EP1602828A2 - Kontrollventil für einen verstellbaren Taumelscheibenkompressor - Google Patents

Kontrollventil für einen verstellbaren Taumelscheibenkompressor Download PDF

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Publication number
EP1602828A2
EP1602828A2 EP05010247A EP05010247A EP1602828A2 EP 1602828 A2 EP1602828 A2 EP 1602828A2 EP 05010247 A EP05010247 A EP 05010247A EP 05010247 A EP05010247 A EP 05010247A EP 1602828 A2 EP1602828 A2 EP 1602828A2
Authority
EP
European Patent Office
Prior art keywords
valve
valve element
hollow cylindrical
solenoid
main
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Withdrawn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
EP05010247A
Other languages
English (en)
French (fr)
Inventor
Hisatoshi Hirota
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.)
TGK Co Ltd
Original Assignee
TGK Co 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 TGK Co Ltd filed Critical TGK Co Ltd
Publication of EP1602828A2 publication Critical patent/EP1602828A2/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • 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
    • F04B2027/1809—Controlled pressure
    • F04B2027/1813—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
    • F04B2027/1863—Controlled by crankcase pressure with an auxiliary valve, controlled by
    • F04B2027/1872—Discharge 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
    • F04B2027/1886—Open (not controlling) fluid passage
    • F04B2027/1895—Open (not controlling) fluid passage between crankcase and suction chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a

Definitions

  • the present invention relates to a control valve according to the preamble of claim 1.
  • a refrigerant compressor in a refrigeration cycle of an automotive air conditioner is driven by the car engine and is designed as a variable displacement compressor capable of varying the refrigerant capacity (the discharge amount of refrigerant) to obtain an adequate cooling capacity without being constrained by the rotational speed of the driving engine.
  • a control valve for the variable displacement compressor is disposed between the discharge port and the crankcase or between the crankcase and the suction port. This control valve maintains the differential pressure at a predetermined value. The value of the differential pressure can be set by externally changing a value of control current supplied to a solenoid of the control valve. When the engine varies, the crankcase pressure varies as well to reduce or increase the compression volume such that the amount of refrigerant discharged from the compressor is maintained constant.
  • a control valve known from JP 2004-116349 includes a variable orifice which changes the refrigerant passage area using an externally controlled solenoid such that the differential pressure across the variable orifice becomes equal to a predetermined value. By holding the differential pressure across the variable orifice set to a certain flow passage area, at the predetermined value, the flow rate through the variable orifice is controlled to be constant.
  • the control valve includes a first control valve for varying the flow passage area, a solenoid section for setting the flow passage area according to a change of external conditions, and a second control valve for sensing the differential pressure across the first control valve and for controlling the crankcase pressure such that the differential pressure becomes equal to the predetermined value.
  • the first control valve for high-pressure refrigerant is controlled by the solenoid section to directly change the flow passage area.
  • the discharged refrigerant is allowed to flow through the main valve.
  • the main valve is set to the first valve lift dependent on the flow rate.
  • the solenoid valve is set to the second valve lift based on the external signal corresponding to a desired flow rate of refrigerant.
  • the first valve lift increases to increase an offset thereof with respect to the second valve lift.
  • the solenoid valve controls the flow rate of refrigerant flowing into the crankcase, based on a change in the discharge flow rate detected by the main valve, such that the discharge flow rate is changed in a direction opposite to a direction of the detected change.
  • the flow rate of refrigerant passing through the main valve to be discharged from the compressor can be maintained at the predetermined value.
  • the main valve and the solenoid valve comprise a valve portion which is commonly used as part of the main valve.
  • the control valve can be realized by a very simple construction. The desired stable flow rate control is possible since the solenoid valve performs actuation control of the valve portion which is smaller than the main valve.
  • variable displacement compressor In the variable displacement compressor, a large differential pressure may occur between an operation phase and a stoppage phase. When the compressor is switched from the operating state into an operation stoppage state, pressure corresponding to the differential pressure would be returned to the discharge chamber at a dash. To prevent this, it is known to place a separate check valve at an outlet port of the compressor.
  • the main valve In the control valve according to the invention, the main valve itself constitutes a check valve structure which opens by a refrigerant flow in one direction. This is advantageous because is possible to dispense with a check valve disposed at the compressor outlet port, and thereby reduce the cost of the compressor.
  • the variable displacement compressor in Fig. 1 includes a crankcase 1 containing a rotating shaft 2. One shaft end extending to the outside of the crankcase 1 carries a pulley 3 being driven by an engine of an automotive vehicle.
  • a wobble plate 4 is fitted on the shaft 2. The inclination angle of the wobble plate 4 can be varied.
  • a plurality of cylinders 5 (one of which is shown in Fig. 1) contains pistons 6 converting the rotation of the wobble plate 4 into reciprocating motion.
  • Each cylinder 5 is connected to a suction chamber 9 and a discharge chamber 10 via a suction relief valve 7 and a discharge relieve valve 8, respectively.
  • a control valve 11 is provided between the discharge chamber 10 and an outlet port and between the discharge chamber 10 and the crankcase 1.
  • An orifice 12 is provided between the crankcase 1 and the suction chamber 9.
  • the outlet port is connected to a condenser 13, from which piping extends to an inlet port to the suction chamber 9 via an expansion valve 14 and an evaporator 15.
  • Each piston 6 draws refrigerant at suction pressure Ps from the suction chamber 9 and compresses and discharges compressed refrigerant at discharge pressure Pd1 into the discharge chamber 10.
  • High-pressure refrigerant from the discharge chamber 10 is decompressed to a discharge pressure Pd2 when passing through the control valve 11, and is delivered to the condenser 13.
  • a part of the high-pressure refrigerant is introduced into the crankcase 1 via the control valve 11.
  • the pressure Pc in the crankcase 1 rises, whereby the inclination angle of the wobble plate 4 is set such that the bottom dead centre of the piston 6 is brought to a position where the pressure in the cylinder 5 and the pressure Pc in the crankcase 1 are balanced. Thereafter, the refrigerant in the crankcase 1 returns to the suction chamber 9 via the orifice 12.
  • the control valve 11 detects the flow rate between the discharge chamber 10 and the condenser 13, and introduces refrigerant into the crankcase 1 at a flow rate dependent on the detected flow rate such that the flow rate between the discharge chamber 10 and the condenser 13 becomes constant.
  • the suction pressure Ps lowers, and the discharge pressure Pd1 rises. If this increases the flow rate between the discharge chamber 10 and the condenser 13 via the control valve 11, the flow rate into the crankcase 1 is also increased, whereby the pressure Pc in the crankcase 1 increases. Accordingly, the wobble plate 4 is adjusted so that it finally will be at right angles to the rotating shaft 2. This decreases the stroke of the pistons 6, to also reduce the discharge flow rate.
  • control valve 11 increases the flow rate into the crankcase 1 according to the increase in the flow rate, whereby the crankcase pressure Pc is increased to reduce the discharge capacity.
  • the discharge flow rate from the compressor is controlled to be constant.
  • the control valve 11 in Figs 2 and 3 has a main valve 20 and a solenoid actuated solenoid valve 21, which are accommodated in a body 22 formed with three ports 23, 24, and 25.
  • the port 23 communicates with the discharge chamber 10 (discharge pressure Pd1).
  • the port 24 communicates with the outlet port of the compressor (discharge pressure Pd2).
  • the port 25 communicates with the crankcase 1 (controlled pressure Pc).
  • a refrigerant passage 26 communicates between the ports 23, 24.
  • a valve seat 27 of the main valve 20 is formed integrally with the body 22. Downstream of the valve seat 27, a valve element 28 is movably disposed opposed to the valve seat 27.
  • This valve element 28 has an axial through hole.
  • a piston 30 hanging from a holder 29 capped on an upper end of the body 22 in Fig. 2 is inserted in the through hole to movably guide and hold the valve element 28.
  • a spring 31 is interposed urging the valve element 28 in valve-closing direction, such that the main valve 20 constitutes a check valve structure.
  • the solenoid valve 21 uses the valve element 28 of the main valve 20 as a movable valve seat.
  • the solenoid valve 21 has a hollow cylindrical valve element 32 that can be inserted in and removed from a valve hole defined by the through hole in the valve element 28 .
  • the valve element 32 forms a slide valve cooperating with the movable valve seat provided by the valve element 28.
  • the valve lift of the valve element 32 is controlled by the solenoid.
  • the valve element 32 is axially movably held in the body 22.
  • a bottomed sleeve 33 is hermetically fixed to the body 22.
  • a core 34 is fitted in the opening of the bottomed sleeve 33.
  • the core 34 has a through hole into which the valve element 32 is loosely fitted.
  • a movable plunger 35 is disposed within the bottomed sleeve 33.
  • the plunger 35 is urged by a spring 36 in a direction away from the core 34.
  • a lower end of the valve element 32 is fitted into the plunger 35.
  • the valve element 32 is guided by the body 22.
  • a coil 37 is provided outside the bottomed sleeve 33, and is surrounded by a yoke 38 integrally formed with the body 22.
  • the yoke 38 has a lower annular plate 39 for closing a magnetic circuit.
  • the valve element 32 has a lateral hole 40 at a location aligned with the port 25.
  • the port 23 (discharge pressure Pd1) and the port 25 communicate via a gap between the valve element 28 of the main valve 20 and the valve element 32 and a hollow part of the hollow cylindrical valve element 32.
  • the valve element 32 has a pressure-equalizing hole 41 in the vicinity of the plunger 35, for communication between the inside of the bottomed sleeve 33 and the port 25, such that the pressure Pc equally acts on the opposite ends of the hollow cylindrical valve element 32, whereby the pressure Pc never influences the control operation of the solenoid valve 21.
  • valve element 32 is removed from the valve hole formed in the valve element 28 to open the solenoid valve 21.
  • Refrigerant flows through a gap between the valve element 32 and the valve element 28 into the crankcase 1 at a flow rate dependent on the size of the produced offset.
  • the compressor performs transition to a state of operation with the predetermined capacity.
  • the suction pressure Ps lowers, and the discharge pressure Pd1 rises.
  • This increases the flow rate from the discharge chamber 10, and accordingly, the valve element 28 of the main valve 20 is further lifted to increase the flow passage area of the main valve 20, which is about to cause an increase in the flow rate of discharged refrigerant.
  • the increasing lift movement of the valve element 28 increases the offset between the valve element 32 and the valve element 28 which forms the movable valve seat for the valve element 32 to increase the flow rate into the crankcase 1 and to increase the crankcase pressure Pc.
  • the compressor acts in the direction of reducing its capacity, and is thus controlled such that the flow rate of discharged refrigerant is reduced.
  • the control valve 11 constantly acts such that it takes a balanced position as shown in Fig. 3. As a result, the flow rate of refrigerant discharged from the compressor is controlled to be constant.
  • the control valve 51 in Fig. 4 differs from the first embodiment by a modified structure of the solenoid valve 21.
  • the solenoid valve 21 in Fig. 4 comprises a hollow cylindrical axially movable valve seat 52 guided in the body 22.
  • a hollow cylindrical valve element 54 having the same diameter as the valve seat 52, is guided in a guide 53 hanging from the holder 29.
  • the valve element 54 is fixed to the valve element 28.
  • the movable valve seat 52 is actuated by a shaft 55 fixed to the plunger 35.
  • One end of the movable valve seat 52 opposed to the valve element 54 is expanded in a funnel-like fashion to form a valve seat face.
  • a hole 56 in the valve seat 52 open towards the port 25, such that the hollow interior of the movable valve seat 52 communicates with the port 25.
  • valve element 28 of the main valve 20 is rigidly fitted on the valve element 54
  • the solenoid valve 21 With a control current of predetermined value supplied to the coil 37, the solenoid valve 21 is stopped at a point where the attractive force of the solenoid and the force of the spring 36 are balanced.
  • the valve seat 52 is set to a valve lift corresponding to a discharge flow rate as a target. This causes the main valve 20 to be lifted according to a flow rate of refrigerant discharged from the discharge chamber 10, and the flow rate is eventually controlled such that it is set to a flow rate set by the solenoid valve 21.
  • the control valve 61 in Fig. 5 differs from the first embodiment by a modified structure for axially movably holding the valve element 28 of the main valve 20.
  • the relation of how the pressure acts on the hollow cylindrical valve element is changed.
  • the core 34 is extended upward in Fig. 5 to the location of the port 23 (discharge pressure Pd1).
  • a hollow cylindrical valve element 62 is axially movably held by the core 34.
  • This valve element 62 has the plunger 35 fixed to a lower end.
  • a plug 63 is fitted in an upper end of the valve element 62 which is urged by the spring 64 downward.
  • the valve element 28 of the main valve 20 is fitted on the valve element 62 in the vicinity of the upper end.
  • the valve element 28 is movable back and forth by using the hollow cylindrical valve element 62 as an axial guide.
  • the valve element 62 has a lateral hole 65 cooperating with the valve element 28 to form a valve portion of the solenoid valve 21, and further has a lateral hole 66 communicating with the port 25.
  • the core 34 has a pressure-equalizing hole 67 parallel to the hole holding the valve element 62, such that discharge pressure Pd1 is introduced into the bottomed sleeve 33 of the solenoid.
  • the valve element 62 receives the discharge pressure Pd1 in an upward direction and the discharge pressure Pd2 in a downward direction.
  • the differential pressure across the valve element 28 is very small compared with the discharge pressure Pd1, and hence substantially the same pressure acts on the opposite ends of the valve element 62 which prevent the control operation of the solenoid valve 21 from being adversely affected.
  • the control valve 61 controls the compressor such that the flow rate of refrigerant delivered from the discharge chamber 10 becomes constant.
  • the control valve 71 in Fig. 6 differs from the third embodiment in that a part of the solenoid is divided.
  • a hollow cylindrical valve element 72 is supported by the core 34.
  • a plug 73 is fixedly inserted into a portion of the hollow part of the valve element below the location of the port 25.
  • the port 25 and the bottomed sleeve 33 are fluidically separated from each other.
  • Disposed between the plug 73 and the plunger 35 is a shaft 74.
  • One end of the shaft 74 abuts at the plug 73.
  • the other end of the shaft is fitted into the plunger 35. Axial motions of the plunger 35 are transmitted to the valve element 72 via the shaft 74 and the plug 73.
  • This control valve 71 controls the flow rate into the crankcase 1 according to the lift of the main valve 20, thereby controlling the compressor such that the discharge flow rate of refrigerant becomes constant.
  • the control valve 81 in Fig. 7 differs from the fourth embodiment in that the pressure introduced into the solenoid is set to the discharge pressure Pd2 downstream of the main valve 20.
  • the body 22 is provided with an axial initial pressure-equalizing hole 82.
  • the core 34 has an axial interior pressure-equalizing hole 83 communicating with the pressure-equalizing hole 82.
  • the discharge pressure Pd2 acts on the opposite ends of the valve element 72 which prevents discharge pressure Pd2 from adversely affecting the control operation of the solenoid valve 21.
  • the control valve 91 in Fig. 8 differs from the second embodiment in that damper means is added to the main valve 20.
  • the valve element 20 has a cup-shaped valve element 92 axially movably guided within a cylinder 93 recessed inside the holder 29.
  • the hollow cylindrical valve element 54 of the solenoid valve 21 fixed to the valve element 92 of the main valve 20 is also movably guided within the guide 53 hanging from the holder 29.
  • the upper opening of the holder 29 is closed by a plate 94.
  • a space defined between the inside of the valve element 92 and the outside of the valve element 54 contains the spring 31 and forms an approximately hermetically closed chamber as part of the damper means.
  • valve element 92 of the main valve 20 When the discharge pressure Pd1 at the port 23 is suddenly changed, the valve element 92 of the main valve 20 is about to be fluctuated due to a sudden change in the received pressure. However, a progressive increase or decrease of the volume of the hermetically closed chamber absorbs the sudden change in the received pressure, whereby the valve element 92 is prevented from being suddenly fluctuated. A vibrating noise generated by fluctuating motions of the valve element 92 can be reduced.
  • the control valve 101 of Fig. 9 differs from the first embodiment in that the solenoid valve 21 is implemented by a poppet valve.
  • a frustoconical valve element 95 is fitted on the upper end of the hollow cylindrical valve element 32. This forms the valve portion of the solenoid valve 21.
  • the valve element 95 has an axial through hole of the same inner diameter as the hollow cylindrical valve element 32. The valve element 95 moves to and away from the rim of the through hole in the valve element 28 in a manner interlocked to the axial motion of the hollow cylindrical valve element 32. This causes the valve element 95 to be closely seated on the valve seat formed on the valve element 28 of the main valve 20, which reduces leakage from the solenoid valve 21.
  • the control valve 111 in Figs 10, 11A, 11B and 12 differ from the first to seventh embodiments by a modified structure of the main valve 20.
  • the main valve 20 includes a valve element 112 which is movable relative to the valve seat 27 formed in the refrigerant passage 26.
  • the valve element 112 is integrally formed with a hollow cylindrical skirt 113 which slidably extends into a valve hole of the main valve 20.
  • a lower end of a hollow cylindrical portion 115 forms a valve seat 114 of the solenoid valve 21. Inserted into the hollow cylindrical portion 115 is a guide 116 hanging from the holder 29.
  • the solenoid valve 21 has a hollow cylindrical valve element 117 axially movably guided in the body 22 relative to the valve seat 114.
  • the hollow cylindrical valve element 117 has a lateral valve hole 118 communicating with the port 25.
  • An upper end of the hollow cylindrical valve element 117 on a side opposed to the valve seat 114 has a frustoconical shape, and defines a poppet valve co-operating with the valve seat 114.
  • the valve element 112 of the main valve 20 in Figs 11A, B has an outer tapered portion 119 for closely seating on the valve seat 27, in order to maintain a sufficient closed state when the main valve 20 has to function as a check valve.
  • the skirt 113 integral with the valve element 112 has at least one slit 120 in a circumferential direction.
  • the slit 120 is formed by cutting the skirt 113 along the axis of the main valve 20.
  • the slit 120 forms a flow passage area-variable refrigerant passage of the main valve 20, the opening area of which is changed according to the lift amount.
  • the valve element 112 of the main valve 20 is configured such that the opening width of the slit 120 decreases in axial direction towards the tapered portion 119.
  • the valve element 112 starts to open from the fully-closed state on the valve seat 27, it is possible to modify the rate of change in the opening area with respect to the amount of motion of the valve element 112.
  • the change in the flow rate relative to the value of electric current supplied to the solenoid is not linear, when the valve seat 27 is positioned in a region where the opening width of the slit 120 is changing after the valve element 112 has started to be lifted.
  • the increase of the flow rate responsive to an increase of the electric current is relatively small, while the change of the flow rate relative to the electric current behaves is proportional when the valve element 27 is positioned in a region where the opening width of the slit 120 is constant.
  • control valve has to be disposed in a discharge-side refrigerant passage of the variable displacement compressor to control the flow rate into the crankcase 1, but the control valve may instead be disposed in a suction-side refrigerant passage, such that then the main valve senses the flow rate through the suction-side refrigerant passage, to control the flow rate from the crankcase 1 into the suction chamber instead.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Magnetically Actuated Valves (AREA)
EP05010247A 2004-05-31 2005-05-11 Kontrollventil für einen verstellbaren Taumelscheibenkompressor Withdrawn EP1602828A2 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2004162122 2004-05-31
JP2004162122 2004-05-31
JP2004196230 2004-07-02
JP2004196230A JP4331653B2 (ja) 2004-05-31 2004-07-02 可変容量圧縮機用制御弁

Publications (1)

Publication Number Publication Date
EP1602828A2 true EP1602828A2 (de) 2005-12-07

Family

ID=34936403

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05010247A Withdrawn EP1602828A2 (de) 2004-05-31 2005-05-11 Kontrollventil für einen verstellbaren Taumelscheibenkompressor

Country Status (4)

Country Link
US (1) US20050265853A1 (de)
EP (1) EP1602828A2 (de)
JP (1) JP4331653B2 (de)
KR (1) KR20060046254A (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4516892B2 (ja) * 2005-06-08 2010-08-04 イーグル工業株式会社 容量可変型圧縮機の容量制御弁
JP4925800B2 (ja) * 2006-11-30 2012-05-09 カルソニックカンセイ株式会社 可変容量コンプレッサの制御弁
JP4833820B2 (ja) * 2006-12-25 2011-12-07 株式会社鷺宮製作所 容量制御弁および容量可変型圧縮機並びに空気調和装置
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JP2006017035A (ja) 2006-01-19

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