JP2017014928A - Control valve for compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a control valve for compressor capable of suppressing malfunction of a valve body caused by a foreign substance mixed in a fluid.SOLUTION: A control valve 50 for compressor includes: a valve housing; a valve storage hole 51H provided at the valve housing; a valve body 80 capable of reciprocating in the valve storage hole 51H; and a pressure sensitive mechanism 73 for reciprocating the valve body 80 according to the pressure in a pressure sensitive chamber 73. In the valve housing, a valve seat 79, an upstream side space 72 located on the further upstream side than the valve seat 79 in a control passage, and a downstream side space 78 located on the further downstream side than the valve seat 79 in the control passage are formed. The valve body 80 includes: a valve part 81 which can be seated on the valve seat 79; a substantially columnar partition part 83 for partitioning between the pressure sensitive chamber 73 and the upstream side space 72 by sliding with an inner peripheral surface 70S of the valve storage hole 51H; and a connection part 82 for connecting the valve part 81 and the partition part 83. On a first end surface 83E on the connection part 82 side of the partition part 83, an annular first groove 91 is formed so as to dent toward the central side from an outer edge 83A side.SELECTED DRAWING: Figure 8

Description

  The present invention relates to a control valve for a compressor.

  For example, as shown in FIG. 11, a conventional compressor control valve disclosed in Patent Document 1 adjusts the opening of an air supply passage 940 that communicates a crank chamber and a discharge chamber. The crank chamber pressure is controlled, and the discharge capacity of the compressor is controlled. This compressor control valve is provided in the valve housing 950C, communicates with a suction chamber, a valve body 980 that opens and closes an air supply passage 940, a solenoid that changes a load applied to the valve body 980 according to an input current value, and the like. And a pressure-sensitive mechanism that changes the applied load of the valve body 980 according to the pressure of the pressure-sensitive chamber 973.

  The valve body 980 is connected to the valve seat 981 formed in the valve housing 950C and is slidable into contact with the inner peripheral surface 970S of the valve housing 950C and connected to the pressure sensing mechanism, and is pressure sensitive. It has a partition part 983 that partitions between the chamber and the air supply passage 940, and a connecting part 982 that connects the valve part 981 and the partition part 983. The connecting portion 982 has a smaller diameter than the valve portion 981 and the partition portion 983.

  A tapered surface 991 </ b> A is formed on the end surface 983 </ b> E of the partition part 983 connected to the coupling part 982. Between the inner peripheral surface 970S of the valve housing 950C and the tapered surface 991A, a space A901 having a wedge-shaped cross section that becomes narrower as the pressure sensitive chamber 973 is approached is formed.

JP 2002-39059 A

  By the way, in the conventional compressor control valve, when the valve portion 981 is separated from the valve seat 979 and the fluid flows in the air supply passage 940, fluid stagnation easily occurs in the space A901 having a wedge-shaped cross section. The foreign matter P1 mixed in the fluid tends to accumulate in the space A901. In this state, after the valve portion 981 is seated on the valve seat 979, when the valve portion 981 is separated from the valve seat 979, the foreign matter P1 collected in the wedge-shaped space A901 is the inner peripheral surface 970S of the valve housing 950C. And the end face 983E of the partition part 983, there is a possibility that the valve body 980 may malfunction.

  This invention is made | formed in view of the said conventional situation, Comprising: It is the problem which should be solved to provide the control valve for compressors which can suppress the malfunctioning of the valve body by the foreign material mixed in the fluid.

The compressor control valve of the present invention is used in a compressor body having a high pressure chamber and a low pressure chamber, and having a control pressure chamber communicating with the high pressure chamber or the low pressure chamber via a control passage. In the control valve for the compressor that controls the discharge capacity of the compressor body by adjusting the opening,
A valve housing;
A valve housing hole provided in the valve housing;
A valve body extending including a central region of the valve accommodation hole and capable of reciprocating in the valve accommodation hole;
A pressure-sensitive chamber in communication with the low-pressure chamber, and a pressure-sensitive mechanism for reciprocating the valve body in accordance with the pressure in the pressure-sensitive chamber;
A valve seat on which the valve body can be seated;
An upstream space located upstream of the valve seat in the control passage;
A downstream space located downstream from the valve seat in the control passage,
The valve body includes a valve portion that can be seated on the valve seat;
A substantially cylindrical partition section that slidably contacts the inner peripheral surface of the valve housing hole and partitions the pressure-sensitive chamber and the upstream space;
A connecting portion that connects the valve portion and the partition portion;
The first end surface of the partition part on the connection part side is formed to be recessed from the outer edge side toward the center side.

  In the compressor control valve according to the present invention, the first end surface of the partition portion on the connection portion side is formed so as to be recessed from the outer edge side toward the center side. It becomes a scraper shape with respect to the inner peripheral surface of the hole. For this reason, when the valve part is separated from the valve seat, the first end edge of the partition part peels off the foreign matter from the inner peripheral surface of the valve accommodating hole, the foreign matter is guided to the first end face, and the first end face It is collected in the dent. As a result, it is difficult for foreign matter to be caught between the inner peripheral surface of the valve accommodation hole and the first end edge of the partition portion.

  Therefore, in the control valve for a compressor of the present invention, it is possible to suppress malfunction of the valve body due to foreign matter mixed in the fluid. In addition, when a filter for removing foreign matter from the fluid is provided in the compressor body, the mesh size of the filter can be increased, so that pressure loss due to the filter can be reduced.

  It is desirable that the valve housing hole has a cylindrical shape and extends in the axial direction. It is desirable that the valve portion, the connecting portion, and the partition portion have a columnar shape and can reciprocate in the axial direction. It is desirable that the connecting part has a smaller diameter than the partition part. And it is desirable for the 1st end surface to form the annular | circular shaped 1st groove | channel recessed so that it may approach a pressure sensitive chamber centering on an axial center. According to this structure, it is easy to form a valve accommodation hole and a valve body, and it is easy to form a 1st groove | channel in a 1st end surface.

  The first groove desirably includes a first reverse tapered surface that approaches the pressure-sensitive chamber while reducing the diameter from the outer edge of the first end surface. According to this configuration, the scraper shape of the first edge in the partition portion is further clarified by the first reverse tapered surface, so that the first edge surely removes foreign matter from the inner peripheral surface of the valve housing hole. Can demonstrate.

  The valve body desirably has a pressure-sensitive rod portion that protrudes into the pressure-sensitive chamber integrally with the partition portion on the side opposite to the connecting portion and that can enter the valve housing hole. And it is desirable to form the 2nd end surface by the side of the pressure-sensitive rod part of a division part so that it may dent toward the center side from an outer edge side.

  In this case, since the second end surface of the partition portion on the pressure-sensitive rod portion side is formed to be recessed from the outer edge side toward the center side, the second end edge of the partition portion is the inner peripheral surface of the valve housing hole. Scraper shape. For this reason, when the valve portion is seated on the valve seat, the second end edge of the partition portion peels off the foreign matter from the inner peripheral surface of the valve housing hole, and the foreign matter is guided to the second end surface, so that the second end surface is recessed. To be collected. As a result, it is difficult for foreign matter to be caught between the inner peripheral surface of the valve housing hole and the second end edge of the partition portion.

  It is desirable that the valve housing hole has a cylindrical shape and extends in the axial direction. It is desirable that the valve portion, the connecting portion, the partition portion, and the pressure-sensitive rod portion have a cylindrical shape and can reciprocate in the axial direction. It is desirable that the pressure-sensitive rod portion has a smaller diameter than the partition portion. And it is desirable for the 2nd end surface to form the annular | circular shaped 2nd groove | channel recessed so that it may space apart from a pressure sensitive chamber centering on an axial center. According to this structure, it is easy to form a valve accommodation hole and a valve body, and it is easy to form a 2nd groove | channel in a 2nd end surface.

  It is desirable that the second groove includes a second reverse tapered surface that is reduced in diameter from the outer edge of the second end surface and is separated from the pressure sensitive chamber. According to this configuration, the scraper shape of the second end edge in the partition portion is further clarified by the second reverse taper surface, so that the second end edge reliably removes foreign matter from the inner peripheral surface of the valve housing hole. Can demonstrate.

  The compressor main body is supported by a main body housing in which a suction chamber, a discharge chamber, a crank chamber and a cylinder bore are formed, a drive shaft rotatably supported in the crank chamber, and a drive shaft rotatably in the crank chamber. And a swash plate that is supported so that the inclination angle can be changed, and a piston that forms a compression chamber in the cylinder bore and reciprocates in the cylinder bore by the swash plate, and has a variable displacement swash plate compressor together with a control valve for the compressor It is desirable to constitute. The high pressure chamber is preferably a discharge chamber, the low pressure chamber is a suction chamber, and the control pressure chamber is preferably a crank chamber communicating with the discharge chamber via a control passage.

  According to this configuration, the compressor control valve adjusts the opening degree of the control passage that connects the crank chamber and the discharge chamber by reciprocating movement of the valve element driven by the pressure-sensitive mechanism. As a result, in the compressor main body, fluid appropriately flows from the high-pressure discharge chamber to the crank chamber via the upstream space and the downstream space, the pressure in the crank chamber changes, and the inclination angle of the swash plate is changed. The As a result, the discharge capacity of the variable capacity swash plate compressor is changed.

  In this compressor control valve, when the variable displacement swash plate compressor is in operation, the upstream side space communicating with the high pressure discharge chamber, the low pressure suction chamber, with the valve portion seated on the valve seat, Due to the pressure difference between the pressure sensing chamber and the communicating pressure chamber, foreign matter may accumulate on the first edge of the partition part. However, the foreign matter is separated from the inner peripheral surface of the valve housing hole and the partition by the action of the depression of the first end surface described above. It is difficult to bite between the first end edge of the part.

  In addition, in this compressor control valve, there is a possibility that foreign matter may accumulate on the second edge of the partition part during vacuuming when the variable capacity swash plate compressor is assembled to an air conditioner or the like. 2 Due to the action of the recesses on the opposite side, the foreign matter is not easily caught between the inner peripheral surface of the valve housing hole and the second end edge of the partition part.

  The compressor control valve of the present invention can suppress the malfunction of the valve body due to foreign matter mixed in the fluid.

FIG. 1 is a sectional view of a variable displacement swash plate compressor in which the compressor control valve of the first embodiment is used. FIG. 2 is a cross-sectional view of the compressor control valve according to the first embodiment. FIG. 3 is a partial cross-sectional view of the compressor control valve according to the first embodiment. FIG. 4 is an enlarged cross-sectional view of a main part showing the periphery of the first groove in the compressor control valve according to the first embodiment. FIG. 5 is a partial perspective view illustrating the periphery of the first groove in the valve body according to the compressor control valve of the first embodiment. FIG. 6 is an enlarged cross-sectional view of a main part illustrating the operation of the valve body and the first groove in the compressor control valve according to the first embodiment. FIG. 7 is an enlarged cross-sectional view of a main part illustrating the operation of the valve body and the first groove in the compressor control valve according to the first embodiment. FIG. 8 is an enlarged cross-sectional view of a main part for explaining the operation of the valve body and the first groove in the compressor control valve according to the first embodiment. FIG. 9 is an enlarged cross-sectional view of a main part illustrating the operation of the valve body and the second groove in the compressor control valve according to the second embodiment. FIG. 10 is an enlarged cross-sectional view of a main part for explaining the operation of the valve body and the second groove in the compressor control valve according to the second embodiment. FIG. 11 is an enlarged cross-sectional view of a main part of a conventional compressor control valve.

  Embodiments 1 and 2 embodying the present invention will be described below with reference to the drawings.

Example 1
As shown in FIG.1 and FIG.2, the capacity | capacitance control valve 50 of Example 1 is an example of the specific aspect of the control valve for compressors of this invention. As shown in FIG. 1, the capacity control valve 50 is used in a compressor body 10 that compresses a refrigerant, and forms a variable capacity swash plate compressor (hereinafter referred to as “compressor”) together with the compressor body 10. doing.

  In the compressor body 10, a plurality of cylinder bores 1 </ b> A are formed in the cylinder block 1 in parallel at equal angular intervals. The cylinder block 1 is sandwiched between a front housing 3 positioned at the front and a rear housing 5 positioned at the rear, and is fastened by a plurality of bolts 7 in this state. A crank chamber 9 is formed inside the cylinder block 1 and the front housing 3. The rear housing 5 is formed with a suction chamber 5A and a discharge chamber 5B. A low-pressure refrigerant flows into the suction chamber 5A from the outside of the compressor body 10, and the compressed high-pressure refrigerant is discharged into the discharge chamber 5B. The crank chamber 9 is an example of the “control pressure chamber” in the present invention. The discharge chamber 5B is an example of the “high pressure chamber” in the present invention. The suction chamber 5A is an example of the “low pressure chamber” in the present invention.

  A shaft hole 3A is formed in the front housing 3. The cylinder block 1 is formed with a shaft hole 1B. A drive shaft 11 is rotatably supported in the shaft holes 3A and 1B via a shaft seal device 9A and radial bearings 9B and 9C. A pulley or electromagnetic clutch (not shown) is provided on the drive shaft 11, and a belt (not shown) driven by a vehicle engine or motor is wound around the pulley or electromagnetic clutch.

  In the crank chamber 9, a lug plate 13 is press-fitted into the drive shaft 11. A thrust bearing 15 is provided between the lug plate 13 and the front housing 3. A swash plate 17 is inserted through the drive shaft 11. The lug plate 13 and the swash plate 17 are connected by a link mechanism 19 that supports the swash plate 17 so that the tilt angle can be changed.

  A piston 21 is housed in each cylinder bore 1A so as to be able to reciprocate. A valve unit 23 is provided between the cylinder block 1 and the rear housing 5. The valve unit 23 includes a suction valve plate 25, a valve plate 27, a discharge valve plate 29 and a retainer plate 31. The valve plate 27 is provided with a discharge port 23B and a suction port 23A. The cylinder block 1, the front housing 3, the rear housing 5, and the valve unit 23 are examples of the “main body housing” of the present invention.

  The suction valve plate 25 is formed with a suction lead portion 25A capable of opening and closing the suction port 23A by elastic deformation. The discharge valve plate 29 is formed with a discharge lead portion 29B that can open and close the discharge port 23B by elastic deformation.

  Between the swash plate 17 and each piston 21, shoes 33 </ b> A and 33 </ b> B that make a pair in front and rear are provided. The swinging motion of the swash plate 17 is converted into the reciprocating motion of each piston 21 by the pair of shoes 33A and 33B. Each compression chamber 24 is formed by the cylinder bore 1 </ b> A, the piston 21, and the valve unit 23.

  The crank chamber 9 and the suction chamber 5A communicate with each other through an extraction passage 40D. The crank chamber 9 and the discharge chamber 5B communicate with each other through an air supply passage 40. The air supply passage 40 is an example of the “control passage” in the present invention.

  The rear housing 5 is provided with a capacity control valve 50. The capacity control valve 50 and the suction chamber 5A are connected by a detection passage 40C. As will be described below, the capacity control valve 50 adjusts the opening degree of the air supply passage 40 to appropriately supply a high-pressure refrigerant from the discharge chamber 5B to the crank chamber 9, thereby controlling the compressor body 10.

  More specifically, as shown in FIGS. 2 to 4, the capacity control valve 50 includes a valve housing 50 </ b> C. The valve housing 50 </ b> C includes a valve housing main body 51 and a tip cover 52.

  The valve housing main body 51 is formed with a valve accommodation hole 51H for accommodating a valve body 80 described later. The valve housing hole 51 </ b> H includes a valve hole 70. Further, the valve housing hole 51H includes a valve chamber 71 that is a space surrounded by the inner peripheral surface 71S on the proximal end 50R side with respect to the valve hole 70. Further, the valve accommodating hole 51H includes a pressure sensitive chamber 73 located on the tip 50T side with respect to the valve hole 70.

  The valve hole 70 has a cylindrical shape and extends in the direction of the axis X1. Here, one end side in the axial center X1 direction is the base end 51R side of the valve housing main body 51, and the other end side in the axial center X1 direction is the distal end 51T side of the valve housing main body 51. 2 to 10 is the base end 51R side of the valve housing main body 51, and the left side of the paper is the front end 51T side of the valve housing main body 51.

  In the valve housing body 51, an annular flat surface surrounding the opening edge on the base end 51 </ b> R side of the valve hole 70 is a valve seat 79.

  As shown in FIGS. 2 to 4, a valve chamber 71 defined by a cylindrical inner peripheral surface 71 </ b> S having a diameter larger than that of the valve hole 70 on the base end 51 </ b> R side of the valve housing 79 from the valve seat 79. A downstream space 78 is formed by the control hole 71A extending from the inner peripheral surface 71S in the radially outward direction of the axis X1. The downstream space 78 constitutes a part of a section located on the downstream side of the valve seat 79 in the supply passage 40 and communicates with the crank chamber 9.

  An upstream space 72 is formed in the valve housing body 51 on the tip 51T side of the valve seat 79. The upstream space 72 is partitioned by a cylindrical inner peripheral surface 70S of the valve hole 70 and an introduction hole 72A extending from the inner peripheral surface 70S in the radially outward direction of the axis X1. The upstream space 72 constitutes a part of a section located on the upstream side of the valve seat 79 in the air supply passage 40, and the discharge pressure Pd that is the pressure of the discharge chamber 5B is introduced.

  As shown in FIGS. 2 and 3, a pressure sensitive chamber 73 is formed on the tip 51 </ b> T side of the valve hole 70 in the valve housing body 51. The pressure sensing chamber 73 communicates with the valve hole 70 from the tip 51T side, and has a stepped cylindrical shape having a larger diameter than the valve hole 70 and extends in the direction of the axis X1.

  The tip cover 52 is fixed to the tip 51T of the valve housing body 51 and covers the pressure sensitive chamber 73. A bellows 54 whose inside is evacuated is attached to the tip cover 52. The bellows 54 and the pressure sensitive chamber 73 are examples of the “pressure sensitive mechanism” of the present invention. The bellows 54 is accommodated in the pressure sensitive chamber 73 so as to be expandable and contractible in the direction of the axis X1. The tip of a rod 61 extending in the direction of the axis X1 is fixed to the washer 54A of the bellows 54.

  A spring 55 is provided between the bellows 54 and the valve housing body 51 to urge the bellows 54 so as to contract. A plurality of pressure sensitive holes 52 </ b> A are provided in the distal end cover 52. The pressure sensitive hole 52A communicates with the detection passage 40C shown in FIG. For this reason, the suction pressure Ps that is the pressure of the suction chamber 5A is introduced into the pressure sensing chamber 73 via the detection passage 40C and the pressure sensing hole 52A.

  As shown in FIG. 2, a fixed iron core 56, a guide 57, and a connecting member 58 are fixed to the base end 51 </ b> R of the valve housing main body 51. A movable iron core 59 is provided in the guide 57 so as to be movable in the direction of the axis X1. A control spring 60 is provided between the fixed iron core 56 and the movable iron core 59. A shaft hole 56 </ b> A is formed in the fixed iron core 56. A shaft hole 59 </ b> A is formed in the movable iron core 59. The rear end of the rod 61 extending in the direction of the axis X1 is press-fitted into the shaft hole 59A of the movable iron core 59. The rod 61 is slidably inserted into the shaft hole 56 </ b> A of the fixed iron core 56.

  A control coil 65 is fixed around the guide 57. A connector 62 is fixed to the control coil 65 from the side opposite to the valve housing body 51 in the direction of the axis X1. The periphery of the control coil 65 and the periphery of a part of the connector 62 are covered with a coil cover 63. The connector 62 and the control coil 65 are connected by a lead wire (not shown). The fixed iron core 56, the guide 57, the movable iron core 59, the control spring 60, and the control coil 65 constitute a solenoid 69.

  The bellows 54 and the solenoid 69 reciprocate the rod 61 in the direction of the axis X1. A valve body 80 is provided on the distal end side of the rod 61 extending in the direction of the axis X1 in the valve housing body 51. The valve body 80 can be reciprocated from the proximal end 51R side to the distal end 51T side in the valve housing hole 51H of the valve housing body 51 by being driven by the bellows 54 and the solenoid 69.

  As shown in FIGS. 2 to 8, the valve body 80 includes a valve portion 81, a connecting portion 82, a partition portion 83, and a pressure-sensitive rod portion 84 each having a columnar shape and extending in the direction of the axis X <b> 1. The valve portion 81, the connecting portion 82, the partition portion 83, and the pressure-sensitive rod portion 84 are integrated in this order from the proximal end 51R side to the distal end 51T side.

  As shown in FIGS. 2 to 4 and the like, the valve portion 81 is provided in the valve chamber 71. The valve portion 81 has the same diameter as the portion of the rod 61 that is inserted through the shaft hole 56 </ b> A of the fixed iron core 56. The end surface on the tip 51T side of the valve portion 81 is an annular flat surface centered on the axis X1. As shown in FIG. 7, the valve portion 81 is seated on the valve seat 79 as the valve body 80 moves toward the tip 51 </ b> T in the valve housing main body 51. On the other hand, the valve portion 81 moves away from the valve seat 79 as shown in FIGS. 2 to 4, 6, and 8 when the valve body 80 moves toward the base end 51 </ b> R in the valve housing body 51. To do.

  As shown in FIGS. 3 to 5 and the like, the connecting portion 82 has a smaller diameter than the valve portion 81. The base end 51 </ b> R side of the connecting portion 82 is connected to the valve portion 81. Further, the connecting part 82 has a smaller diameter than the valve hole 70 and the partition part 83. The distal end 51T side of the connecting portion 82 enters the valve hole 70 and extends to a position beyond the introduction hole 72A. The connecting portion 82 moves in the valve hole 70 by the reciprocating motion of the valve body 80. A communication passage 87 is formed between the outer peripheral surface 82S of the connecting portion 82 and the inner peripheral surface 70S of the valve hole 70. The communication path 87 has a cylindrical shape and extends in the direction of the axis X1 to constitute a part of the upstream space 72.

  The partition 83 is provided in the valve hole 70. In the partition part 83, the first end face 83E located on the connecting part 82 side and the first end edge 83A that is the outer edge of the first end face 83E are located closer to the tip 51T than the introduction hole 72A. In the partition part 83, the second end face 83F located on the pressure-sensitive rod part 84 side and the second end edge 83B that is the outer edge of the second end face 83F are located in the pressure-sensitive chamber 73. The second end surface 83F is a tapered surface that approaches the pressure sensitive chamber 73 while reducing the diameter from the second end edge 83B.

  The outer diameter of the partition portion 83 is slightly smaller than the inner diameter of the valve hole 70, and a slight gap is secured between the outer peripheral surface 83S of the partition portion 83 and the inner peripheral surface 70S of the valve hole 70. . A plurality of oil seal grooves 83 </ b> D are recessed in the outer peripheral surface 83 </ b> S of the partition part 83. The partition part 83 moves in the valve hole 70 by the reciprocating motion of the valve body 80. At this time, the partition 83 is in sliding contact with the inner peripheral surface 70S while interposing the lubricating oil contained in the refrigerant between the outer peripheral surface 83S and the inner peripheral surface 70S, so that the upstream space 72 and the pressure sensitive chamber 73 are in contact with each other. Seal the gap.

  A first groove 91A is formed in almost the entire area of the first end face 83E. The first groove 91 is an annular groove including a first cylindrical surface 91B and a first reverse tapered surface 91A, each centered on the axis X1. The first cylindrical surface 91B is a cylindrical surface having the same diameter as the outer peripheral surface 82S of the connecting portion 82 and extends toward the tip 51T side. 91 A of 1st reverse taper surfaces reduce in diameter as it goes to the front-end | tip 51T side from the annular | circular shaped 1st edge 83A of the division part 83, and are connected with the 1st cylindrical surface 91B.

  That is, the 1st groove | channel 91 is dented so that it may go to the front-end | tip 51T side from the 1st end edge 83A by the side of the base end 51R of the division part 83, approaching the axial center X1 located in a center area. Further, due to the first groove 91, the first end edge 83 </ b> A of the partition part 83 has a scraper shape with respect to the inner peripheral surface 70 </ b> S of the valve hole 70.

  The pressure sensitive rod portion 84 is provided in the pressure sensitive chamber 73. The pressure-sensitive rod portion 84 is connected to the second end face 83F of the partition portion 83, extends in a cylindrical shape toward the tip 51T side, and the tip is fixed to the washer 54A of the bellows 54.

  Although not shown, a condenser is connected to the discharge chamber 5B of the compressor via a check valve, the condenser is connected to the expansion valve, the expansion valve is connected to the evaporator, and the evaporator is connected to the compressor. It is connected to the suction chamber 5A. These compressors, condensers, expansion valves, and evaporators constitute an air conditioner that is mounted on a vehicle and performs air conditioning in the passenger compartment.

  In the compressor configured as described above, when the drive shaft 11 is rotationally driven, the lug plate 13 and the swash plate 17 rotate in synchronization with the drive shaft 11, and each stroke is performed according to the inclination angle of the swash plate 17. The piston 21 reciprocates in each cylinder bore 1A. For this reason, the refrigerant in the suction chamber 5A is sucked into the compression chambers 24 and compressed, and is discharged into the discharge chamber 5B.

  During this time, a control unit (not shown) controls the control coil 65 of the solenoid 69 based on external signals such as a preset cabin temperature, a detected temperature obtained from the evaporator temperature sensor, and a detected temperature obtained from the cabin temperature sensor. An input current value for driving is appropriately set. In the capacity control valve 50, the solenoid 69 changes the load applied to the valve body 80 according to the input current value, and the bellows 53 is applied to the valve body 80 according to the suction pressure Ps introduced into the pressure sensing chamber 73. The applied load is changed, and the valve body 80 is operated by the total force of the applied loads. Thus, the capacity control valve 50 controls the discharge capacity of the compressor body 10 by adjusting the distance that the valve portion 81 and the valve seat 79 are separated in the direction of the axis X1, that is, the opening of the air supply passage 40. . A specific example of control of the capacity control valve 50 will be described below.

  That is, in accordance with an input current value according to a cooling request from a control unit (not shown), the movable iron core 59 is urged to approach the fixed iron core 56 in a state where the control coil 65 of the solenoid 69 is excited. If the heat load is small in this state and the suction pressure Ps is lower than the set pressure, the bellows 54 shown in FIG. 2 extends. For this reason, as shown in FIG. 6, the valve body 80 moves to the base end 51 </ b> R side, the valve portion 81 is separated from the valve seat 79, and the upstream space 72 and the downstream space 78 communicate with each other. 40 causes the discharge chamber 5B and the crank chamber 9 to communicate with each other. For this reason, the high-pressure refrigerant in the discharge chamber 5B is introduced into the crank chamber 9, and the crank pressure Pc increases. For this reason, the inclination angle of the swash plate 17 becomes small, the stroke of each piston 21 becomes short, and the discharge capacity per one rotation of the drive shaft 11 becomes small.

  In the state where the control coil 65 is excited, if the heat load is large and the suction pressure Ps is higher than the set pressure, the bellows 54 is reduced. For this reason, as shown in FIG. 7, the valve body 80 moves to the tip 51T side, the valve portion 81 is seated on the valve seat 79, and the upstream space 72 and the downstream space 78 do not communicate with each other. For this reason, the air supply passage 40 is blocked, and the discharge chamber 5B and the crank chamber 9 are not communicated with each other. For this reason, the high-pressure refrigerant in the discharge chamber 5 </ b> B is not introduced into the crank chamber 9. On the other hand, the refrigerant in the crank chamber 9 flows out to the suction chamber 5A via the extraction passage 40D, and the crank pressure Pc gradually decreases. For this reason, the inclination angle of the swash plate 17 is increased, the stroke of each piston 21 is increased, and the discharge capacity per one rotation of the drive shaft 11 is increased. Thus, in this compressor, the operation is continued with the discharge capacity corresponding to the heat load.

<Effect>
There is a possibility that foreign matters may be mixed in the refrigerant circulating through the compressor, the condenser, the expansion valve, and the evaporator constituting the air conditioner. In the capacity control valve 50, as shown in FIG. 6, the valve body 80 moves to the base end 51R side, the valve portion 81 is separated from the valve seat 79, and the discharge chamber 5B and the crank chamber 9 communicate with each other. Then, the foreign matter P1 mixed in the refrigerant passes through the upstream space 72 and the downstream space 78. At this time, stagnation is likely to occur between the connecting portion 82 of the valve body 80 and the partition portion 83, particularly around the first end edge 83A of the partition portion 83, and the foreign matter P1 may accumulate in the stagnation.

  Next, as shown in FIG. 7, when the valve body 80 moves to the tip 51T side, the valve portion 81 is seated on the valve seat 79, and the upstream space 72 and the downstream space 78 are not in communication, the upstream side A differential pressure Pd−Ps between the discharge pressure Pd introduced into the space 72 and the suction pressure Ps introduced into the pressure sensing chamber 73 acts on the periphery of the first end edge 83A of the partition part 83, and the foreign matter P1 becomes the first end. It becomes easier to collect around the edge 83A.

  Here, in this capacity control valve 50, as shown in FIGS. 5 to 7, etc., the first edge 91 of the partition portion 83 is formed by the first groove 91 formed in the almost entire area of the first end face 83 </ b> E of the partition portion 83. 83A has a scraper shape with respect to the inner peripheral surface 70S of the valve hole 70. In particular, since the first groove 91 includes the first reverse tapered surface 91 </ b> A, the scraper shape of the first end edge 83 </ b> A in the partition portion 83 is further clarified.

  For this reason, the valve body 80 in the state shown in FIG. 7 then moves to the base end 51R side as shown in FIG. 8, and the valve portion 81 moves away from the valve seat 79, so that the discharge chamber 5B and the crank chamber 9, the scraper-shaped first end edge 83A of the partition part 83 peels off the foreign matter P1 from the inner peripheral surface 70S of the valve hole 70, and the foreign matter P1 is guided to the first reverse tapered surface 91A to be centered. The foreign matter P <b> 1 is collected in the vicinity of the central region of the first groove 91. As a result, the foreign matter P1 is not easily caught between the inner peripheral surface 70S of the valve hole 70 and the first end edge 83A and the outer peripheral surface 83S of the partition part 83.

  Therefore, in the capacity control valve 50 of the first embodiment, it is possible to suppress the malfunction of the valve body 80 due to the foreign matter P1 mixed in the refrigerant. Moreover, when the filter for removing the foreign material P1 from the refrigerant is provided in the compressor body 10, the mesh size of the filter can be increased, so that pressure loss due to the filter can be reduced.

  Further, in the capacity control valve 50, as shown in FIG. 5 and the like, the first groove 91 is directed from the annular first end edge 83A of the partition portion 83 toward the tip 51T as it approaches the axis X1. It is a recessed annular groove. For this reason, it is easy to form the first groove 91 in the first end face 83E by lathe processing or the like.

(Example 2)
As shown in FIGS. 9 and 10, in the capacity control valve of the second embodiment, the second end face 83 </ b> F and the second end edge 83 </ b> B of the partition part 83 are located in the valve hole 70, and the pressure-sensitive rod part. 84 is changed to be able to enter the valve hole 70. And the shape of the 2nd end surface 83F of the division part 83 is changed, and the 2nd groove | channel 92 is formed in the substantially whole area of the 2nd end surface 83F. Other configurations of the second embodiment are the same as those of the first embodiment. For this reason, about the same structure as Example 1, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

  The second groove 92 is an annular groove including a second cylindrical surface 92B and a second reverse tapered surface 92A, each centered on the axis X1. The second cylindrical surface 92B is a cylindrical surface having the same diameter as the outer peripheral surface 84S of the pressure-sensitive rod portion 84, and extends toward the base end 51R side. The second reverse tapered surface 92A has a diameter that decreases from the annular second end edge 83B of the partition portion 83 toward the base end 51R, and is connected to the second cylindrical surface 92B.

  That is, the second groove 92 is recessed from the second end edge 83B on the distal end 51T side of the partition part 83 toward the proximal end 51R as it approaches the axis X1 located in the central region. Then, due to the second groove 92, the second end edge 83 </ b> B of the partition part 83 has a scraper shape with respect to the inner peripheral surface 70 of the valve hole 70.

  In the capacity control valve of Example 2 having such a configuration, as shown in FIG. 9, during the vacuuming operation before the compressor is assembled in the air conditioner and the refrigerant is filled in the air conditioner, as shown in FIG. 80 moves to the base end 51R side, the valve portion 81 is separated from the valve seat 79, and the upstream space 72, the downstream space 78, and the pressure sensing chamber 53 are also evacuated. At this time, there is a possibility that foreign matters generated in the manufacturing process of the compressor, the condenser, the expansion valve, and the evaporator constituting the air conditioner are mixed into the discharged air. Then, the foreign matter P2 mixed in the discharged air may reach the pressure sensing chamber 73 and accumulate around the second end edge 83B of the partition part 83.

  Here, in this capacity control valve, the second end edge 83 </ b> B of the partition portion 83 is formed on the inner peripheral surface 70 </ b> S of the valve hole 70 by the second groove 92 formed in almost the entire area of the second end surface 83 </ b> F of the partition portion 83. On the other hand, it has a scraper shape. In particular, since the second groove 92 includes the second reverse tapered surface 92A, the scraper shape of the second end edge 83B in the partition part 83 is further clarified.

  Therefore, when the valve body 80 in the state shown in FIG. 9 is moved to the tip 51T side and the valve part 81 is seated on the valve seat 79 as shown in FIG. The second edge 83B peels off the foreign matter P2 from the inner peripheral surface 70S of the valve hole 70, and the foreign matter P2 is guided by the second reverse tapered surface 92A and moves toward the center region. It is collected near the central area. As a result, in the capacity control valve according to the second embodiment, the foreign matter P2 is not easily caught between the inner peripheral surface 70S of the valve hole 70 and the second end edge 83B and the outer peripheral surface 83S of the partition part 83. 80 malfunctions can be reliably suppressed.

  In the above, the present invention has been described with reference to the first and second embodiments. However, the present invention is not limited to the first and second embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.

  For example, in the first and second embodiments, a compressor body having a control pressure chamber as a crank chamber, a high pressure chamber as a discharge chamber, and a low pressure chamber as a suction chamber is employed, and the compressor control valve is used as the crank chamber and the discharge chamber. However, the present invention is not limited to this configuration. For example, the compressor control valve may adjust the opening degree of the extraction passage that communicates the crank chamber and the suction chamber. Further, the compressor control valve may adjust the opening of the supply passage and the extraction passage.

  In addition, an actuator is provided in the swash plate chamber, the cylinder chamber in the actuator is used as a control pressure chamber, the high pressure chamber is used as a discharge chamber, and the low pressure chamber is used as a suction chamber. It is also possible.

  Further, the shapes of the valve housing hole, the valve body, the communication path, the first and second grooves, and the like are not limited to those in the first and second embodiments. For example, the connecting portion of the valve body has the same diameter as the partition portion, the communication path is recessed in the outer peripheral surface of the connecting portion, and extends in the axial direction to communicate the upstream space with the valve seat. Good. In this case, the first groove is not an annular groove like the first groove 91 according to the first embodiment, but is a concave portion that is recessed from the end of the groove-shaped communication path.

  The present invention can be used for a compressor constituting an air conditioner, a fluid machine, or the like.

50. Control valve for compressor (capacity control valve)
5B ... High pressure chamber (discharge chamber)
5A ... Low pressure chamber (suction chamber)
9 ... Control pressure chamber (crank chamber)
40 ... Control passage (supply passage)
DESCRIPTION OF SYMBOLS 10 ... Compressor main body 50C ... Valve housing 51H ... Valve accommodation hole 70 ... Valve hole 80 ... Valve body 73 ... Pressure sensing chamber 54, 73 ... Pressure sensing mechanism (54 ... Bellows, 73 ... Pressure sensing chamber)
79 ... Valve seat 72 ... Upstream space 78 ... Downstream space 81 ... Valve portion 70S ... Inner peripheral surface of valve accommodating hole (inner peripheral surface of valve hole)
83 ... partitioning part 82 ... connecting part 83E ... first end face 83A ... outer edge (first end edge) of the first end face
X1 ... shaft center 91 ... first groove 91A ... first reverse taper surface 84 ... pressure-sensitive rod portion 83F ... second end surface 83B ... outer edge (second end edge) of the second end surface
92 ... 2nd groove 92A ... 2nd reverse taper surface 1A ... Cylinder bore 1, 3, 5, 23 ... Body housing (1 ... Cylinder block, 3 ... Front housing, 5 ... Rear housing, 23 ... Valve unit)
DESCRIPTION OF SYMBOLS 11 ... Drive shaft 17 ... Swash plate 24 ... Compression chamber 21 ... Piston

Claims (7)

The compressor has a high-pressure chamber and a low-pressure chamber, and has a control pressure chamber that communicates with the high-pressure chamber or the low-pressure chamber via a control passage, and adjusts the opening of the control passage to adjust the compressor. In the control valve for the compressor that controls the discharge capacity of the main body,
A valve housing;
A valve housing hole provided in the valve housing;
A valve body extending including a central region of the valve accommodation hole and capable of reciprocating in the valve accommodation hole;
A pressure-sensitive chamber in communication with the low-pressure chamber, and a pressure-sensitive mechanism for reciprocating the valve body in accordance with the pressure in the pressure-sensitive chamber;
A valve seat on which the valve body can be seated;
An upstream space located upstream of the valve seat in the control passage;
A downstream space located downstream from the valve seat in the control passage,
The valve body includes a valve portion that can be seated on the valve seat;
A substantially cylindrical partition section that slidably contacts the inner peripheral surface of the valve housing hole and partitions the pressure-sensitive chamber and the upstream space;
A connecting portion that connects the valve portion and the partition portion;
The compressor control valve according to claim 1, wherein the first end surface of the partition portion on the connection portion side is formed to be recessed from the outer edge side toward the center side. The valve housing hole has a cylindrical shape and extends in the axial direction,
The valve part, the connecting part, and the partition part are columnar and can reciprocate in the axial direction.
The connecting part has a smaller diameter than the partition part,
2. The compressor control valve according to claim 1, wherein an annular first groove is formed in the first end face to be recessed so as to approach the pressure sensitive chamber with the axis as a center.   3. The control valve for a compressor according to claim 2, wherein the first groove includes a first reverse tapered surface that approaches the pressure-sensitive chamber while being reduced in diameter from the outer edge of the first end surface. The valve body has a pressure-sensitive rod portion that is integral with the partition portion on the side opposite to the connecting portion and protrudes into the pressure-sensitive chamber, and that can enter the valve housing hole,
The control valve for a compressor according to any one of claims 1 to 3, wherein a second end surface of the partitioning portion on the pressure-sensitive rod portion side is formed to be recessed from the outer edge side toward the center side. The valve housing hole has a cylindrical shape and extends in the axial direction,
The valve part, the connecting part, the partition part, and the pressure-sensitive rod part can be reciprocated in the axial direction in a cylindrical shape,
The pressure-sensitive rod portion has a smaller diameter than the partition portion,
5. The compressor control valve according to claim 4, wherein an annular second groove is formed in the second end surface so as to be recessed from the pressure sensitive chamber with the shaft center as a center.   The control valve for a compressor according to claim 5, wherein the second groove includes a second reverse tapered surface that is reduced in diameter from the outer edge of the second end surface and is separated from the pressure sensitive chamber. The compressor body includes a body housing in which a suction chamber, a discharge chamber, a crank chamber, and a cylinder bore are formed, a drive shaft that is rotatably supported in the crank chamber, and can rotate integrally with the drive shaft in the crank chamber. A control valve for a compressor, comprising: a swash plate that is supported and supported so as to change an inclination angle; and a piston that forms a compression chamber in the cylinder bore and reciprocates in the cylinder bore by the swash plate. Together with a variable capacity swash plate compressor,
The high-pressure chamber is the discharge chamber;
The low pressure chamber is the suction chamber;
The control valve for a compressor according to any one of claims 1 to 6, wherein the control pressure chamber is the crank chamber communicating with the discharge chamber via the control passage.

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