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WO2006006560A1 - Capacity control valve for clutchless variable displacement swash plate-type compressor - Google Patents

Capacity control valve for clutchless variable displacement swash plate-type compressor Download PDF

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Publication number
WO2006006560A1
WO2006006560A1 PCT/JP2005/012760 JP2005012760W WO2006006560A1 WO 2006006560 A1 WO2006006560 A1 WO 2006006560A1 JP 2005012760 W JP2005012760 W JP 2005012760W WO 2006006560 A1 WO2006006560 A1 WO 2006006560A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
control valve
capacity
swash plate
pressure
Prior art date
Application number
PCT/JP2005/012760
Other languages
French (fr)
Japanese (ja)
Inventor
Yukihiko Taguchi
Original Assignee
Sanden Corporation
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 Sanden Corporation filed Critical Sanden Corporation
Priority to DE602005013969T priority Critical patent/DE602005013969D1/en
Priority to EP05758283A priority patent/EP1775470B1/en
Priority to US11/571,884 priority patent/US20070183904A1/en
Publication of WO2006006560A1 publication Critical patent/WO2006006560A1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14Control
    • F04B27/16Control of pumps with stationary cylinders
    • F04B27/18Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804Controlled by crankcase pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14Control
    • F04B27/16Control of pumps with stationary cylinders
    • F04B27/18Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804Controlled by crankcase pressure
    • F04B2027/1809Controlled pressure
    • F04B2027/1813Crankcase pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14Control
    • F04B27/16Control of pumps with stationary cylinders
    • F04B27/18Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804Controlled by crankcase pressure
    • F04B2027/1822Valve-controlled fluid connection
    • F04B2027/1827Valve-controlled fluid connection between crankcase and discharge chamber
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14Control
    • F04B27/16Control of pumps with stationary cylinders
    • F04B27/18Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804Controlled by crankcase pressure
    • F04B2027/184Valve controlling parameter
    • F04B2027/1854External parameters
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14Control
    • F04B27/16Control of pumps with stationary cylinders
    • F04B27/18Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804Controlled by crankcase pressure
    • F04B2027/184Valve controlling parameter
    • F04B2027/1859Suction pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14Control
    • F04B27/16Control of pumps with stationary cylinders
    • F04B27/18Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804Controlled by crankcase pressure
    • F04B2027/1863Controlled by crankcase pressure with an auxiliary valve, controlled by
    • F04B2027/1881Suction pressure

Definitions

  • the present invention relates to a capacity control valve for a clutchless variable displacement swash plate compressor that is directly connected to a drive source without a clutch.
  • Capacity control of a clutchless variable displacement swash plate compressor that opens and closes a valve hole formed in a communication path between a discharge chamber and a crank chamber of a variable displacement swash plate compressor to control the discharge capacity of the compressor
  • a valve hole that communicates with the crank chamber at all times, an internal control valve that opens and closes the valve hole by a valve element that operates in response to expansion and contraction of a pressure-sensitive member that senses suction pressure, and an internal control valve
  • the internal control valve is set to an operating state in which the valve body opens and closes the valve hole in response to expansion and contraction of the pressure-sensitive member, and an inoperative state in which the valve body opens the valve hole regardless of expansion and contraction of the pressure-sensitive member.
  • Patent Document 1 discloses a capacity control valve that includes an electromagnetic solenoid for switching and controls the discharge capacity so that the suction pressure and the discharge pressure have a predetermined correlation. Patent Document 1 describes that in the region of Pd> Pd, the capacity control characteristic is expressed by the following equation.
  • Patent Document 1 Japanese Patent Laid-Open No. 7-127566
  • the capacity control valve disclosed in Patent Document 1 has the following problems. Since the discharge pressure Pd biases the valve body in the closing direction, in order to demagnetize the electromagnetic solenoid and force the valve body to open, the force of the opening panel of the electromagnetic solenoid must be (Pd-Pc) S or higher.
  • an object of the present invention is to provide a capacity control valve for a clutchless variable capacity swash plate compressor that can be made smaller than the capacity control valve disclosed in Patent Document 1. There is to do.
  • a capacity control valve of a clutchless variable displacement swash plate compressor opens and closes a communication path between a discharge chamber and a crank chamber of the variable displacement swash plate compressor.
  • An internal control valve that opens and closes the valve hole by a valve element that operates in response to expansion and contraction of the pressure-sensitive member, and is connected to the internal control valve, and the internal control valve is used to expand and contract the pressure-sensitive member.
  • the valve body has an operation switching device that switches between an operation state in which the valve body opens and closes the valve hole and a non-operation state in which the valve body opens the valve hole regardless of expansion and contraction of the pressure-sensitive member. It consists of the capacity
  • valve hole is always in communication with the discharge chamber, the force by which the discharge pressure Pd urges the valve body in the closing direction is reduced compared to the capacity control valve of Patent Document 1 described above.
  • the switching device that forcibly opens the valve disc can be downsized.
  • the operation switching device has an electromagnetic solenoid, and when the electromagnetic solenoid is energized, the internal control valve is activated, and the electromagnetic solenoid is demagnetized. It is preferable that the internal control valve is configured to be in an inactive state when it is! With this configuration, the variable capacity swash plate compressor can be switched between the capacity control state and the minimum capacity state by exciting and demagnetizing the electromagnetic solenoid.
  • the control device for the variable capacity swash plate compressor is simplified.
  • the electromagnetic solenoid positions the internal control valve in the operating position when the electromagnetic solenoid is excited, and the movable iron core connected to the internal control valve. It is preferable to have a positioning member. By arranging the positioning member, it is possible to position the internal control valve to the operating position by exciting the electromagnetic solenoid, and it is possible to switch to the operating state of the variable capacity swash plate compressor by exciting the electromagnetic solenoid. .
  • the positioning member is formed by one end of the pressure-sensitive member and an end surface of the case of the electromagnetic solenoid. Positioning member force By forming one end of the pressure-sensitive member and the case of the electromagnetic solenoid, it is not necessary to separately provide a special positioning member, and the structure of the capacity control valve is simplified.
  • the electromagnetic solenoid has an open panel that urges the movable iron core in a direction away from the fixed iron core force.
  • the control valve is deactivated. If the electromagnetic solenoid release panel renders the internal control valve inactive, there is no need to separately provide a panel for disabling the internal control valve, and the structure of the capacity control valve is simplified.
  • the internal control valve has a pressure-sensitive rod formed in the valve housing and slidably inserted into a hole communicating with the valve hole and connected to the valve body.
  • the cross-sectional area of the pressure-sensitive rod is set larger than the cross-sectional area of the valve hole.
  • the internal control valve has a pressure-sensitive rod formed in a valve housing and slidably inserted into a hole communicating with the valve hole and connected to the valve body.
  • the cross-sectional area of the pressure-sensitive rod is set smaller than the cross-sectional area of the valve hole.
  • the valve hole is always in communication with the discharge chamber, so that the force by which the discharge pressure urges the valve body in the closing direction is provided.
  • the switching device for forcibly opening the valve body can be made smaller than the capacity control valve of Patent Document 1. Therefore, the capacity control valve of the clutchless variable capacity swash plate compressor according to the present invention can be reduced in size compared to the capacity control valve of Patent Document 1.
  • FIG. 1 is a longitudinal sectional view of a clutchless variable displacement swash plate compressor provided with a displacement control valve according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view of a capacity control valve according to an embodiment of the present invention
  • FIGS. 2 (A) and 2 (B) are diagrams showing the operation of the internal control valve when the electromagnetic solenoid is excited
  • FIG. 2 (C) is a diagram showing the operation of the internal control valve when the electromagnetic solenoid is demagnetized
  • FIG. 2 (D) is an enlarged partial sectional view of the internal control valve.
  • FIG. 3 is a control characteristic diagram of a displacement control valve according to an embodiment of the present invention
  • FIG. 3 (A) is a control characteristic diagram when Sr> Sv
  • FIG. 3 (B) is a control characteristic when Sr> Sv.
  • a variable capacity swash plate compressor 1 includes a main shaft 10, a rotor 11 fixed to the main shaft 10, and a swash plate 12 supported on the main shaft 10 so that the tilt angle is variable.
  • the swash plate 12 is connected to the rotor 11 via a link mechanism 13 that allows the tilt angle of the swash plate 12 to be changed, and rotates in synchronization with the rotor 11 and the main shaft 10.
  • the piston 15 is engaged with the swash plate 12 via a pair of slides 14 that are in sliding contact with the outer peripheral edge of the swash plate 12.
  • the piston 15 is inserted into a cylinder bore 16a formed in the cylinder block 16 !.
  • a plurality of pistons 15 are arranged around the main shaft 10 at intervals in the circumferential direction.
  • a crank chamber 17 that houses the main shaft 10, the rotor 11, and the swash plate 12 is formed by a cylinder block 16 and a dish-shaped front housing 18.
  • the main shaft 10 extends through the front housing 18 to the outside.
  • a shaft sealing member 19 for sealing the front housing penetrating portion of the main shaft 10 is disposed in the front housing 18.
  • a pulley 20 is fixed to the tip of the main shaft 10.
  • the pulley 20 is connected to a vehicle engine (not shown) via a belt (not shown), for example.
  • a cylinder head 23 that forms a suction chamber 21 and a discharge chamber 22 is disposed at a position opposite to the front housing 18 of the cylinder block 16.
  • the suction chamber 21 is connected to an external circuit, for example, an evaporator (not shown) provided in the refrigeration cycle of the vehicle air conditioner via a suction port (not shown).
  • the discharge chamber 22 is connected to a discharge port (not shown).
  • it is connected to an external circuit, for example, a condenser (not shown) provided in the refrigeration cycle of the vehicle air conditioner.
  • a valve plate 24 is formed between the cylinder block 16 and the cylinder head 23.
  • the valve plate 24 has a suction port 2la communicating with the cylinder bore 16a and a discharge port 22a.
  • a discharge valve and a suction valve are mounted on the valve plate 24 (not shown).
  • the crank chamber 17 and the suction chamber 21 communicate with each other through an orifice hole 24 a formed in the valve plate 24.
  • the front housing 18, the cylinder block 16, the valve plate 24, and the cylinder head 23 are integrated by a plurality of through bolts 25 that are spaced apart from each other along a circumference centered on the main shaft 10. It is concluded.
  • a capacity control valve 2 for controlling the discharge capacity of the variable capacity swash plate compressor 1 is fitted and fixed in a recess 26 formed in the cylinder head 23 adjacent to the discharge chamber 22. As shown in FIGS. 1 and 2, the capacity control valve 2 includes an internal control valve 100 and an electromagnetic solenoid 120.
  • the internal control valve 100 has a cylindrical valve housing 101.
  • Two O-rings 101a and 101b closely fitted to the outer peripheral surface of the valve housing 101 and one O-ring 121a tightly fitted to the outer peripheral surface of the case 121 of the electromagnetic solenoid 120
  • the valve housing 101 is formed with a transverse partition wall 104 that divides the internal space of the valve housing 101 into a pressure-sensitive chamber 102 on one end side and a valve chamber 103 on the other end side.
  • the transverse partition wall 104 is formed with a rod through hole 105 communicating with the pressure sensing chamber 102 and a valve hole 106 communicating with the valve chamber 103.
  • the rod through hole 105 and the valve hole 106 are arranged coaxially and communicate with each other.
  • a communication hole 107 is formed in the horizontal partition wall 104 so as to pass through the horizontal partition wall 104 in the radial direction through a communication portion between the rod through hole 105 and the valve hole 106.
  • the pressure sensing chamber 102 communicates with the suction chamber 21 via a communication hole 108 formed in the peripheral wall of the valve housing 101, a closed space 27c, and a communication passage 23a formed in the cylinder head 23. ing .
  • the communication hole 107 communicates with the discharge chamber 22 via a closed space 27b and a communication passage 23b formed in the cylinder head 23.
  • the valve hole 106 communicating with the communication hole 107 is always in communication with the discharge chamber 22.
  • the valve chamber 103 communicates with the crank chamber 17 through a closed space 27a, a communication path 23c formed in the cylinder head 23, and a communication path 16b formed in the cylinder block 16. ing.
  • a base assembly 109 functioning as a pressure sensing device in which the inside is evacuated and the panel is arranged is disposed.
  • One end of the pressure sensitive rod 110 is connected to one end 109a of the bellows assembly 109, and the other end is slidably inserted into the rod through hole 105.
  • a small-diameter rod 111 extending from the other end of the pressure-sensitive rod 110 is passed through the valve hole 106 so as to be freely movable.
  • a valve body 112 connected to the end of the small-diameter rod 111 is disposed in the valve chamber 103.
  • a panel 113 that urges the valve body 112 toward the valve hole 106 is disposed in the valve chamber 103.
  • the internal control valve 100 is formed by a series of structures from the valve housing 101 to the panel 113.
  • the end of the valve housing 101 of the internal control valve 100 on the pressure sensing chamber 102 side is press-fitted and fixed to one end of the case 121 of the electromagnetic solenoid 120.
  • the O-ring 121a that forms the closed space 27c is fitted to the outer peripheral surface on one end side of the case 121.
  • the electromagnetic solenoid 120 includes a fixed iron core 122 disposed in the case 121, a movable iron core 123 disposed with one end facing the one end of the fixed iron core 122, and the movable iron core 123 from the fixed iron core. It has an open panel 124 that urges in a separating direction, and an electromagnetic coil 125 that surrounds the fixed iron core 122 and the movable iron core 123.
  • the space for accommodating the movable iron core 123 communicates with the pressure sensing chamber 102 and is at the same pressure as the pressure sensing chamber 102.
  • the other end 109b of the bellows assembly 109 is connected to the other end of the movable iron core 123.
  • the other end 109b is disposed so as to be engageable with the end surface inner edge portion 121a in the vicinity of the one end of the case 121 of the electromagnetic solenoid 120.
  • the electromagnetic coil 125 is excited to attach the open panel 124 as shown in FIGS. 2 (A) and 2 (B).
  • the movable iron core 123 toward the fixed iron core 122 against the force, and bring the other end 10 9b of the bellows assembly 109 into contact with the inner edge 12 lb of the end face 121 of the electromagnetic solenoid 120.
  • the internal control valve 100 enters an operation state in which the valve body 112 opens and closes the valve hole 106 in response to expansion and contraction of the bellows assembly 109 that is a pressure-sensitive member.
  • the bellows assembly 109 contracts and is connected to the bellows assembly 109 via the pressure-sensitive rod 110 and the small-diameter rod 111, as shown in FIG.
  • the valve hole 106 is closed. Thereby, the supply of the high-pressure refrigerant gas from the discharge chamber 22 to the crank chamber 17 is stopped.
  • the orifice passage 24a has a sufficient cross-sectional area to discharge blow-by gas leaking from the cylinder bore 16a to the crank chamber 17 to the suction chamber 21 when the piston 15 compresses the refrigerant gas in the cylinder bore 16a.
  • the crank chamber pressure gradually decreases.
  • the swash plate inclination angle increases, the discharge capacity of the variable displacement swash plate compressor 1 increases!], And the suction pressure gradually decreases.
  • the opening and closing of the valve hole 106 is repeated so that the suction pressure becomes a set value, and the discharge capacity of the variable capacity swash plate compressor 1 is variably controlled.
  • the other end 109b of the bellows assembly 109 receives the biasing force of the open panel 124 and the inner edge 121b of the end surface of the case 121 of the electromagnetic solenoid 120 as shown in FIG. ,
  • the bellows assembly 109 is positioned in the inoperative position and the internal control valve 100 is positioned in the inoperative position.
  • the internal control valve 100 is in an inoperative state in which the valve body 112 opens the valve hole 106 regardless of the expansion and contraction of the bellows assembly 109 that is a pressure-sensitive member.
  • the lift amount of the valve body 112 is regulated by the end 109 a of the bellows assembly 109 coming into contact with the horizontal partition wall 104.
  • variable capacity swash plate compressor 1 In this state, high-pressure refrigerant gas is supplied from the discharge chamber 22 to the crank chamber 17, the crank chamber pressure increases, the swash plate inclination decreases to the minimum inclination, and the discharge capacity of the variable capacity swash plate compressor 1 increases. Reduced to minimum capacity and maintained at minimum capacity. Since the discharge capacity of the variable capacity swash plate compressor 1 can be minimized by demagnetizing the electromagnetic coil 125, the capacity control valve 2 is connected to an external drive source without a clutch. Can be used as a variable capacity swash plate compressor.
  • the discharge pressure Pd acts on the valve body 112 and the pressure-sensitive rod 110, so the force that the discharge pressure Pd urges in the direction to close the valve body 112 is (Sr ⁇ Sv) Pd. Since (Sr ⁇ Sv) is very small, (Sr ⁇ Sv) Pd is much smaller than PdSv in Patent Document 1 described above. Therefore, the capacity control valve 2 can be reduced in size compared to the capacity control valve of Patent Document 1.
  • the slope of the correlation line of Ps with respect to Pd is-(Sr-Sv) Z ⁇ Sb- (Sr-Sv) ⁇ , so if the cross-sectional area Sr of the pressure-sensitive rod is changed, The inclination can be changed without changing the cross sectional area Sv of the valve hole and the effective cross sectional area Sb of the bellows assembly, which are the basic specifications of the capacity control valve 2. Therefore, the capacity control characteristic can be easily changed.
  • the slope of the correlation line of Ps with respect to Pd is — (Sr—Sv) Z ⁇ Sb— (Sr—Sv) ⁇ , so the cross sectional area Sv of the valve hole 106 must be changed.
  • the bellows effective cross-sectional area Sb can be reduced without changing the slope of the correlation line of Ps with respect to Pd. Therefore, downsizing is easy.
  • the capacity control valve 2 can switch the clutchless variable capacity swash plate compressor 1 between the capacity control state and the minimum capacity state by exciting and demagnetizing the electromagnetic solenoid 120. If used, the control device of the variable capacity swash plate compressor 1 is simplified.
  • the positioning member constituted by the other end 109b of the bellows assembly 109 and the end surface inner edge 121b of the case 121 of the electromagnetic solenoid 120 is disposed, Positioning of the internal control valve 100 to the operating position by excitation is possible, and switching to the capacity control state of the variable displacement swash plate compressor 1 by excitation of the electromagnetic solenoid 120 is possible.
  • the positioning member is formed by the other end 109b of the bellows assembly 109 and the inner edge 121b of the end surface 121 of the case 121 of the electromagnetic solenoid 120, so there is no need to separately provide a special positioning member.
  • the valve structure has been simplified.
  • variable capacity swash plate compressor 1 discharge capacity is reduced.
  • variable capacity swash plate compressor 1 is operated with an excessive load, and the occurrence of damage is suppressed.
  • the positioning member is formed by the other end 109b of the bellows assembly 109 and the inner edge portion 12 lb of the end surface 121 of the electromagnetic solenoid 120.
  • the adsorbing portion of the movable iron core 123 and the fixed iron core 122 A positioning member may be formed.
  • an adjustment member that adjusts the urging force of the panel 113 from the outside may be provided.
  • the present invention can be widely used for a capacity control valve of a clutchless variable capacity swash plate compressor.
  • it is suitable as a capacity control valve for a compressor provided in a refrigeration cycle of a vehicle air conditioner.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

A capacity control valve for a clutchless variable displacement swash plate-type compressor, in which the discharge capacity of the compressor is controlled by opening and closing a communication path between a discharge chamber and a crank chamber. The capacity control valve has a valve hole (106) formed in the communication path and always communicating with the discharge chamber, an inside control valve (100) for opening and closing the valve hole (106) by a valve body (112) operated in response to expansion and contraction of a pressure sensing member (109) for sensing a suction pressure, and an operation switchover device (120) connected to the inside control valve and switching the inside control valve between an operation state where the valve body opens and closes the valve hole in response to the expansion and contraction of the pressure sensing member and a non-operation state where the valve body opens the valve hole independent of the expansion and retraction of the pressure sensing member. In this capacity control valve, because a discharge pressure Pd acts on both the valve body (112) and a pressure sensing rod (110), that force of the discharge pressure Pd which urges the valve body (112) in a valve opening direction is (Sr - Sv)Pd. The capacity control valve (2) can be made smaller than conventional capacity control valves because (Sr - Sv) is very small.

Description

明 細 書  Specification
クラッチレス可変容量斜板式圧縮機の容量制御弁  Capacity control valve for clutchless variable displacement swash plate compressor
技術分野  Technical field
[0001] 本発明は、クラッチを介することなく駆動源に直結したクラッチレス可変容量斜板式 圧縮機の容量制御弁に関する。  The present invention relates to a capacity control valve for a clutchless variable displacement swash plate compressor that is directly connected to a drive source without a clutch.
背景技術  Background art
[0002] 可変容量斜板式圧縮機の吐出室とクランク室との間の連通路に形成された弁孔を 開閉して圧縮機の吐出容量を制御するクラッチレス可変容量斜板式圧縮機の容量 制御弁であって、クランク室に常時連通する弁孔と、吸入圧を感知する感圧部材の 伸縮に応答して動作する弁体により弁孔を開閉する内部制御弁と、内部制御弁に連 結され、内部制御弁を、感圧部材の伸縮に応答して弁体が弁孔を開閉する作動状 態と、感圧部材の伸縮に関わり無く弁体が弁孔を開放する非作動状態とに切り替え る電磁ソレノイドとを備え、吸入圧と吐出圧とが所定の相関を有するように吐出容量を 制御する容量制御弁が特許文献 1に開示されている。この特許文献 1には、 Pd>Pd の領域では、容量制御特性は次式で表される旨記載されて 、る。  [0002] Capacity control of a clutchless variable displacement swash plate compressor that opens and closes a valve hole formed in a communication path between a discharge chamber and a crank chamber of a variable displacement swash plate compressor to control the discharge capacity of the compressor A valve hole that communicates with the crank chamber at all times, an internal control valve that opens and closes the valve hole by a valve element that operates in response to expansion and contraction of a pressure-sensitive member that senses suction pressure, and an internal control valve The internal control valve is set to an operating state in which the valve body opens and closes the valve hole in response to expansion and contraction of the pressure-sensitive member, and an inoperative state in which the valve body opens the valve hole regardless of expansion and contraction of the pressure-sensitive member. Patent Document 1 discloses a capacity control valve that includes an electromagnetic solenoid for switching and controls the discharge capacity so that the suction pressure and the discharge pressure have a predetermined correlation. Patent Document 1 describes that in the region of Pd> Pd, the capacity control characteristic is expressed by the following equation.
0  0
Ps = P - (Pd-Pc) S /S  Ps = P-(Pd-Pc) S / S
0 1 2  0 1 2
ここで、  here,
Pd:吐出圧力、  Pd: discharge pressure,
Pc :クランク室圧力、  Pc: Crank chamber pressure,
Ps :吸入圧力、  Ps: suction pressure,
P :べローズの等価内圧、  P: Equivalent internal pressure of bellows,
0  0
s :弁孔横断面積、  s: valve hole cross-sectional area,
1  1
s :べローズ有効横断面積、  s: Bellows effective cross-sectional area,
2  2
である。  It is.
特許文献 1 :特開平 7— 127566号公報  Patent Document 1: Japanese Patent Laid-Open No. 7-127566
発明の開示  Disclosure of the invention
発明が解決しょうとする課題 [0003] し力しながら、上記特許文献 1に開示された容量制御弁には以下の問題がある。 吐出圧力 Pdが弁体を閉弁する方向へ付勢するので、電磁ソレノイドを消磁して弁 体を強制開弁させるためには、電磁ソレノイドの開放パネの力を (Pd—Pc) S 以上に Problems to be solved by the invention However, the capacity control valve disclosed in Patent Document 1 has the following problems. Since the discharge pressure Pd biases the valve body in the closing direction, in order to demagnetize the electromagnetic solenoid and force the valve body to open, the force of the opening panel of the electromagnetic solenoid must be (Pd-Pc) S or higher.
1 設定する必要がある。吐出圧力 Pdが高い領域で弁体を強制開弁させるためにはバ ネ力の大きな開放パネを使用する必要があり、電磁ソレノイドを励磁して開放パネの パネ力に杭して可動鉄心を吸引するために大きな電磁力を発生させる必要があり、 電磁ソレノイドが大型化する。  1 Must be set. In order to forcibly open the valve body in the region where the discharge pressure Pd is high, it is necessary to use an open panel with a large spring force. The electromagnetic core is excited and piled on the panel force of the open panel to attract the movable iron core. It is necessary to generate a large electromagnetic force to increase the size of the electromagnetic solenoid.
[0004] そこで本発明の目的は、上記のような問題に鑑み、特許文献 1に開示された容量制 御弁よりも小型化が可能なクラッチレス可変容量斜板式圧縮機の容量制御弁を提供 することにある。  In view of the above problems, an object of the present invention is to provide a capacity control valve for a clutchless variable capacity swash plate compressor that can be made smaller than the capacity control valve disclosed in Patent Document 1. There is to do.
課題を解決するための手段  Means for solving the problem
[0005] 上記課題を解決するために、本発明に係るクラッチレス可変容量斜板式圧縮機の 容量制御弁は、可変容量斜板式圧縮機の吐出室とクランク室との間の連通路を開閉 して可変容量斜板式圧縮機の吐出容量を制御するクラッチレス可変容量斜板式圧 縮機の容量制御弁であって、前記連通路に形成され、前記吐出室に常時連通する 弁孔と、吸入圧を感知する感圧部材の伸縮に応答して動作する弁体により前記弁孔 を開閉する内部制御弁と、該内部制御弁に連結され、該内部制御弁を、前記感圧部 材の伸縮に応答して前記弁体が前記弁孔を開閉する作動状態と、前記感圧部材の 伸縮に関わり無く前記弁体が前記弁孔を開放する非作動状態とに切り替える作動切 り替え装置とを有することを特徴とする容量制御弁からなる。 In order to solve the above problems, a capacity control valve of a clutchless variable displacement swash plate compressor according to the present invention opens and closes a communication path between a discharge chamber and a crank chamber of the variable displacement swash plate compressor. A capacity control valve of a clutchless variable capacity swash plate type compressor for controlling the discharge capacity of the variable capacity swash plate compressor, a valve hole formed in the communication passage and always communicating with the discharge chamber, and a suction pressure An internal control valve that opens and closes the valve hole by a valve element that operates in response to expansion and contraction of the pressure-sensitive member, and is connected to the internal control valve, and the internal control valve is used to expand and contract the pressure-sensitive member. In response, the valve body has an operation switching device that switches between an operation state in which the valve body opens and closes the valve hole and a non-operation state in which the valve body opens the valve hole regardless of expansion and contraction of the pressure-sensitive member. It consists of the capacity | capacitance control valve characterized by this.
[0006] 本発明においては、弁孔を吐出室に常時連通させたので、吐出圧力 Pdが弁体を 閉弁する方向へ付勢する力を前述の特許文献 1の容量制御弁に比べて低減でき、 弁体を強制開弁させる切り替え装置を小型化することができる。  [0006] In the present invention, since the valve hole is always in communication with the discharge chamber, the force by which the discharge pressure Pd urges the valve body in the closing direction is reduced compared to the capacity control valve of Patent Document 1 described above. The switching device that forcibly opens the valve disc can be downsized.
[0007] このような本発明に係る容量制御弁においては、上記作動切り替え装置は、電磁ソ レノイドを有し、該電磁ソレノイドを励磁した時に上記内部制御弁が作動状態になり、 電磁ソレノイドを消磁した時に内部制御弁が非作動状態になるように構成されて!、る ことが好ましい。このように構成すれば、電磁ソレノイドの励磁、消磁により、可変容量 斜板式圧縮機を、容量制御状態と、最小容量状態とに切り替えることができるので、 可変容量斜板式圧縮機の制御装置が簡素化される。 In such a capacity control valve according to the present invention, the operation switching device has an electromagnetic solenoid, and when the electromagnetic solenoid is energized, the internal control valve is activated, and the electromagnetic solenoid is demagnetized. It is preferable that the internal control valve is configured to be in an inactive state when it is! With this configuration, the variable capacity swash plate compressor can be switched between the capacity control state and the minimum capacity state by exciting and demagnetizing the electromagnetic solenoid. The control device for the variable capacity swash plate compressor is simplified.
[0008] また、本発明に係る容量制御弁にぉ 、ては、電磁ソレノイドは、内部制御弁と連結 された可動鉄心と、電磁ソレノイドを励磁した時に内部制御弁を作動位置に位置決 めする位置決め部材とを有することが好ましい。位置決め部材を配設することにより、 電磁ソレノイドの励磁による内部制御弁の作動位置への位置決めが可能になり、電 磁ソレノイドの励磁による可変容量斜板式圧縮機の作動状態への切り替えが可能に なる。  [0008] Further, in the capacity control valve according to the present invention, the electromagnetic solenoid positions the internal control valve in the operating position when the electromagnetic solenoid is excited, and the movable iron core connected to the internal control valve. It is preferable to have a positioning member. By arranging the positioning member, it is possible to position the internal control valve to the operating position by exciting the electromagnetic solenoid, and it is possible to switch to the operating state of the variable capacity swash plate compressor by exciting the electromagnetic solenoid. .
[0009] また、本発明に係る容量制御弁にお!、ては、上記位置決め部材は、感圧部材のー 端と電磁ソレノイドのケースの端面とにより形成されて 、ることが好ま 、。位置決め 部材力 感圧部材の一端と電磁ソレノイドのケースとにより形成されていることにより、 特別な位置決め部材を別途配設する必要が無くなり、容量制御弁の構造が簡素化さ れる。  [0009] Further, in the capacity control valve according to the present invention, it is preferable that the positioning member is formed by one end of the pressure-sensitive member and an end surface of the case of the electromagnetic solenoid. Positioning member force By forming one end of the pressure-sensitive member and the case of the electromagnetic solenoid, it is not necessary to separately provide a special positioning member, and the structure of the capacity control valve is simplified.
[0010] また、本発明に係る容量制御弁においては、上記電磁ソレノイドは、可動鉄心を固 定鉄心力 離間する方向へ付勢する開放パネを有し、電磁ソレノイドを消磁すると、 開放パネにより内部制御弁が非作動状態になることが好ましい。電磁ソレノイドの開 放パネが内部制御弁を非作動状態にすれば、内部制御弁を非作動状態にするパネ を別途配設する必要が無くなり、容量制御弁の構造が簡素化される。  [0010] Further, in the capacity control valve according to the present invention, the electromagnetic solenoid has an open panel that urges the movable iron core in a direction away from the fixed iron core force. Preferably, the control valve is deactivated. If the electromagnetic solenoid release panel renders the internal control valve inactive, there is no need to separately provide a panel for disabling the internal control valve, and the structure of the capacity control valve is simplified.
[0011] また、本発明の好ましい態様においては、上記内部制御弁は、弁ハウジングに形 成され弁孔に連通する孔に摺動可能に挿通され弁体に連結された感圧ロッドを有し ており、該感圧ロッドの横断面積は弁孔横断面積よりも大きく設定される。このように 構成すれば、吐出圧力が増加すると吸入圧力が低下する制御特性になるので、吐 出圧力の高い高熱負荷領域では吐出容量が増加する。従って、この容量制御弁を 有する可変容量斜板式圧縮機を備える冷房装置は、吐出圧力の高い高熱負荷領域 でも冷房性能が悪化しない。  [0011] In a preferred aspect of the present invention, the internal control valve has a pressure-sensitive rod formed in the valve housing and slidably inserted into a hole communicating with the valve hole and connected to the valve body. The cross-sectional area of the pressure-sensitive rod is set larger than the cross-sectional area of the valve hole. With this configuration, since the suction pressure decreases when the discharge pressure increases, the suction pressure decreases. Therefore, the discharge capacity increases in a high heat load region where the discharge pressure is high. Therefore, the cooling device provided with the variable capacity swash plate compressor having the capacity control valve does not deteriorate the cooling performance even in the high heat load region where the discharge pressure is high.
[0012] あるいは、本発明の好ましい態様においては、上記内部制御弁は、弁ハウジングに 形成され前記弁孔に連通する孔に摺動可能に挿通され前記弁体に連結された感圧 ロッドを有しており、該感圧ロッドの横断面積は弁孔横断面積よりも小さく設定される 。このように構成すれば、吐出圧力が増加すると吸入圧力が増加する制御特性にな るので、吐出圧力の高い領域では吐出容量が低減する。この結果、圧縮機が過大な 負荷で作動する事態の発生が抑制される。 Alternatively, in a preferred aspect of the present invention, the internal control valve has a pressure-sensitive rod formed in a valve housing and slidably inserted into a hole communicating with the valve hole and connected to the valve body. The cross-sectional area of the pressure-sensitive rod is set smaller than the cross-sectional area of the valve hole. With this configuration, the control characteristic is such that the suction pressure increases as the discharge pressure increases. Therefore, the discharge capacity is reduced in the region where the discharge pressure is high. As a result, the occurrence of a situation where the compressor operates with an excessive load is suppressed.
発明の効果  The invention's effect
[0013] 本発明に係るクラッチレス可変容量斜板式圧縮機の容量制御弁においては、弁孔 を吐出室に常時連通させたので、吐出圧力が弁体を閉弁する方向へ付勢する力を 前述の特許文献 1の容量制御弁に比べて低減でき、弁体を強制開弁させる切り替え 装置を特許文献 1の容量制御弁に比べて小型化することができる。従って、本発明 に係るクラッチレス可変容量斜板式圧縮機の容量制御弁は、特許文献 1の容量制御 弁に比べて小型化が可能である。  [0013] In the capacity control valve of the clutchless variable capacity swash plate compressor according to the present invention, the valve hole is always in communication with the discharge chamber, so that the force by which the discharge pressure urges the valve body in the closing direction is provided. Compared with the capacity control valve of Patent Document 1, the switching device for forcibly opening the valve body can be made smaller than the capacity control valve of Patent Document 1. Therefore, the capacity control valve of the clutchless variable capacity swash plate compressor according to the present invention can be reduced in size compared to the capacity control valve of Patent Document 1.
図面の簡単な説明  Brief Description of Drawings
[0014] [図 1]本発明の実施例に係る容量制御弁を備えたクラッチレス可変容量斜板式圧縮 機の縦断面図である。  FIG. 1 is a longitudinal sectional view of a clutchless variable displacement swash plate compressor provided with a displacement control valve according to an embodiment of the present invention.
[図 2]本発明の実施例に係る容量制御弁の断面図であり、図 2 (A)、図 2 (B)は電磁 ソレノイドが励磁されている時の内部制御弁の作動を示す図であり、図 2 (C)は電磁 ソレノイドが消磁されている時の内部制御弁の作動を示す図であり、図 2 (D)は内部 制御弁の拡大部分断面図である。  FIG. 2 is a cross-sectional view of a capacity control valve according to an embodiment of the present invention, and FIGS. 2 (A) and 2 (B) are diagrams showing the operation of the internal control valve when the electromagnetic solenoid is excited. FIG. 2 (C) is a diagram showing the operation of the internal control valve when the electromagnetic solenoid is demagnetized, and FIG. 2 (D) is an enlarged partial sectional view of the internal control valve.
[図 3]本発明の実施例に係る容量制御弁の制御特性図であり、図 3 (A)は Sr>Svの 場合の制御特性図、図 3 (B)は Srく Svの場合の制御特性図である。  FIG. 3 is a control characteristic diagram of a displacement control valve according to an embodiment of the present invention, FIG. 3 (A) is a control characteristic diagram when Sr> Sv, and FIG. 3 (B) is a control characteristic when Sr> Sv. FIG.
符号の説明  Explanation of symbols
[0015] 1:クラッチレス可変容量斜板式圧縮機 [0015] 1: Clutchless variable displacement swash plate compressor
2 :容量制御弁  2: Capacity control valve
17 :クランク室  17: Crank chamber
21 :吸入室  21: Inhalation chamber
22 :吐出室  22: Discharge chamber
26 :凹部  26: recess
100 :内部制御弁  100: Internal control valve
101 :弁ハウジング  101: Valve housing
102 :感圧室 103 :弁室 102: Pressure sensitive chamber 103: Valve room
106 :弁孔  106: Valve hole
109 :ベローズ組立体  109: Bellows assembly
110 :感圧ロッド  110: Pressure sensitive rod
112 :弁体  112: Valve
120 :電磁ソレノイド  120: Electromagnetic solenoid
発明を実施するための最良の形態  BEST MODE FOR CARRYING OUT THE INVENTION
[0016] 以下に、本発明に係るクラッチレス可変容量斜板式圧縮機の容量制御弁の望まし い実施の形態について、図面を参照して説明する。  Hereinafter, preferred embodiments of the capacity control valve of the clutchless variable capacity swash plate compressor according to the present invention will be described with reference to the drawings.
図 1、図 2に、本発明の一実施例に係る容量制御弁を備えた可変容量斜板式圧縮 機を示す。図 1に示すように、可変容量型斜板式圧縮機 1は、主軸 10と、主軸 10に 固定されたローター 11と、傾角可変に主軸 10に支持された斜板 12とを備えて 、る。 斜板 12は、斜板 12の傾角変更を許容するリンク機構 13を介してローター 11に連結 され、ローター 11および主軸 10に同期して回転する。斜板 12の外周縁部に摺接す る一対のシユー 14を介してピストン 15が斜板 12に係合されている。ピストン 15は、シ リンダブロック 16に形成されたシリンダボア 16aに挿入されて!、る。主軸 10周りに周 方向に互いに間隔を隔てて、複数のピストン 15が配設されている。  1 and 2 show a variable displacement swash plate compressor provided with a displacement control valve according to an embodiment of the present invention. As shown in FIG. 1, a variable capacity swash plate compressor 1 includes a main shaft 10, a rotor 11 fixed to the main shaft 10, and a swash plate 12 supported on the main shaft 10 so that the tilt angle is variable. The swash plate 12 is connected to the rotor 11 via a link mechanism 13 that allows the tilt angle of the swash plate 12 to be changed, and rotates in synchronization with the rotor 11 and the main shaft 10. The piston 15 is engaged with the swash plate 12 via a pair of slides 14 that are in sliding contact with the outer peripheral edge of the swash plate 12. The piston 15 is inserted into a cylinder bore 16a formed in the cylinder block 16 !. A plurality of pistons 15 are arranged around the main shaft 10 at intervals in the circumferential direction.
[0017] 主軸 10、ローター 11、斜板 12を収容するクランク室 17が、シリンダブロック 16と、 皿状のフロントハウジング 18により形成されている。主軸 10は、フロントハウジング 18 を貫通して外部へ延びている。フロントハウジング 18内には、主軸 10のフロントハウ ジング貫通部を密封する軸封部材 19が配設されている。主軸 10の先端部にはブー リー 20が固定されている。可変容量型斜板式圧縮機 1が車両用空調装置の冷凍サ イタルに使用される圧縮機である場合には、プーリー 20は、例えば、図示しないベル トを介して、図示しない車両エンジンに連結される。  A crank chamber 17 that houses the main shaft 10, the rotor 11, and the swash plate 12 is formed by a cylinder block 16 and a dish-shaped front housing 18. The main shaft 10 extends through the front housing 18 to the outside. A shaft sealing member 19 for sealing the front housing penetrating portion of the main shaft 10 is disposed in the front housing 18. A pulley 20 is fixed to the tip of the main shaft 10. When the variable displacement swash plate compressor 1 is a compressor used for a refrigeration site of a vehicle air conditioner, the pulley 20 is connected to a vehicle engine (not shown) via a belt (not shown), for example. The
[0018] シリンダブロック 16のフロントハウジング 18とは反対側の位置には、吸入室 21と吐 出室 22とを形成するシリンダヘッド 23が配設されている。吸入室 21は、図示しない 吸入ポートを介して、外部回路、例えば、車両用空調装置の冷凍サイクルに設けられ た図示しない蒸発器に接続されている。吐出室 22は、図示しない吐出ポートを介し て、外部回路、例えば、車両用空調装置の冷凍サイクルに設けられた図示しない凝 縮器に接続されている。 A cylinder head 23 that forms a suction chamber 21 and a discharge chamber 22 is disposed at a position opposite to the front housing 18 of the cylinder block 16. The suction chamber 21 is connected to an external circuit, for example, an evaporator (not shown) provided in the refrigeration cycle of the vehicle air conditioner via a suction port (not shown). The discharge chamber 22 is connected to a discharge port (not shown). In addition, it is connected to an external circuit, for example, a condenser (not shown) provided in the refrigeration cycle of the vehicle air conditioner.
[0019] シリンダブロック 16とシリンダヘッド 23との間にシリンダボア 16aに連通する吸入口 2 laと吐出口 22aとが形成された弁板 24が配設されている。弁板 24に吐出弁と吸入 弁とが装着されている(図示略)。弁板 24に形成されたオリフィス孔 24aを介して、クラ ンク室 17と吸入室 21とが連通している。  [0019] A valve plate 24 is formed between the cylinder block 16 and the cylinder head 23. The valve plate 24 has a suction port 2la communicating with the cylinder bore 16a and a discharge port 22a. A discharge valve and a suction valve are mounted on the valve plate 24 (not shown). The crank chamber 17 and the suction chamber 21 communicate with each other through an orifice hole 24 a formed in the valve plate 24.
[0020] フロントハウジング 18、シリンダブロック 16、弁板 24、シリンダヘッド 23は、主軸 10 を中心とする円周に沿って互いに間隔を隔てて配設された複数の通しボルト 25によ り一体に締結されている。  [0020] The front housing 18, the cylinder block 16, the valve plate 24, and the cylinder head 23 are integrated by a plurality of through bolts 25 that are spaced apart from each other along a circumference centered on the main shaft 10. It is concluded.
[0021] 吐出室 22に隣接してシリンダヘッド 23に形成された凹部 26内に、可変容量斜板式 圧縮機 1の吐出容量を制御する容量制御弁 2が嵌合固定されている。図 1、図 2に示 すように、容量制御弁 2は、内部制御弁 100と、電磁ソレノイド 120とを備えている。  A capacity control valve 2 for controlling the discharge capacity of the variable capacity swash plate compressor 1 is fitted and fixed in a recess 26 formed in the cylinder head 23 adjacent to the discharge chamber 22. As shown in FIGS. 1 and 2, the capacity control valve 2 includes an internal control valve 100 and an electromagnetic solenoid 120.
[0022] 内部制御弁 100は、円筒状の弁ハウジング 101を有している。弁ハウジング 101の 外周面に緊密に嵌合された 2個の Oリング 101a、 101bと、電磁ソレノイド 120のケー ス 121の外周面に緊密に嵌合された 1個の Oリング 121aとにより、弁ハウジング 101 の周囲に、 3個の閉鎖空間 27a、 27b、 27cが形成されている。  The internal control valve 100 has a cylindrical valve housing 101. Two O-rings 101a and 101b closely fitted to the outer peripheral surface of the valve housing 101 and one O-ring 121a tightly fitted to the outer peripheral surface of the case 121 of the electromagnetic solenoid 120 Around the housing 101, three closed spaces 27a, 27b, 27c are formed.
[0023] 弁ハウジング 101には、弁ハウジング 101の内部空間を一端側の感圧室 102と他 端側の弁室 103とに分割する横隔壁 104が形成されている。横隔壁 104には、感圧 室 102に連通するロッド揷通孔 105と、弁室 103に連通する弁孔 106とが形成されて いる。ロッド揷通孔 105と弁孔 106とは同軸上に配設されて互いに連通している。ロッ ド揷通孔 105と弁孔 106との連通部を通って横隔壁 104を径方向に貫通する連通孔 107が横隔壁 104に形成されている。  The valve housing 101 is formed with a transverse partition wall 104 that divides the internal space of the valve housing 101 into a pressure-sensitive chamber 102 on one end side and a valve chamber 103 on the other end side. The transverse partition wall 104 is formed with a rod through hole 105 communicating with the pressure sensing chamber 102 and a valve hole 106 communicating with the valve chamber 103. The rod through hole 105 and the valve hole 106 are arranged coaxially and communicate with each other. A communication hole 107 is formed in the horizontal partition wall 104 so as to pass through the horizontal partition wall 104 in the radial direction through a communication portion between the rod through hole 105 and the valve hole 106.
[0024] 感圧室 102は、弁ハウジング 101の周壁に形成された連通孔 108と、閉鎖空間 27 cと、シリンダヘッド 23に形成された連通路 23aとを介して、吸入室 21に連通している 。連通孔 107は、閉鎖空間 27bと、シリンダヘッド 23に形成された連通路 23bを介し て、吐出室 22に連通している。連通孔 107に連通する弁孔 106は吐出室 22に常時 連通している。弁室 103は、閉鎖空間 27aと、シリンダヘッド 23に形成された連通路 2 3cと、シリンダブロック 16に形成された連通路 16bとを介して、クランク室 17に連通し ている。 [0024] The pressure sensing chamber 102 communicates with the suction chamber 21 via a communication hole 108 formed in the peripheral wall of the valve housing 101, a closed space 27c, and a communication passage 23a formed in the cylinder head 23. ing . The communication hole 107 communicates with the discharge chamber 22 via a closed space 27b and a communication passage 23b formed in the cylinder head 23. The valve hole 106 communicating with the communication hole 107 is always in communication with the discharge chamber 22. The valve chamber 103 communicates with the crank chamber 17 through a closed space 27a, a communication path 23c formed in the cylinder head 23, and a communication path 16b formed in the cylinder block 16. ing.
[0025] 感圧室 102内に、内部を真空にしてパネを配置した感圧装置として機能するべ口 ーズ組立体 109が配設されて!/、る。感圧ロッド 110の一端がベローズ組立体 109の 一端 109aに連結され、他端がロッド揷通孔 105に摺動可能に挿入されている。感圧 ロッド 110の他端力 伸びる小径ロッド 111が、遊動可能に弁孔 106に揷通されてい る。小径ロッド 111の端部に連結された弁体 112が弁室 103内に配設されている。弁 体 112を弁孔 106に接近する方向へ付勢するパネ 113が弁室 103内に配設されて いる。内部制御弁 100は、弁ハウジング 101からパネ 113までの一連の構造によって 形成されている。  [0025] In the pressure sensing chamber 102, a base assembly 109 functioning as a pressure sensing device in which the inside is evacuated and the panel is arranged is disposed. One end of the pressure sensitive rod 110 is connected to one end 109a of the bellows assembly 109, and the other end is slidably inserted into the rod through hole 105. A small-diameter rod 111 extending from the other end of the pressure-sensitive rod 110 is passed through the valve hole 106 so as to be freely movable. A valve body 112 connected to the end of the small-diameter rod 111 is disposed in the valve chamber 103. A panel 113 that urges the valve body 112 toward the valve hole 106 is disposed in the valve chamber 103. The internal control valve 100 is formed by a series of structures from the valve housing 101 to the panel 113.
[0026] 内部制御弁 100の弁ハウジング 101の、感圧室 102側端部が、電磁ソレノイド 120 のケース 121の一端に圧入固定されている。ケース 121の一端側の外周面に、前述 のように、閉鎖空間 27cを形成する Oリング 121aが嵌合されている。  The end of the valve housing 101 of the internal control valve 100 on the pressure sensing chamber 102 side is press-fitted and fixed to one end of the case 121 of the electromagnetic solenoid 120. As described above, the O-ring 121a that forms the closed space 27c is fitted to the outer peripheral surface on one end side of the case 121.
[0027] 電磁ソレノイド 120は、ケース 121内に配設された固定鉄心 122と、固定鉄心 122 の一端に一端を対畤させて配設された可動鉄心 123と、可動鉄心 123を固定鉄心か ら離間する方向へ付勢する開放パネ 124と、固定鉄心 122と可動鉄心 123とを取り 囲む電磁コイル 125とを有している。可動鉄心 123を収容する空間は、感圧室 102 に連通しており、感圧室 102と同圧になっている。可動鉄心 123の他端に、ベローズ 組立体 109の他端 109bが連結されている。他端 109bは、電磁ソレノイド 120のケー ス 121の、上記一端近傍部の端面内縁部 121 aに係合可能に配設されて 、る。  [0027] The electromagnetic solenoid 120 includes a fixed iron core 122 disposed in the case 121, a movable iron core 123 disposed with one end facing the one end of the fixed iron core 122, and the movable iron core 123 from the fixed iron core. It has an open panel 124 that urges in a separating direction, and an electromagnetic coil 125 that surrounds the fixed iron core 122 and the movable iron core 123. The space for accommodating the movable iron core 123 communicates with the pressure sensing chamber 102 and is at the same pressure as the pressure sensing chamber 102. The other end 109b of the bellows assembly 109 is connected to the other end of the movable iron core 123. The other end 109b is disposed so as to be engageable with the end surface inner edge portion 121a in the vicinity of the one end of the case 121 of the electromagnetic solenoid 120.
[0028] 次に、容量制御弁 2の作動について説明する。  Next, the operation of the capacity control valve 2 will be described.
クラッチレス可変容量斜板式圧縮機 1を容量制御状態で作動させる場合には、電 磁コイル 125を励磁して、図 2 (A)、図 2 (B)に示すように、開放パネ 124の付勢力に 抗して可動鉄心 123を固定鉄心 122側へ移動させ、ベローズ組立体 109の他端 10 9bを電磁ソレノイド 120のケース 121の端面内縁部 12 lbに当接させて、ベローズ組 立体 109を作動位置に位置決めし、ひいては内部制御弁 100を作動位置に位置決 めする。内部制御弁 100は、感圧部材であるべローズ組立体 109の伸縮に応答して 弁体 112が弁孔 106を開閉する作動状態になる。  When the clutchless variable displacement swash plate compressor 1 is operated in the capacity control state, the electromagnetic coil 125 is excited to attach the open panel 124 as shown in FIGS. 2 (A) and 2 (B). Move the movable iron core 123 toward the fixed iron core 122 against the force, and bring the other end 10 9b of the bellows assembly 109 into contact with the inner edge 12 lb of the end face 121 of the electromagnetic solenoid 120. Position it in the operating position, and consequently position the internal control valve 100 in the operating position. The internal control valve 100 enters an operation state in which the valve body 112 opens and closes the valve hole 106 in response to expansion and contraction of the bellows assembly 109 that is a pressure-sensitive member.
[0029] 内部制御弁 100が作動状態にある時には、吸入圧が設定値よりも低いと、図 2 (B) に示すように、ベローズ組立体 109が伸長し、感圧ロッド 110と小径ロッド 111とを介 してべローズ糸且立体 109に連結された弁体 112力 ベローズ糸且立体 109の伸長に応 答して弁孔 106を開く。吐出室 22から、連通孔 23bと連通孔 107と弁孔 106と弁室 1 03と閉鎖空間 27aと連通路 23cと連通路 16bとを介して、高圧の冷媒ガスがクランク 室 17に供給される。クランク室圧力が上昇し、斜板傾角が減少し、可変容量斜板式 圧縮機 1の吐出容量が減少し、吸入圧が徐々に上昇する。 [0029] When the internal control valve 100 is in an operating state, if the suction pressure is lower than the set value, the flow rate is reduced as shown in FIG. As shown in Fig. 1, the bellows assembly 109 extends, and the valve body 112 connected to the bellows thread and solid 109 via the pressure-sensitive rod 110 and the small diameter rod 111 responds to the expansion of the bellows thread and solid 109. Then, the valve hole 106 is opened. From the discharge chamber 22, high-pressure refrigerant gas is supplied to the crank chamber 17 through the communication hole 23b, the communication hole 107, the valve hole 106, the valve chamber 103, the closed space 27a, the communication path 23c, and the communication path 16b. . The crank chamber pressure increases, the swash plate tilt angle decreases, the discharge capacity of the variable capacity swash plate compressor 1 decreases, and the suction pressure gradually increases.
[0030] 吸入圧が設定値を超えると、図 2 (A)に示すように、ベローズ組立体 109が収縮し、 感圧ロッド 110と小径ロッド 111とを介してべローズ組立体 109に連結された弁体 11 2力 ベローズ組立体 109の収縮に応答して弁孔 106を閉じる。これにより、吐出室 2 2からクランク室 17への高圧冷媒ガスの供給が停止する。オリフィス通路 24aは、ビス トン 15がシリンダボア 16a内の冷媒ガスを圧縮する際にシリンダボア 16aからクランク 室 17へ漏出するブローバイガスを吸入室 21へ排出するのに充分な断面積を有して いるので、クランク室圧は徐々に低下する。クランク室圧が低下すると、斜板傾角が 増加し、可変容量斜板式圧縮機 1の吐出容量が増力!]して、吸入圧が徐々に低下す る。 [0030] When the suction pressure exceeds the set value, the bellows assembly 109 contracts and is connected to the bellows assembly 109 via the pressure-sensitive rod 110 and the small-diameter rod 111, as shown in FIG. In response to the contraction of the bellows assembly 109, the valve hole 106 is closed. Thereby, the supply of the high-pressure refrigerant gas from the discharge chamber 22 to the crank chamber 17 is stopped. The orifice passage 24a has a sufficient cross-sectional area to discharge blow-by gas leaking from the cylinder bore 16a to the crank chamber 17 to the suction chamber 21 when the piston 15 compresses the refrigerant gas in the cylinder bore 16a. The crank chamber pressure gradually decreases. When the crank chamber pressure decreases, the swash plate inclination angle increases, the discharge capacity of the variable displacement swash plate compressor 1 increases!], And the suction pressure gradually decreases.
[0031] このように、内部制御弁 100の作動により、吸入圧が設定値になるように弁孔 106 の開閉が繰り返され、可変容量斜板式圧縮機 1の吐出容量が可変制御される。  As described above, by the operation of the internal control valve 100, the opening and closing of the valve hole 106 is repeated so that the suction pressure becomes a set value, and the discharge capacity of the variable capacity swash plate compressor 1 is variably controlled.
[0032] 電磁コイル 125を消磁すると、図 2 (C)に示すように、開放パネ 124の付勢力を受け てべローズ組立体 109の他端 109bが電磁ソレノイド 120のケース 121の端面内縁部 121bから離れ、ベローズ組立体 109は非作動位置に位置決めされ、内部制御弁 10 0は非作動位置に位置決めされる。これにより、内部制御弁 100は、感圧部材である ベローズ組立体 109の伸縮に関わり無く弁体 112が弁孔 106を開放する非作動状 態となる。弁体 112のリフト量は、ベローズ組立体 109の一端 109aが横隔壁 104に 当接することにより、規制される。この状態では、吐出室 22から高圧の冷媒ガスがクラ ンク室 17に供給され、クランク室圧力が上昇し、斜板傾角が最小傾角まで減少し、可 変容量斜板式圧縮機 1の吐出容量が最小容量まで減少し、最小容量に維持される。 電磁コイル 125の消磁により、可変容量斜板式圧縮機 1の吐出容量を最小にできる ので、容量制御弁 2は、クラッチを介することなく外部駆動源に直結されたクラッチレ ス可変容量斜板式圧縮機として使用可能である。 When the electromagnetic coil 125 is demagnetized, the other end 109b of the bellows assembly 109 receives the biasing force of the open panel 124 and the inner edge 121b of the end surface of the case 121 of the electromagnetic solenoid 120 as shown in FIG. , The bellows assembly 109 is positioned in the inoperative position and the internal control valve 100 is positioned in the inoperative position. As a result, the internal control valve 100 is in an inoperative state in which the valve body 112 opens the valve hole 106 regardless of the expansion and contraction of the bellows assembly 109 that is a pressure-sensitive member. The lift amount of the valve body 112 is regulated by the end 109 a of the bellows assembly 109 coming into contact with the horizontal partition wall 104. In this state, high-pressure refrigerant gas is supplied from the discharge chamber 22 to the crank chamber 17, the crank chamber pressure increases, the swash plate inclination decreases to the minimum inclination, and the discharge capacity of the variable capacity swash plate compressor 1 increases. Reduced to minimum capacity and maintained at minimum capacity. Since the discharge capacity of the variable capacity swash plate compressor 1 can be minimized by demagnetizing the electromagnetic coil 125, the capacity control valve 2 is connected to an external drive source without a clutch. Can be used as a variable capacity swash plate compressor.
[0033] 容量制御弁 2の制御特性は次式(1)で表される。  [0033] The control characteristic of the displacement control valve 2 is expressed by the following equation (1).
Ps=— (Sr-Sv) Pd/{Sb- (Sr— Sv) } + (f+ a Sv-F) /{Sb- (Sr— Sv) } (1)  Ps = — (Sr-Sv) Pd / {Sb- (Sr— Sv)} + (f + a Sv-F) / {Sb- (Sr— Sv)} (1)
ここで、  here,
Pd:吐出圧力、  Pd: discharge pressure,
a:クランク室と吸入室の圧力差、  a: Pressure difference between crank chamber and suction chamber,
F:内部にパネを配設したべローズ組立体 109の付勢力、  F: Energizing force of bellows assembly 109 with a panel inside,
f :パネ 113の付勢力、  f: Power of panel 113,
Sb:ベローズ組立体 109の有効横断面積、  Sb: effective cross-sectional area of bellows assembly 109,
Sv:弁孔 106の横断面積、  Sv: cross-sectional area of valve hole 106,
Sr:感圧ロッド 110の横断面積、  Sr: Cross-sectional area of pressure-sensitive rod 110,
である。  It is.
[0034] 容量制御弁 2においては、吐出圧 Pdは弁体 112と感圧ロッド 110とに作用するので 、吐出圧力 Pdが弁体 112を閉弁する方向へ付勢する力は、(Sr— Sv) Pdとなる。 (S r—Sv)は微小なので、(Sr— Sv) Pdは、前述の特許文献 1の PdSvに比べて遥かに 小さい。従って、容量制御弁 2は特許文献 1の容量制御弁に比べて小型化できる。  In the capacity control valve 2, the discharge pressure Pd acts on the valve body 112 and the pressure-sensitive rod 110, so the force that the discharge pressure Pd urges in the direction to close the valve body 112 is (Sr− Sv) Pd. Since (Sr−Sv) is very small, (Sr−Sv) Pd is much smaller than PdSv in Patent Document 1 described above. Therefore, the capacity control valve 2 can be reduced in size compared to the capacity control valve of Patent Document 1.
[0035] 前述の特許文献 1の容量制御弁においては、 Pdに対する Psの相関線の傾きは S ZS なので、容量制御弁の基本仕様である弁孔の横断面積 S やべローズ有効 [0035] In the displacement control valve of Patent Document 1 described above, the slope of the correlation line of Ps with respect to Pd is S ZS.
1 2 1 1 2 1
横断面積 s を変更しなければ前記傾きを変更することができない。すなわち容量制  The inclination cannot be changed without changing the cross-sectional area s. That is, capacity system
2  2
御特性を容易に変更することができない。これに対し、容量制御弁 2においては、 Pd に対する Psの相関線の傾きは—(Sr—Sv)Z{Sb— (Sr-Sv) }なので、感圧ロッド の断面積 Srを変更すれば、容量制御弁 2の基本仕様である弁孔の横断面積 Svやべ ローズ組立体の有効横断面積 Sbを変更しなくても、前記傾きを変更することができる 。従って、容量制御特性を容易に変更することができる。  The characteristics cannot be easily changed. On the other hand, in the capacity control valve 2, the slope of the correlation line of Ps with respect to Pd is-(Sr-Sv) Z {Sb- (Sr-Sv)}, so if the cross-sectional area Sr of the pressure-sensitive rod is changed, The inclination can be changed without changing the cross sectional area Sv of the valve hole and the effective cross sectional area Sb of the bellows assembly, which are the basic specifications of the capacity control valve 2. Therefore, the capacity control characteristic can be easily changed.
[0036] また、前述の特許文献 1の容量制御弁においては、 Pdに対する Psの相関線の傾き を変更することなぐひいては容量制御特性を変更することなぐ容量制御弁を小型 化しようとすると、 S 、S を同時に小さくする必要を生ずる。弁孔の横断面積 S を小 さくすると、弁体を強制開放した後に弁孔を通ってクランク室へ流入する高圧冷媒ガ スの流速が減少し、斜板式圧縮機の容量が最小容量になるまでに要する時間が増 加し、容量制御性能が悪化する。従って、小型化が困難である。これに対し、容量制 御弁 2においては、 Pdに対する Psの相関線の傾きは—(Sr— Sv)Z{Sb— (Sr— Sv ) }なので、弁孔 106の横断面積 Svを変更することなぐ感圧ロッド 110の横断面積 Sr を変更することにより、 Pdに対する Psの相関線の傾きを変更することなぐベローズ 有効横断面積 Sbを小さくすることでできる。従って、小型化が容易である。 [0036] In the capacity control valve of Patent Document 1 described above, if it is attempted to downsize the capacity control valve without changing the slope of the correlation line of Ps with respect to Pd and thus without changing the capacity control characteristic, S , S must be simultaneously reduced. Small cross-sectional area S of valve hole As a result, the flow rate of the high-pressure refrigerant gas flowing into the crank chamber through the valve hole after forcibly opening the valve body decreases, and the time required for the capacity of the swash plate compressor to increase to the minimum capacity increases. Capacity control performance deteriorates. Therefore, downsizing is difficult. On the other hand, in the capacity control valve 2, the slope of the correlation line of Ps with respect to Pd is — (Sr—Sv) Z {Sb— (Sr—Sv)}, so the cross sectional area Sv of the valve hole 106 must be changed. By changing the cross-sectional area Sr of the pressure-sensitive rod 110, the bellows effective cross-sectional area Sb can be reduced without changing the slope of the correlation line of Ps with respect to Pd. Therefore, downsizing is easy.
[0037] 容量制御弁 2は、電磁ソレノイド 120の励磁、消磁により、クラッチレス可変容量斜 板式圧縮機 1を、容量制御状態と、最小容量状態とに切り替えることができるので、 容量制御弁 2を使用すれば、可変容量斜板式圧縮機 1の制御装置が簡素化される。  [0037] The capacity control valve 2 can switch the clutchless variable capacity swash plate compressor 1 between the capacity control state and the minimum capacity state by exciting and demagnetizing the electromagnetic solenoid 120. If used, the control device of the variable capacity swash plate compressor 1 is simplified.
[0038] また、容量制御弁 2においては、ベローズ組立体 109の他端 109bと電磁ソレノイド 120のケース 121の端面内縁部 121bとにより構成される位置決め部材を配設したの で、電磁ソレノイド 120の励磁による内部制御弁 100の作動位置への位置決めが可 能であり、電磁ソレノイド 120の励磁による可変容量斜板式圧縮機 1の容量制御状態 への切り替えが可能である。容量制御弁 2においては、ベローズ組立体 109の他端 1 09bと電磁ソレノイド 120のケース 121の端面内縁部 121bとにより位置決め部材を形 成したので、特別な位置決め部材を別途配設する必要が無くなり、弁の構造が簡素 化されている。  [0038] In the capacity control valve 2, since the positioning member constituted by the other end 109b of the bellows assembly 109 and the end surface inner edge 121b of the case 121 of the electromagnetic solenoid 120 is disposed, Positioning of the internal control valve 100 to the operating position by excitation is possible, and switching to the capacity control state of the variable displacement swash plate compressor 1 by excitation of the electromagnetic solenoid 120 is possible. In the displacement control valve 2, the positioning member is formed by the other end 109b of the bellows assembly 109 and the inner edge 121b of the end surface 121 of the case 121 of the electromagnetic solenoid 120, so there is no need to separately provide a special positioning member. The valve structure has been simplified.
[0039] また、容量制御弁 2においては、電磁ソレノイド 120の開放パネ 124が内部制御弁 100を非作動状態にするので、内部制御弁 100を非作動状態にするパネを別途配 設する必要が無くなり、弁の構造が簡素化されている。  [0039] Further, in the capacity control valve 2, since the open panel 124 of the electromagnetic solenoid 120 puts the internal control valve 100 into the non-operating state, it is necessary to separately arrange a panel for putting the internal control valve 100 into the non-operating state. The valve structure has been simplified.
[0040] 容量制御弁 2にお 、て、感圧ロッド 110の横断面積 Srを弁孔横断面積 Svよりも大き く設定すると、図 3 (A)に示すように、吐出圧力 Pdが増加すると吸入圧力 Psが低下 する制御特性になるので、吐出圧力の高 、高熱負荷領域では可変容量斜板式圧縮 機 1の吐出容量が増加する。従って、容量制御弁 2を有する可変容量斜板式圧縮機 1を備えた冷房装置は、吐出圧力の高い高熱負荷領域でも冷房性能が悪ィ匕しない。  [0040] In the displacement control valve 2, when the cross-sectional area Sr of the pressure-sensitive rod 110 is set larger than the cross-sectional area Sv of the valve hole, as shown in Fig. 3 (A), the suction is increased when the discharge pressure Pd increases. Since the control characteristic is such that the pressure Ps decreases, the discharge capacity of the variable capacity swash plate compressor 1 increases in the high discharge pressure and high heat load range. Therefore, the cooling device provided with the variable capacity swash plate compressor 1 having the capacity control valve 2 does not deteriorate the cooling performance even in the high heat load region where the discharge pressure is high.
[0041] 一方、容量制御弁 2にお 、て、感圧ロッド 110の横断面積 Srを弁孔横断面積 Svよ りも小さく設定すると、図 3 (B)に示すように、吐出圧力 Pdが増加すると吸入圧力 Ps が増加する制御特性になるので、吐出圧力の高!ヽ領域では可変容量斜板式圧縮機[0041] On the other hand, when the cross sectional area Sr of the pressure sensitive rod 110 is set smaller than the valve hole cross sectional area Sv in the displacement control valve 2, the discharge pressure Pd increases as shown in FIG. 3 (B). Then suction pressure Ps Since the control characteristics increase, the variable capacity swash plate compressor is used in the high discharge pressure range.
1の吐出容量が低減する。この結果、可変容量斜板式圧縮機 1が過大な負荷で作動 し、損傷する事態の発生が抑制される。 1 discharge capacity is reduced. As a result, the variable capacity swash plate compressor 1 is operated with an excessive load, and the occurrence of damage is suppressed.
[0042] 上記実施例では、ベローズ組立体 109の他端 109bと電磁ソレノイド 120のケース 1 21の端面内縁部 12 lbとにより位置決め部材を形成したが、可動鉄心 123と固定鉄 心 122の吸着部とにより位置決め部材を形成してもよい。さらに、パネ 113の付勢力 を外部から調整する調整部材を設けてもょ ヽ。  In the above embodiment, the positioning member is formed by the other end 109b of the bellows assembly 109 and the inner edge portion 12 lb of the end surface 121 of the electromagnetic solenoid 120. However, the adsorbing portion of the movable iron core 123 and the fixed iron core 122 A positioning member may be formed. Furthermore, an adjustment member that adjusts the urging force of the panel 113 from the outside may be provided.
産業上の利用可能性  Industrial applicability
[0043] 本発明は、クラッチレス可変容量斜板式圧縮機の容量制御弁に広く利用可能であ る。とくに、車両用空調装置の冷凍サイクルに設けられる圧縮機の容量制御弁として 好適なものである。 [0043] The present invention can be widely used for a capacity control valve of a clutchless variable capacity swash plate compressor. In particular, it is suitable as a capacity control valve for a compressor provided in a refrigeration cycle of a vehicle air conditioner.

Claims

請求の範囲 The scope of the claims
[1] 可変容量斜板式圧縮機の吐出室とクランク室との間の連通路を開閉して可変容量 斜板式圧縮機の吐出容量を制御するクラッチレス可変容量斜板式圧縮機の容量制 御弁であって、前記連通路に形成され、前記吐出室に常時連通する弁孔と、吸入圧 を感知する感圧部材の伸縮に応答して動作する弁体により前記弁孔を開閉する内 部制御弁と、該内部制御弁に連結され、該内部制御弁を、前記感圧部材の伸縮に 応答して前記弁体が前記弁孔を開閉する作動状態と、前記感圧部材の伸縮に関わ り無く前記弁体が前記弁孔を開放する非作動状態とに切り替える作動切り替え装置 とを有することを特徴とするクラッチレス可変容量斜板式圧縮機の容量制御弁。  [1] The capacity control valve of the clutchless variable displacement swash plate compressor that controls the discharge capacity of the variable displacement swash plate compressor by opening and closing the communication path between the discharge chamber and the crank chamber of the variable displacement swash plate compressor An internal control that opens and closes the valve hole by a valve hole that is formed in the communication passage and communicates with the discharge chamber at all times, and a valve element that operates in response to expansion and contraction of a pressure-sensitive member that senses suction pressure. A valve and an internal control valve connected to the internal control valve. The internal control valve is related to an operating state in which the valve element opens and closes the valve hole in response to expansion and contraction of the pressure sensitive member, and expansion and contraction of the pressure sensitive member. And a switching control device for switching the valve body to a non-operating state in which the valve hole is opened. A capacity control valve for a clutchless variable displacement swash plate compressor.
[2] 前記作動切り替え装置は、電磁ソレノイドを有し、該電磁ソレノイドを励磁した時に 前記内部制御弁が作動状態になり、前記電磁ソレノイドを消磁した時に前記内部制 御弁が非作動状態になることを特徴とする、請求項 1に記載のクラッチレス可変容量 斜板式圧縮機の容量制御弁。  [2] The operation switching device has an electromagnetic solenoid, and when the electromagnetic solenoid is energized, the internal control valve is activated, and when the electromagnetic solenoid is demagnetized, the internal control valve is deactivated. The capacity control valve for a clutchless variable capacity swash plate compressor according to claim 1, wherein:
[3] 前記電磁ソレノイドは、前記内部制御弁と連結された可動鉄心と、前記電磁ソレノィ ドを励磁した時に前記内部制御弁を作動位置に位置決めする位置決め部材とを有 することを特徴とする、請求項 2に記載のクラッチレス可変容量斜板式圧縮機の容量 制御弁。 [3] The electromagnetic solenoid includes a movable iron core connected to the internal control valve, and a positioning member that positions the internal control valve in an operating position when the electromagnetic solenoid is excited. A capacity control valve for a clutchless variable capacity swash plate compressor according to claim 2.
[4] 前記位置決め部材は、前記感圧部材の一端と前記電磁ソレノイドのケースの端面 とにより形成されていることを特徴とする、請求項 3に記載のクラッチレス可変容量斜 板式圧縮機の容量制御弁。  [4] The capacity of the clutchless variable displacement swash plate compressor according to claim 3, wherein the positioning member is formed by one end of the pressure-sensitive member and an end face of the case of the electromagnetic solenoid. Control valve.
[5] 前記電磁ソレノイドは、可動鉄心を固定鉄心力 離間する方向へ付勢する開放バ ネを有し、前記電磁ソレノイドを消磁すると、前記開放パネにより前記内部制御弁が 非作動状態になることを特徴とする、請求項 2乃至 4の何れかに記載のクラッチレス 可変容量斜板式圧縮機の容量制御弁。  [5] The electromagnetic solenoid has an open panel that urges the movable iron core in a direction away from the fixed iron core force. When the electromagnetic solenoid is demagnetized, the internal control valve is deactivated by the open panel. The capacity control valve for a clutchless variable capacity swash plate compressor according to any one of claims 2 to 4, wherein
[6] 前記内部制御弁は、弁ハウジングに形成され前記弁孔に連通する孔に摺動可能 に挿通され前記弁体に連結された感圧ロッドを有しており、該感圧ロッドの横断面積 は弁孔横断面積よりも大きく設定されていることを特徴とする、請求項 1乃至 5の何れ 力に記載のクラッチレス可変容量斜板式圧縮機の容量制御弁。 [7] 前記内部制御弁は、弁ハウジングに形成され前記弁孔に連通する孔に摺動可能 に挿通され前記弁体に連結された感圧ロッドを有しており、該感圧ロッドの横断面積 は弁孔横断面積よりも小さく設定されていることを特徴とする、請求項 1乃至 5の何れ 力に記載のクラッチレス可変容量斜板式圧縮機の容量制御弁。 [6] The internal control valve has a pressure-sensitive rod formed in a valve housing and slidably inserted into a hole communicating with the valve hole and connected to the valve body. 6. The capacity control valve for a clutchless variable displacement swash plate compressor according to any one of claims 1 to 5, wherein the area is set to be larger than a valve hole cross-sectional area. [7] The internal control valve has a pressure-sensitive rod formed in a valve housing and slidably inserted in a hole communicating with the valve hole and connected to the valve body. 6. The capacity control valve for a clutchless variable capacity swash plate compressor according to any one of claims 1 to 5, wherein the area is set smaller than a valve hole cross-sectional area.
PCT/JP2005/012760 2004-07-13 2005-07-11 Capacity control valve for clutchless variable displacement swash plate-type compressor WO2006006560A1 (en)

Priority Applications (3)

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DE602005013969T DE602005013969D1 (en) 2004-07-13 2005-07-11 QUANTITY CONTROL VALVE FOR CLUTCH-FREE ADJUSTABLE SLICED DISC COMPRESSORS
EP05758283A EP1775470B1 (en) 2004-07-13 2005-07-11 Capacity control valve for clutchless variable displacement swash plate-type compressor
US11/571,884 US20070183904A1 (en) 2004-07-13 2005-07-11 Displacement control valve of clutchless variable displacement inclined plate-type compressor

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JP2004206550A JP2006029150A (en) 2004-07-13 2004-07-13 Displacement control valve of clutchless variable displacement swash plate type compressor
JP2004-206550 2004-07-13

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US20070183904A1 (en) 2007-08-09
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EP1775470B1 (en) 2009-04-15
CN1985090A (en) 2007-06-20
CN100507267C (en) 2009-07-01
EP1775470A4 (en) 2007-08-08

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