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WO2000050775A1 - Vanne de reglage a deplacement variable pour compresseur - Google Patents

Vanne de reglage a deplacement variable pour compresseur Download PDF

Info

Publication number
WO2000050775A1
WO2000050775A1 PCT/JP1999/000786 JP9900786W WO0050775A1 WO 2000050775 A1 WO2000050775 A1 WO 2000050775A1 JP 9900786 W JP9900786 W JP 9900786W WO 0050775 A1 WO0050775 A1 WO 0050775A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
valve
chamber
peripheral surface
rod
Prior art date
Application number
PCT/JP1999/000786
Other languages
English (en)
Japanese (ja)
Inventor
Kazuya Kimura
Hiroaki Kayukawa
Original Assignee
Kabushiki Kaisha Toyoda Jidoshokki Seisakusho
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
Priority to JP23101097A priority Critical patent/JP3591234B2/ja
Priority claimed from JP23101097A external-priority patent/JP3591234B2/ja
Application filed by Kabushiki Kaisha Toyoda Jidoshokki Seisakusho filed Critical Kabushiki Kaisha Toyoda Jidoshokki Seisakusho
Priority to US09/600,504 priority patent/US6443707B1/en
Priority to EP99905271A priority patent/EP1081379A4/fr
Priority to PCT/JP1999/000786 priority patent/WO2000050775A1/fr
Publication of WO2000050775A1 publication Critical patent/WO2000050775A1/fr

Links

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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1854—External parameters
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1859—Suction pressure

Definitions

  • the present invention relates to, for example, a control valve of a variable displacement compressor used in a vehicle air conditioning system.
  • variable displacement compressor has a control passage that connects the discharge pressure area and the crankcase, and controls the discharge capacity by adjusting the pressure in the crankcase to change the inclination of the cam plate. What is known is.
  • a control valve of this type for a conventional variable displacement compressor is disclosed, for example, in Japanese Patent Application Laid-Open No. HEI 4-119271.
  • a valve chamber 101 is defined at a distal end portion of a valve housing 102.
  • the valve chamber 101 is connected to the discharge pressure region via a control passage 103 on the upstream side, and has a valve hole 104 and a valve hole 10 formed in the axial direction of the valve housing 102. It is connected to the crank chamber via a port 105 orthogonal to 4 and a downstream control passage 103.
  • a valve body 106 for opening and closing the valve hole 104 is housed in the valve chamber 101.
  • the pressure sensing chamber 107 is formed adjacent to the valve chamber 101 and is connected to the suction pressure area.
  • a bellows 108 for sensing the pressure in the suction pressure region is housed in a pressure-sensitive chamber 107.
  • the guide hole 109 extends continuously from the valve hole 104 to the partition wall 102a of the valve housing 102 that separates the valve chamber 101 from the pressure-sensitive chamber 1 ⁇ 7. The two rooms are connected by 101 and 107.
  • the rod 110 is slidably passed through the guide hole 109 to operatively connect the bellows 108 and the valve body 106. Accordingly, the displacement of the bellows 108 responsive to the pressure of the sucked refrigerant gas is transmitted to the valve body 106 via the rod 110.
  • the solenoid part 111 is joined to the base end side of the valve housing 102, and is operatively connected to the valve body 106 via a bellows 108.
  • Solenoid part 1 1 1 1 Excitation and demagnetization change the attraction force between the fixed iron core 112 and the movable iron core 113, and change the load applied to the valve element 106. Therefore, the opening degree of the control passage 103 is determined by the balance between the biasing force from the solenoid node 111, the biasing force from the bellows 108, and the like.
  • the rod 110 and the guide hole 109 are connected between the high-pressure side port 105 side and the low-pressure side pressure-sensitive chamber 107 side while ensuring slidability. It is processed with great care to reduce gas leakage. However, a slight machining error is inevitable, and the gap between the outer peripheral surface of the rod 110 and the inner peripheral surface of the guide hole 109 is between the port 105 side and the pressure-sensitive chamber 107. Different on the side.
  • the pressure difference between the port 105 and the pressure sensing chamber 107 causes the outer peripheral surface of the port 110 to Lateral force may be generated in the direction in which the rod 110 is pressed against the inner peripheral surface of the guide hole 109, and the resistance of the rod 110 to slide in the guide hole 109 is increased (fluid sticking phenomenon). ).
  • control valves have tended to reduce the size of the solenoid section 111 in order to achieve downsizing of the compressor.
  • the bellows 108 have been downsized accordingly, and the solenoid section 111 and the bellows have been reduced.
  • the valve body 106 is operated with a balance of a small force between the valve body 106 and the valve body 106. Therefore, the control valve is susceptible to an increase in sliding resistance between the rod 110 and the guide hole 109 due to the fluid sticking phenomenon described above.
  • the sliding resistance which can be almost neglected, causes hysteresis, causing a problem that capacity controllability is greatly reduced. Disclosure of the invention
  • the present invention has been made in view of the problems existing in the prior art described above, and its object is to prevent an increase in sliding resistance between a rod and a guide hole.
  • An object of the present invention is to provide a control valve for a variable displacement compressor.
  • a control passage connecting a suction pressure area or a discharge pressure area to a control pressure chamber so as to change a discharge capacity of a variable displacement compressor is provided.
  • a valve body is provided so as to open and close the control passage.
  • the valve body side and the drive unit side are connected by the provided guide hole, and a variable capacity in which a port for operatively connecting the valve body and the drive unit is slidably inserted into the guide hole.
  • a control valve for the compressor wherein at least one of an outer peripheral surface of the rod and an inner peripheral surface of the guide hole is provided with means for preventing occurrence of a fluid sticking phenomenon.
  • a control valve for a compressor is provided.
  • the means for preventing the occurrence of the fluid sticking phenomenon between the rod and the guide hole is provided, so that the hysteresis of the control valve can be reduced and the capacity controllability is reduced. Can be prevented.
  • the means may be configured such that a gap between an outer peripheral surface of the rod and an inner peripheral surface of the guide hole is widened toward a higher pressure side of the valve body or the drive unit.
  • the outer peripheral surface of the head or the inner peripheral surface of the guide hole may include at least one tapered surface.
  • a plurality of the tapered surfaces may be formed in an axial direction of the rod.
  • the guide hole penetrates the partition wall. It is not troublesome to insert a tool into a narrow guide hole and correct the inner peripheral surface to a tapered surface.
  • at least one of the outer peripheral surface of the rod and the inner peripheral surface of the guide hole may include an annular groove formed in a circumferential direction thereof.
  • the pressure-sensitive member is displaced by the pressure in the suction pressure area or the control pressure chamber introduced into the pressure-sensitive chamber, and this displacement is transmitted to the valve via the rod.
  • the drive unit includes a solenoid unit, the solenoid unit operates a plunger housed in a plunger chamber by excitation and demagnetization, and the opening operates the plunger and the valve body. They may be connected.
  • the plunger is displaced by excitation and demagnetization of the solenoid, and the displacement is transmitted to the valve via the rod.
  • the driving unit includes a pressure-sensitive mechanism and a solenoid unit, and the pressure-sensitive mechanism is connected to the suction pressure area or the control pressure chamber via a pressure detection passage;
  • a pressure-sensitive member disposed in the pressure-sensitive chamber, wherein the solenoid operates a plunger housed in the plunger chamber by excitation and demagnetization, and the rod connects the pressure-sensitive member and the valve body. It may include a first rod portion that is operatively connected, and a second mouth portion that is operatively connected between the plunger and the valve body.
  • the degree of opening of the control passage by the valve body is determined by the balance between the urging force from the pressure-sensitive mechanism and the urging force from the solenoid.
  • the control passage may connect a discharge pressure region and a control pressure chamber.
  • the discharge capacity is controlled by adjusting the amount of the discharged refrigerant gas introduced into the control pressure chamber, and a high-pressure discharged refrigerant gas is circulated inside the control valve. Therefore, the fluid sticking phenomenon that occurs between the rod and the guide hole is more likely to occur in the rod than in the control valve that controls the discharge capacity of the compressor by adjusting the amount of refrigerant gas discharged from the control pressure chamber. Since the degree of pressing against the guide hole is increased, the effect when the present invention is applied is large.
  • FIG. 1A is a longitudinal sectional view showing a capacity control valve according to a first embodiment of the present invention, in which an outer peripheral surface of a rod is a tapered surface.
  • FIG. 1B is a longitudinal sectional view showing the capacity control valve in which the inner peripheral surface of the guide hole is a tapered surface in the first embodiment.
  • FIGS. 1C and 1D are enlarged cross-sectional views of main parts of the capacity control valve in which the outer peripheral surface of the mouth and the inner peripheral surface of the guide hole are both tapered in the first embodiment.
  • FIG. 2 is a longitudinal sectional view showing a clutchless variable displacement compressor.
  • FIG. 3 is an enlarged sectional view of a main part showing a minimum discharge capacity state of the compressor.
  • FIG. 4 is a schematic diagram illustrating the operation.
  • FIG. 5A is an enlarged sectional view of a main part of a capacity control valve having a plurality of taper surfaces on an outer peripheral surface of a rod according to a second embodiment.
  • FIG. 5B is an enlarged cross-sectional view of a main part of the capacity control valve having a plurality of tapered surfaces on the inner peripheral surface of the guide hole in the second embodiment.
  • FIG. 5C is an enlarged sectional view of a main part of the capacity control valve having a plurality of tapered surfaces on both the outer peripheral surface of the rod and the inner peripheral surface of the guide hole in the second embodiment.
  • FIG. 6A is a longitudinal sectional view showing a capacity control valve having a plurality of annular grooves on an outer peripheral surface of a rod according to a third embodiment.
  • FIG. 6B is a longitudinal sectional view showing the capacity control valve having a plurality of annular grooves on the inner peripheral surface of the guide hole in the third embodiment.
  • FIG. 6C is an enlarged sectional view of a main part of the capacity control valve having a plurality of annular grooves on both the outer peripheral surface of the rod and the inner peripheral surface of the guide hole in the third embodiment.
  • FIG. 7 is a longitudinal sectional view showing a conventional capacity control valve. BEST MODE FOR CARRYING OUT THE INVENTION
  • the front housing 11 is fixed to the front end of the cylinder block 12.
  • the rear housing 13 is fixed to the rear end of the cylinder block 12 via a valve forming body 14.
  • a crankcase 15 as a control pressure chamber is partitioned by a front housing 11 and a cylinder block 12.
  • the drive shaft 16 is rotatably supported between the front housing 11 and the cylinder block 12 so as to pass through the crank chamber 15.
  • the pulley 17 is rotatably supported by the front housing 11.
  • the pulley 17 is connected to a drive shaft 16, and is directly connected to a vehicle engine 20 via a belt 19 wound around the outer periphery thereof without an electromagnetic clutch or the like.
  • the drive shaft 16 is inserted into the inside of the blocking body 28 with its rear end.
  • the radial bearing 30 is interposed between the rear end of the drive shaft 16 and the inner peripheral surface of the breaker 28, and can slide along the breaker 28 along the axis L with respect to the drive shaft 16. It is.
  • the suction passage 32 constituting the suction pressure region is formed at the center of the rear housing 13 and the valve forming body 14.
  • the suction passage 32 communicates with the accommodation hole 27, and a positioning surface 33 is formed around the opening that appears on the front surface of the valve forming body 14.
  • the blocking surface 34 is formed on the distal end surface of the blocking member 28, and is moved toward and away from the positioning surface 33 by the movement of the blocking member 28. Since the blocking surface 34 is in contact with the positioning surface 33, the communication between the suction passage 32 and the inner space of the housing hole 27 is blocked by the sealing action between the two surfaces 33, 34.
  • the thrust bearing 35 is interposed between the swash plate 23 and the interrupter 28 and is supported on the drive shaft 16 so as to be slidable.
  • the thrust bearing 35 is urged by a spring 29 and is usually held between the swash plate 23 and the blocking body 28. Then, as the swash plate 23 tilts toward the interrupter 28, the tilt of the swash plate 23 is transmitted to the interrupter 28 via the thrust bearing 35. Therefore, the blocking body 28 is moved toward the positioning surface 33 against the urging force of the panel 29, and the blocking body 28 is moved to the blocking surface 34. Is brought into contact with the positioning surface 3.
  • the blocking surface 34 is brought into contact with the positioning surface 33, further tilting of the swash plate 23 is restricted, and in this restricted state, the swash plate 23 becomes a minimum slightly larger than 0 °. It becomes a tilt angle.
  • the cylinder bore 12a is formed through the cylinder block 12 and the single-headed screw 36 is housed in the cylinder bore 12a.
  • the piston 36 is moored to the outer periphery of the swash plate 23 via the shoe 37, and is reciprocated back and forth within the cylinder bore 12a by rotation of the swash plate 23.
  • the suction chamber 38 that forms the suction pressure region and the discharge chamber 39 that forms the discharge pressure region are formed separately in the rear housing 13.
  • the suction port 40, the suction valve 41 for opening and closing the suction port 40, the discharge port 42, and the discharge valve 43 for opening and closing the discharge port 42 are formed in the valve forming body 14, respectively.
  • the refrigerant gas in the suction chamber 38 is sucked into the cylinder bore 12a via the suction port 40 and the suction valve 41 by the reciprocating operation of the piston 36.
  • the refrigerant gas drawn into the cylinder bore 12a is compressed to a predetermined pressure by the forward movement of the piston 36, and is discharged to the discharge chamber 39 via the discharge port 42 and the discharge valve 43.
  • the suction chamber 38 communicates with the accommodation hole 27 via a communication port 45 formed through the valve forming body 14. Then, when the blocking body 28 is brought into contact with the positioning surface 33 with its blocking surface 34, the opening 45 is blocked from the suction passage 32.
  • the passage 46 is formed in the axis of the drive shaft 16, and the crank chamber 25 and the inner space of the shutoff 28 communicate with each other through the passage 46.
  • the pressure release port 47 extends through the peripheral surface of the blocking body 28, and the internal space of the blocker 28 and the internal space of the housing hole 27 are communicated through the pressure releasing port 47.
  • the control passage 48 communicates the discharge chamber 39 with the crank chamber 15.
  • the capacity control valve 49 is provided in the middle of the control passage 48.
  • the pressure detection passage 50 is formed between the suction passage 32 and the displacement control valve 49.
  • An external refrigerant circuit 52 connects the suction passage 32 for introducing the refrigerant gas into the suction chamber 38 and the discharge flange 51 for discharging the refrigerant gas from the discharge chamber 39.
  • the condenser 53, the expansion valve 54, and the evaporator 55 are interposed on the external refrigerant circuit 52.
  • the sensor 56 is installed near the evaporator 55. The sensor 56 detects the temperature in the evaporator 55, and the detected temperature information is sent to the computer 57.
  • a temperature setting device 58 for setting the temperature in the cabin of the vehicle, a sensor 59 for detecting the temperature in the cabin, and an air conditioner switch 60 are connected to a computer 57.
  • the computer 57 includes, for example, a room temperature specified in advance by a setting device 58, a detected temperature obtained from the sensor 56, a detected temperature obtained from the sensor 59, and an external signal such as an ON or OFF signal from the air switch 60.
  • the current value is commanded to the drive circuit 61 based on the signal.
  • the drive circuit 61 outputs the commanded current value to the capacity control valve 49.
  • Other external signals include signals from a sensor (not shown) for detecting the outside air temperature and a sensor for detecting the rotational speed of the engine, and the current value is determined according to the environment of the vehicle.
  • the displacement control valve 49 is configured by joining a valve housing 71 and a solenoid 72 near the center.
  • the valve chamber 73 is formed between the valve housing 71 and the solenoid 72.
  • the valve chamber 73 is connected to the discharge chamber 39 via a port 77 and a control passage 48 on the upstream side.
  • the valve element 74 is housed in the valve chamber 73.
  • the valve hole 75 is opened in the valve chamber 73 so as to face the valve element 74.
  • the valve hole 75 is formed so as to extend in the axial direction of the valve housing 71.
  • the spring 76 is interposed between the valve element 74 and the inner wall surface of the valve chamber 73, and biases the valve element 74 in a direction to open the valve hole 75.
  • the guide hole 8 8 is provided through the partition wall 7 1 a of the valve housing 71 that separates the pressure sensing chamber 84 and the valve chamber 73, and connects the pressure sensing chamber 84 and the valve chamber 73. .
  • the guide hole 88 is formed continuously with the valve hole 75.
  • Rod 89 can slide in guide hole 88 It is inserted and its tip is fitted to bellows 87.
  • the rod 89 is integrally formed with the valve element 74 and operatively connects the bellows 87 and the valve element 74.
  • the portion of 89 that is continuous with the valve element 74 has a small diameter in order to secure the passage of the refrigerant gas in the valve hole 75.
  • the port 90 is formed between the valve chamber 73 and the pressure-sensitive chamber 84 on the partition wall 71 a of the valve housing 71. Port 90 is orthogonal to valve hole 75.
  • the port 90 communicates with the crank chamber 15 via a control passage 48 on the downstream side. That is, the port 77, the valve chamber 73, the valve hole 75 and the port 90 constitute a part of the control passage 48.
  • the plunger chamber 91 is formed in a solenoid part 72, and a fixed iron core 92 is fitted into an upper opening of the plunger chamber 91 so as to be separated from the valve chamber 73.
  • the movable iron core 93 as a plunger has a substantially closed cylindrical shape, and is accommodated in the plunger chamber 91 so as to be able to reciprocate in the axial direction of the valve housing 71.
  • the follower spring 94 is interposed between the movable iron core 93 and the bottom of the plunger chamber 91.
  • a guide hole 95 is formed in a fixed iron core 92 as a partition wall, and connects the plunger chamber 91 and the valve chamber 73.
  • the rod 96 is formed integrally with the valve body 74 and has a guide hole.
  • the plunger chamber 91 has a communication groove 81 formed in the side surface of the fixed iron core 92, a communication hole 82 formed in the non-return housing 71, and a capacity control valve 49 when the rear housing 1 is mounted. It communicates with the port 90 through a small chamber 83 formed between the inner wall of the third and the inner wall of the third. That is, the plunger chamber 91 has the same crank chamber pressure as the port 90.
  • the cylindrical coil 97 is disposed outside the fixed iron core 92 and the movable iron core 93 so as to straddle both the iron cores 92 and 93.
  • a predetermined current is supplied to the coil 97 from the drive circuit 61 based on a command from the computer 57.
  • the portion of the outer peripheral surface of the rod 89 facing the inner peripheral surface 88 a of the guide hole 88 has a cylindrical sealing surface 89. a and a tapered surface 89 b continuous with the sealing surface 89 a on the port 90 side (valve body side) and having a smaller diameter toward the port 90 side. Therefore, the gap between the taper surface 89b of the rod 89 and the inner peripheral surface 88a of the guide hole 88 is such that the port 90 side is larger than the pressure sensing chamber 84 side (drive unit side). I have.
  • the portion of the outer peripheral surface of the rod 96 facing the inner peripheral surface 95a of the guide hole 95 has a cylindrical sealing surface 96a and a sealing surface 96a.
  • a tapered surface 96b which is continuous on the valve chamber 73 side (valve body side) and has a smaller diameter toward the valve chamber 73 side. Therefore, the gap between the tapered surface 96 b of the rod 96 and the inner peripheral surface 95 a of the guide hole 95 is such that the valve chamber 73 side is larger than the plunger chamber 91 side (drive section side). I have.
  • the tapered surfaces 89b and 96b of the rod 89 and the mouth 96 are machined so that the port 90 side and the valve chamber 73 side have small diameters including machining errors.
  • the outer surfaces of the rods 89, 96 were machined so that the gaps between the inner surfaces 88a, 95a of the guide holes 88, 95 became larger on the high pressure side.
  • the slopes of the tapered surfaces 89 b and 96 b are exaggerated for easy understanding.
  • the diameter difference between the large diameter side and the small diameter side is actually larger. Is about several m to several tens of m.
  • the computer 57 is connected to the solenoid. Command the excitation of the oscillating section 72. Then, a predetermined current is supplied to the coil 97 via the drive circuit 61, and an attractive force corresponding to the current value is generated between the two cores 92, 93. This suction force is transmitted to the valve element 74 against the urging force of the spring 76, and acts on the valve element 74 in a direction in which the opening of the valve hole 75 decreases.
  • the solenoid 72 when the solenoid 72 is energized, the bellows 87 It is displaced from 32 according to the fluctuation of the suction pressure introduced into the pressure sensing chamber 84 via the pressure detection passage 50. Then, the displacement of the bellows 87 is transmitted to the valve element 74 via the rod 89. Therefore, in the capacity control valve 49, the opening of the valve hole 75 is determined by the balance between the urging force from the solenoid 72, the urging force from the bellows 87, and the urging force of the spring 76. .
  • the opening degree of the valve hole 75 becomes smaller, the amount of refrigerant gas flowing from the discharge chamber 39 through the control passage 48 into the crank chamber 15 becomes smaller.
  • the refrigerant gas in the crank chamber 15 flows out to the suction chamber 38 via the passage 46, the pressure release port 47, the accommodation hole 27 and the port 45. For this reason, the pressure in the crank chamber 15 decreases.
  • the pressure in the suction chamber 38 is also high, and the difference between the pressure in the crank chamber 15 and the pressure in the cylinder bore 12a becomes small. For this reason, the inclination angle of the swash plate 23 becomes large.
  • the cooling load is small.
  • the computer 57 instructs the drive circuit 61 to decrease the current value as the detected temperature is lower. For this reason, the suction force between the fixed iron core 92 and the movable iron core 93 is weakened, and the urging force on the valve element 74 in the direction of decreasing the opening of the valve hole 7 & is reduced. Then, the valve hole 75 is opened and closed with a higher suction pressure. Therefore, the capacity control valve 49 operates so as to maintain a higher suction pressure by reducing the current value.
  • the degree of opening of the valve hole 75 increases, the amount of coolant gas flowing into the crank chamber 15 from the discharge chamber 39 increases, and the pressure in the crank chamber 15 increases.
  • the cooling load is small, the pressure in the suction chamber 38 is low, and the difference between the pressure in the crank chamber 15 and the pressure in the cylinder bore 12a increases. For this reason, the inclination angle of the swash plate 23 becomes small.
  • the temperature at the evaporator 55 decreases so as to approach the temperature at which frost occurs.
  • the computer 57 instructs the drive circuit 61 to demagnetize the solenoid 72.
  • This set temperature is a temperature at which frost is likely to occur in the evaporator 55. Then, the supply of current to the coil 97 is stopped, the solenoid 72 is demagnetized, and the attractive force between the fixed core 92 and the movable core 93 disappears.
  • valve element 74 is moved downward by the urging force of the spring 76 against the urging force of the follower panel 94 acting via the movable iron core 93. Then, the valve element 74 shifts to the opening position where the valve hole 75 is opened to the maximum. Therefore, a large amount of the high-pressure refrigerant gas in the discharge chamber 39 is supplied to the crank chamber 15 via the control passage 48, and the pressure in the crank chamber 15 increases. Due to the pressure increase in the crank chamber 15, the inclination angle of the swash plate 23 is minimized as shown in FIG.
  • the computer 57 instructs demagnetization of the solenoid 72, and this demagnetization also minimizes the tilt angle of the swash plate 23.
  • the opening / closing operation of the capacity control valve 49 is controlled by the coil 97 of the solenoid 72. It changes according to the magnitude of the current value. That is, when the current value increases, the control passage 48 is opened and closed at a low suction pressure, and when the current value decreases, the control passage 48 opens and closes at a high suction pressure.
  • the compressor changes the inclination of the swash plate 23 so as to maintain the set suction pressure, and changes the discharge capacity.
  • the capacity control valve 49 has a role of changing the set value of the suction pressure by changing the current value and a role of performing the minimum capacity operation regardless of the suction pressure.
  • the compressor plays a role of changing the refrigeration capacity of the refrigeration circuit.
  • the blocking body 28 contacts the positioning surface 33 with the blocking surface 34, and the suction passage 32 is blocked. In this state, the passage cross-sectional area in the suction passage 32 becomes zero, and the flow of the refrigerant gas from the external refrigerant circuit 52 into the suction chamber 38 is prevented.
  • the blocking body 28 is disposed at the closed position that blocks communication between the suction passage 32 and the accommodation hole 27, the inclination angle of the swash plate 23 is minimized.
  • the minimum inclination angle of the swash plate 23 is set to be slightly larger than 0 °.
  • the blocking body 28 is arranged between the position where the suction passage 32 is closed and the position where the suction passage 32 is opened, in conjunction with the tilt of the swash plate 23.
  • the refrigerant gas is discharged from the cylinder bore 12a to the discharge chamber 38 even at the minimum inclination angle.
  • the refrigerant gas discharged from the cylinder bore 12 a into the discharge chamber 38 flows into the crank chamber 15 through the control passage 48.
  • the refrigerant gas in the crank chamber 15 flows into the suction chamber 38 through the passage 46, the inside of the blocker 28, the pressure relief port 47, the housing hole 27, and the port 45.
  • the refrigerant gas in the suction chamber 38 is drawn into the cylinder bore 12a, and is discharged again to the discharge chamber 39.
  • the present embodiment having the above configuration has the following effects.
  • the gap between the outer peripheral surface (89a, 89b) of the rod 89 and the inner peripheral surface 88a of the guide hole 88 is a port on the high-pressure side.
  • the 90 side is the low pressure side. It is larger than the pressure sensitive chamber 84 side. Therefore, the fluid sticking phenomenon can be prevented from occurring between the rod 89 and the guide hole 88, and the hysteresis of the capacity control valve 49 can be reduced, thereby preventing the capacity controllability from lowering.
  • the solenoid 72 can be downsized, and the compressor can be downsized.
  • the gap between the outer peripheral surface (96a, 96b) of the rod 96 and the inner peripheral surface 96a of the guide hole 96 is a valve on the high pressure side.
  • the chamber 73 side is larger than the plunger chamber 91 side which is the low pressure side. Therefore, the same operation and effect as the above (1) can be obtained.
  • the compressor has a configuration in which the discharge capacity is controlled by adjusting the amount of refrigerant gas discharged into the crank chamber 15, and the high pressure discharge is supplied to the valve chamber 73 of the capacity control valve 49. Refrigerant gas is introduced. Therefore, the fluid sticking phenomenon occurring between the rod 96 and the guide hole 95 is more likely to occur in the rod 96 than in the compressor configured to regulate the amount of refrigerant gas discharged from the crank chamber 15. Increase the degree of pressing against guide holes 9 5 You. In the present embodiment, since the means for preventing the fluid sticking phenomenon is applied to such a capacity control valve 49 of the compressor, the effect is particularly large.
  • the tapered surface is not located on the side of the openings 89, 96 but on the side of the guide holes 88, 95 as shown by the enlarged circles A ′ and B ′ in FIG. 1B.
  • the gap between the outer peripheral surfaces of the rods 89, 96 and the inner peripheral surfaces of the guide holes 88, 95 may be configured such that the high pressure side is wider than the low pressure side. In this case, the diameter of the tapered surface increases toward the high pressure side.
  • the tapered surface must be formed on both the rods 89 and 96 and the guide holes 88 and 95.
  • the gap between the outer peripheral surfaces of the rods 89 and 96 and the inner peripheral surfaces of the guide holes 88 and 95 may be configured such that the high pressure side is wider than the low pressure side.
  • FIG. 5A shows a second embodiment.
  • the rods 89 and 96 have a plurality of tapered surfaces 89b and 96b in the axial direction. Therefore, the gap between each tapered surface 89b, 96b and the inner peripheral surface 88a, 95a of the guide hole 88, 95 is such that the high pressure side (73, 90) is on the low pressure side (73, 90). 8 4, 9 1) It is larger.
  • the rod 100 has a cylindrical shape, and operatively connects the valve element 74 and the diaphragm 99.
  • the annular groove 100 Ob is formed in the outer circumferential surface 100 a of the rod 100 facing the guide hole 88 in the circumferential direction thereof, and a plurality of annular grooves are arranged at predetermined intervals in the axial direction.
  • the present embodiment also has the same effect as the effect (1) of the first embodiment.
  • the annular groove is not formed on the outer peripheral surface 100 a of the rod 100, but on the guide hole as shown by 88 b in the enlarged circle C ′ in FIG. 6B. It may be formed on the inner peripheral surface 8 8 a of 8 8.
  • annular groove is formed on both the outer peripheral surface 100a of the mouth 100 and the inner peripheral surface 88a of the guide hole 88. Is also good.
  • the annular groove is preferably formed on the outer peripheral surface 100a side of the mouthpiece 100.
  • the reason is that, for example, when an annular groove is provided on the inner peripheral surface 88a side of the guide hole 88, the guide hole 88 extends through the partition wall 71a, and the narrow guide hole Inserting a tool into 8 8 has the trouble of forming an annular groove on its inner peripheral surface 8 8 a. is there.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

L'invention concerne une vanne de réglage à déplacement variable pour compresseur, exempte de tout blocage hydraulique entre une tige et un trou de guidage, caractérisée en ce qu'une première tige (89) est insérée dans un premier trou de guidage (88) pour connecter, par liaison coopérante, un soufflet (87) à une tête de soupape (74), une seconde tige (96) est insérée dans un second trou de guidage (95) pour connecter, par liaison coopérante, un noyau de fer mobile (93) à la tête de soupape (74), des surfaces coniques (89b, 96b) sont formées sur les surfaces périphériques externes de la première et de la seconde tiges (89, 96), et en ce que les espaces entre les surfaces périphériques internes (88a, 95a) du premier et du second trous de guidage (88, 95) mutuellement opposées, et les surfaces coniques, sont plus grands sur les côtés haute pression (73, 90) que sur les côtés basse pression (84, 91).
PCT/JP1999/000786 1997-08-27 1999-02-23 Vanne de reglage a deplacement variable pour compresseur WO2000050775A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP23101097A JP3591234B2 (ja) 1997-08-27 1997-08-27 可変容量型圧縮機用制御弁
US09/600,504 US6443707B1 (en) 1997-08-27 1999-02-23 Control valve for variable displacement compressor
EP99905271A EP1081379A4 (fr) 1999-02-23 1999-02-23 Vanne de reglage a deplacement variable pour compresseur
PCT/JP1999/000786 WO2000050775A1 (fr) 1997-08-27 1999-02-23 Vanne de reglage a deplacement variable pour compresseur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP23101097A JP3591234B2 (ja) 1997-08-27 1997-08-27 可変容量型圧縮機用制御弁
PCT/JP1999/000786 WO2000050775A1 (fr) 1997-08-27 1999-02-23 Vanne de reglage a deplacement variable pour compresseur

Publications (1)

Publication Number Publication Date
WO2000050775A1 true WO2000050775A1 (fr) 2000-08-31

Family

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Application Number Title Priority Date Filing Date
PCT/JP1999/000786 WO2000050775A1 (fr) 1997-08-27 1999-02-23 Vanne de reglage a deplacement variable pour compresseur

Country Status (2)

Country Link
EP (1) EP1081379A4 (fr)
WO (1) WO2000050775A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017129042A (ja) * 2016-01-19 2017-07-27 サンデン・オートモーティブコンポーネント株式会社 可変容量圧縮機の容量制御弁

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4031945B2 (ja) * 2002-04-09 2008-01-09 サンデン株式会社 可変容量圧縮機の容量制御弁
JP4422512B2 (ja) * 2003-04-09 2010-02-24 株式会社不二工機 可変容量型圧縮機用の制御弁

Citations (3)

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Publication number Priority date Publication date Assignee Title
JPS61145141U (fr) * 1985-02-28 1986-09-08
JPH04119271A (ja) 1990-09-07 1992-04-20 Saginomiya Seisakusho Inc 電磁式制御弁
JPH0942510A (ja) * 1995-07-27 1997-02-14 Daikin Ind Ltd 冷凍装置用電動膨張弁及び冷凍装置

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JPS56120873A (en) 1981-01-29 1981-09-22 Toyooki Kogyo Co Ltd Solenoid vavle
JP2616511B2 (ja) 1991-05-27 1997-06-04 株式会社豊田自動織機製作所 可変容量型揺動斜板式圧縮機における容量制御弁
JP3186340B2 (ja) 1993-06-11 2001-07-11 株式会社豊田自動織機製作所 クラッチレス片側ピストン式可変容量圧縮機及びその容量制御方法

Patent Citations (3)

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Publication number Priority date Publication date Assignee Title
JPS61145141U (fr) * 1985-02-28 1986-09-08
JPH04119271A (ja) 1990-09-07 1992-04-20 Saginomiya Seisakusho Inc 電磁式制御弁
JPH0942510A (ja) * 1995-07-27 1997-02-14 Daikin Ind Ltd 冷凍装置用電動膨張弁及び冷凍装置

Non-Patent Citations (1)

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Title
See also references of EP1081379A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017129042A (ja) * 2016-01-19 2017-07-27 サンデン・オートモーティブコンポーネント株式会社 可変容量圧縮機の容量制御弁

Also Published As

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EP1081379A1 (fr) 2001-03-07
EP1081379A4 (fr) 2004-07-07

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