JP2009150224A - Variable displacement compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement compressor preventing as much as possible the flapping of a wash plate caused by pressure fluctuation, and performing stable control. <P>SOLUTION: In this variable displacement compressor 1, a rotor 11 fixed to a drive shaft 4 and a journal 13 are connected to each other through a connection link 14, the connection link 14 rotates around the rotor 11, the inclination angle of the journal 13 is varied together with the swash plate 15 by the rotation of the connection link, and the reciprocating stroke of each piston 9 is varied in response to the inclination angle of the swash plate 15. A sliding resistance applying means 30 with a sliding resistance cylindrical body 31 fixed by a ring pin 32 is provided on the inner periphery of a sleeve 12, thereby applying a constant sliding resistance when the journal 13 and swash plate 15 are moved to vary their inclination angles. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a variable displacement compressor that varies a discharge capacity of a piston according to an inclination angle of a swash plate.

  A conventional variable displacement compressor of this type is disclosed in Patent Document 1.

  The variable displacement compressor 100 includes a housing 101 as shown in FIG. The housing 101 is assembled by assembling a cylinder block 101a, a front head 101b disposed on one end side of the cylinder block 101a, and a rear head 101c disposed on the other end side of the cylinder block 101a via a valve plate 102. It is mainly composed.

  A drive shaft 103 is disposed at the center of the housing 101. Both end sides of the drive shaft 103 are rotatably supported by the housing 101 via a radial bearing portion 104 and a radial bearing portion 105.

  In the cylinder block 101a, a plurality of cylinder bores 106 are formed on the circumference around the drive shaft 103, and pistons 107 are slidably disposed in the cylinder bores 106, respectively. A crank chamber 108 communicating with the plurality of cylinder bores 106 is formed in the front head 101b. In the crank chamber 108, a rotor 109 fixed to the outer periphery of the drive shaft 103, a sleeve 110 disposed on the outer periphery of the drive shaft 103 so as to be movable in the axial direction, and an outer peripheral side of the sleeve 110 are connected to each other. A journal 112 connected to the rotor 109 via 111 and a swash plate 113 fixed to the outer periphery of the journal 112 are provided. Each piston 107 is engaged with the outer peripheral portion of the swash plate 113 via a pair of shoes 114.

  First and second springs S1 and S2 are disposed at both ends of the sleeve 110, respectively, and the swash plate 113 is returned to the initial driving position after the operation is stopped by the balance of the spring force of the first and second springs S1 and S2. It is.

  The connection link 111 is connected to the rotor 109 by the first rotation fulcrum 111a and to the journal 112 by the second rotation fulcrum 111b.

  When the drive shaft 103 rotates, each piston 107 reciprocates in the cylinder bore 106 by the rotor 109, the swash plate 113, and the like, and the reciprocating stroke of each piston 107 is varied by the inclination angle of the swash plate 113.

  A suction chamber 120 and a discharge chamber 121 are formed in the rear head 101c.

  A valve plate 102 interposed between the cylinder block 101 a and the rear head 101 c partitions the plurality of cylinder bores 106 from the suction chamber 120 and the discharge chamber 121.

  In the above configuration, when the drive shaft 103 is driven to rotate, the swash plate 113 swings and each piston 107 reciprocates. In the suction stroke of each piston 107, the refrigerant is supplied from the suction chamber 120 into the cylinder bore 106, and the supplied refrigerant is compressed in the compression stroke of the piston 107 and discharged to the discharge chamber 121. The discharged refrigerant circulates in the refrigeration cycle, is used for cooling or the like, and returns to the variable capacity compressor 100 again.

  When the variable capacity compressor 100 is driven and the heat load of the refrigeration cycle increases, the pressure in the crank chamber 108 is adjusted to the low pressure side. Then, the balance between the counterclockwise moment due to the crank chamber pressure as the back pressure of each piston 107 and the spring force of the first spring S1 and the clockwise moment due to the front pressure of each piston 107 and the spring force of the second spring S2 is lost, With respect to the integral member of the swash plate 113 and the journal 112, the clockwise moment in the direction of increasing the inclination angle of the swash plate 113 around the second rotation fulcrum 111b becomes large, and the connecting link 111 is moved to a position where both moments are balanced. It rotates in the direction of arrow a in FIG. The rotation angle of the connecting link 111 increases the inclination angle of the swash plate 113. As the inclination angle of the swash plate 113 increases, the reciprocating stroke of each piston 107 increases, the refrigerant discharge capacity increases, and the cooling capacity and the like increase.

  Further, when the heat load of the refrigeration cycle is reduced, the pressure in the crank chamber 108 is adjusted to the high pressure side. Then, the balance between the counterclockwise moment due to the crank chamber pressure as the back pressure of each piston 107 and the spring force of the first spring S1 and the clockwise moment due to the front pressure of each piston 107 and the spring force of the second spring S2 is lost, The counterclockwise moment in the direction of decreasing the inclination angle of the swash plate 113 around the second rotation fulcrum 111b with respect to the integral member of the swash plate 113 and the journal 112 increases, and the connecting link 111 reaches a position where both moments balance. Rotates in the direction of the arrow b in FIG. By the rotation of the connecting link 111, the inclination angle of the swash plate 113 is reduced. When the inclination angle of the swash plate 113 is reduced, the reciprocating stroke of each piston 107 is reduced, the refrigerant discharge capacity is reduced, and the cooling capacity and the like are reduced. The variable displacement compressor 100 saves power by such operation.

In the conventional variable displacement compressor 100, the rotor 109 and the journal 112 are connected via the connecting link 111 as described above. In such a link connection structure using the connection link 111, the inclination angle of the swash plate 113 can be varied with almost no sliding resistance regardless of the inclination angle of the swash plate 113, and stable control is possible.
JP 2006-233855 A JP-A-8-109879

  By the way, the swash plate 113 except the full stroke position and the destroke position, the crank chamber pressure that is the back pressure of each piston 107 and the counterclockwise moment by the spring force of the first spring S1, the front pressure of each piston 107, and It is located at an inclined position where the clockwise moment due to the spring force of the second spring S2 is balanced. Therefore, as in the conventional example, when there is almost no sliding resistance during the movement for changing the inclination angle of the swash plate 113, the pressure fluctuation between the crank chamber pressure which is the back pressure of each piston 107 and the front pressure of each piston 107. Therefore, the swash plate 113 is likely to flutter. When the swash plate 113 flutters, there is a problem such as abnormal noise.

  In particular, at a position where the first spring S1 and the second spring S2 are balanced (position where the discharge capacity is about 5% to 10%), a periodic motion that repeats expansion and contraction, which is a spring characteristic, is likely to occur. For this reason, the spring balance position is likely to flutter due to the spring characteristics, the above-described pressure fluctuations, and the synergistic action of the spring characteristics and the pressure fluctuations.

  On the other hand, as a connection structure between the rotor 109 and the journal 112, there is a kidney connection structure in which a guide long groove is provided in one of the rotor 109 and the journal 112, and a guide pin moving in the guide long hole is provided in the other (Patent Document 2). reference). In this kidney connection structure, since the guide pin slides in the guide groove, there is a sliding resistance when changing the inclination of the swash plate 113, but the direction in which the guide pin slides in the guide groove is inclined. Since it is not constant depending on the position of the inclination angle of the plate 113, the sliding resistance changes. Thus, when the sliding resistance changes depending on the inclination angle of the swash plate 113, stable control cannot be performed.

  Therefore, an object of the present invention is to provide a variable displacement compressor that can prevent the swash plate from flapping due to pressure fluctuations as much as possible and that can be stably controlled.

  The invention of claim 1, which achieves the above object, is provided with a plurality of cylinder bores and a crank chamber communicating with the cylinder bore in the housing, and a drive shaft is rotatably provided in the housing so as to penetrate the precursor crank chamber. A rotor is fixed to the drive shaft, a sleeve is provided on the outer periphery of the drive shaft so as to be movable in the axial direction, and a journal on which an inclination change is guided to the sleeve is provided on the outer periphery of the sleeve, and the journal and the rotor A connecting link is provided to connect the swash plates to the outer periphery of the journal, and a swash plate that swings by rotation of the jar is provided, and a plurality of pistons that reciprocate in the cylinder bores by swinging the swash plate are provided. By adjusting the crank chamber pressure, which is the back pressure of each piston, the rotation fulcrum of the rotor and the connecting link is centered. Then, the moment acting on the integral member of the journal and the swash plate is adjusted, and the inclination angle is varied while the integral member of the journal and the swash plate is guided by the connecting link and the sleeve, In a variable capacity compressor in which the reciprocating stroke of each piston is varied by varying the inclination angle, a sliding resistance adding means is provided for applying a certain sliding resistance during movement to vary the inclination angle of the journal and the swash plate. It is characterized by that.

  A second aspect of the present invention is the variable displacement compressor according to the first aspect, wherein the spring forces of the first spring and the second spring are applied to both ends of the sleeve, respectively.

  A third aspect of the present invention is the variable displacement compressor according to the first or second aspect, wherein the sliding resistance adding means is provided between an inner peripheral surface of the sleeve and an outer peripheral surface of the drive shaft. A variable capacity compressor having a sliding resistance member.

  A fourth aspect of the present invention is the variable capacity compressor according to the third aspect, wherein the sliding resistance member is a sliding resistance cylinder in which a cylindrical part is opened, and the sliding resistance cylinder is The drive shaft is pressed against the outer periphery by the elastic return force of the pair of ring pins.

  According to the first aspect of the present invention, the journal and the swash plate have a fluctuation in the back pressure and the front pressure of each piston in a state where the integral member of the journal and the swash plate is located at the balance position of the moment acting on both. Since the sliding resistance acts by the sliding resistance adding means even if it is going to move in the direction of changing the inclination angle, flapping of the swash plate can be prevented as much as possible. Further, when the inclination angle of the journal and the swash plate is varied, a certain sliding resistance acts by the sliding resistance adding means, so that stable control is possible.

  According to the second aspect of the present invention, in addition to the effect of the first aspect of the invention, the variable displacement compressor can return the swash plate to the initial driving position after the operation is stopped by the balance of the spring force of the first and second springs. Therefore, fluttering of the swash plate can be prevented as much as possible. In particular, the swash plate is likely to flutter at a position where the spring forces of the first spring and the second spring are balanced, but fluttering of the swash plate at such a position can be prevented.

  According to the invention of claim 3, in addition to the effect of the invention of claim 1 or 2, since the sleeve linearly moves with respect to the drive shaft, a constant sliding resistance is provided between the relatively linearly moving members. Since it only has to act, the configuration of the sliding resistance member may be simple.

  According to the invention of claim 4, in addition to the effect of the invention of claim 3, the sliding resistance cylinder continues to press against the drive shaft even when the sliding resistance cylinder is worn. A predetermined sliding resistance is maintained.

  According to the invention of claim 5, in addition to the effect of the invention of claim 4, since the sliding resistance cylinder and the sleeve are integrated, the assembling and handling properties of the sliding resistance cylinder are good.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  1 to 6 show an embodiment of the present invention, FIG. 1 is an overall cross-sectional view of a variable displacement compressor, FIG. 2 is an enlarged cross-sectional view of a main part, and FIG. 3 is a cross-sectional view taken along line AA in FIG. 4 (a) is a plan view of the sleeve and the sliding resistance means, FIG. 4 (b) is a front view of the sleeve and the sliding resistance means, FIG. 4 (c) is a sectional view taken along line BB in FIG. 4 (b), 5A is a plan view of the sliding resistance cylinder, FIG. 5B is a front view of the sliding resistance cylinder, and FIG. 5C is a cross-sectional view taken along the line CC of FIG. 5B. 6 (a) is a front view of the ring pin, and FIG. 6 (b) is a sectional view taken along the line DD of FIG. 6 (a).

  As shown in FIG. 1, the variable displacement compressor 1 has a housing 2. The housing 2 is assembled with a cylinder block 2a, a front head 2b disposed on one side surface of the cylinder block 2a, and a rear head 2c disposed on the other side surface of the cylinder block 2a via a valve body 3. Is made up of.

  A drive shaft 4 is disposed in the cylinder block 2a and the front head 2b so as to penetrate a crank chamber 10 described below. Both ends of the drive shaft 4 are rotatably supported by the cylinder block 2a and the front head 2b via radial bearing portions 5 and 6. One end of the drive shaft 4 protrudes outward from the front head 2b, and a pulley 7 that receives engine rotation is fixed to the protruding portion. The drive shaft 4 is configured to rotate by receiving a driving force from the pulley 7 fixed to one end side in this way.

  A plurality of cylinder bores 8 are formed in the cylinder block 2a. The plurality of cylinder bores 8 are formed at equal intervals on the circumference around the drive shaft 4. A piston 9 is slidably disposed in each cylinder bore 8.

  A crank chamber 10 communicating with the plurality of cylinder bores 8 is formed in the front head 2b. The crank chamber 10 includes a rotor 11 fixed to the outer periphery of the drive shaft 4, a sleeve 12 that is axially movable on the outer periphery of the drive shaft 4, and a journal 13 that is disposed on the outer peripheral side of the sleeve 12. The connecting link 14 connecting the journal 13 and the rotor 11, the swash plate 15 fixed to the outer periphery of the journal 13, and each piston 9 engaged with the outer peripheral portion of the swash plate 15 via a pair of shoes 16. Each of the rear end sides is provided.

  The outer peripheral surface of the sleeve 12 is formed in a substantially arc shape, and guides the journal 13 so that the inclination angle can be smoothly changed. First and second springs S1 and S2 are disposed at both ends of the sleeve 12, respectively, and the swash plate 15 is moved to the initial drive position (discharge) after the operation is stopped by the balance of the spring force of the first and second springs S1 and S2. The position is returned to a position where the capacity is about 5% to 10%. On the inner peripheral side of the sleeve 12, there is provided a sliding resistance adding means 30 for adding a certain sliding resistance during movement for changing the inclination angle of the journal 13 and the swash plate 15. The detailed configuration of the sliding resistance adding means 30 will be described in detail below.

  The connection link 14 is connected to the rotor 11 by the first rotation fulcrum part 14a and to the journal 13 by the second rotation fulcrum part 14b.

  When the drive shaft 4 rotates, the rotation is transmitted to the swash plate 15 by the rotor 11, the connecting link 14, and the journal 13, and each piston 9 reciprocates in the cylinder bore 8. Further, the stroke of each piston 9 is varied depending on the inclination angle of the swash plate 15, and the discharge capacity of the refrigerant is varied. The mechanism by which the inclination angle of the swash plate 15 is adjusted will be described in the place of action.

  A refrigerant gas suction chamber 20 and a discharge chamber 21 are formed in the rear head 2c. The suction chamber 20 is connected to the outlet side of the evaporator of the refrigeration cycle. The discharge chamber 21 is connected to the inlet side of the condenser of the refrigeration cycle. The suction chamber 20 and the discharge chamber 21 are partitioned by the cylinder bores 8 via the valve bodies 3. A suction hole (not shown) with a suction valve and a discharge hole 22 with a discharge valve are formed in the valve body 3 partitioning both chambers.

  In addition, a bleed passage (not shown) that is in continuous communication is formed between the crank chamber 10 and the suction chamber 20. An air supply passage 23 is formed between the crank chamber 10 and the discharge chamber 21. A pressure control valve 24 is disposed in the air supply passage 23. The pressure of the crank chamber 10 can be adjusted by controlling the opening of the pressure control valve 24.

  Next, the configuration of the sliding resistance adding means 30 will be described. As shown in FIGS. 2 to 4, the sliding resistance adding means 30 includes a sliding resistance cylinder 31 that is a sliding resistance member disposed on the inner periphery of the sleeve 12, and an outer periphery of the sliding resistance cylinder 31. It is comprised from a pair of ring pin 32 inserted by the both ends.

  As shown in detail in FIGS. 5A to 5C, the sliding resistance cylindrical body 31 is a cylindrical body having an opening 31a in a part of the cylindrical shape, and can move with a certain sliding resistance. It is made of wear material. The material of the sliding resistance cylinder 31 is preferably Zytel 103 HSL (trade name) and nylon manufactured by Dupout. The sliding resistance cylinder 31 has recesses 31b at both ends of the outer peripheral surface.

  As shown in FIGS. 6A and 6B, each ring pin 32 is a ring having an opening 32a in a part of the ring shape. Each ring pin 32 is fitted in a recess 31 b on both sides of the sliding resistance cylinder 31. Each ring pin 32 has an inner diameter slightly smaller than the diameter of the bottom surface of the recess 31 b of the sliding resistance cylinder 31, and presses the sliding resistance cylinder 31 against the drive shaft 4 by an elastic restoring force. The sleeve 12 is disposed on the outer peripheral surface of the sliding resistance cylinder 31 so as to be sandwiched between a pair of ring pins 32. The sliding resistance cylinder 31 and the sleeve 12 are formed as a single member by a pair of ring pins 32.

  In the above configuration, when the drive shaft 4 rotates, the rotational force causes the swash plate 15 to rotate, and the plurality of pistons 9 reciprocate in the cylinder bore 8. In the suction stroke of the piston 9 (stroke moving from the top dead center to the bottom dead center), a suction hole (not shown) is opened by the pressure reduction in the cylinder bore 8. As a result, the refrigerant gas is supplied from the suction chamber 20 to the cylinder bore 8.

  In the compression stroke of the piston 9 (stroke moving from the bottom dead center to the top dead center), the suction hole (not shown) is closed, and the refrigerant gas in the cylinder bore 8 is adiabatically compressed by the piston 9. The compressed high-temperature and high-pressure refrigerant gas is discharged from the discharge hole 22 to the discharge chamber 21. The high-temperature and high-pressure refrigerant discharged into the discharge chamber 21 is discharged out of the variable capacity compressor 1 through a discharge port (not shown). The discharged refrigerant circulates in the refrigeration cycle, is used for cooling or the like, and returns to the variable capacity compressor 1 again.

  When the variable capacity compressor 1 is driven and the heat load of the refrigeration cycle increases, the pressure in the crank chamber 10 is adjusted to the low pressure side. Then, the balance between the counterclockwise moment due to the crank chamber pressure as the back pressure of each piston 9 and the spring force of the first spring S1 and the clockwise moment due to the front pressure of each piston 9 and the spring force of the second spring S2 is lost. Further, with respect to the integral member of the swash plate 15 and the journal 13, the clockwise moment in the direction of increasing the inclination angle of the swash plate 15 about the second rotation fulcrum portion 14b becomes large, and the connecting link 14 reaches a position where both moments balance. Rotates in the direction of arrow a in FIGS. The rotation angle of the connecting link 14 increases the inclination angle of the swash plate 15. When the inclination angle of the swash plate 15 increases, the reciprocating stroke of each piston 9 increases, the refrigerant discharge capacity increases, and the cooling capacity and the like increase.

  Further, when the heat load of the refrigeration cycle is reduced, the pressure in the crank chamber 10 is adjusted to the high pressure side. Then, the balance between the counterclockwise moment due to the crank chamber pressure as the back pressure of each piston 9 and the spring force of the first spring S1 and the clockwise moment due to the front pressure of each piston 9 and the spring force of the second spring S2 is lost. The counterclockwise moment in the direction of decreasing the inclination angle of the swash plate 15 about the second rotation fulcrum portion 14b with respect to the integral member of the swash plate 15 and the journal 13 is increased, and the link is linked to a position where both moments balance. 14 rotates in the direction of the arrow b in FIGS. The inclination angle of the swash plate 15 is reduced by the rotation of the connecting link 14. When the inclination angle of the swash plate 15 is reduced, the reciprocating stroke of each piston 9 is reduced, the refrigerant discharge capacity is reduced, and the cooling capacity and the like are reduced. The variable displacement compressor 1 saves power by such operation.

  In the operation process of the variable displacement compressor 1 described above, the sliding resistance cylinder 31 on the inner surface side of the sleeve 12 slides on the outer peripheral surface of the drive shaft 4 during the movement for changing the inclination angle of the swash plate 15. Regardless of the position of the inclination angle of the swash plate 15, a certain sliding resistance is applied by the sliding resistance cylinder 31. Therefore, when the integral member of the journal 13 and the swash plate 15 is located at the moment balance position described above, the back pressure and the front pressure of each piston 9 fluctuate, and the journal 13 and the swash plate 15 have an inclination angle. Even if an attempt is made to move in the changing direction, the sliding resistance is applied by the sliding resistance adding means 30, and therefore the fluttering of the swash plate 15 can be prevented as much as possible. In addition, when the journal 13 and the swash plate 15 are moved to change the inclination angle, a constant sliding resistance is applied by the sliding resistance adding means 30, so that stable control is possible.

  In this embodiment, the spring forces of the first spring S1 and the second spring S2 are applied to both ends of the sleeve 12, respectively. Therefore, in the variable displacement compressor 1 that can return the swash plate 15 to the initial drive position after the operation is stopped by the balance of the spring force of the first and second springs S1 and S2, the fluttering of the swash plate 15 can be prevented as much as possible. . In particular, the swash plate 15 is likely to flutter at a position where the spring forces of the first spring S1 and the second spring S2 are balanced, but fluttering of the swash plate 15 at such a position can be prevented.

  In this embodiment, the sliding resistance adding means 30 has a sliding resistance cylinder 31 provided between the inner peripheral surface of the sleeve 12 and the outer peripheral surface of the drive shaft 4. Accordingly, since the sleeve 12 moves linearly with respect to the drive shaft 4, it is only necessary to apply a certain sliding resistance between the members that move relatively linearly, so that the configuration of the sliding resistance cylinder 31 may be simple. .

  In this embodiment, the sliding resistance member is a sliding resistance cylinder 31 having a cylindrical opening, and the sliding resistance cylinder 31 is driven by an elastic return force of a pair of ring pins 32. 4, even when the sliding resistance cylinder 31 is worn, the sliding resistance cylinder 31 is reduced in diameter and continues to press against the drive shaft 4. Maintain sliding resistance.

  In this embodiment, the sleeve 12 is arranged so as to be sandwiched between the pair of ring pins 32 on the outer peripheral surface of the sliding resistance cylinder 31, and the sliding resistance cylinder 31 and the sleeve 12 are integrally formed by the pair of ring pins 32. It is said that. Therefore, since the sliding resistance cylindrical body 31 and the sleeve 12 are integrated, the assembling property and handling property of the sliding resistance cylindrical body 31 are good.

  In this embodiment, the sliding resistance adding means 30 is provided between the sleeve 12 and the drive shaft 4, but a certain sliding resistance can be applied when moving to change the inclination angle of the swash plate 15. If possible, the installation position and its configuration are not limited.

1 is an overall cross-sectional view of a variable displacement compressor according to an embodiment of the present invention. 1 is an enlarged cross-sectional view of a main part of a variable capacity compressor, showing an embodiment of the present invention. FIG. 3 shows an embodiment of the present invention and is a cross-sectional view taken along line AA in FIG. 2. 1 shows an embodiment of the present invention, where (a) is a plan view of a sleeve and sliding resistance adding means, (b) is a front view of the sleeve and sliding resistance adding means, and (c) is FIG. 4 (b). It is a BB sectional view. 1 shows an embodiment of the present invention, (a) is a plan view of a sliding resistance cylinder, (b) is a front view of the sliding resistance cylinder, and (c) is a CC line in FIG. 5 (b). It is sectional drawing. 1 shows an embodiment of the present invention, in which (a) is a front view of a ring pin, and (b) is a cross-sectional view taken along line DD of FIG. 6 (a). It is sectional drawing of the variable capacity compressor of a prior art example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Variable capacity compressor 2 Housing 4 Drive shaft 8 Cylinder bore 9 Piston 10 Crank chamber 11 Rotor 12 Sleeve 13 Journal 14 Connection link 15 Swash plate 10
30 Sliding resistance adding means 31 Sliding resistance cylinder (sliding resistance member)
32 Ring pin

Claims (5)

A plurality of cylinder bores (8) and a crank chamber (10) communicating with the cylinder bores (8) are provided in the housing (2), and the drive shaft (4) is rotatable in the housing (2) so as to penetrate the precursor crank chamber. A rotor (11) is fixed to the drive shaft (4), a sleeve (12) is provided on the outer periphery of the drive shaft (4) so as to be movable in the axial direction, and the outer periphery of the sleeve (12) is The sleeve (12) is provided with a journal (13) for guiding the change of inclination, and the connecting link (14) for connecting the journal (13) and the rotor (11) is provided, and the outer periphery of the journal (13). Is provided with a swash plate (15) that swings by the rotation of the jar (13), and a plurality of pistons (9) that reciprocate in the cylinder bores (8) by the swing of the swash plate (15). Provided,
By adjusting the crank chamber pressure, which is the back pressure of each piston (9), the journal (13) and the swash plate (15) around the rotation fulcrum of the rotor (11) and the connecting link (14). The moment acting on the integral member is adjusted, and the inclination angle is varied while the integral member of the journal (13) and the swash plate (15) is guided by the connecting link (14) and the sleeve (12), In the variable displacement compressor (1) in which the reciprocating stroke of each piston (9) is varied by varying the inclination angle of the swash plate (15),
A variable displacement compressor (30) provided with a sliding resistance adding means (30) for applying a certain sliding resistance during movement of varying the inclination angle of the journal (13) and the swash plate (15). 1). Variable displacement compressor (1) according to claim 1,
The variable capacity compressor (1) is characterized in that the spring force of the first spring (S1) and the second spring (S2) is applied to both ends of the sleeve (12). A variable displacement compressor (1) according to claim 1 or claim 2,
The sliding resistance adding means (30) includes a sliding resistance member (31) provided between the inner peripheral surface of the sleeve (12) and the outer peripheral surface of the drive shaft (4). Variable capacity compressor (1). Variable displacement compressor (1) according to claim 3,
The sliding resistance member (31) is a sliding resistance cylinder (31) having a cylindrical opening, and the sliding resistance cylinder (31) is an elastic member of a pair of ring pins (32). The variable capacity compressor (1), which is pressed against the outer periphery of the drive shaft (4) by a restoring force. Variable displacement compressor (1) according to claim 4,
The sleeve (12) is disposed on the outer peripheral surface of the sliding resistance cylinder (31) so as to be sandwiched by the pair of ring pins (32), and the sliding resistance cylinder is formed by the pair of ring pins (32). A variable displacement compressor (1), wherein the body (31) and the sleeve (12) are formed as an integral member.

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