WO2019146388A1 - 可変容量型圧縮機用制御弁 - Google Patents

可変容量型圧縮機用制御弁 Download PDF

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Publication number
WO2019146388A1
WO2019146388A1 PCT/JP2019/000120 JP2019000120W WO2019146388A1 WO 2019146388 A1 WO2019146388 A1 WO 2019146388A1 JP 2019000120 W JP2019000120 W JP 2019000120W WO 2019146388 A1 WO2019146388 A1 WO 2019146388A1
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WO
WIPO (PCT)
Prior art keywords
valve body
main valve
valve
chamber
pressure
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.)
Ceased
Application number
PCT/JP2019/000120
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
恒 浅野
伊東　雅晴
慎太郎 田野
裕貴 浅野
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.)
Fujikoki Corp
Original Assignee
Fujikoki Corp
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 Fujikoki Corp filed Critical Fujikoki Corp
Priority to CN201980010725.XA priority Critical patent/CN111670305A/zh
Priority to KR1020207024761A priority patent/KR20200110440A/ko
Priority to US16/964,044 priority patent/US20210048010A1/en
Priority to EP19743098.6A priority patent/EP3748157A4/en
Publication of WO2019146388A1 publication Critical patent/WO2019146388A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • 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
    • F04B27/10—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 having stationary cylinders
    • F04B27/1009—Distribution members
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/04—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only lift valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • 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
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • 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
    • F04B2027/185—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
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1859—Suction pressure
    • 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 for a variable displacement compressor used in a car air conditioner or the like, and more particularly to a control valve for a variable displacement compressor capable of canceling the influence of refrigerant pressure acting on a valve body.
  • a discharge pressure Pd is introduced from a discharge chamber of the compressor, and the discharge pressure Pd is adjusted in accordance with a suction pressure Ps of the compressor.
  • An electromagnetic actuator having a valve body, a main valve body (valve rod) for opening and closing the valve port, and a plunger for moving the main valve body in the valve port opening and closing direction, suction pressure Ps from the compressor Is through the Ps entrance and exit And includes a sensing chamber to be introduced, and sensitive ⁇ rotary members of the bellows arrangement such that urges the main valve body the valve port opening and closing directions in response to pressure sensitive chamber, a Te.
  • the control valve for a variable displacement compressor described in Patent Document 2 and the like described below releases the pressure Pc of the crank chamber to the suction chamber of the compressor via the Ps inlet and outlet.
  • an auxiliary valve body (ball valve body) for opening and closing the in-valve escape passage, and the plunger is continuously moved upward from the lowest position by the suction force of the electromagnetic actuator.
  • Patent No. 5553514 gazette Patent No. 4550651
  • variable displacement compressor control valve if the force in the valve opening direction and the force in the valve closing direction due to the refrigerant pressure applied to the main valve body (valve rod) are different, the control is adversely affected (control accuracy And the like) (for example, see the above-mentioned Patent Document 2 etc.). Therefore, for example, in the conventional control valve for a variable displacement compressor described in Patent Document 1, the lower end portion of the main valve body faces the Ps introduction chamber into which the suction pressure Ps is introduced, and the main valve body The suction pressure Ps acts on the lower end of the valve, and the suction pressure Ps is introduced to the pressure-sensitive response member in the valve body, and the suction pressure Ps acts on the upper end of the main valve body. A suction pressure passage for introducing the pressure Ps is provided, and the control by the pressure of the refrigerant acting on the main valve body described above is not easily affected.
  • the present invention has been made in view of the above circumstances, and an object of the present invention is to provide a variable displacement type that can cancel the influence of the refrigerant pressure acting on the main valve body without increasing the size of the valve body. It is providing a control valve for a compressor.
  • a control valve for a variable displacement compressor is basically provided with a main valve body having a main valve body portion and a valve opening at which the main valve body portion contacts and separates. And a P.sub.s inlet and outlet communicating with the suction chamber of the compressor, and a Pd inlet communicating with the discharge chamber of the compressor is provided on the upstream side of the valve opening and on the downstream side of the valve opening.
  • a valve body provided with a Pc inlet / outlet communicating with a crank chamber of the compressor, an electromagnetic actuator for moving the main valve body in the valve opening / closing direction, and a suction pressure Ps from the compressor
  • a pressure-sensitive chamber introduced through an outlet, and a pressure-sensitive response member urging the main valve body in the valve opening / closing direction according to the pressure in the pressure-sensitive chamber, one end of the main valve body
  • the Ps inlet / outlet or the pressure sensing chamber is provided to operate the suction pressure Ps
  • the suction pressure Ps is introduced to the main valve body to a Ps introduction chamber provided at the other end of the main valve body, and suction is applied to cause the suction pressure Ps to act on the other end of the main valve body.
  • a pressure passage is provided.
  • one end side guide hole is provided on one end side of the valve port in the valve body, into which the one end side insertion portion of the main valve body is slidably inserted, and from the valve port in the valve body
  • the other end side is provided with the other end side guide hole in which the other end side inserting portion of the main valve body is slidably inserted, and one end side of the one end side guide hole has the Ps inlet / outlet or the pressure sensing A chamber is provided, and the Ps introduction chamber is provided on the other end side of the other end side guide hole, and the force in the valve opening direction and the force in the valve closing direction by the refrigerant pressure acting on the main valve body are the same.
  • the cross sectional area of the one end side insertion part of the main valve body, the cross sectional area of the other end side insertion part of the main valve body, and the opening area of the valve port (ie, pressure receiving area or effective opening area). ) Is set equal.
  • a lid-like guide member having the other end side guide hole is airtightly fixed to the valve body so as to form the Ps introduction chamber.
  • a biasing member for biasing the main valve body in the valve closing direction is attached to the Ps introduction chamber.
  • the main valve body is constituted by a cylindrical member having the main valve body portion, and a shaft-like member fitted and fixed to the cylindrical member, and the cylindrical member and the shaft-like member The suction pressure passage is formed between the members.
  • the suction pressure passage extends linearly in the valve opening and closing direction.
  • an in-valve relief passage for evacuating the pressure Pc of the crank chamber to the suction chamber of the compressor via the Ps inlet / outlet is provided in the main valve body or the valve body, and An auxiliary valve body is provided for opening and closing the in-valve relief passage.
  • the in-valve relief passage includes a through-hole formed in a crank shape in the main valve body.
  • an in-valve relief passage for escaping the pressure Pc of the crank chamber to the suction chamber of the compressor via the Ps inlet and outlet is provided in the main valve body, and the relief passage in the valve is A sub valve body which opens and closes is provided, and the main valve body is constituted by a cylindrical member having the main valve body portion, and a shaft member fixedly fitted in the cylindrical member, and the cylindrical member
  • the suction pressure passage is formed between the axial member and the axial member, and the in-valve release passage includes a vertical hole provided in the axial member.
  • the suction pressure Ps acting on one end of the main valve is guided to the Ps introduction chamber provided at the other end of the main valve, and suctioned to the other end of the main valve. Since the suction pressure passage for applying the pressure Ps is provided, for example, it acts on the main valve body without increasing the size of the valve body as compared with the conventional one in which the suction pressure passage and the like are provided in the valve body. It is possible to cancel the influence of the pressure of the refrigerant.
  • the suction pressure Ps is caused to act on one end of the main valve body, and a Ps introduction chamber in which the suction pressure Ps is introduced is provided at the other end of the main valve body. Since a suction pressure passage for guiding the suction pressure Ps to the Ps introduction chamber is provided, the cross-sectional area of the one end side insertion portion of the main valve body, the cross sectional area of the other end side insertion portion of the main valve body, and the valve opening If the opening area (that is, the pressure receiving area or the effective opening area) is the same, the force applied in the valve opening direction by the refrigerant pressure acting on the main valve body and the force applied in the valve closing direction are the same (cancelled). The adverse effect on the control due to the refrigerant pressure acting on the main valve body can be reduced.
  • the main valve body is constituted by a cylindrical member having a main valve body portion, and a shaft-shaped member fitted and fixed to the cylindrical member, and a suction pressure passage is formed between the cylindrical member and the shaft-shaped member. Since it is formed, the suction pressure passage can be formed with a simple structure, and the influence of the refrigerant pressure acting on the main valve body can be canceled.
  • an in-valve relief passage for escaping the pressure Pc of the crank chamber of the compressor to the suction chamber of the compressor via the Ps inlet / outlet is provided in the main valve body or in the valve body and Since the sub valve body which opens and closes is provided, startability improvement can be aimed at with a simple structure.
  • the longitudinal cross-sectional view which shows the state (at the time of normal control) of the main valve of one Embodiment of the control valve for variable displacement type compressors which concerns on this invention open, subvalve: closed state.
  • the longitudinal cross-sectional view which shows the state (at the time of compressor starting transfer) of the main valve of one Embodiment of the control valve for variable displacement type compressors which concerns on this invention closed, subvalve: closed state.
  • the longitudinal cross-sectional view which shows the state (at the time of compressor start) of the main valve of one Embodiment of the control valve for variable displacement type compressors which concerns on this invention closed, subvalve: open state.
  • First Embodiment 1 to 3 are longitudinal sectional views showing an embodiment of a control valve for a variable displacement compressor according to the present invention
  • FIG. 1 shows a state of main valve: open
  • sub valve: closed (during normal control) 2 and 3 show the main valve: closed and sub valve: closed (during compressor start transition)
  • FIG. 3 shows the main valve: closed and sub valve: open (during compressor start).
  • the gap formed between the members, the separation distance between the members, and the like are large in comparison with the dimensions of the respective constituent members in order to facilitate understanding of the invention and for convenience in drawing. Or it may be drawn small.
  • the control valve 1 of the illustrated embodiment basically includes a valve main body 20 provided with a valve port 22, a main valve body 10 for opening and closing the valve port 22, and a main valve body 10 in a valve opening / closing direction
  • the electromagnetic actuator 30 for moving in the vertical direction), and the bellows device 40 as a pressure sensitive response member.
  • the electromagnetic actuator 30 includes a bobbin 38, a coil 32 for energization and excitation provided outside the bobbin 38, a stator 33 and a suction element 34 disposed on the inner peripheral side of the coil 32, a lower end of the stator 33 and the suction element 34 A guide pipe 35 whose upper end is joined to the outer periphery (step portion) by welding, and a bottomed cylindrical plunger slidably disposed vertically in the inner peripheral side of the guide pipe 35 below the suction element 34.
  • a holder 29 is provided between the lower end of the pipe 35 and the upper end of the valve body 20 to fix them.
  • a cylindrical suction element 34 having an insertion hole 34a smaller in diameter than the inner diameter of the stator 33 is formed integrally with the lower inner periphery of the cylindrical stator 33 (along the axis O). It is done.
  • a ring-shaped mounting plate 39 is disposed between the outer peripheral step portion formed on the upper portion of the stator 33 and the inner peripheral step portion formed on the upper portion of the housing 60, and the upper end portion (thin portion ) Is caulked and fixed in an annular fitting concave groove 31a provided on the outer periphery of the connector portion 31 in order to mount an O-ring 31A as a sealing material (crimped portion 61).
  • a portion including the coil 32, the stator 33, the suction element 34 and the like excluding the plunger 37 is referred to as a solenoid unit 30A.
  • a short cylindrical stator 65 is fixed to the upper portion of the stator 33 by press fitting or the like. Between the stator 65 and the suction element 34 on the inner peripheral side of the stator 33, a pressure-sensitive chamber 45 is formed, into which the suction pressure Ps of the compressor is introduced.
  • a bellows device 40 comprising a bellows 41, a downward convex upper stopper 42, a downward concave lower stopper 43, and a compression coil spring 44 is disposed. Further, on the lower side of the bellows device 40, a stepped rod-like push rod 46 as a thrust transfer member is disposed along the axis O.
  • An approximate center of the push rod 46 has a large diameter (large diameter portion 46 b), and the upper end 46 d of the push rod 46 is inserted and supported in the recess of the lower stopper 43, and the insertion hole 34 a of the suction element 34
  • the large diameter portion 46b of the push rod 46 is inserted (with a slight gap 34b).
  • the lower portion of the push rod 46 is inserted into the concave hole 17b of the auxiliary valve body 17 having a concave cross section described later, and the lower end 46a thereof is a concave fitting insertion hole 17c formed at the center of the bottom of the concave hole 17b. Is embedded in the
  • the sub valve body 17 having a concaved cross section having a recessed hole 17b having substantially the same diameter as the insertion hole 34a of the suction element 34 is inserted into and fixed to the plunger 37 by press fitting or the like. They move up and down together.
  • the upper end of the sub valve body 17 is aligned with the upper end of the plunger 37 (in other words, the upper end is positioned on the inner periphery of the upper end of the plunger 37), and the lower end thereof is separated from the bottom of the plunger 37
  • a held state (to be described in detail later, in a state in which the hook-shaped locking portion 10k of (the axial member 10B of the main valve body 10 has a clearance to be slightly vertically movable)) It is inserted in 37.
  • a concave insertion hole 17c into which the lower end 46a of the push rod 46 is inserted is formed.
  • a plunger spring (opening valve spring) 47 formed of a cylindrical compression coil spring is compressed between the upper surface of The plunger 37 is urged downward (in the valve opening direction) via the sub valve body 17 by (the compression force of) the plunger spring 47, and the bellows device 40 is in the pressure sensing chamber 45 via the push rod 46. Is held by. Further, the sub valve body 17 is biased in the direction to close the in-valve relief passage 16 (through escape hole 16A) described later by (the compression force of) the plunger spring 47.
  • the flat surface is a sub valve body portion 17a that opens and closes the in-valve relief passage 16 (described in detail later).
  • the height (in the vertical direction) of the slit 37s (that is, the thickness (height in the vertical direction) of the bottom of the plunger 37) is slightly smaller than the height of the upper small diameter portion 10e of the main valve body
  • the valve body 10 is vertically movable with respect to the plunger 37 (described in detail later).
  • the width (in the lateral direction) of the slit 37s is the outer diameter of the upper small diameter portion 10e of the main valve body 10 (that is, the outside of the axial member 10B constituting the main valve body 10)
  • the outer diameter of the slit 37s on the upper surface of the bottom of the plunger 37 is the ridge of the main valve body 10.
  • the inner hook-shaped hooking part 37k is used to hook the hook-shaped locking part 10k.
  • a communication groove 17d consisting of a D-cut surface or one or more longitudinal grooves or the like is formed at a predetermined position on the outer periphery of the sub valve body 17 (the upper side of the slit 37s in the illustrated example).
  • a clearance 36 is formed between the outer periphery of the sub valve body 17 and the inner periphery of the plunger 37 by the communication groove 17 d.
  • the communication groove 17 may be provided on the outer periphery of the plunger 37, and the gap 36 may be formed between the outer periphery of the plunger 37 and the inner periphery of the guide pipe 35.
  • the main valve body 10 disposed on the lower side of the plunger 37 and the sub valve body 17 described above is, for example, a nonmagnetic metal member, and a stepped cylindrical tubular member 10A disposed along the axis O;
  • the cylindrical member 10A has a two-part configuration of a shaft-like member 10B inserted and fixed in a fitting hole 13 provided at the center of the cylindrical member 10A (that is, along the axis O).
  • the cylindrical member 10A has, in order from the bottom, a lower fitting portion 10b, a main valve body portion 10a having a diameter slightly larger than that of the lower fitting portion 10b, and a middle small diameter portion having a smaller diameter than the lower fitting portion 10b and the main valve body portion 10a. It consists of 10c and the upper insertion part 10d.
  • the outer diameters (crossing areas) of the lower insertion portion 10b and the upper insertion portion 10d are set to be substantially equal (described in detail later).
  • the fitting hole 13 formed in the cylindrical member 10A is composed of a lower small diameter hole 13b having substantially the same diameter as the shaft member 10B and an upper large diameter hole 13a slightly larger in diameter than the shaft member 10B.
  • a portion corresponding to the lower insertion portion 10b and the main valve body portion 10a of the cylindrical member 10A is a lower small diameter hole 13b
  • a portion corresponding to the middle small diameter portion 10c and the upper insertion portion 10d is an upper portion. It is considered as the diameter hole 13a.
  • the shaft-like member 10B is provided at its upper end with a hook-shaped locking part 10k of a relatively large diameter (and smaller than the outer diameter of the sub valve body 17) and includes the hook-shaped locking part 10k.
  • the upper portion is inserted into the upper large diameter hole 13a (with an annular gap) so that the upper portion protrudes, and the lower portion is inserted into and fixed to the lower small diameter hole 13b by press fitting or the like.
  • the shaft-like member 10B is integrated.
  • the upper small diameter portion 10e is loosely fitted in the slit 37s of the plunger 37, and the upper hook-like locking portion 10k of the upper small diameter portion 10e is lower than the sub valve body 17 inside the plunger 37 (in other words, For example, it is loosely fitted in the space between the bottom of the plunger 37 and the lower end of the secondary valve body 17).
  • the hook-shaped locking portion 10k has a diameter larger than the width of the slit 37s, and when the plunger 37 is moved upward with respect to the main valve body 10, the outer peripheral portion of the slit 37s The inner hook-shaped hooking portion 37k is hooked on the hook-shaped locking portion 10k and is locked in place.
  • one or a plurality of longitudinal grooves extending upward from the lower end portion and continuing to the upper large diameter hole 13a on the lower outer periphery (the portion fitted into the lower small diameter hole 13b) of the shaft member 10B. 10f is formed, and the vertical groove 10f forms a gap extending in the longitudinal direction between the outer periphery of the axial member 10B and the inner periphery (lower small diameter hole 13b) of the cylindrical member 10A.
  • valve body 20 is made of metal such as stainless steel (SUS), high hardness brass, aluminum or the like, and the upper end (surface) thereof becomes a stopper 20A for defining the lowest position of the plunger 37 ing.
  • SUS stainless steel
  • high hardness brass aluminum or the like
  • valve body 20 In the valve body 20, the lower slide hole 19B and the upper fitting portion 10d in which the lower fitting portion 10b of (the cylindrical member 10A of the main valve body 10) is slidably fitted are slidably fitted
  • a valve port (valve seat portion) 22 having an upper slide hole 19D to be inserted and opened and closed by the main valve body portion 10a of the main valve body 10 is provided between the lower guide hole 19B and the upper guide hole 19D.
  • the valve chamber 21 is provided.
  • the main valve portion 11 is constituted by the main valve body portion 10 a and the valve port 22.
  • an insertion hole 18 larger in diameter than the upper guide hole 19D and the main valve body portion 10a for inserting the main valve body 10 at the time of assembly is provided in the lower center of the valve main body 20.
  • a lid-like guide member 24 with a bottomed cylindrical shape (in other words, a concave shape in cross section) is airtightly inserted and fixed (fixed) by press-fitting or the like.
  • the inner periphery of the lid-like guide member 24 is a lower guide hole 19B in which the lower fitting portion 10b of the main valve body 10 (the cylindrical member 10A) is slidably fitted, and the lid-like guide member A suction pressure Ps is introduced between (the inner surface of) and the lower end portion (lower fitting portion 10b of the main valve body 10) (lower side of the lower guide hole 19B) via a suction pressure passage 14 described later.
  • the Ps introduction chamber 24A is formed.
  • a valve closing spring (biasing member) 50 consisting of a cylindrical compression coil spring is contracted (mounted).
  • the main valve body 10 is biased in the valve closing direction (upward) by the biasing force of the valve closing spring 50, and the upper end portion of the main valve body 10 (the hook-like locking portion 10k thereof) is the lower end portion of the sub valve body 17. (The auxiliary valve body 17a) is pressed.
  • the stepped portion formed between the insertion hole 18 and the upper guide hole 19D is a valve port 22 opened and closed by contacting and separating the main valve body portion 10a of the main valve body 10 from the lower side.
  • a concave hole 19C larger in diameter than the upper fitting portion 10d of the main valve body 10 (the cylindrical member 10A) and smaller in diameter than the outer diameter of the plunger 37 is provided at the upper center of the valve body 20.
  • the periphery of the recessed hole 19C in the upper end portion (surface) of the valve main body 20 is the stopper portion 20A, and the upper guide hole 19D is continuously provided in the center of the bottom portion of the recessed hole 19C.
  • the concave hole 19C (in other words, the outer periphery of the upper insertion portion 10d of the main valve body 10 inserted into the concave hole 19C) is used as a Ps inlet / outlet chamber 28 of the suction pressure Ps of the compressor.
  • a plurality of Ps inlets and outlets 27 are formed on the outer peripheral portion of the chamber 28.
  • the suction pressure Ps introduced from the Ps inlet / outlet 27 into the Ps inlet / outlet chamber 28 (in the recessed hole 19C) is a gap formed between the inside of the plunger 37 (slit 37s and between the sub valve body 17 and the plunger 37). 36)
  • the pressure is introduced into the pressure sensing chamber 45 through a gap 34b and the like formed between the outer periphery of the push rod 46 and the suction element 34.
  • a filter 25A communicated with the discharge chamber of the compressor is provided on the outer peripheral portion (upstream side from the valve port 22) of the lower portion of the upper sliding hole 19D (the portion through which the middle small diameter portion 10c of the main valve body 10 is inserted).
  • a plurality of Pd inlet ports 25 are opened, and an outer peripheral portion (downstream side of the valve port 22) of the valve chamber 21 (in other words, the insertion hole 18) communicates with the crank chamber of the compressor.
  • the Pc inlet / outlet 26 has the Pd inlet through the gap between the valve chamber 21 ⁇ the valve port 22 and the main valve body 10 a ⁇ the gap between the lower portion of the upper slide hole 19 D and the middle small diameter portion 10 c. It communicates with 25.
  • O-rings 51, 52, 53 as sealing materials are disposed at important points on the outer peripheral portion of the control valve 1 so that the suction pressure Ps, the discharge pressure Pd, and the pressure Pc in the crank chamber do not leak. There is.
  • a through escape hole 16A for communicating the Pc inlet / outlet 26 with the Ps inlet / outlet chamber 28 (Ps inlet / outlet 27) is provided in the main valve body 10.
  • a vertical hole 16a extending in the direction of the axis O from the upper end to near the lower end (main valve body portion 10a of the cylindrical member 10A) is provided at the center of the axial member 10B constituting the main valve body 10
  • a lateral hole 16b is provided from the vicinity of the lower end of the to point in a direction perpendicular to the axis O direction.
  • the main valve body portion 10a of the cylindrical member 10A which is encased in the shaft member 10B has a diameter slightly larger than the lateral hole 16b which is continuous with the lateral hole 16b and opened to the valve chamber 21 (and Pc inlet / outlet 26).
  • a through hole 16c is formed, which is a lateral hole.
  • the through hole 16A communicating the Pc inlet / outlet 26 with the Ps inlet / outlet chamber 28 is formed by the through hole 16c of the cylindrical member 10A and the horizontal hole 16b and the vertical hole 16a of the shaft member 10B.
  • the through escape hole 16A constitutes a part of the in-valve escape passage 16, and the upper end of the through escape hole 16A (that is, the upper end of the vertical hole 16a) is the lower end of the sub valve body 17 (sub valve The body portion 17a is a sub valve seat portion 23 which contacts and separates (detailed later).
  • the sub valve portion 12 is configured by the sub valve seat portion 23 and the sub valve body portion 17 a.
  • An in-valve relief passage 16 for escaping the pressure Pc of the crank chamber to the suction chamber of the compressor via the Ps inlet / outlet 27 is formed, and a sub valve seat portion which is an upper end edge portion of the through relief hole 16A of the main valve body 10
  • the sub valve body portion (lower end portion) 17a of the sub valve body 17 comes into contact with the inverted frusto-conical surface portion 23, the in-valve escape passage 16 is opened and closed.
  • the force in the valve opening direction (downward) and the force in the valve closing direction (upward) due to the refrigerant pressure acting on the main valve body 10 are balanced (cancel the differential pressure) The following measures have been taken to achieve this.
  • the Ps inlet / outlet chamber 28 (Ps inlet / outlet 27) provided on the upper end side of the main valve body 10 or the pressure sensitive chamber 45 and the lower end portion of the main valve body 10 are provided.
  • a suction pressure passage 14 is provided to communicate with the Ps introduction chamber 24A.
  • the upper large diameter hole 13a of the cylindrical member 10A of the main valve body 10 and the longitudinal groove 10f of the lower outer periphery of the shaft member 10B allow the cylindrical member 10A of the main valve body 10 and the shaft member 10B to A suction pressure passage 14 is formed between the Ps inlet / outlet chamber 28 (Ps inlet / outlet 27) or the pressure sensitive chamber 45 and the Ps inlet chamber 24A.
  • the suction pressure passage 14 is disposed around the through escape hole 16A formed in the main valve body 10.
  • the suction pressure Ps acting on the upper end portion side of the main valve body 10 is introduced to the Ps introduction chamber 24 A provided at the lower end portion of the main valve body 10 by the suction pressure passage 14, and the lower end portion of the main valve body 10
  • the suction pressure Ps is applied to (the lower fitting portion 10b) (always).
  • the outer diameter (crossing area Ab) of the lower insertion portion 10b of the main valve body 10 in other words, the hole diameter of the lower sliding hole 19B (opening area or pressure receiving area)
  • the diameter of the valve port 22 crossing area or The effective opening area Ac
  • the outer diameter (crossing area Ad) of the upper insertion portion 10d of the main valve body 10 in other words, the hole diameter of the upper sliding hole 19D (opening area or pressure receiving area)
  • the main valve body 10 is configured as a two-part configuration of the cylindrical member 10A and the shaft-like member 10B, and between the cylindrical member 10A and the shaft-like member 10B
  • the suction pressure passage 14 extending substantially linearly in the opening / closing direction of the valve port 22 is formed
  • the main valve body 10 is configured in one piece, and the suction pressure passage 14 is formed inside the main valve body 10 Of course it may be done.
  • the in-valve relief passage 16 for escaping the pressure Pc of the crank chamber to the suction chamber of the compressor via the Ps inlet / outlet 27 is a through relief formed in the main valve body 10 in a crank shape.
  • the hole 16A is included, for example, the in-valve relief passage 16 may be provided on the valve body 20 side (not in the main valve body 10), as a matter of course. Also, it goes without saying that the in-valve escape passage 16 itself may be omitted.
  • suction pressure passage 14 and the in-valve escape passage 16 are not limited to the illustrated example.
  • the plunger 37, the main valve body 10, and the sub valve body 17 are in the lowest position (the lower end surface of the plunger 37 is a stopper portion In the case where the main valve body 11 is fully open and the sub valve 12 is fully closed), the vertical separation distance between the main valve body 10 a of the main valve body 10 and the valve port (valve seat portion) 22 Is the first lift amount La, and the separation distance between the inner hook-shaped locking portion 37k of the plunger 37 and the hook-shaped locking portion 10k of the main valve body 10 is a predetermined amount Ly.
  • the second lift amount Lb lift amount from the lowermost position to the highest position of the plunger 37) is equal to the first lift amount La + the predetermined amount Ly.
  • control valve 1 Next, the operation of the control valve 1 configured as described above will be outlined.
  • the force in the valve opening direction (downward) and the force in the valve closing direction (upward) due to the refrigerant pressure acting on the main valve body 10 through the suction pressure passage 14 described above The force acting in the moving direction of the body 10 (the direction of the axis O) is always balanced (the differential pressure is canceled).
  • the lift amount of the plunger 37 (and the sub valve body 17) is at most the first lift amount La at maximum, and when the compressor is started (during Pc ⁇ Ps control)
  • the lift amount of the plunger 37 (and the sub valve body 17) is set to the second lift amount Lb.
  • the bellows device 40 (the inside is a vacuum pressure) expands and contracts (contracts when the suction pressure Ps is high and stretches when it is low) according to the pressure (suction pressure Ps) of the pressure sensing chamber 45.
  • the displacement is transmitted to the main valve body 10 through the push rod 46, the sub valve body 17 and the like, whereby the valve opening degree (the separation distance between the valve port 22 and the main valve body portion 10a) is adjusted, and the valve The pressure Pc in the crank chamber is adjusted according to the opening degree.
  • the main valve body 10 is always urged upward by the urging force of the valve closing spring 50, and the sub valve body 17 is always urged downward by the urging force of the valve opening spring 47.
  • the valve body portion 17 a is in a state of being pressed against the sub valve seat portion 23 (the sub valve portion 12 is closed), and the in-valve release passage 16 is shut off in the main valve body 10. Therefore, the pressure Pc in the crank chamber does not escape to the suction chamber through the in-valve escape passage 16.
  • the solenoid unit 30A is energized and excited, and the plunger 37 and the sub valve body 17 are drawn together (upwardly) by the suction element 34, and the main valve body 10 follows the upward movement. Is moved upward, and after the valve port 22 is closed by the main valve body portion 10a of the main valve body 10, the plunger 37 and the sub valve body 17 are further moved upward, whereby the sub valve body 17 is moved. , And the pressure Pc in the crank chamber is released to the suction chamber through the valve release passage 16.
  • the biasing force of the valve closing spring 50 of the main valve body 10 causes the plunger 37 and the sub valve body 17 to It moves in the valve closing direction so as to follow the upward movement, and when the upward movement amount reaches the first lift amount La, the valve opening 22 is closed by the main valve body 10a of the main valve body 10 (see FIG. 2), the plunger 37 and the sub valve body 17 are further moved upward by the predetermined amount Ly from the closed state of the main valve portion 11 (state shown in FIG. 3).
  • the pressure Pc of the crank chamber is released to the suction chamber through the in-valve release passage 16 at the time of compressor start, so the discharge capacity is large at the time of compressor start. The time required to become can be greatly reduced. Further, at the time of normal control (during Pd ⁇ Pc control), the in-valve relief passage 16 is closed by the sub valve body 17, so that the operating efficiency of the compressor does not decrease.
  • the main valve body 10 guides the suction pressure Ps acting on the upper end portion of the main valve body 10 to the Ps introduction chamber 24A provided at the lower end portion of the main valve body 10 Since the suction pressure passage 14 for applying suction pressure Ps (always) to the lower end portion of the main valve body 10 is provided, for example, compared with the conventional one in which the suction pressure passage and the like are provided in the valve body, The influence of the refrigerant pressure acting on the main valve body 10 can be canceled without increasing the size of the body 20.
  • control valve 1 of the present embodiment is configured such that the suction pressure Ps is applied to the upper end portion of the main valve body 10 and Ps is introduced such that the suction pressure Ps is introduced to the lower end portion of the main valve body 10 Since the chamber 24A is provided and the main valve body 10 is provided with the suction pressure passage 14 for guiding the suction pressure Ps to the Ps introduction chamber 24A, the cross sectional area Ab of the lower insertion portion 10b of the main valve body 10, valve opening If the effective opening area Ac of 22 and the cross-sectional area Ad of the upper insertion portion 10d are made the same, the force applied in the valve opening direction by the refrigerant pressure acting on the main valve body 10 and the force applied in the valve closing direction are the same. Because the pressure is offset (canceled), the control by the pressure of the refrigerant acting on the main valve body 10 can be less likely to be adversely affected.
  • the main valve body 20 is constituted by a cylindrical member 10A having a main valve body portion 10a and the like, and an axial member 10B fitted and fixed to the cylindrical member 10A.
  • the cylindrical member 10A and the axial member 10B Since the suction pressure passage 14 is formed therebetween, the suction pressure passage 14 can be formed with a simple structure, and the influence of the refrigerant pressure acting on the main valve body 10 can be canceled.
  • Control valve 10 for variable displacement compressor Main valve body 10A Cylindrical member 10B Shaft-like member 10a Main valve body portion 10b Lower fitting portion 10c Middle small diameter portion 10d Upper fitting portion 10e Upper small diameter portion 10f Vertical groove 10k Wedge shape Locking part 11 Main valve part 12 Sub valve part 13 Fitting hole 13a Upper large diameter hole 13b Lower small diameter hole 14 Suction pressure passage 16 In-valve relief passage 16A Through escape hole 16a Vertical hole 16b Lateral hole 16b Through hole 17 Sub valve body 17a Valve body 17d Communication groove 18 Insertion hole 19B Lower guide hole 19C Lower hole 19D Upper guide hole 20 Valve body 20A Stopper 21 Valve chamber 22 Valve port 23 Sub valve seat 24 Lid guide member 24A Ps Introduction chamber 25 Pd introduction Port 26 Pc inlet / outlet 27 Ps inlet / outlet 28 Ps inlet / outlet chamber 30 electromagnetic actuator 30 A solenoid portion 32 coil 33 stator 34 suction element 7 plunger 37s slit 40 bellows arrangement (sensitive

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Magnetically Actuated Valves (AREA)
PCT/JP2019/000120 2018-01-29 2019-01-08 可変容量型圧縮機用制御弁 Ceased WO2019146388A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN201980010725.XA CN111670305A (zh) 2018-01-29 2019-01-08 可变容量型压缩机用控制阀
KR1020207024761A KR20200110440A (ko) 2018-01-29 2019-01-08 가변용량형 압축기용 제어밸브
US16/964,044 US20210048010A1 (en) 2018-01-29 2019-01-08 Variable-capacity compressor control valve
EP19743098.6A EP3748157A4 (en) 2018-01-29 2019-01-08 REGULATION VALVE FOR VARIABLE FLOW COMPRESSOR

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018012181A JP6906233B2 (ja) 2018-01-29 2018-01-29 可変容量型圧縮機用制御弁
JP2018-012181 2018-01-29

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WO2019146388A1 true WO2019146388A1 (ja) 2019-08-01

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US (1) US20210048010A1 (enExample)
EP (1) EP3748157A4 (enExample)
JP (1) JP6906233B2 (enExample)
KR (1) KR20200110440A (enExample)
CN (1) CN111670305A (enExample)
WO (1) WO2019146388A1 (enExample)

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JP2008223482A (ja) * 2007-03-08 2008-09-25 Tgk Co Ltd 可変容量圧縮機用制御弁
JP4550651B2 (ja) 2005-04-14 2010-09-22 株式会社不二工機 可変容量型圧縮機用制御弁
JP5553514B2 (ja) 2009-02-10 2014-07-16 株式会社不二工機 可変容量型圧縮機用制御弁

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JP4550651B2 (ja) 2005-04-14 2010-09-22 株式会社不二工機 可変容量型圧縮機用制御弁
JP2008223482A (ja) * 2007-03-08 2008-09-25 Tgk Co Ltd 可変容量圧縮機用制御弁
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EP3748157A1 (en) 2020-12-09
JP6906233B2 (ja) 2021-07-21
JP2019132132A (ja) 2019-08-08
CN111670305A (zh) 2020-09-15
KR20200110440A (ko) 2020-09-23
US20210048010A1 (en) 2021-02-18
EP3748157A4 (en) 2021-12-01

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