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WO2017057160A1 - Valve de régulation de compresseur à cylindrée variable - Google Patents

Valve de régulation de compresseur à cylindrée variable Download PDF

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Publication number
WO2017057160A1
WO2017057160A1 PCT/JP2016/077916 JP2016077916W WO2017057160A1 WO 2017057160 A1 WO2017057160 A1 WO 2017057160A1 JP 2016077916 W JP2016077916 W JP 2016077916W WO 2017057160 A1 WO2017057160 A1 WO 2017057160A1
Authority
WO
WIPO (PCT)
Prior art keywords
chamber
pressure
communication
valve
crank
Prior art date
Application number
PCT/JP2016/077916
Other languages
English (en)
Japanese (ja)
Inventor
幸生 風早
栄 林
Original Assignee
株式会社ヴァレオジャパン
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 株式会社ヴァレオジャパン filed Critical 株式会社ヴァレオジャパン
Priority to JP2017543203A priority Critical patent/JPWO2017057160A1/ja
Publication of WO2017057160A1 publication Critical patent/WO2017057160A1/fr

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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
    • 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
    • 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
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/126—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a diaphragm, bellows, or the like

Definitions

  • the present invention is attached to a variable capacity compressor used in a vehicle air conditioner or the like, and supplies the pressure in the discharge pressure region to the crank chamber and releases the pressure in the crank chamber to the suction pressure region.
  • the present invention relates to a control valve that controls
  • the control valve shown in FIG. 10 includes a valve chamber 102 that communicates with the extraction passage via the valve hole 101, a valve body 103 that is accommodated in the valve chamber 102 and opens and closes the valve hole 101, Connected via a pressure-sensitive rod 104 provided on one side and expanded / contracted according to the pressure of the fluid, and connected via a solenoid rod 106 provided on the other side of the valve body 103,
  • a solenoid unit 107 that applies electromagnetic force to the body 103, the solenoid unit 107 includes a plunger chamber 109 that houses a plunger 108 that contacts the solenoid rod 106, and a partition wall that partitions the plunger chamber 109 and the valve chamber 102
  • the solenoid rod guide hole 110 is provided in the solenoid rod guide hole 110, and the solenoid
  • the valve body 103 directly receives the valve hole 103 when the valve body 103 closes the valve hole 101.
  • the pressure receiving area of the internal pressure and the pressure receiving area of the pressure in the valve hole indirectly received by the valve body 103 via the pressure sensing rod 104 can be made the same. The influence can be eliminated, and the valve chamber 102 and the plunger chamber 109 which are adjacent to each other through the partition wall are in the same crank chamber pressure environment, so the valve body 103 closes the valve hole 101.
  • a space (valve hole) for introducing the discharge pressure (Pd) is arranged in the center, and a space (pressure sensing chamber) for introducing the suction pressure (Ps) is arranged on one side of the valve hole. Since the space (valve chamber) communicating with the crank chamber is arranged on the other side, the space for introducing the discharge pressure (Pd) and the space for introducing the suction pressure (Ps) are adjacent to each other.
  • the space (valve chamber) communicating with the crank chamber is arranged on the other side, the space for introducing the discharge pressure (Pd) and the space for introducing the suction pressure (Ps) are adjacent to each other.
  • the present invention has been made in view of such circumstances, and is a control valve that adjusts the pressure introduction amount from the discharge chamber to the crank chamber, and has a function of discharging pressure from the crank chamber to the suction chamber, and a discharge pressure introduction space.
  • the main object is to provide a control valve for a variable displacement compressor that can eliminate the inconvenience of refrigerant leakage into the suction pressure introduction space.
  • a control valve of a variable displacement compressor includes a housing, a drive shaft provided in the housing, a rotation angle with the drive shaft, and a variable inclination angle with respect to the drive shaft.
  • a plurality of reciprocating pistons, a compression chamber defined by the cylinder and the piston, a crank chamber formed on the anti-compression chamber side of the piston, and a suction stroke of the piston are sucked into the compression chamber.
  • this pressure control valve A pressure-sensitive member provided in the suction chamber communication chamber and extending and contracting in the axial direction based on the pressure in the suction chamber communication chamber; A through hole formed so as to penetrate a partition wall between the crank chamber communication chamber and the suction chamber communication chamber; A feeling of being displaced through the through-hole and axially displacing the inside of the through-hole based on the expansion and contraction of the pressure-sensitive member.
  • the pressure sensing rod is formed integrally with the discharge chamber communicating chamber, and is provided with a valve body that opens and closes the opening from the discharge chamber communicating chamber side to the crank chamber communicating chamber, Inside or inside the pressure-sensitive rod, all or part of a communication passage that allows communication from the crank chamber communication chamber to the suction chamber communication chamber is formed, When the pressure-sensitive member extends and is in contact with the pressure-sensitive rod, the contact portion between the pressure-sensitive member and the pressure-sensitive rod causes the crank chamber communication chamber to pass through the communication path to the suction chamber communication chamber.
  • valve body opens an opening from the discharge chamber communication chamber to the crank chamber communication chamber,
  • the pressure-sensitive member contracts and is separated from the pressure-sensitive rod
  • communication from the crank chamber communication chamber to the suction chamber communication chamber via the communication passage is opened, and the valve body causes the discharge chamber to The opening from the communication chamber to the crank chamber communication chamber is closed.
  • a crank chamber communication chamber is disposed in the center, a suction chamber communication chamber in which a pressure-sensitive member is accommodated is disposed on one side of the crank chamber communication chamber, and a discharge chamber communicates with the other side of the crank chamber communication chamber. Since the discharge chamber communication chamber into which the discharge pressure is introduced is arranged, the discharge chamber communication chamber into which the discharge pressure is introduced and the suction chamber communication chamber into which the suction pressure is introduced are not adjacent to each other, and the pressure sensitive rod It is possible to avoid the disadvantage that the refrigerant leaks from the discharge chamber pressure to the suction chamber pressure through the clearance of the sliding portion.
  • the length of the communication passage can be shortened, so that the workability is excellent. At the same time, it is possible to reduce the possibility of foreign matter accumulating and clogging in the communication path.
  • a solenoid portion is further provided at an end portion of the control valve on the discharge chamber communication chamber side.
  • the solenoid portion is a coil that generates an electromagnetic force in response to energization, and is attracted by the electromagnetic force.
  • a plunger chamber that accommodates the plunger so as to be movable in the axial direction.
  • the plunger chamber and the discharge chamber communication chamber communicate with each other via a solenoid-side through hole.
  • the solenoid rod is inserted into the solenoid-side through hole, and one end protrudes into the plunger chamber and contacts the plunger.
  • the plunger suction force is transmitted to the valve body via the solenoid rod, and the discharge chamber communication chamber is opened to the crank chamber communication chamber. The may be biased in a direction to close.
  • the degree of opening of the valve body that opens and closes the opening between the discharge chamber communication chamber and the crank chamber communication chamber depends on not only the suction pressure that expands and contracts the pressure-sensitive member but also the energization amount to the solenoid. It becomes possible to adjust.
  • the valve body that opens and closes the opening from the discharge chamber communication chamber to the crank chamber communication chamber, the pressure-sensitive member side through-hole, and one end of which is A pressure-sensitive rod that is positioned in the crank chamber communication chamber so as to be able to contact and separate from the valve body and that is displaced in the axial direction in the through hole based on expansion and contraction of the pressure-sensitive member; Forms a communication passage that allows communication from the crank chamber communication chamber to the suction chamber communication chamber, and when the pressure sensitive rod is in contact with the valve body by extension of the pressure sensitive member, A contact portion between the pressure rod and the valve body blocks communication from the crank chamber communication chamber to the suction chamber communication chamber via the communication passage, and the valve body is connected to the discharge chamber communication chamber from the crank chamber.
  • the pressure sensitive member When the pressure-sensitive rod is separated from the valve body by contraction, communication from the crank chamber communication chamber to the suction chamber communication chamber via the communication path is opened, and the discharge chamber communication chamber is opened by the valve body.
  • the opening to the crank chamber communication chamber may be closed.
  • valve body and the pressure-sensitive rod as separate members, the length of the valve forming body can be shortened, and the burden of management such as bending of the valve forming body can be reduced. It becomes possible.
  • the crank chamber communication chamber for introducing the crank chamber pressure is disposed in the center, and the suction chamber communication chamber in which the pressure sensing chamber is accommodated is disposed on one side of the crank chamber communication chamber.
  • a discharge chamber communication chamber into which discharge pressure is introduced is disposed on the other side of the crank chamber communication chamber, and a plunger housing chamber is disposed through the discharge chamber communication chamber.
  • the suction pressure is introduced from the discharge pressure introduction space through the clearance of the sliding portion of the valve forming body. There is no inconvenience that the refrigerant leaks into the introduction space.
  • the control valve is arranged in the radial direction from the peripheral surface of the housing.
  • the suction chamber and the Ps space suction chamber communication chamber
  • the discharge chamber and the Pd space discharge chamber communication chamber
  • FIG. 1 is a cross-sectional view showing a variable displacement compressor according to the present invention.
  • FIG. 2 is a cross-sectional view showing a first embodiment of a control valve used in a variable displacement compressor.
  • 3 is a cross-sectional view showing the movement of the control valve shown in FIG. 2, wherein (a) is a diagram showing the state of the control valve when the compressor is stopped, and (b) is a high load on the compressor. The figure which shows the state of the control valve at the time of driving
  • FIG. 4 is a diagram for explaining the positional relationship between the suction chamber and the discharge chamber when the control valve is attached to the rear head by inserting it in the radial direction from the peripheral wall.
  • FIG. 5 is a cross-sectional view showing a second embodiment of the control valve used in the variable displacement compressor. 6 is a cross-sectional view showing the movement of the control valve shown in FIG. 5, (a) is a diagram showing the state of the control valve when the compressor is stopped, and (b) is a high load on the compressor. The figure which shows the state of the control valve at the time of driving
  • FIG. 7 is a cross-sectional view showing a third embodiment of the control valve used in the variable displacement compressor.
  • 8 is a cross-sectional view showing the movement of the control valve shown in FIG. 7, where (a) is a diagram showing the state of the control valve when the compressor is stopped, and (b) is a high load on the compressor. The figure which shows the state of the control valve at the time of driving
  • FIG. 9 is a cross-sectional view showing a modification of the control valve shown in FIG.
  • FIG. 10 is a cross-sectional view showing a conventional control valve.
  • FIG. 11 is a cross-sectional view showing another conventional control valve.
  • FIG. 1 shows a variable capacity compressor according to the present invention.
  • the variable capacity compressor includes a cylinder block 1, a rear head 3 assembled on the rear side (right side in the figure) of the cylinder block 1 via a valve plate 2, and a front side (in the figure, The front head 5 is assembled so as to close the left side) and defines the crank chamber 4.
  • the front head 5, the cylinder block 1, the valve plate 2, and the rear head 3 are These are fastened in the axial direction by fastening bolts 6 to constitute a compressor housing.
  • the crank chamber 4 provided by the front head 5 and the cylinder block 1 accommodates a drive shaft 7 whose front end protrudes from the front head 5.
  • a drive pulley (not shown) is provided at a portion of the drive shaft 7 protruding from the front head 5 so that the rotational power applied to the drive pulley is transmitted to the drive shaft 7 via an electromagnetic clutch.
  • the front end side of the drive shaft 7 is hermetically sealed with the front head 5 through a seal member 11 provided between the front shaft 5 and is rotatably supported by a radial bearing 12.
  • the rear end side of the drive shaft 7 is rotatably supported via a radial bearing 14 that is accommodated in an accommodation hole 13 formed substantially at the center of the cylinder block 1.
  • the radial bearings 13 and 14 may be rolling bearings or plain bearings.
  • the cylinder block 1 is formed with an accommodation hole 13 in which the radial bearing 14 is accommodated, and a plurality of cylinder bores 15 arranged at equal intervals on the circumference around the accommodation hole 13. 15, a single-head piston 16 is inserted so as to be slidable back and forth.
  • a thrust flange 17 that rotates integrally with the drive shaft 7 is fixed to the drive shaft 7 in the crank chamber 4.
  • the thrust flange 17 is rotatably supported on the inner surface of the front head 5 via a thrust bearing 18, and a swash plate 20 is connected to the thrust flange 17 via a link member 19.
  • the swash plate 20 is provided so as to be tiltable about a hinge ball 21 slidably provided on the drive shaft 7, and is integrated with the rotation of the thrust flange 17 via the link member 19. It is designed to rotate. And the engaging part 16a of the single-headed piston 16 is moored by the peripheral part through the pair of shoes 22 at the swash plate 20.
  • the valve plate 2 is formed with suction holes 31 and discharge holes 32 corresponding to the respective cylinder bores 15, and the rear head 3 has a suction chamber 33 for storing the working fluid compressed in the compression chamber 23.
  • a discharge chamber 34 for accommodating the working fluid compressed and discharged in the compression chamber 23 is provided.
  • the suction chamber 33 is formed in a portion near the center of the rear head 3 and communicates with a suction port (not shown) that leads to the outlet side of the evaporator, and through the suction hole 31 that is opened and closed by a suction valve (not shown). Communication with the compression chamber 23 is possible.
  • the discharge chamber 34 is formed around the suction chamber 33 and can communicate with the compression chamber 23 through the discharge hole 32 opened and closed by a discharge valve (not shown), as well as the valve plate 2 and the cylinder. It communicates with a discharge space 35 formed in the peripheral wall portion of the cylinder block 1 through passages 2a, 1a formed in the block 1.
  • the discharge space 35 is defined by the cylinder block 1 and a cover 36 attached thereto.
  • the cover 36 has a discharge port 37 leading to the inlet side of the condenser, and the discharge space 35 from the condenser.
  • a check valve 38 for preventing the refrigerant from flowing backward is provided.
  • the discharge capacity of this compressor is determined by the stroke of the piston 16, and this stroke is determined by the inclination angle of the swash plate 20 with respect to the plane perpendicular to the drive shaft 7.
  • the inclination angle of the swash plate 20 depends on the moment resulting from the difference between the pressure in the compression chamber 23 (pressure in the cylinder bore) acting on each piston 16 and the pressure in the crank chamber 4, and the inertial force of the swash plate 20 and piston 16. Balance is made at an angle at which the sum of the moments derived from the moment and the moments derived from the biasing force of the destroke spring 24 that biases the hinge ball 21 becomes zero.
  • the piston stroke is determined and the discharge capacity is determined.
  • the discharge chamber 34 and the crank chamber 4 are communicated with each other by a passage 3b formed in the rear head 3, a through hole 2b formed in the valve plate 2, and a passage 1b formed in the cylinder block 1.
  • An air supply passage 40 is formed.
  • a bleed passage 41 for communicating the crank chamber 4 and the suction chamber 33 is formed through an orifice hole 2c formed in the valve plate 2 communicated with the communication hole 1c.
  • the oil separation passage 7c formed in the drive shaft 7 constituting a part of the bleed passage 41 is an axial passage formed on the axis of the drive shaft 7 from the rear end toward the front end to the vicinity of the front end.
  • the drive shaft is configured by a hole 7c-1 and a radial through hole 7c-2 that communicates with the axial through hole 7c-1 and is formed in the radial direction of the drive shaft 7 and opens into the crank chamber 4.
  • 7 has a function of separating oil from the working fluid flowing in from the radial through hole 7c-2 by the centrifugal force generated by the rotation of 7.
  • a control valve 50 is provided on the air supply passage 40, and the amount of refrigerant gas flowing from the discharge chamber 34 into the crank chamber 4 through the air supply passage 40 is adjusted by the control valve 50. . Further, the control valve 50 allows the refrigerant gas to be discharged from the crank chamber 4 to the suction chamber 33 (having a function as the auxiliary extraction passage 42).
  • the control valve 50 is configured by joining a valve main body 53 that accommodates a first valve forming body 51 and a second valve forming body 52 and a solenoid portion 54 via a joining member 55.
  • the valve main body 53 is configured by combining a valve housing 56 and a cylindrical outer cover member 57 that is fitted on the opposite side of the valve housing 56 from the solenoid portion 54.
  • a valve chamber 58 constituting a discharge chamber communication chamber defined between the solenoid portion 54 (a fixed iron core 71 described later) and an axial direction extending to the opposite side of the solenoid portion 54 following the valve chamber 58.
  • a pressure sensing chamber 60 constituting a suction chamber communication chamber defined between the valve hole 59 constituting the crank chamber communication chamber and the outer cover member 57 at the end opposite to the valve chamber 58.
  • a pressure-sensitive rod guide hole 61 constituting a through-hole penetrating the partition wall between the valve hole 59 and the pressure-sensitive chamber 60.
  • the cross-sectional area (diameter) of the valve hole 59 is formed smaller than the cross-sectional area (diameter) of the valve chamber 58, and the cross-sectional area (diameter) of the pressure-sensitive rod guide hole 61 is It is formed smaller than the area (diameter).
  • the valve housing 56 is formed with a pressure introduction port 62 communicating with the valve chamber 58.
  • the pressure introduction port 62 is formed in the radial direction so as to communicate with the valve chamber 58 from the outer peripheral surface of the valve housing 56 on the side close to the solenoid portion 54.
  • the opening on the outer peripheral surface of the pressure introduction port 62 communicates with the discharge chamber 34 via a passage 3b provided in a rear head that constitutes a part of the air supply passage. It is led to the valve chamber 58.
  • a pressure discharge port 63 is formed on the peripheral surface of the outer cover member 57 that defines the pressure sensing chamber 60.
  • the peripheral surface opening of the pressure exhaust passage 63 communicates with the suction chamber 33 through a passage 3d formed in the rear head constituting a part of the auxiliary bleed passage 42, whereby the refrigerant in the suction chamber 33 is The pressure is transmitted to the pressure sensing chamber 60 and the refrigerant in the pressure sensing chamber 60 is discharged to the suction chamber 33.
  • a small diameter is formed on the outer periphery of the valve housing 56 between the pressure introduction port 62 and the pressure discharge port 63 so as to form an annular small space with the inner wall of the housing when the control valve 50 is mounted on the compressor.
  • a portion 64 is formed. From the outer peripheral surface of the small diameter portion 64, a pressure adjusting port 65 penetrating in the radial direction and communicating with the valve hole 59 is formed.
  • the annular space formed by the small diameter portion 64 is formed in the passage 3b formed in the rear head that constitutes a part of the air supply passage, the through hole 2b formed in the valve plate, and the cylinder block 1.
  • the crank chamber 4 communicates with the passage 1b.
  • the first valve forming body 51 includes a valve body 511 accommodated in the valve chamber 58, extends in the axial direction on one end side of the valve body 511, and passes through the valve hole 59.
  • a pressure-sensitive rod 512 that slidably passes through a pressure-sensitive rod guide hole 61 that communicates with the pressure-sensitive chamber 60 and projects into the pressure-sensitive chamber 60, and extends in the axial direction on the other end side of the valve body 511.
  • a solenoid rod 513 that is slidably inserted through a solenoid rod guide hole 79 formed in a fixed iron core 71 of the solenoid portion 54 described later is integrated with a solenoid rod 513 that protrudes into the plunger chamber 76.
  • the valve body 511 is formed such that an end on one end (the stepped portion 511 a that moves to the pressure-sensitive rod 512 of the valve body 511) that faces the seat portion 59 a on the opening periphery of the valve hole 59 is larger than the diameter of the valve hole 59. Therefore, the valve hole 59 is closed by the end periphery of the valve body 511 coming into contact with the seat portion 59a at the opening periphery of the valve hole 59 (the valve body 511 has an opening from the valve chamber 58 to the valve hole 59). The valve hole 59 and the valve chamber 58 are disconnected from each other.
  • an enlarged diameter portion 511b having a larger diameter of the valve body 511 is formed on the other end side of the valve body 511, and between the enlarged diameter portion 511b and a portion outside the seat portion 59a of the valve housing 56.
  • An opening spring 66 is elastically mounted, and the opening spring 66 constantly urges the valve body 511 away from the seat portion 59a.
  • the pressure-sensitive rod 512 is integrally formed on the axial center of the valve body 511.
  • the pressure-sensitive rod 512 is formed following the valve body 511, and has a small-diameter portion 512a disposed in the valve hole 59, and the small-diameter portion 512a. And a large-diameter portion 512b that slides in the pressure-sensitive rod guide hole 61. Therefore, the large-diameter portion 512b of the pressure-sensitive rod 512 is formed to have a cross-sectional area (diameter) smaller than the cross-sectional area (diameter) of the valve hole 59, and the small-diameter portion 512a of the pressure-sensitive rod 512 is disposed in the valve hole 59.
  • the small diameter portion 512a does not contact the inner surface of the valve hole 59, and a passage for the refrigerant gas is secured.
  • the pressure-sensitive rod 512 includes a vertical hole 515a that is formed in the axial direction from the tip of the large-diameter portion 512b that protrudes into the pressure-sensitive chamber 60 to the small-diameter portion 512a, and the vertical hole 515a in the small-diameter portion 512a.
  • a communication passage 515 including a lateral hole 515 b penetrating in the radial direction so as to communicate is formed, and the valve hole 59 and the pressure sensing chamber 60 can communicate with each other via the communication passage 515.
  • a bellows 67 constituting a pressure sensitive member is accommodated in the pressure sensitive chamber 60.
  • the bellows 67 has one end joined to a fixed end member 68 fixed to the outer cover member 57, and the other end joined to a movable end member 69 slidably accommodated in the pressure sensitive chamber.
  • the inside of the bellows 67 is sealed with a vacuum or a predetermined working body so that predetermined expansion and contraction characteristics can be obtained with respect to ambient pressure.
  • an internal spring 70 is provided in the bellows 67 so as to give a predetermined spring load to the bellows.
  • the second valve forming body 52 is constituted by the movable end member 69 joined integrally with a bellows 67 accommodated in the pressure sensitive chamber 60. As the bellows 67 extend and contract, the movable end member 69 varies in distance from the tip of the pressure-sensitive rod 512, and adjusts the opening of the communication passage 515 opened at the tip of the pressure-sensitive rod 512. It has become.
  • a guide recess 56a in which the movable end member 69, which is the second valve forming body 52, slides in the axial direction is formed at the tip of the valve housing 56, and the pressure-sensitive rod 512 is formed in the guide recess 56a. Although it is provided so as to protrude, even when the movable end member 69 extends to a position where the pressure-sensitive rod 512 comes into contact with the guide recess 56a, the inside of the guide recess 56a communicates with the space that houses the bellows 67.
  • a communication groove 56b is formed in the peripheral wall of the guide recess 56a.
  • the solenoid portion 54 is fixed to the inside of the joining member 55, and the fixed iron core 71 that defines the valve chamber 58 together with the nozzle housing 56, the fixed iron core 71 is fitted to the opening end portion, and the fixed iron core 71
  • a bottomed cylindrical cylinder 72 having an open end fixed between the joining member 55, a bobbin 73 fixed around the cylinder 72, an exciting coil 74 wound around the bobbin 73, a bobbin 73 and a cylindrical case 75 that is fixed to the outer peripheral surface of the joining member 55 so as to cover the periphery of the exciting coil 74 and caulks the lower end of the bobbin 73, and a plunger chamber 76 defined between the cylinder 72 and the fixed iron core 71.
  • the plunger 77 is arranged coaxially with the fixed iron core 71 and is slidably received in the plunger chamber 76, and is elastically mounted between the plunger 77 and the bottom of the cylinder 72. It is configured to include a sub spring 78.
  • reference numeral 89 denotes a lead wire for supplying a current to the exciting coil 74.
  • the fixed iron core 71 is formed with a solenoid rod guide hole 79 that allows the valve chamber 58 and the plunger chamber 76 to communicate with each other.
  • the solenoid rod 513 of the first valve forming body 51 is formed on the axial center of the valve body 511.
  • the solenoid rod guide hole 79 is slidably inserted and protrudes into the plunger chamber 76, and the tip thereof is in contact with the top of the plunger 77 urged by the follower spring 78.
  • the sectional area (diameter) of the solenoid rod guide hole 79 is formed to be equal to the sectional area (diameter) of the valve hole 59, and the spring load of the follower spring 78 is the spring load of the release spring 66. Is set smaller than.
  • a communication groove 80 extending in the axial direction is formed on the side surface of the fixed iron core 71, and a communication hole 81 communicating with the communication groove 80 is formed in the valve housing 56 in the axial direction.
  • the communication hole 81 communicates the plunger chamber 76 and the recess 64, and a balance passage 82 is formed which communicates the plunger chamber 76 with a portion communicating with the crank chamber 4. Therefore, due to the balance passage 82, the plunger chamber 76 and the valve hole 59 are under the same pressure environment, and in this example, the crank chamber pressure Pc is set.
  • the valve body 511 has the plunger 71 against the spring load of the follower spring 78 via the solenoid rod 513 of the first valve forming body 51, and the bottom of the cylinder 72.
  • the valve hole 59 is maintained in the open state (the valve body 511 sets the opening from the valve chamber 58 to the valve hole 59 in the open state). Therefore, the pressure introduction port 62 communicates with the pressure adjustment port 65 via the valve chamber 58 and the valve hole 59, and the air supply passage 40 is opened.
  • the suction chamber pressure Ps becomes higher than that during the operation of the compressor, and the bellows (pressure-sensitive portion) 67 contracts to form the second valve forming body 52 ( The movable end member 69) is separated from the tip of the pressure-sensitive rod 512 of the first valve forming body 51, and the communication path 515 is maintained in the open state. Therefore, the pressure adjustment port 65 and the pressure discharge port 63 communicate with each other through the valve hole 59, the communication passage 515, and the pressure sensing chamber 60, and the auxiliary extraction passage 42 is opened.
  • the bellows (pressure-sensitive part) 67 contracts and the second valve forming body 52 (movable end member). 69) is separated from the tip of the pressure-sensitive rod 512 of the first valve forming body 51, and the communication passage 515 is opened (the auxiliary bleed passage 42 is opened).
  • the air supply passage 40 is closed when the valve body 511 closes the valve hole 59, so that the high-pressure refrigerant is not supplied to the crank chamber 4, while the refrigerant in the crank chamber 4 passes through the auxiliary extraction passage 42 (pressure adjustment port 65 ⁇ Valve hole 59 ⁇ Communication passage 515 ⁇ Pressure sensing chamber 60 ⁇ Pressure exhaust port 63) to be discharged into the suction chamber 33. Therefore, in addition to the pressure discharge of the crank chamber 4 by the bleed passage 41 of the compressor, the pressure of the crank chamber 4 is discharged through the auxiliary bleed passage 42, so that the compressor is quickly started (returned).
  • the plunger chamber 76 and a portion (valve hole 59) communicating with the crank chamber 4 communicate with each other via the balance passage 82, so that the high-pressure refrigerant flows from the valve chamber 58 to the solenoid rod 513 and the solenoid rod guide hole 79. Even if it leaks into the plunger chamber 76 through the clearance between them, the pressure of the plunger chamber 76 can be kept at the crank chamber pressure, and the influence of the discharge chamber pressure (Pd) acting on the valve body 511 can be eliminated. It becomes possible.
  • the pressure arrangement from the valve body 53 to the solenoid 54 is as follows: pressure sensing chamber (Ps) ⁇ valve hole (Pc) ⁇ valve chamber (Pd) ⁇ plunger chamber (Pc) Therefore, it is easy to form a passage communicating the pressure sensing chamber 60 and the suction chamber 33 and a passage communicating the valve chamber 58 and the discharge chamber 34. That is, in FIG. 1, for convenience of explanation, the air supply passage 40 and the auxiliary bleed passage 42 are schematically described so as to be seen in a plan view, but the suction chamber 33 is disposed near the center of the rear head 3, In the rear head 3 in which the discharge chamber 34 is actually arranged on the radially outer side, as shown in FIG.
  • the suction chamber 33 and the valve chamber 58 and the discharge chamber 34 can be brought close to each other, it is easy to form a passage connecting them. Furthermore, in the configuration example described above, the communication passage 515 formed in the first valve forming body 51 is formed only in the pressure-sensitive rod 512 (formed between the pressure-sensitive chamber 60 and the valve hole 59). Therefore, the passage length of the communication passage 515 can be shortened, the workability is excellent, and the possibility that foreign matter accumulates in the communication passage 515 and becomes clogged can be reduced.
  • a second embodiment of the control valve 50 according to the present invention is shown.
  • the communication path 515 formed in the first valve forming body 51 is different from the first embodiment.
  • the communication passage 515 has a total length from one end to the other end (so as to penetrate the pressure-sensitive rod 512, the valve body 511, and the solenoid rod 513 in the axial direction) at the axial center of the first valve forming body 51.
  • the plunger chamber 76 and the pressure sensitive chamber 60 can communicate with each other. That is, the pressure sensing chamber 60 can be communicated with a portion (valve hole 59) communicating with the crank chamber 4 via the communication passage 515, the plunger chamber 76, and the balance passage 82.
  • valve chamber 58 which is the introduction space for the discharge chamber pressure (Pd)
  • the pressure sensing chamber 60 which is the introduction space for the suction chamber pressure (Ps). It is possible to eliminate the leakage of the refrigerant from 58 to the pressure sensitive chamber 60.
  • the plunger chamber 76 and a portion (valve hole 59) communicating with the crank chamber 4 communicate with each other via the balance passage 82, so that the high-pressure refrigerant flows from the valve chamber 58 to the solenoid rod 513 and the solenoid rod guide hole 79.
  • the pressure in the plunger chamber 76 can be kept at the crank chamber pressure, and the influence of the discharge chamber pressure (Pd) acting on the valve body 511 can be eliminated. It becomes. Further, in this example, since it is not necessary to machine a lateral hole in the valve body 511, it is possible to avoid a decrease in the strength of the small diameter portion 512a of the pressure-sensitive rod 512 that is particularly concerned about a decrease in the strength of the first valve forming body 51. It becomes possible.
  • FIG. 7 and 8 show a third embodiment of the control valve according to the present invention.
  • the contact position of the first valve forming body 51 and the second valve forming body 52 is changed with respect to the configuration of the first embodiment.
  • the first valve forming body 51 includes the valve body 511 and the solenoid rod 513.
  • the second valve forming body 52 includes a movable end member 69 connected to the bellows 67 and a pressure-sensitive rod 69a integrally formed therewith and extending toward the first valve forming body 52. Yes.
  • the pressure sensing rod 69a is slidably inserted through the pressure sensing rod guide hole 61 that communicates the valve hole 59 and the pressure sensing chamber 60, and is set to a length that projects into the valve hole 59.
  • the tip of the valve body 511 of the forming body 51 can be brought into contact with and separated from the valve hole 59.
  • the pressure-sensitive rod 69a has a vertical hole 515a drilled in the axial direction from the front end facing the valve body 511, and the pressure-sensitive chamber 60 and the vertical hole in a state where the pressure-sensitive rod 69a is separated from the front end portion of the valve body 511.
  • a communication path 515 is formed which includes a lateral hole 515 b communicating with 515 a, and the communication path 515 is opened and closed by the tip of the valve body 511. Since other configurations are the same as those of the first embodiment, the same portions are denoted by the same reference numerals and description thereof is omitted.
  • valve chamber 58 which is the introduction space for the discharge chamber pressure (Pd)
  • pressure sensing chamber 60 which is the introduction space for the suction chamber pressure (Ps). It becomes possible to eliminate the leakage of the refrigerant into the chamber 60.
  • the plunger chamber 76 and a portion (valve hole 59) communicating with the crank chamber 4 communicate with each other via the balance passage 82, so that the high-pressure refrigerant flows from the valve chamber 58 to the solenoid rod 513 and the solenoid rod guide hole 79.
  • the contact portion between the first valve forming body 51 and the second valve forming body 52 is a part of the valve hole 59, the length of each valve forming body can be shortened, and the valve forming body It becomes possible to reduce the burden of management such as bending.
  • the pressure-sensitive rod 69a is integrated with the movable end member 69 fixed to the bellows 67.
  • the pressure-sensitive rod 69a is movable as in the modification shown in FIG.
  • a spring receiving portion 69b is provided around the portion facing the movable end member 69, separately from the end member 69, and a compression spring 90 is provided between the spring receiving portion 69b and the bottom surface of the guide recess 56a of the valve housing 56.
  • the pressure-sensitive rod 69a may always be brought into contact with the movable end member 69 by interposing the above.

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

Abstract

L'invention aborde le problème de la réalisation d'une fonction de décharge de pression d'une chambre de vilebrequin vers une chambre d'aspiration et d'élimination d'une fuite d'un espace d'introduction de pression de décharge vers un espace d'introduction de pression d'aspiration dans une valve de régulation destinée à ajuster une quantité d'introduction de pression d'une chambre de décharge vers une chambre de vilebrequin. L'invention réalise à cet effet une valve de régulation (50) qui comprend : une chambre de valve (58) (chambre de connexion de chambre de valve) qui se connecte à une chambre de décharge ; un trou de valve (59) (chambre de connexion de chambre de vilebrequin) qui est disposé à proximité de la chambre de valve (58) dans le sens axial et se raccorde à une chambre de vilebrequin ; et une chambre sensible à la pression (60) (chambre de connexion de chambre d'aspiration) qui est formée sur un côté opposé à la chambre de valve (58) dans le sens axial par rapport au trou de valve (59) par l'intermédiaire d'une paroi de séparation et se connecte à la chambre d'aspiration. La valve de régulation (50) comprend : un soufflet (67) (élément sensible à la pression) qui est disposé dans la chambre sensible à la pression (60) et se déploie et se contracte sous l'effet de la pression à l'intérieur de la chambre sensible à la pression ; un trou de guidage de tige sensible à la pression (61) (trou traversant) qui est formé dans la paroi de séparation ; une tige sensible à la pression (512) qui déplace le trou de guidage de tige sensible à la pression (61) en accompagnement du déploiement et de la contraction du soufflet (67) ; un corps de valve (51) qui est logé dans la chambre de valve (58) et qui ouvre et ferme une ouverture depuis la chambre de valve (58) vers le trou de valve (59) ; et un trajet de connexion (515) qui est formé dans la tige sensible à la pression (512) et permet de connecter le trou de valve (59) et la chambre sensible à la pression (60).
PCT/JP2016/077916 2015-09-29 2016-09-22 Valve de régulation de compresseur à cylindrée variable WO2017057160A1 (fr)

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Cited By (31)

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WO2019167912A1 (fr) * 2018-02-27 2019-09-06 イーグル工業株式会社 Soupape de réglage de capacité
WO2020116436A1 (fr) * 2018-12-04 2020-06-11 イーグル工業株式会社 Vanne à commande de déplacement
WO2020116435A1 (fr) * 2018-12-04 2020-06-11 イーグル工業株式会社 Vanne à commande de déplacement
JPWO2020204135A1 (fr) * 2019-04-03 2020-10-08
JPWO2020204134A1 (fr) * 2019-04-03 2020-10-08
US11156301B2 (en) 2018-01-26 2021-10-26 Eagle Industry Co., Ltd. Capacity control valve
US11225962B2 (en) 2018-05-23 2022-01-18 Eagle Industry Co., Ltd. Capacity control valve
US11319940B2 (en) 2018-02-15 2022-05-03 Eagle Industry Co., Ltd. Capacity control valve
US11378194B2 (en) 2018-11-07 2022-07-05 Eagle Industry Co., Ltd. Capacity control valve
US11401923B2 (en) 2018-02-15 2022-08-02 Eagle Industry Co., Ltd. Capacity control valve
US11473683B2 (en) 2018-08-08 2022-10-18 Eagle Industry Co., Ltd. Capacity control valve
US11480166B2 (en) 2018-07-13 2022-10-25 Eagle Industry Co., Ltd. Capacity control valve
US11536257B2 (en) 2018-07-12 2022-12-27 Eagle Industry Co., Ltd. Capacity control valve
US11555489B2 (en) 2018-07-12 2023-01-17 Eagle Industry Co., Ltd. Capacity control valve
US11598437B2 (en) 2019-03-01 2023-03-07 Eagle Industry Co., Ltd. Capacity control valve
US11802552B2 (en) 2019-07-12 2023-10-31 Eagle Industry Co., Ltd. Capacity control valve
US11821540B2 (en) 2019-04-03 2023-11-21 Eagle Industry Co., Ltd. Capacity control valve
US11841090B2 (en) 2019-04-03 2023-12-12 Eagle Industry Co., Ltd. Capacity control valve
US11873805B2 (en) 2018-08-08 2024-01-16 Eagle Industry Co., Ltd. Capacity control valve
US11927275B2 (en) 2019-04-03 2024-03-12 Eagle Industry Co., Ltd. Capacity control valve
US11988296B2 (en) 2019-04-24 2024-05-21 Eagle Industry Co., Ltd. Capacity control valve
US11994120B2 (en) 2018-07-12 2024-05-28 Eagle Industry Co., Ltd. Capacity control valve
US12012948B2 (en) 2018-08-08 2024-06-18 Eagle Industry Co., Ltd. Capacity control valve
US12018663B2 (en) 2020-04-23 2024-06-25 Eagle Industry Co., Ltd. Capacity control valve
US12025237B2 (en) 2020-05-25 2024-07-02 Eagle Industry Co., Ltd. Capacity control valve
US12031531B2 (en) 2019-04-24 2024-07-09 Eagle Industry Co., Ltd. Capacity control valve
US12072035B2 (en) 2019-04-03 2024-08-27 Eagle Industry Co., Ltd. Capacity control valve
US12110882B2 (en) 2020-05-25 2024-10-08 Eagle Industry Co., Ltd. Capacity control valve
US12129840B2 (en) 2019-10-28 2024-10-29 Eagle Industry Co., Ltd. Capacity control valve
DE112018002801B4 (de) 2017-05-30 2024-11-07 Hanon Systems Steuerventil für einen Verdichter variabler Kapazität mit mehreren Ventilbohrungen zwischen Kurbelkammer und Ansaugkammer
US12140243B2 (en) 2019-04-24 2024-11-12 Eagle Industry Co., Ltd. Capacity control valve

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Cited By (49)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112018002801B4 (de) 2017-05-30 2024-11-07 Hanon Systems Steuerventil für einen Verdichter variabler Kapazität mit mehreren Ventilbohrungen zwischen Kurbelkammer und Ansaugkammer
US11156301B2 (en) 2018-01-26 2021-10-26 Eagle Industry Co., Ltd. Capacity control valve
US11319940B2 (en) 2018-02-15 2022-05-03 Eagle Industry Co., Ltd. Capacity control valve
US11401923B2 (en) 2018-02-15 2022-08-02 Eagle Industry Co., Ltd. Capacity control valve
JP7139084B2 (ja) 2018-02-27 2022-09-20 イーグル工業株式会社 容量制御弁
JPWO2019167912A1 (ja) * 2018-02-27 2021-02-04 イーグル工業株式会社 容量制御弁
US11873804B2 (en) 2018-02-27 2024-01-16 Eagle Industry Co., Ltd. Capacity control valve
WO2019167912A1 (fr) * 2018-02-27 2019-09-06 イーグル工業株式会社 Soupape de réglage de capacité
US11225962B2 (en) 2018-05-23 2022-01-18 Eagle Industry Co., Ltd. Capacity control valve
US11536257B2 (en) 2018-07-12 2022-12-27 Eagle Industry Co., Ltd. Capacity control valve
US11994120B2 (en) 2018-07-12 2024-05-28 Eagle Industry Co., Ltd. Capacity control valve
US11555489B2 (en) 2018-07-12 2023-01-17 Eagle Industry Co., Ltd. Capacity control valve
US11480166B2 (en) 2018-07-13 2022-10-25 Eagle Industry Co., Ltd. Capacity control valve
US11873805B2 (en) 2018-08-08 2024-01-16 Eagle Industry Co., Ltd. Capacity control valve
US11473683B2 (en) 2018-08-08 2022-10-18 Eagle Industry Co., Ltd. Capacity control valve
US12012948B2 (en) 2018-08-08 2024-06-18 Eagle Industry Co., Ltd. Capacity control valve
US11378194B2 (en) 2018-11-07 2022-07-05 Eagle Industry Co., Ltd. Capacity control valve
JP7326329B2 (ja) 2018-12-04 2023-08-15 イーグル工業株式会社 容量制御弁
US11391388B2 (en) 2018-12-04 2022-07-19 Eagle Industry Co., Ltd. Capacity control valve
CN113167263A (zh) * 2018-12-04 2021-07-23 伊格尔工业股份有限公司 容量控制阀
JP7326330B2 (ja) 2018-12-04 2023-08-15 イーグル工業株式会社 容量制御弁
US11473684B2 (en) 2018-12-04 2022-10-18 Eagle Industry Co., Ltd. Capacity control valve
JPWO2020116436A1 (ja) * 2018-12-04 2021-10-21 イーグル工業株式会社 容量制御弁
JPWO2020116435A1 (ja) * 2018-12-04 2021-10-21 イーグル工業株式会社 容量制御弁
WO2020116435A1 (fr) * 2018-12-04 2020-06-11 イーグル工業株式会社 Vanne à commande de déplacement
WO2020116436A1 (fr) * 2018-12-04 2020-06-11 イーグル工業株式会社 Vanne à commande de déplacement
US11598437B2 (en) 2019-03-01 2023-03-07 Eagle Industry Co., Ltd. Capacity control valve
CN113646531A (zh) * 2019-04-03 2021-11-12 伊格尔工业股份有限公司 容量控制阀
WO2020204135A1 (fr) * 2019-04-03 2020-10-08 イーグル工業株式会社 Soupape de commande de capacité
US11754194B2 (en) 2019-04-03 2023-09-12 Eagle Industry Co., Ltd. Capacity control valve
JPWO2020204135A1 (fr) * 2019-04-03 2020-10-08
US11821540B2 (en) 2019-04-03 2023-11-21 Eagle Industry Co., Ltd. Capacity control valve
US11841090B2 (en) 2019-04-03 2023-12-12 Eagle Industry Co., Ltd. Capacity control valve
CN113661322A (zh) * 2019-04-03 2021-11-16 伊格尔工业股份有限公司 容量控制阀
US12072035B2 (en) 2019-04-03 2024-08-27 Eagle Industry Co., Ltd. Capacity control valve
JP7419349B2 (ja) 2019-04-03 2024-01-22 イーグル工業株式会社 容量制御弁
JP7423169B2 (ja) 2019-04-03 2024-01-29 イーグル工業株式会社 容量制御弁
US11927275B2 (en) 2019-04-03 2024-03-12 Eagle Industry Co., Ltd. Capacity control valve
US20220213877A1 (en) * 2019-04-03 2022-07-07 Eagle Industry Co., Ltd. Capacity control valve
WO2020204134A1 (fr) * 2019-04-03 2020-10-08 イーグル工業株式会社 Soupape de régulation de capacité
JPWO2020204134A1 (fr) * 2019-04-03 2020-10-08
US11988296B2 (en) 2019-04-24 2024-05-21 Eagle Industry Co., Ltd. Capacity control valve
US12031531B2 (en) 2019-04-24 2024-07-09 Eagle Industry Co., Ltd. Capacity control valve
US12140243B2 (en) 2019-04-24 2024-11-12 Eagle Industry Co., Ltd. Capacity control valve
US11802552B2 (en) 2019-07-12 2023-10-31 Eagle Industry Co., Ltd. Capacity control valve
US12129840B2 (en) 2019-10-28 2024-10-29 Eagle Industry Co., Ltd. Capacity control valve
US12018663B2 (en) 2020-04-23 2024-06-25 Eagle Industry Co., Ltd. Capacity control valve
US12025237B2 (en) 2020-05-25 2024-07-02 Eagle Industry Co., Ltd. Capacity control valve
US12110882B2 (en) 2020-05-25 2024-10-08 Eagle Industry Co., Ltd. Capacity control valve

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