１０８と減速機付き電動モータ制御部１０９を介してＡＴＣ１０６と電動モータ９０を前記のようなタイムチャートとなるように駆動制御する。その結果、油圧発生装置３０において発生させた油圧をアンクランプ用油圧シリンダ２０の油圧作動室２４へ所定のタイミングで供給し、油圧作動室２５の油圧を排出し、クランプ機構１５をアンクランプ状態に切換えた状態で、電動モータ９０を所定時間停止させる。この際、カム部材６３Ａの第２凹部６６を従動ローラ６１Ａに係合させた状態にしてプランジャ部材５１Ａを下死点に短時間保持する。 When replacing the tool holder 8, the control unit 100 drives and controls the ATC 106 and the electric motor 90 so as to form the time chart as described above via the ATC control unit 108 and the electric motor control unit 109 with a reduction gear. . As a result, the hydraulic pressure generated in the hydraulic pressure generating device 30 is supplied to the hydraulic pressure operating chamber 24 of the unclamping hydraulic cylinder 20 at a predetermined timing, the hydraulic pressure in the hydraulic pressure operating chamber 25 is discharged, and the clamp mechanism 15 is unclamped. In the switched state, the electric motor 90 is stopped for a predetermined time. At this time, the plunger member 51A is held at the bottom dead center for a short time with the second recess 66 of the cam member 63A engaged with the driven roller 61A.
　この工具ホルダ８交換の為にカム部材６３Ａが回転し油圧作動室２４に油圧を供給している時に、カム部材６３Ｂも回転するのでプランジャ部材５１Ｂは第１凹部６５を経由する。そのため、油圧作動室２５の油圧を連通隙間より排出することができる。排出されるまでの余分の油圧はアキュムレータ５９Ｂに貯留される。その後、カム部材６３Ｂの第１凹部６５から回転方向に少し移動した点に従動ローラ６１Ｂが当接した状態になり、上死点から少し下降した位置に保持される。 When the cam member 63A rotates to supply the hydraulic pressure to the hydraulic operation chamber 24 for replacing the tool holder 8, the cam member 63B also rotates, and the plunger member 51B passes through the first recess 65. Therefore, the hydraulic pressure of the hydraulic actuation chamber 25 can be discharged from the communication gap. The excess hydraulic pressure until discharged is stored in the accumulator 59B. Thereafter, the driven roller 61B is in contact with a point slightly moved in the rotational direction from the first concave portion 65 of the cam member 63B, and is held at a position slightly lowered from the top dead center.
　その後、工具ホルダ８をクランプする為に、電動モータ９０の停止を解除してプランジャ部材５１Ａを上昇させ、アンクランプ用油圧シリンダ２０の油圧作動室２４から油圧を抜き、プランジャ部材５１Ｂを下降させ、油圧作動室２５に油圧を供給して、カム部材６３Ｂの第２凹部６６を従動ローラ６１Ｂに係合させた状態（初期位置）にしてプランジャ部材５１Ｂを下死点に保持する。 Thereafter, in order to clamp the tool holder 8, the electric motor 90 is released from the stop to raise the plunger member 51A, remove the hydraulic pressure from the hydraulic operation chamber 24 of the unclamping hydraulic cylinder 20, and lower the plunger member 51B. The hydraulic pressure is supplied to the hydraulic operation chamber 25 so that the second concave portion 66 of the cam member 63B is engaged with the driven roller 61B (initial position) to hold the plunger member 51B at the bottom dead center.
　この工具ホルダ８のクランプ動作中では、カム部材６３Ａの回転に伴いプランジャ部材５１Ａは第１凹部６５を経由するので、油圧作動室２４の油圧を連通隙間より排出することができる。排出されるまでの余分の油圧はアキュムレータ５９Ａに貯留される。その後、プランジャ部材５１Ａは、カム部材６３Ａの第１凹部６５を少し超えたところに従動ローラ６１Ａが当接した状態になり、上死点から少し下降した位置に保持される。 During the clamping operation of the tool holder 8, the plunger member 51A passes through the first recess 65 as the cam member 63A rotates, so that the hydraulic pressure of the hydraulic actuation chamber 24 can be discharged from the communication gap. The excess hydraulic pressure until discharged is stored in the accumulator 59A. Thereafter, the plunger member 51A is in a state in which the driven roller 61A is in contact with a position slightly beyond the first concave portion 65 of the cam member 63A, and is held at a position slightly lowered from the top dead center.
　このように、この油圧発生装置３０は、電動モータ９０により１対のカム機構６０Ａ，６０Ｂを介して１対のプランジャポンプ５０Ａ，５０Ｂを夫々駆動するので、１台の電動モータ９０で２系統の油圧供給系への油圧の供給が可能になる。さらに、アンクランプ動作とクランプ動作を交互にする際に、追従性が高いカム機構６０Ａ，６０Ｂを介することで、電動モータ９０のオン・オフ制御により容易に間欠吐出が可能となる。従って、間欠吐出させる場合に、電動モータ９０の電力消費量を節減できる。 As described above, since the hydraulic pressure generation device 30 drives the pair of plunger pumps 50A and 50B by the electric motor 90 via the pair of cam mechanisms 60A and 60B, two systems of one electric motor 90 are used. Hydraulic pressure can be supplied to the hydraulic pressure supply system. Further, when the unclamping operation and the clamping operation are alternately performed, intermittent discharge can be easily performed by the on / off control of the electric motor 90 through the cam mechanisms 60A and 60B having high followability. Therefore, when intermittently discharging, the power consumption of the electric motor 90 can be reduced.
　カム部材６３Ａ，６３Ｂの外周カム面６４に形成した第２凹部６６を従動ローラ６１Ａ，６１Ｂに係合させることで、プランジャポンプ５０Ａ，５０Ｂのプランジャ部材５１Ａ，５１Ｂが下死点に達した時にカム部材６３Ａ，６３Ｂを精度よく停止させることができる。従って、ブレーキ機構やサーボ機構のない電動モータを採用することが可能となるため、製作コストを節減できる。しかも、自動工具交換の高速化を図ることも可能になる。 By engaging the second recessed portion 66 formed on the outer peripheral cam surface 64 of the cam members 63A, 63B with the driven rollers 61A, 61B, the cams when the plunger members 51A, 51B of the plunger pumps 50A, 50B reach the bottom dead center The members 63A and 63B can be stopped accurately. Therefore, since it becomes possible to employ an electric motor without a brake mechanism or a servo mechanism, the manufacturing cost can be reduced. Moreover, it also becomes possible to speed up automatic tool change.
　本実施例の場合では、プランジャ部材５１Ａ，５１Ｂが上死点に達したときには停止させていないが、電動モータ９０を停止させ上死点で停止させても良い。この場合、カム部材６３Ａ，６３Ｂの外周カム面６４に形成した各第１凹部６５を従動ローラ６１Ａ，６１Ｂに係合させることで、プランジャポンプ５０Ａ，５０Ｂの各プランジャ部材５１Ａ，５１Ｂが上死点に達した時にカム部材６３Ａ，６３Ｂを精度よく停止させることができる。 In the case of the present embodiment, the plunger members 51A and 51B are not stopped when reaching the top dead center, but the electric motor 90 may be stopped and stopped at the top dead center. In this case, the first concave portions 65 formed on the outer peripheral cam surfaces 64 of the cam members 63A and 63B are engaged with the driven rollers 61A and 61B, whereby the plunger members 51A and 51B of the plunger pumps 50A and 50B are at the top dead center. The cam members 63A and 63B can be accurately stopped when reaching the
　電動モータ９０は、短時間定格高トルクモータであるため、連続定格モータに比較して小型のモータで済み、製作コストも安価になる。しかも、カム部材６３Ａ，６３Ｂの回転方向と反対向きに第１凹部６５から第２凹部６６に至る油圧生成用カム面部分６７は、第２凹部６６から第１凹部６５に至る復帰用カム面部分６８よりも長く形成されたため、油圧生成用カム面部分６７の半径増加勾配を小さくして電動モータ９３の小型化を図ることができる。 Since the electric motor 90 is a short time rated high torque motor, it can be a small motor as compared with the continuous rated motor, and the manufacturing cost is also low. Moreover, the oil pressure generating cam surface portion 67 extending from the first recess 65 to the second recess 66 in the direction opposite to the rotational direction of the cam members 63A and 63B is a return cam surface portion extending from the second recess 66 to the first recess 65 Since it is formed to be longer than 68, it is possible to miniaturize the electric motor 93 by reducing the radius increasing slope of the hydraulic pressure generating cam surface portion 67.
　プランジャ部材５１Ａ，５１Ｂがその鉛直軸心回りに回転しないように規制する１対の回転規制機構８６を設けたため、各従動ローラ６１とカム部材６３との軸心を平行に保ち、線接触状態を維持できるため、耐久性を確保することができる。 Since a pair of rotation restricting mechanisms 86 are provided to restrict the plunger members 51A and 51B from rotating about their vertical axes, the axial centers of the driven rollers 61 and the cam member 63 are kept parallel to achieve line contact. Since it can maintain, durability can be secured.
　プランジャポンプ５０Ａ，５０Ｂの下部の外周側部分に対応する部分には、プランジャポンプ５０Ａ，５０Ｂに供給する為の油を収容する油収容室４０が形成されたため、プランジャポンプ５０Ａ，５０Ｂへ油を供給する構造が簡単化する。各プランジャ５２の下端部の外周には下方程小径化するテーパ部５２ａが形成され、プランジャ部材５１Ａ，５１Ｂが上死点のとき、テーパ部５２ａの外周側にプランジャ孔３７と油収容室４０を連通する連通隙間が形成されたため、簡単な構造により、油収容室４０からプランジャ孔３７Ａ，３７Ｂへ油を確実に供給することができ、チェックバルブ等を省略することができ、しかも、クランプ機構１５をクランプ作動させる際には、アンクランプ用油圧シリンダ２０から油収容室４０へ油を戻すことができる。 Since the oil storage chamber 40 for storing oil for supplying the plunger pumps 50A, 50B is formed in a portion corresponding to the outer peripheral side portion of the lower portion of the plunger pumps 50A, 50B, oil is supplied to the plunger pumps 50A, 50B. Structure is simplified. A tapered portion 52a is formed on the outer periphery of the lower end portion of each plunger 52 so as to decrease in diameter toward the lower side, and when the plunger members 51A and 51B are at top dead center, the plunger hole 37 and the oil accommodating chamber 40 are formed on the outer peripheral side of the tapered portion 52a. Since the communication gap communicating is formed, the oil can be reliably supplied from the oil storage chamber 40 to the plunger holes 37A and 37B by a simple structure, and the check valve etc. can be omitted. The oil can be returned from the unclamping hydraulic cylinder 20 to the oil storage chamber 40 when the clamping operation is performed.
　プランジャ部材５１Ａ，５１Ｂの各プランジャ５２には下端開放状の凹入穴５２ｂが形成され、この凹入穴５２ｂとプランジャ孔３７Ａ，３７Ｂにプランジャ部材５１Ａ，５１Ｂを上方へ弾性付勢する圧縮コイルスプリング５７が装着されたため、プランジャ部材５１Ａ，５１Ｂの構造が複雑化することがない。 A lower end open recessed hole 52b is formed in each plunger 52 of the plunger members 51A and 51B, and a compression coil spring which elastically biases the plunger members 51A and 51B upward to the recessed hole 52b and the plunger holes 37A and 37B. Since 57 is mounted, the structure of the plunger members 51A, 51B is not complicated.
　本体ケース３１の上端部分に、平面視にて所定の大きさの油補給用凹部９５が形成され、本体ケース３１に、油補給用凹部９５と油収容室４０の上端を連通する少なくとも２つの流体通路９９ａ，９９ｂが形成されたため、油収容室４０に油を補充する際に、油の流れ込みと、油収容室４０内の空気の排気が円滑になる。 An oil replenishing recess 95 having a predetermined size in plan view is formed in the upper end portion of the main body case 31, and at least two fluids connecting the oil replenishing recess 95 and the upper end of the oil storage chamber 40 to the main body case 31. Since the passages 99a and 99b are formed, when the oil storage chamber 40 is refilled with oil, the inflow of oil and the exhaust of air in the oil storage chamber 40 become smooth.
　プランジャ孔３７Ａ，３７Ｂから油圧を吐出する吐出口３３Ａ，３３Ｂに接続されたアキュムレータ５９Ａ，５９Ｂを設けたため、アンクランプの際に、アンクランプ用油圧シリンダ２０に充填されずに余る余分の油圧をアキュムレータ５９Ａ，５９Ｂに吸収させることができ、また、クランプ機構１５をクランプ作動させる際にプランジャ部材５１が上昇する際に、アキュムレータ５９Ａ，５９Ｂに吸収させた油圧をプランジャ孔３７Ａ，３３Ｂに回収することができる。 Since the accumulators 59A, 59B connected to the discharge ports 33A, 33B for discharging the hydraulic pressure from the plunger holes 37A, 37B are provided, the excess hydraulic pressure remaining without being filled in the unclamping hydraulic cylinder 20 is accumulated when unclamping. 59A, 59B, and when the clamp member 15 is moved up when the clamp mechanism 15 is operated, the hydraulic pressure absorbed by the accumulators 59A, 59B can be recovered in the plunger holes 37A, 33B. it can.
　図１０～図１３に示すように、油圧発生装置３０を、ＡＴＣと同期して作動させることにより、小型の電動モータ９０で駆動される上記の油圧発生装置３０を用いて、工具交換を最短時間で迅速に実行することができる。
　この油圧発生装置３０は、吐出口３３Ａ，３３Ｂに接続されたアキュムレータ５９Ａ，５９Ｂを備えているため、油圧発生装置３０の容量は、アンクランプ用油圧シリンダ２０の油圧作動室２４，２５の容量よりも大きく設定することができるため、この油圧発生装置３０は種々のサイズのアンクランプ用油圧シリンダ２２に接続して使用することができるから、汎用性に優れる。 As shown in FIG. 10 to FIG. 13, by operating the hydraulic pressure generator 30 in synchronization with the ATC, using the above-described hydraulic pressure generator 30 driven by the small electric motor 90, the tool replacement time is shortest. Can be done quickly.
Since the hydraulic pressure generating device 30 includes the accumulators 59A and 59B connected to the discharge ports 33A and 33B, the volume of the hydraulic pressure generating device 30 is equal to the volume of the hydraulic operating chambers 24 and 25 of the unclamping hydraulic cylinder 20. Because the hydraulic pressure generating device 30 can be used by connecting to various sizes of unclamping hydraulic cylinders 22, it is excellent in versatility.
　この油圧発生装置３０は、電動モータ９０により１対のカム機構６０Ａ，６０Ｂを介して１対のプランジャポンプ５０Ａ，５０Ｂを夫々駆動するので、１台の電動モータ９０で２系統への油圧供給が可能になる。１対のカム機構６０Ａ，６０Ｂのカム部材６３Ａ，６３Ｂの形状を異ならせることにより、異なる吐出圧・吐出量の２系統の油圧を発生できるため、種々の油圧アクチュエータへ供給する油圧を発生させることができるから、汎用性に優れる。しかも、油路に方向切換弁や減圧弁を採用する必要がないので、製作コストを節減することができる。カム機構６０Ａ，６０Ｂのカム部材６３Ａ，６３Ｂを交換することで、吐出圧・吐出量を容易に変更することができるから、油圧発生装置を製作する際の汎用性に優れる。 The hydraulic pressure generation device 30 drives the pair of plunger pumps 50A and 50B by the electric motor 90 via the pair of cam mechanisms 60A and 60B, so that hydraulic supply to two systems by one electric motor 90 is possible. It will be possible. By changing the shape of the cam members 63A and 63B of the pair of cam mechanisms 60A and 60B, it is possible to generate two systems of hydraulic pressure of different discharge pressure and discharge amount, so generate hydraulic pressure supplied to various hydraulic actuators. It is excellent in versatility because it can Moreover, since it is not necessary to adopt a directional switching valve or a pressure reducing valve in the oil passage, the manufacturing cost can be reduced. Since the discharge pressure and the discharge amount can be easily changed by replacing the cam members 63A and 63B of the cam mechanisms 60A and 60B, the versatility in manufacturing the hydraulic pressure generating device is excellent.
　カム機構６０Ａ，６０Ｂは、各プランジャ部材５１Ａ，５１Ｂの上死点のタイミングを駆動軸の回転角度にて１８０°異ならせるように構成されたので、駆動軸に作用する負荷の平準化を図ることができるから、電動モータの小型化を図ることができる。 The cam mechanisms 60A and 60B are configured to make the timing of the top dead center of each of the plunger members 51A and 51B different by 180 degrees in the rotation angle of the drive shaft, so balancing of the load acting on the drive shaft is achieved. The size of the electric motor can be reduced.
　次に、前記実施例を部分的に変更する例について説明する。
１］前記減速機付き電動モータ９０の代わりに、減速機付き且つブレーキ付きの電動モータを採用してもよく、電動モータとしては連続定格の電動モータを採用してもよい。
２］前記第１，第２凹部６５，６６の形状は、図示のものに限定されず、従動ローラ６１Ａ，６１Ｂの頂部と係合可能な種々の形状の凹部であってもよい。 Next, an example in which the embodiment is partially changed will be described.
1) Instead of the electric motor 90 with a reduction gear, an electric motor with a reduction gear and with a brake may be adopted, and an electric motor with a continuous rating may be adopted as the electric motor.
2) The shapes of the first and second recesses 65 and 66 are not limited to those shown in the drawings, and may be recesses of various shapes engageable with the tops of the driven rollers 61A and 61B.
３］前記カム機構６０Ａ，６０Ｂは、２つのプランジャ部材５１Ａ，５１Ｂの上死点のタイミングを駆動軸の回転角度にて９０°以上異ならせるように構成されても良い。
４］主軸２を回転駆動する電動モータ１７は、主軸ケース５の内部に組み込んだ内蔵型の電動モータであってもよい。 3) The cam mechanisms 60A and 60B may be configured to make the timing of the top dead center of the two plunger members 51A and 51B different by 90 ° or more at the rotation angle of the drive shaft.
4) The electric motor 17 that rotationally drives the spindle 2 may be a built-in electric motor incorporated in the spindle case 5.
５］前記実施例は、縦向き姿勢の主軸を有する縦型マシニングセンタを例にして説明したが、水平姿勢の主軸を有する横型マシニングセンタにも同様に適用することができるし、パンチングマシンにも同様に適用することができるし、種々の工作機械にも同様に適用することができる。
６］その他、当業者ならば本発明の趣旨を逸脱しない範囲で前記実施例に種々の変更を付加した形態で実施可能である。 5) Although the foregoing embodiment has been described by taking the vertical machining center having the main spindle in the vertical orientation as an example, the present invention can be applied to a horizontal machining center having the main spindle in the horizontal orientation as well. It can be applied, as well as to various machine tools.
6) Besides, those skilled in the art can implement various modifications to the above embodiment without departing from the scope of the present invention.
　この油圧発生装置は、工作機械や建設機械等の種々の油圧アクチュエータに接続される２系統の油圧供給系に油圧を間欠的に供給するのに好適で電力消費量を節減できるものである。２種類の吐出圧・吐出量を容易に設定でき且つ簡単な構成のものである。吐出圧・吐出量の特性を容易に変更できるものである。 This hydraulic pressure generating device is suitable for intermittently supplying hydraulic pressure to two hydraulic pressure supply systems connected to various hydraulic actuators such as machine tools and construction machines, and can reduce power consumption. Two types of discharge pressure and discharge amount can be easily set and have a simple configuration. The characteristics of the discharge pressure and the discharge amount can be easily changed.

Claims (11)

  1. 　２系統の油圧供給系に油圧を供給するための油圧発生装置において、
    　本体ケースと、
    　この本体ケースに夫々立向きに組み込まれ下端に吐出口を夫々有する１対のプランジャポンプと、
    　これらプランジャポンプを駆動する共通の駆動軸及びこの駆動軸を回転駆動する為の減速機付き電動モータと、
    　前記駆動軸に連結されて１対のプランジャポンプを駆動する１対のカム機構とを備え、
    　前記各カム機構は、プランジャポンプのプランジャ部材の上端に水平な支持ピンにて回転自在に装着された従動ローラと、前記駆動軸に装着されて従動ローラの外周面の上端に当接する外周カム面を有するカム部材とを有し、
    　１対のカム機構は、２つのプランジャ部材の上死点のタイミングを駆動軸の回転角度にて９０°以上異ならせるように構成されたことを特徴とする油圧発生装置。     In a hydraulic pressure generating device for supplying hydraulic pressure to two hydraulic pressure supply systems,
    Body case,
    A pair of plunger pumps, each of which is vertically installed in the main body case and has a discharge port at its lower end;
    A common drive shaft for driving the plunger pumps, and an electric motor with a reduction gear for rotationally driving the drive shaft;
    And a pair of cam mechanisms connected to the drive shaft to drive a pair of plunger pumps,
    Each cam mechanism has a driven roller rotatably mounted on the upper end of a plunger member of a plunger pump by a horizontal support pin, and an outer peripheral cam surface mounted on the drive shaft and abutting on the upper end of the outer peripheral surface of the driven roller And a cam member having
    A hydraulic pressure generating device characterized in that a pair of cam mechanisms make the timing of the top dead center of two plunger members differ by 90 degrees or more by the rotation angle of a drive shaft.
  2. 　前記各カム機構のカム部材の外周カム面に、プランジャ部材が上死点に達した時に前記従動ローラに係合する第１凹部と、プランジャ部材が下死点に達した時に前記従動ローラに係合する第２凹部とを形成したことを特徴とする請求項１に記載の油圧発生装置。 When the plunger member reaches the top dead center on the outer peripheral cam surface of the cam member of each cam mechanism, the first recess engaged with the driven roller and the plunger member engaged with the driven roller when the plunger member reaches the bottom dead center The hydraulic pressure generating device according to claim 1, wherein the second concave portion is formed.
  3. 　前記電動モータは、同容量の連続定格モータに比較して高トルクを発揮する短時間定格高トルクモータであり、工作機械の主軸の工具の交換毎に電動モータを起動すると共に自動工具交換装置の自動工具交換アームの動作と前記各カム機構のカム部材の回転動作が同期するように電動モータを制御する制御手段を設けたことを特徴とする請求項２に記載の油圧発生装置。 The electric motor is a short-time rated high torque motor that exerts high torque as compared to a continuous rated motor of the same capacity, and activates the electric motor every time the tool of the spindle of the machine tool is replaced. 3. A hydraulic pressure generating apparatus according to claim 2, further comprising control means for controlling the electric motor so that the operation of the automatic tool change arm and the rotational operation of the cam member of each cam mechanism are synchronized.
  4. 　前記各プランジャ部材がその鉛直軸心回りに回転しないように規制する回転規制機構を設けたことを特徴とする請求項１～３の何れかに記載の油圧発生装置。 The hydraulic pressure generating device according to any one of claims 1 to 3, further comprising a rotation restricting mechanism which restricts the respective plunger members from rotating about their vertical axes.
  5. 　前記各カム部材の外周カム面のうちの、前記カム部材の回転方向と反対向きに第１凹部から第２凹部に至る油圧生成用カム面部分は、前記カム部材の回転方向と反対向きに第２凹部から第１凹部に至る復帰用カム面部分よりも長く形成されたことを特徴とする請求項４に記載の油圧発生装置。 Of the outer peripheral cam surfaces of each cam member, the oil pressure generating cam surface portion extending from the first recess to the second recess in the direction opposite to the rotation direction of the cam member is opposite to the rotation direction of the cam member. 5. The hydraulic pressure generating device according to claim 4, wherein the oil pressure generating device is formed to be longer than the return cam surface portion from the second recess to the first recess.
  6. 　前記各プランジャ部材が上死点から下死点に移動する下降時間は、下死点から上死点に移動する上昇時間よりも長くなるように前記カム部材が形成されていること特徴とする請求項４に記載の油圧発生装置。 The cam member is formed such that the descent time for moving each plunger member from top dead center to bottom dead center is longer than the rise time for moving from bottom dead center to top dead center. The hydraulic pressure generating device according to Item 4.
  7. 　前記各プランジャ部材の下端部分にはプランジャが形成されると共に、前記各プランジャポンプの下端部分には、前記プランジャが挿入されるプランジャ孔が形成され、
    　前記本体ケースのうち、前記各プランジャポンプの下部の外周側部分に対応する部分には、前記各プランジャポンプに供給する為の油を収容する油収容室が形成されたことを特徴とする請求項４に記載の油圧発生装置。     A plunger is formed at a lower end portion of each of the plunger members, and a plunger hole into which the plunger is inserted is formed at a lower end portion of each of the plunger pumps,
    An oil storage chamber for storing oil to be supplied to each of the plunger pumps is formed in a portion corresponding to the outer peripheral side portion of the lower portion of each of the plunger pumps in the main body case. The hydraulic pressure generating device according to 4.
  8. 　前記各プランジャ部材のプランジャの下端部の外周には下方程小径化するテーパ部が形成され、
    　前記各プランジャ部材が上死点のとき、前記テーパ部の外周側に前記プランジャ孔と油収容室を連通する連通隙間が形成されたことを特徴とする請求項７に記載の油圧発生装置。     A tapered portion is formed on the outer periphery of the lower end portion of the plunger of each of the plunger members so as to decrease in diameter toward the lower side,
    The hydraulic pressure generating device according to claim 7, wherein a communication gap communicating the plunger hole and the oil storage chamber is formed on the outer peripheral side of the tapered portion when each of the plunger members is at the top dead center.
  9. 　前記各プランジャ部材のプランジャには下端開放状の凹入穴が形成され、この凹入穴とプランジャ孔にプランジャ部材を上方へ弾性付勢する圧縮コイルスプリングが装着されたことを特徴とする請求項７に記載の油圧発生装置。 A lower end open recess is formed in the plunger of each of the plunger members, and a compression coil spring for elastically urging the plunger member upward is attached to the recess and the plunger hole. The hydraulic pressure generating device according to 7.
  10. 　前記本体ケースの上端部分に、平面視にて所定の大きさの油補給用凹部が形成され、
    　前記本体ケースに、油補給用凹部と油収容室の上端を連通する流体通路が形成されたことを特徴とする請求項７に記載の油圧発生装置。     An oil replenishing recess of a predetermined size is formed in an upper end portion of the main body case in plan view,
    8. The hydraulic pressure generating device according to claim 7, wherein a fluid passage communicating the oil supply recess and the upper end of the oil storage chamber is formed in the main body case.
  11. 　前記各プランジャ孔から油圧を吐出する吐出口に接続されたアキュムレータを設けたことを特徴とする請求項７に記載の油圧発生装置。 The hydraulic pressure generating apparatus according to claim 7, further comprising an accumulator connected to a discharge port for discharging the hydraulic pressure from each of the plunger holes.
PCT/JP2008/003014 2008-10-24 2008-10-24 Hydraulic pressure generation device WO2010046952A1 (en)

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EP3214306A1 (en) * 2016-03-01 2017-09-06 Cummins, Inc. Systems and methods for reducing the oil volume and windage in fuel pumps
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