EP1026398A2 - Kontrollventil für einen verstellbaren Kompressor - Google Patents

Kontrollventil für einen verstellbaren Kompressor Download PDF

Info

Publication number
EP1026398A2
EP1026398A2 EP00101971A EP00101971A EP1026398A2 EP 1026398 A2 EP1026398 A2 EP 1026398A2 EP 00101971 A EP00101971 A EP 00101971A EP 00101971 A EP00101971 A EP 00101971A EP 1026398 A2 EP1026398 A2 EP 1026398A2
Authority
EP
European Patent Office
Prior art keywords
valve
crank
pressure
chamber
valve body
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP00101971A
Other languages
English (en)
French (fr)
Other versions
EP1026398A3 (de
Inventor
Masaki Ota
Masahiro Kawaguchi
Ken Suitou
Taku Adaniya
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Industries Corp
Original Assignee
Toyoda Jidoshokki Seisakusho KK
Toyoda Automatic Loom Works Ltd
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 Toyoda Jidoshokki Seisakusho KK, Toyoda Automatic Loom Works Ltd filed Critical Toyoda Jidoshokki Seisakusho KK
Publication of EP1026398A2 publication Critical patent/EP1026398A2/de
Publication of EP1026398A3 publication Critical patent/EP1026398A3/de
Withdrawn legal-status Critical Current

Links

Images

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
    • F04B2027/1831Valve-controlled fluid connection between crankcase and suction 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
    • F04B2027/1845Crankcase 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
    • F04B2027/184Valve 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

Definitions

  • the present invention relates to a control valve for variable displacement compressors, more specifically, to a control valve that varies the inclination of the swash plate in accordance with the pressure in the crank chamber.
  • the inclination of the swash plate varies in accordance with the pressure in the crank chamber (crank pressure Pc).
  • a control valve located in the compressor adjusts the crank pressure Pc and varies the inclination of the swash plate as required.
  • the compressor displacement is varied in accordance with the inclination of the swash plate.
  • Japanese Unexamined Patent Publication No. 6-26454 describes an outlet control valve located in a bleed passage, which connects the crank chamber to a suction chamber.
  • the control valve includes a bellows and a valve chamber for accommodating a valve body.
  • the valve body is coupled to the bellows.
  • the control valve also includes a solenoid that urges the valve body in one direction.
  • the force of the solenoid varies in accordance with the supply of electric current to the solenoid.
  • the position of the valve body is varied in accordance with the suction pressure Ps introduced to the valve chamber and the force of the solenoid. This adjusts the opening size of a valve hole that connects the crank chamber to the suction chamber.
  • the outlet control valve controls the gas flow from the crank chamber and adjusts the crank pressure Pc to a required level.
  • the bellows urges the valve body to approach the valve hole.
  • the crank pressure Pc urges the valve body away from the valve hole.
  • the force of the solenoid applied to the valve body determines to a target value of the suction pressure of the compressor. That is, the valve body operates to maintain the target suction pressure in accordance with the force of the solenoid.
  • the crank pressure Pc is continuously applied to the valve body in the control valve. In other words, when determining the target suction pressure by the supply of electric current to the solenoid, the valve body is affected by the crank pressure Pc. Accordingly, since the crank pressure Pc is affected by the operation of the compressor, it is difficult to control the suction pressure Ps. Therefore, supplying a precise amount of current to the solenoid does not necessarily result in precise control of the target suction pressure.
  • An objective of the present invention is to provide a control valve for compressors that is able to set the suction pressure with precision.
  • the present invention provides a control valve located in a compressor to change the displacement of the compressor.
  • the compressor includes a crank chamber, the pressure of which is a crank pressure, a suction chamber, the pressure of which is a suction pressure, and a bleeding passage for connecting the crank chamber to the suction chamber.
  • the control valve is located on the bleeding passage to control the crank pressure by controlling the flow of gas from the crank chamber to the suction chamber.
  • the displacement of the compressor changes in accordance with the crank pressure.
  • a valve chamber forms a part of the bleeding passage.
  • a valve seat is located between a crank pressure zone, which is exposed to the crank pressure, and a suction pressure zone, which is exposed to the suction pressure.
  • the valve seat defines a valve hole that connects the crank pressure zone to the suction pressure zone.
  • a valve body is selectively engaged with and disengaged from the valve seat to control an opening size of the valve hole.
  • a sensing member is located in the crank pressure zone and connected to the valve body. The sensing member always urges the valve body toward the valve seat, and the sensing member moves in accordance with the crank pressure.
  • the sensing member has a predetermined effective area that is affected by the crank pressure. The effective area is approximately the same the cross sectional area of the valve hole.
  • cylinder bores 1a are formed in a cylinder block 1.
  • a front housing member 2 is coupled to the front of the cylinder block 1.
  • a crank chamber 3 is defined between the cylinder block 1 and the front housing member 2.
  • a rear housing member 4 is coupled to the rear of the cylinder block 1 through a valve plate 5.
  • the cylinder block 1, the front housing member 2, the rear housing member 4, and the valve plate 5 form a housing.
  • the valve plate 5 includes a suction plate 6 and a discharge plate 7.
  • the suction plate 6 has suction valves 6a
  • the discharge plate 7 has discharge valves 7a.
  • the rear housing member 4 includes a discharge chamber 9 and a suction chamber 8, which surrounds the discharge chamber 9.
  • the suction chamber 8 is connected to the cylinder bores 1a through suction holes 5a in the valve plate 5.
  • the cylinder bores 1a are connected to the discharge chamber 9 through corresponding discharge holes 5b in the valve plate 5.
  • a drive shaft 12 is supported by the cylinder block 1 and the front housing member 2 through bearings 13.
  • the front end of the drive shaft 12 is connected to an engine E through an electromagnetic clutch 40.
  • the engine E serves as an external drive source.
  • the electromagnetic clutch 40 includes a pulley 42, an annular solenoid coil 43, and an armature 45.
  • the pulley 42 is rotatably supported by the front end of the front housing member 2 through a bearing 41.
  • the armature 45 is coupled to the drive shaft 12 by a plate spring 44.
  • a lug plate 14 is secured to and integrally rotates with the drive shaft 12 in the crank chamber 3.
  • a thrust bearing 15 is located between the lug plate 14 and the inner wall of the front housing member 2.
  • the lug plate 14 includes a support arm 14a, which extends toward the cylinder block 1.
  • the arm 14a includes a guide hole 14b.
  • a bearing plate 17 is coupled to the support arm 14a through a coupler pin 16, which forms a hinge mechanism.
  • a sleeve 19 is located on the drive shaft 12 to slide axially and is coupled to the inner surface of a boss 17a of the bearing plate 17 by a pair of coupler pins 20 (only one shown in Fig. 1).
  • a wobble plate 18 is supported on the periphery of the boss 17a.
  • the bearing plate 17 rotates with respect to the wobble plate 18.
  • a guide rod 21 is located in the crank chamber 3 to prevent the wobble plate 18 from rotating about its axis.
  • the wobble plate 18 inclines and moves along the guide rod 21.
  • the wobble plate 18 is coupled to the pistons 22 through corresponding piston rods 23.
  • a spring receiver 24 is attached to the drive shaft 12.
  • a spring 25 is located between the spring receiver 24 and the sleeve 19.
  • the spring which is preferably a coil spring, urges the plates 17, 18 toward a maximum inclination position (leftward in Fig. 1).
  • the bearing plate 17 rotates with the drive shaft 12, which causes the pistons 22 to reciprocate.
  • the stroke of each piston 22 is varied in accordance with the inclination of the plates 17, 18.
  • refrigerant gas is drawn to the cylinder bores 1a from the suction chamber 8 (suction pressure zone Ps) and compressed.
  • Compressed refrigerant gas in the cylinder bores 1a is discharged to the discharge chamber 9 (discharge pressure zone Pd).
  • the inclination angle of the plates 17, 18 is determined based on a various moments, which include a moment based on centrifugal force during the rotation of the bearing plate 17, a moment produced by the spring 25, a moment of inertia of the piston reciprocation, and a gas pressure moment.
  • the gas pressure moment is generated by the combination of the compression reaction force applied to the pistons 22, the force of the pressure in the cylinder bores 1a applied to the pistons 22 during suction strokes, and the pressure in the crank chamber 3 (crank pressure Pc).
  • crank pressure Pc crank pressure
  • the gas pressure moment is greater than the total of the centrifugal force and the moment of the spring force when the crank pressure Pc is relatively high.
  • This moves the plates 17, 18 to the minimum inclination angle, which is in the range of, for example, 3-5 degrees. Adjusting the crank pressure Pc balances the gas pressure moment with the total of the centrifugal force moment and the spring force moment. Therefore, the inclination of the plates 17, 18 is adjusted to an angle between the maximum inclination and the minimum inclination.
  • the stroke of each piston 22, or the displacement of the compressor is adjusted in accordance with the inclination of the plates 17, 18.
  • the mechanism for controlling the crank pressure Pc is formed by a bleed passage 58, 59 and an outlet control valve 50, which is located in the bleed passage 58, 59.
  • the bleed passage has an upstream part 58 and a downstream part 59.
  • the discharge chamber 9 is connected to the suction chamber 8 through an external refrigerant circuit 30.
  • the external refrigerant circuit 30 and the compressor form a refrigeration circuit of a vehicle air-conditioning system.
  • the external refrigerant circuit 30 includes a condenser 31, a temperature type expansion valve 32 and an evaporator 33.
  • the opening of the expansion valve 32 is feedback-controlled based on the temperature detected by a heat sensitive tube 32a at the outlet of the evaporator 33 and the evaporation pressure.
  • the temperature near the outlet of the evaporator 33 reflects the thermal load on the refrigeration circuit.
  • the expansion valve 32 adjusts the supply of refrigerant to the evaporator in accordance with the thermal load applied to the refrigeration circuit. This adjusts the flow rate of refrigerant in the external refrigerant circuit 30.
  • a temperature sensor 34 is located in the vicinity of the evaporator 33.
  • the temperature sensor 34 detects the temperature of the evaporator 33 and sends the result to a controller 38, which is a computer.
  • the controller 38 controls the vehicle air-conditioning system.
  • the input side of the controller 38 is connected to the temperature sensor 34, a passenger compartment temperature sensor 35, a temperature adjuster 36, which is used to set a target temperature of the passenger compartment, an operation switch 37, and an electronic control unit (ECU) of the engine E.
  • the output side of the controller 38 is connected to a driving circuit 39A, which controls the supply of current to the solenoid 43 of the electromagnetic clutch 40, and a driving circuit 39B, which controls the supply of current to a coil 77 of the outlet control valve 50.
  • the controller 38 controls the clutch 40 and the control valve 50 based on various information, which includes the temperature of the evaporator 33 detected by the temperature sensor 34, the temperature detected by the passenger compartment temperature sensor 35, the target temperature set by a temperature adjuster 36, ON/OFF state of the switch 37, and information from the ECU about the state of the engine E including the engine speed and whether the engine E is on or off.
  • blowby gas flows to the crank chamber 3 from the cylinder bores 1a through the spaces between the pistons 22 and the walls of the cylinder bores 1a.
  • Blowby gas increases the pressure of the crank chamber 3.
  • the outlet control valve 50 controls the crank pressure Pc by adjusting the flow of refrigerant gas from the crank chamber 3 to the suction chamber 8.
  • the control valve 50 includes a valve mechanism 52, which is located in a valve housing 51, and a solenoid 70, which is connected to the valve housing 51.
  • the valve housing 51 includes a body 51a and a cap 51b located on the body.
  • a valve chamber 53 which serves as a passage, is defined in the valve housing 51.
  • An annular valve seat 54 is formed in the inner surface of the body 51a near the center of the valve chamber 53.
  • the valve seat 54 defines a valve hole (55) 55.
  • the valve chamber 53 is divided into a first chamber (crank pressure Pc zone) 53a and a second chamber (suction pressure Ps zone) 53b by the valve seat 54.
  • the cap 51b of the valve housing 51 includes an inlet port 56, which is connected to the first chamber 53a of the valve chamber 53.
  • the body 51a of the valve housing 51 includes an outlet port 57, which is connected to the second chamber 53b of the valve chamber 53.
  • the inlet port 56 connects the first chamber 53a to the crank chamber 3 through a passage 58.
  • the outlet port 57 connects the second chamber 53b to the suction chamber 8 through a passage 59.
  • the passage 58, the inlet port 56, the valve chamber 53, the outlet port 57, and the passage 59 form a bleed passage between the crank chamber 3 and the suction chamber 8.
  • a valve body 60 is accommodated in the first valve chamber 53a of the valve chamber 53 to move along the axis of the control valve.
  • the valve body 60 contacts the valve seat 54 and is separated from the valve seat 54 depending on the direction of its movement.
  • the valve hole (55) 55 is closed, which disconnects the first chamber 53a from the second chamber 53b.
  • the valve body 60 includes an anchor 60a, which extends from the valve body 60 and a recess 60b, which opens downward.
  • a bellows 61 which serves as a pressure sensitive member, is located in the first chamber 53a of the valve chamber 53.
  • a stationary end of the bellows 61 is fixed to the cap 51b.
  • the interior of the bellows 61 is under vacuum, or low-pressure.
  • a spring 62 is located in the bellows 61.
  • the spring 62 urges a movable end of the bellows downward.
  • a recess is formed in the movable end of the bellows 61.
  • a ball 63 and the anchor 60a of the valve body 60 are received in the recess. Force is transmitted between the bellows 61 and the valve body 60 through the ball 63. Accordingly, the bellows 61 is displaced in accordance with the crank pressure Pc.
  • the bellows 61 elastically supports the valve body 60.
  • the bellows 61 which includes the spring 62, urges the valve body 60 to contact the valve seat 54.
  • the effective area A of the bellows 61 is equal to the cross-sectional area B (the area sealed by the valve body 60) of the valve hole (55) 55.
  • the solenoid 70 of the control valve 50 includes an accommodation cylinder 71.
  • a fixed iron core 72 is fitted in the cylinder 71.
  • a solenoid chamber 73 is defined in the cylinder 71.
  • a movable iron core 74 which serves as a plunger, is accommodated in the solenoid chamber 73 to move in the axial direction of the control valve 50.
  • a support pin 74a is fixed in the center of the movable core 74.
  • a solenoid rod 75 which serves as a transmitting member, is received in the center of the fixed core 72 to move axially.
  • One end of the solenoid rod 75 passes through the second chamber 53b of the valve chamber 53 and is fitted in the recess 60b of the valve body 60.
  • the other end of the solenoid rod 75 is located in the solenoid chamber 73 and contacts the upper surface of the movable core 74. Therefore, an axial force is transmitted from the movable end of the bellows 61, through the valve body 60, the solenoid 75, and the movable core 74.
  • a small annular clearance CL is formed between the peripheral surface of the solenoid rod 75 and the inner surfaces of the valve housing 51 and the fixed core 72.
  • the second chamber 53b is connected to the solenoid chamber 73 through the clearance CL.
  • the pressure of the solenoid chamber 73 is equal to the suction pressure Ps, as is that of the second chamber 53b (See Fig. 3).
  • spring 76 is arranged around the support pin 74a.
  • the spring 76 urges the movable core 74 and the solenoid rod 75 upward (toward the valve body 60). Therefore, the valve body 60 receives a downward force from the bellows 61 and the spring 61 through the movable end of the bellows 61 and an upward force from the spring 76 through the movable core 74 and the rod 75.
  • the initial position of the valve body 60 in the valve chamber 53 is determined by the opposed forces. In other words, the bellows 61, the valve body 60, the solenoid rod 75, and the movable core 74 are always connected.
  • a coil 77 is arranged to surround the fixed core 72 and the movable core 74.
  • the driving circuit 39B supplies the coil 77 with a certain amount of electric current.
  • the coil 77 generates electromagnetic force in accordance with the level I of the supplied current.
  • the electromagnetic force causes the movable core 74 to be attracted to the fixed core 72, which moves the solenoid rod 75 upward, from the point of view of the drawings.
  • the upward movement of the solenoid rod 75 applies an upward force to the valve body 60.
  • the opening size of the outlet control valve 50 is determined by the the equilibrium of the forces of the springs 62, 76, the force of the bellows 61 based on the crank pressure Pc, and the electromagnetic force of the solenoid 70. Changing the electromagnetic force changes a target suction pressure Pset, which varies the operation characteristics of the control valve 50.
  • the bellows 61 and the spring 62 form a first spring mechanism that urges the valve body 60 to contact the valve seat 54.
  • the plunger 74, the rod 75, and the spring 76 form a second spring mechanism that urges the valve body 60 away from the valve seat 54.
  • the first and second spring mechanisms form an elastic support mechanism that elastically supports the valve body 60 to contact and to separate from the valve seat 54.
  • the controller When the switch 37 is turned on, the controller commands the driving circuit 39A to supply current to the solenoid coil 43 of the clutch 40. This connects the compressor to the engine and drives the compressor.
  • the controller also commands the driving circuit 39B to supply current to the coil 77 of the control valve 50.
  • the level I of the current supply to the coil 77 is calculated by a control program, based on the difference between the temperature detected by the passenger compartment temperature sensor 35 and the target temperature set by the temperature adjuster 36 and other information including the temperature detected by the temperature sensor 34.
  • An electromagnetic attraction force is generated between the cores 72, 74 in accordance with the current supply level I, which applies an upward force F to the solenoid rod 75.
  • the opening size of the control valve 50 is adjusted in accordance with the force F.
  • the opening size of the control valve 50 determines the crank pressure Pc and the suction pressure Ps.
  • Fig. 3 diagrammatically shows the forces applied to the internal mechanism of the control valve 50.
  • the total of the downward forces of the bellows 61 and the spring 62 is represented by f1.
  • the upward force of the spring 76 is represented by f2.
  • the electromagnetic attraction force (upward force of the solenoid rod 75) when the coil 77 is supplied with a current is represented by F.
  • the effective area A of the bellows 61 represents the area on which the crank pressure Pc is applied to the bellows 61 with effect. In other words, the bellows 61 has a predetermined area that is affected by the crank pressure Pc.
  • the area B is the area that is sealed by the valve body 60.
  • An area S is the cross-sectional area of the solenoid rod 75 when the cross section is taken perpendicular the axis of the solenoid rod 75.
  • the effective area of the rod 75 on which the suction pressure Ps is applied is equal to the cross-sectional area S of the rod 75. In this case, a force (Ps*S) is applied to the lower end of the rod 75 to urge the rod 75 upward.
  • the upward force applied to the valve body 60 from the rod 75 is F+f2+Ps*S .
  • the downward force applied to the valve body 60 from the bellows 61 is f1-Pc*A .
  • a downward force Pc*B is applied to the upper surface of the valve body 60
  • an upward force Ps(B-S) is applied to the lower surface of the valve body 60.
  • the relationship between the illustrated forces is represented by the following expressions (1), (2).
  • F+f2+Ps*S f1-Pc*A+Pc*B-Ps(B-S)
  • F+f2 f1-Pc*A+Pc*B-Ps*B
  • Ps*B f1-f2-F+Ps(B-A)
  • f1, f2, and B are predetermined constant values.
  • the force F is a variable value, which varies in accordance with the level I of the current supply to the coil 77. Therefore, the predetermined suction pressure Ps, that is, the target suction pressure Pset, is determined by the level I of the current supply to the coil 77. In other words, the target suction pressure Pset is not dependent on the crank pressure Pc.
  • the suction pressure Ps is maximized. The increase of the current supply to the coil 77 increases the force F and lowers the suction pressure Ps.
  • the controller 38 controls the opening size of the control valve 50 by calculating the level I of the current supply to the coil 77 based on the various information mentioned previously. This adjusts the inclination of the plates 17, 18 and the displacement of the compressor. Also, the suction pressure Ps, which is substantially equal to the pressure Ps' in the vicinity of the outlet of the evaporator 33, is maintained around a required pressure (target suction pressure Pset).
  • the purpose of the control by the control valve 50 and the controller 38 is to adjust the displacement of the compressor to keep the pressure Ps' around the target suction pressure Pset.
  • the solenoid 70 and the controller 38 are means for externally controlling the opening size of the control valve 50 such that the suction pressure Ps is equal to the target suction pressure Pset.
  • the target suction pressure Pset is varied by controlling the value I of current supply to the coil 77 from the controller 38.
  • the solenoid 70 and the controller 38 are also means for externally controlling the target suction pressure Pset.
  • the present embodiment has the following advantages.
  • the effective area A of the bellows 61 is equal to the opening area B (that is, the area B sealed by the valve body 60) of the valve hole (55) 55. Therefore, the suction pressure Ps is controlled with precision in accordance with the level I of the current supply to the coil 77, regardless of the crank pressure Pc. Therefore, the control of the target suction pressure Pset is more accurate.
  • the target suction pressure Pset (which is the desired value of the pressure Ps' near the outlet of the evaporator 33) is easily included in the range of the suction pressure Ps that corresponds to the range of the level I of the current supply to the coil 77. As a result, the range of the target suction pressure Pset can be wide.
  • the coupling structure shown in Fig. 4 may be used. That is, the movable end of the bellows 61 is integrally formed with the valve body 60. In this case, most of the upper surface of the valve body 60 is covered with the lower end of the bellows 61.
  • the surface of the upper half of the valve body 60 that is exposed to the crank pressure Pc (B-A) is obtained by subtracting the reception area A of the bellows 61 that is covering the upper surface of the valve body 60 from the sealed area B.
  • the area of the lower half of the valve body 60 that is affected by the suction pressure Ps is (B-S).
  • the diameters of the bellows 61 and the valve body 60 may vary as long as the bellows 60 and the valve body move synchronously.
  • the crank pressure Pc may be applied to the solenoid chamber 73, in which the lower part of the solenoid rod 75 is located.
  • gas can not flow between the second chamber 53b of the valve chamber 53 and the solenoid chamber 73.
  • the expression (5) can be simplified to an expression (6).
  • F+f2-f1 Pc(B-A-S)-Ps(B-S)
  • f1, f2 and A are invariable, predetermined values. Since the electromagnetic force F is a function of the current value supplied to the coil 77, the expression (7) is like the expression (3). Accordingly, the control valve 50 shown in Fig. 5 also varies the target suction pressure regardless of the crank pressure Pc. The control valve of Fig. 5 has the same advantages as the control valve 50 shown in Figs. 2 and 3.
  • a diaphragm may be used as a pressure sensitive member instead of the bellows 61.
  • the present invention may be applied to compressors other than wobble plate-type compressors, such as a compressor having a cam plate that reciprocates the pistons.
  • a control valve (50) located in a compressor to change the displacement of the compressor.
  • the compressor includes a crank chamber (3), the pressure of which is a crank pressure, a suction chamber (8), the pressure of which is a suction pressure.
  • a bleeding passage (53,57,58,59) connects the crank chamber (3) to the suction chamber (8).
  • the control valve (50) is located on the bleeding passage (53,57,58,59) to control the crank pressure by controlling the flow of gas from the crank chamber (3) to the suction chamber (8).
  • a valve seat (54) is located between a crank pressure zone and a suction pressure zone. The valve seat (54) defines a valve hole (55) that connects the crank pressure zone to the suction pressure zone.
  • a valve body (60) is selectively engaged with and disengaged from the valve seat (54) to control an opening size of the valve hole (55).
  • a sensing member (61) is located in the crank pressure zone. The sensing member (61) always urges the valve body (60) toward the valve seat (54), and the sensing member (61) moves in accordance with the crank pressure.
  • the sensing member (61) has a predetermined effective area that is affected by the crank pressure. The effective area is approximately the same the cross sectional area of the valve hole (55).
  • the control valve (50) for compressors that is able to set the suction pressure with precision.

Landscapes

  • 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)
EP00101971A 1999-02-02 2000-02-01 Kontrollventil für einen verstellbaren Kompressor Withdrawn EP1026398A3 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2489699 1999-02-02
JP2489699 1999-02-02
JP28982799A JP3925006B2 (ja) 1999-02-02 1999-10-12 容量可変型圧縮機の制御弁
JP28982799 1999-10-12

Publications (2)

Publication Number Publication Date
EP1026398A2 true EP1026398A2 (de) 2000-08-09
EP1026398A3 EP1026398A3 (de) 2001-01-03

Family

ID=26362474

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00101971A Withdrawn EP1026398A3 (de) 1999-02-02 2000-02-01 Kontrollventil für einen verstellbaren Kompressor

Country Status (2)

Country Link
EP (1) EP1026398A3 (de)
JP (1) JP3925006B2 (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1233182A2 (de) * 2001-02-20 2002-08-21 Kabushiki Kaisha Toyota Jidoshokki Regelventil für einen Verdichter variabler Verdrängung
EP1186777A3 (de) * 2000-09-08 2003-12-10 Kabushiki Kaisha Toyota Jidoshokki Kontrollventil für einen variablen Verdrängungskompressor
EP1186778A3 (de) * 2000-09-08 2004-01-02 Kabushiki Kaisha Toyota Jidoshokki Regelventil für einen Verdichter variabler Verdrängung
US6739843B2 (en) 2001-07-04 2004-05-25 Kabushiki Kaisha Toyota Jidoshokki Control valve and variable displacement compressor having the same
EP1507109A1 (de) * 2003-08-11 2005-02-16 Eagle Industry Co., Ltd. Kapazitätskontrollventil
EP1895162A1 (de) * 2005-06-22 2008-03-05 EAGLE INDUSTRY Co., Ltd. Mengeregelventil

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3733899B2 (ja) * 2001-12-06 2006-01-11 株式会社豊田自動織機 容量可変型圧縮機の電磁弁及びその製造方法
JP4130566B2 (ja) * 2002-09-25 2008-08-06 株式会社テージーケー 可変容量圧縮機用容量制御弁
JP5128466B2 (ja) * 2006-03-29 2013-01-23 イーグル工業株式会社 可変容量型圧縮機用制御弁
JP5269391B2 (ja) * 2007-11-02 2013-08-21 株式会社不二工機 可変容量型圧縮機用制御弁
JP6064131B2 (ja) * 2012-10-17 2017-01-25 株式会社テージーケー 可変容量圧縮機用制御弁

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0626454A (ja) 1992-07-07 1994-02-01 Saginomiya Seisakusho Inc 電磁式比例制御弁

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5174727A (en) * 1987-11-30 1992-12-29 Sanden Corporation Slant plate type compressor with variable displacement mechanism
JPH0331581A (ja) * 1989-06-28 1991-02-12 Sanden Corp 容量可変型斜板式圧縮機
JPH0724630Y2 (ja) * 1991-05-22 1995-06-05 株式会社ゼクセル 可変容量型揺動板式圧縮機
JPH09228956A (ja) * 1996-02-20 1997-09-02 Toyota Autom Loom Works Ltd 可変容量型圧縮機

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0626454A (ja) 1992-07-07 1994-02-01 Saginomiya Seisakusho Inc 電磁式比例制御弁

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1186777A3 (de) * 2000-09-08 2003-12-10 Kabushiki Kaisha Toyota Jidoshokki Kontrollventil für einen variablen Verdrängungskompressor
EP1186778A3 (de) * 2000-09-08 2004-01-02 Kabushiki Kaisha Toyota Jidoshokki Regelventil für einen Verdichter variabler Verdrängung
EP1233182A2 (de) * 2001-02-20 2002-08-21 Kabushiki Kaisha Toyota Jidoshokki Regelventil für einen Verdichter variabler Verdrängung
EP1233182A3 (de) * 2001-02-20 2004-07-14 Kabushiki Kaisha Toyota Jidoshokki Regelventil für einen Verdichter variabler Verdrängung
CN100402847C (zh) * 2001-02-20 2008-07-16 株式会社丰田自动织机 变容式压缩机的控制阀
US6739843B2 (en) 2001-07-04 2004-05-25 Kabushiki Kaisha Toyota Jidoshokki Control valve and variable displacement compressor having the same
EP1507109A1 (de) * 2003-08-11 2005-02-16 Eagle Industry Co., Ltd. Kapazitätskontrollventil
EP1895162A1 (de) * 2005-06-22 2008-03-05 EAGLE INDUSTRY Co., Ltd. Mengeregelventil
US7644729B2 (en) 2005-06-22 2010-01-12 Eagle Industry Co., Ltd. Capacity control valve
EP1895162A4 (de) * 2005-06-22 2011-11-16 Eagle Ind Co Ltd Mengeregelventil

Also Published As

Publication number Publication date
JP3925006B2 (ja) 2007-06-06
EP1026398A3 (de) 2001-01-03
JP2000291542A (ja) 2000-10-17

Similar Documents

Publication Publication Date Title
EP1059443B1 (de) Kapazitätskontrollventil
US6358017B1 (en) Control valve for variable displacement compressor
US6517323B2 (en) Displacement control mechanism for variable displacement type compressor
US6398516B1 (en) Variable displacement compressors and control valves for variable displacement compressors
EP0848164B1 (de) Regelventil für einen Kompressor mit veränderlicher Verdrängung
EP0953766B1 (de) Kontrollventil
US6352416B1 (en) Device and method for controlling displacement of variable displacement compressor
JP3789023B2 (ja) 電磁制御弁
EP0854288B1 (de) Regelventil für einen Verdichter mit veränderlicher Förderleistung und Verfahren zur Herstellung
US6257836B1 (en) Displacement control valve for variable displacement compressor
EP1138946A2 (de) Regelventil für einen Verdichter variabler Verdrängung
EP0997640A2 (de) Kompressor mit veränderlicher Fördermenge
KR19980070616A (ko) 가변 용량 압축기용 제어 밸브 및 장착 방법
US6217291B1 (en) Control valve for variable displacement compressors and method for varying displacement
EP1186777A2 (de) Kontrollventil für einen variablen Verdrängungskompressor
US6672844B2 (en) Apparatus and method for controlling variable displacement compressor
EP1026398A2 (de) Kontrollventil für einen verstellbaren Kompressor
EP0945617A2 (de) Kontrollventil zur Kapazitätseinstellung eines Verstellkompressors
JP2002285956A (ja) 容量可変型圧縮機の制御弁
EP1155888A2 (de) Klimaanlage
EP1024286A2 (de) Kontrollventil für einen verstellbaren Taumelscheibenverdichter
EP1172558B1 (de) Kontrollventil für einen verstellbaren Taumelscheibenkomressor
US6520749B2 (en) Control valve for variable displacement compressor
US6783332B2 (en) Control valve of variable displacement compressor with pressure sensing member
EP1099578A1 (de) Fahrzeugklimaanlage

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20000201

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE FR IT

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

AKX Designation fees paid

Free format text: DE FR IT

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20020903