JP2005163673A - Variable displacement swash plate type compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement swash plate type compressor capable of preventing abnormal noise (striking noise) at the time of torque fluctuation. <P>SOLUTION: A front side spring 150 is twisted around a central axis and arranged between a swash plate 101 and a plate 110, such that a drive hole 111 and a drive pin 102 constituting hinge mechanisms 102, 111 are always in an abutting state as is the case with at the time of rotation. Due to this, the front side spring 150 can not only energize the swash plate 101 in a shaft 100 direction but also apply, to the swash plate 101, rotational torque which is enough to overcome negative torque at the time of torque fluctuation. As a result, the drive hole 111 and the drive pin 102 can be kept in the abutting state all the time as is the case with at the time of rotation, and generation of abnormal noise can be prevented at the time of torque fluctuation. Therefore, in a specific rotational speed range (abnormal noise generating rotational speed range NL to NH) where torque fluctuation exceeds a certain level, even when minimum capacity operation of the compressor is performed, generation of abnormal noise can be suppressed. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to an engine-driven variable displacement swash plate compressor in which a variable displacement swash plate compressor whose capacity can be continuously varied is driven by an engine without using a magnet clutch. For example, it is suitable for use as a refrigerant compressor of a vehicle air conditioner or the like.

  Conventionally, a cylinder is provided in the housing, the piston is reciprocated by swinging the swash plate in the cylinder, and the reciprocating stroke of the piston is varied by varying the inclination angle between the swash plate and the shaft, There is known a variable capacity swash plate compressor capable of continuously changing the compression capacity.

  In a vehicle air conditioner or the like, this variable capacity swash plate compressor is used as a refrigerant compressor for compressing a refrigerant, and a cooling load that changes depending on an engine load or a passenger compartment temperature, or air immediately after a refrigerant evaporator. There is one in which the compression capacity of the refrigerant compressor is controlled in accordance with the frost state of the refrigerant evaporator indicated by the temperature.

  In this type of device, since the refrigerant compressor is continuously driven, the driving force of the refrigerant compressor is reduced compared to a device that performs ON / OFF control in which the refrigerant compressor is stopped and then driven again. Therefore, the refrigerant can be efficiently compressed. When the vehicle air conditioner is turned off, or during MIN operation control during capacity control operation, the variable capacity swash plate compressor has the minimum capacity to improve fuel efficiency and internal lubrication of the refrigerant compressor. (For example, 0.5 to 1% capacity).

  However, in the conventional vehicle having the configuration in which the refrigerant compressor is continuously driven as described above, the rotation of the refrigerant compressor is also large due to the rotation fluctuation of the diesel engine or auxiliary equipment (for example, an alternator) having a large torque fluctuation. There is a problem that fluctuations occur and abnormal noise such as a striking sound is generated in the clearance portion provided in each sliding portion.

With respect to such a problem, Patent Document 1 discloses a technique of providing a buffer member at a site where a hitting sound is generated. Further, in Patent Document 2 filed in the past by the present applicant, the force of a spring biasing the swash plate is biased to generate a rotational moment to maintain the state of the swash plate, and abnormal noise is generated when torque changes. Is preventing.
JP 2001-123944 A JP 2001-295758 A

  In recent years, there has been a demand for lower noise in vehicles, and countermeasures against hitting sound have been implemented by reviewing the above-described conventional technology and clearances of each part. However, the situation is not completely solved yet. The present invention has been made in view of the above-described conventional problems, and an object of the present invention is to provide a variable capacity swash plate compressor that can prevent generation of abnormal noise during torque fluctuation.

  In order to achieve the above object, the present invention employs technical means described in claims 1 to 7. That is, in the first aspect of the present invention, the plate side hole (111) and the swash plate side pin (102) constituting the hinge mechanism (102, 111) are always in the contact state similar to that during rotation driving. Thus, the front-side spring (150) is twisted around the central axis and is arranged between the swash plate (101) and the plate (110).

  FIG. 5 is a graph showing an example of the relationship between the rotational speed of the engine and the torque fluctuation level applied to the compressor. As shown in the graph, the torque fluctuation due to the engine and the auxiliary machinery has a characteristic having a peak in a specific rotational speed range close to a low speed. When the minimum capacity operation of the compressor is performed in a specific rotational speed range (abnormal noise generation rotational speed range NL to NH) in which the torque fluctuation becomes larger than a certain level, abnormal noise is generated, and in other rotational speed ranges, there is a problem. I understand that there is no.

  FIG. 6 is a graph showing a state when the torque fluctuation applied to the conventional compressor is large. As shown in the graph, the torque applied from the engine to the compressor greatly fluctuates within one rotation due to fluctuations in the rotation of the engine and accessories, so it can be viewed as a combined torque combined with the torque for driving the compressor. However, there is a portion (hatching portion) that varies greatly and periodically becomes negative torque. From this, it can be seen that the compressor is instantaneously rotated in the reverse direction, which is the cause of the impact sound caused by backlash at the clearance.

  However, according to the first aspect of the present invention, the swash plate (101) is biased in the axial direction of the shaft (100) by arranging the front side spring (150) twisted around the central axis. In addition to the above, a rotational torque that can overcome the negative torque described above can be applied, so that the plate-side hole portion (111) and the swash plate-side pin portion (102) always come into contact with each other as in rotational driving. The state can be maintained, and the generation of abnormal noise at the time of torque fluctuation can be prevented. Thereby, even if the minimum capacity operation of the compressor is performed in a specific rotation speed range (abnormal noise generation rotation speed range NL to NH) in which the torque fluctuation becomes larger than a certain level, generation of abnormal noise is suppressed.

  In the invention according to claim 2, the swash plate (101) and the plate (110) are each provided with a locking portion (101a, 110a) for locking the end of the front side spring (150). It is characterized by that. According to the second aspect of the present invention, the rotational torque of the front side spring (150) twisted and assembled is reliably and continuously applied between the swash plate (101) and the plate (110). Necessary.

  In the invention according to claim 3, the plate side hole portion (111) and the swash plate side pin portion (102) constituting the hinge mechanism (102, 111) are always in a contact state similar to that during rotation driving. Thus, the elastic member (112) is disposed between the plate-side hole (111) and the swash plate-side pin (102).

  According to the third aspect of the present invention, by inserting the elastic member (112), the plate side hole portion (111) and the swash plate side pin portion (102) are always in a contact state similar to that during rotation driving. Can be maintained, and the generation of abnormal noise during torque fluctuations can be prevented. Thereby, even if the minimum capacity operation of the compressor is performed in a specific rotation speed range (abnormal noise generation rotation speed range NL to NH) in which the torque fluctuation becomes larger than a certain level, generation of abnormal noise is suppressed.

  In the invention according to claim 4, the holding shape portion (113) that holds the elastic member (112) on the surface of the plate side hole portion (111) that faces the surface that the swash plate side pin portion (102) abuts. ). According to the fourth aspect of the invention, it is necessary to continuously hold the inserted elastic member (112). However, the groove shape is not limited to that shown in FIG.

  Further, in the invention according to claim 5, the swash plate side pin is arranged so as to close the clearance between the plate side hole portion (111) constituting the hinge mechanism (102, 111) and the swash plate side pin portion (102). A split groove (103) is provided on the tip side of the portion (102) to form a split pin shape, and the swash plate side pin portion (102) is lightly press-fitted into the plate side hole portion (111). Yes.

  According to the fifth aspect of the present invention, the plate side hole (111) and the swash plate side pin are formed by lightly press-fitting the swash plate side pin (102) into the plate side hole (111) in the form of a split pin. Since the clearance with the portion (102) is reduced and there is no play, it is possible to prevent the generation of abnormal noise during torque fluctuation. Thereby, even if the minimum capacity operation of the compressor is performed in a specific rotation speed range (abnormal noise generation rotation speed range NL to NH) in which the torque fluctuation becomes larger than a certain level, generation of abnormal noise is suppressed.

  The invention according to claim 6 is characterized in that an R shape is applied to the groove bottom of the split groove (103). According to the sixth aspect of the present invention, it is possible to prevent the swash plate side pin portion (102) from being cracked due to stress concentration. However, the shape of the dividing groove (103) is not limited to that illustrated in FIG.

  Further, the invention according to claim 7 is characterized in that the variable displacement swash plate compressor is driven without a magnet clutch. According to the seventh aspect of the present invention, any of the first to sixth aspects of the invention described above is suitable for use in a clutchless type compressor that is operated with a minimum discharge capacity even during a compression stop. It depends on what. In addition, the code | symbol in the bracket | parenthesis of each said means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

(First embodiment)
Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a cross-sectional view of a variable displacement swash plate compressor according to a first embodiment of the present invention. In FIG. 1, reference numeral 130 denotes an aluminum alloy rear housing, in which a plurality of cylinders 131 are formed. In the present embodiment, the cylinders 131 are arranged at six equal intervals on the concentric circle. A piston 132 is slidably disposed in the cylinder 131. The piston 132 is subjected to a surface treatment so that good sliding with the cylinder 131 occurs.

  Reference numeral 133 in FIG. 1 denotes a front housing that is airtightly arranged with respect to the rear housing 130 via an O-ring. This front housing is also made of an aluminum alloy, and a control pressure chamber 134 for holding the swash plate 101 is formed therein. The shaft 100 is rotatably held by the front housing 133 and the rear housing 130 via bearings 135 and 136, respectively. One end of the shaft 100 is exposed outward from the boss portion 137 of the front housing 133, and the hub 139 of the pulley 138 is fixed to the exposed portion by a bolt 140.

  The pulley 138 is rotatably disposed on the outer surface of the boss portion 137 of the front housing 133 described above via a bearing 141. This pulley 138 receives the rotational force of the vehicle running engine via a V belt (not shown). Accordingly, the front and rear housings 133 and 130 are also attached to the side surface of the vehicle travel engine.

  An iron lug plate (plate) 110 is press-fitted and fixed to the iron shaft 100. Therefore, the lug plate 110 rotates in the control pressure chamber 134 of the front housing 133 integrally with the shaft 100. The lug plate 110 is supported by a thrust bearing 142, and rotates in the control pressure chamber 134 while receiving an axial load by the front housing 133 via the thrust bearing 142.

  The swash plate 101 is attached to the outer periphery of the shaft 100 so that the inclination angle θ (shown in FIG. 2) can be varied. Specifically, the drive pin 102 of the swash plate 101 comes into contact with the inner surface of the drive hole 111 of the lug plate 110 to transmit the rotation of the lug plate 110 to the swash plate 101. A predetermined clearance is formed between the swash plate 101 and the shaft 100, and the swash plate 101 can move along the outer surface of the shaft 100 using this clearance.

  A front-side spring 150 is disposed between the front housing 133 and the swash plate 101. The front-side spring 150 reduces the inclination angle θ of the swash plate 101, in other words, the swash plate 101 rises and the piston is lifted. A load in a direction in which the reciprocating stroke 132 is reduced is applied. Since the front side spring 150 is a main part of the present invention, details will be described later.

  Conversely, a rear spring 151 is disposed between the rear housing 130 and the swash plate 101. The rear spring 151 urges a load in a direction in which the inclination angle θ of the swash plate 101 is increased, in other words, in a direction in which the swash plate 101 is inclined with respect to the shaft 100 and the reciprocating stroke of the piston 132 is increased. Yes.

  In FIG. 1, reference numeral 152 denotes an end housing disposed behind the rear housing 130, and a suction passage 153 is formed therein. In the end housing 152, an electromagnetic valve 154 that switches and controls the pressure Pc in the control pressure chamber 134 is disposed. That is, although not shown, a control pressure passage is formed between the control pressure chamber 134 and the electromagnetic valve 154, and the pressure supplied to the control pressure chamber 134 through this control pressure passage is reduced to the suction passage 153 side. Switching is made between the suction pressure Ps and the discharge pressure Pd on the discharge chamber 155 side.

  Power transmission is performed between the swash plate 101 and the piston 132 by the spherical shoes 160 and 161. The spherical shoes 160 and 161 hold both surfaces of the swash plate 101, and the outer shape of both the shoes 160 and 161 is a sphere when arranged on both surfaces. Therefore, even if the inclination angle θ between the swash plate 101 and the piston 132 is variable, the reciprocating stroke of the swash plate 101 is reliably transmitted to the piston 132 via the spherical shoes 160 and 161. Further, tapered portions 162 and 163 are formed on the surface of the spherical shoes 160 and 161 on the swash plate 101 side, so that the lubricating oil is satisfactorily supplied between the spherical shoes 160 and 161 and the swash plate 101. ing.

  A passage hole 170 is formed inside the shaft 100, and the passage hole 170 is connected to the control pressure chamber 134 via a communication hole 171 opened near the front bearing 135. The end face of the passage hole 170 opens into the suction pressure chamber 172. Therefore, the refrigerant in the control pressure chamber 134 is sucked to the suction chamber 172 side through the passage hole 170. However, the passage is narrowed between the control pressure chamber 134 and the communication hole 171 so that the refrigerant suction is not excessive.

  A biasing member 180 is disposed between the rear spring 151 and the swash plate 101 so that the spring load partially strikes the swash plate 101. Only a part of the end face of the rear spring 151 can abut against the swash plate 101 via the offset member 180.

  Next, the operation of the compressor having the above configuration will be described. When a vehicle travel engine (not shown) is driven to rotate, the pulley 138 receives the rotation via a V belt (not shown). The rotation of the pulley 138 is transmitted to the shaft 100 via the hub 139, and the shaft 100 is supported by bearings 135 and 136 in the housings 133 and 130 and rotates. This rotation is transmitted to the lug plate 110 press-fitted into the shaft 100, and the lug plate 110 also rotates in the control pressure chamber 134. The rotation of the lug plate 110 is transmitted to the swash plate 101 via the drive hole 111 and the drive pin 102, and the swash plate 101 also rotates in the control pressure chamber 134.

  The rotation of the swash plate 101 is transmitted to the piston 132 through the spherical shoes 160 and 161. The circumferential movement of the swash plate 101 is released when the spherical shoes 160 and 161 slide on the outer periphery of the swash plate, and only the reciprocating stroke generated when the swash plate 101 is inclined with respect to the shaft 100 is transmitted to the piston 132. The As a result, the piston 132 reciprocates in the cylinder 131 with a reciprocating stroke corresponding to the inclination angle θ of the swash plate 101.

  Along with this reciprocation, low-temperature and low-pressure refrigerant sucked from the refrigerant evaporator side (not shown) of the vehicle air conditioner is sucked into the cylinder 132 from the suction passage 153 through the suction chamber 172. When the refrigerant in the cylinder 131 is compressed with the reciprocating stroke of the piston 132 and the refrigerant pressure becomes higher than the pressure Pd on the discharge chamber 155 side, a discharge valve (not shown) is opened and the refrigerant is discharged to the discharge chamber 155 side. The

  Here, the inclination angle θ of the swash plate 101 is controlled solely by the pressure Pc in the control pressure chamber 134. When the pressure Pc in the control pressure chamber 134 is increased, it is difficult for the piston 132 to move toward the control pressure chamber 134 due to the pressure balance. That is, when the pressure Pc in the control pressure chamber 134 is increased, the reciprocating stroke of the piston 132 is decreased, and conversely, when the pressure Pc in the control pressure chamber 134 is decreased, the reciprocating stroke of the piston 132 is increased. The inclination angle [theta] increases.

  By controlling the pressure Pc in the control pressure chamber 134 in this way, the tilt angle θ of the swash plate 101 and, consequently, the reciprocating stroke of the piston 132 can be controlled. Pressure control in the control pressure chamber 134 is performed by an electromagnetic valve 154. The electromagnetic valve 154 uses a normally open type electromagnetic valve. When the electromagnetic valve 154 is not excited, the high pressure on the discharge chamber 155 side is supplied into the control pressure chamber 134. That is, when the solenoid valve 154 is not excited, the pressure Pc in the control pressure chamber 134 is increased, the inclination angle θ of the swash plate 101 is decreased, and the piston 132 performs the minimum capacity operation.

  Conversely, the suction pressure chamber 172 and the control pressure chamber 134 communicate with each other by exciting the electromagnetic valve 154. As a result, the pressure Pc in the control pressure chamber 134 is reduced, the inclination angle θ of the swash plate 101 is increased, the reciprocating stroke of the piston 132 is increased, and the capacity of the compressor is increased. FIG. 2 shows a state where the discharge capacity of the compressor is maximized by decreasing the pressure Pc in the control pressure chamber 134 to increase the inclination angle θ of the swash plate 101.

  Next, the main part of the present invention will be described. The drive hole (plate side hole) 111 and the drive pin (swash plate side pin) 102 constituting the hinge mechanisms 102 and 111 of the swash plate 101 and the lug plate 110 are always in the same contact state as in the rotational drive. Thus, the front side spring 150 is twisted around the central axis and disposed between the swash plate 101 and the lug plate 110.

  According to this, by arranging the front side spring 150 to be twisted around the central axis, not only the swash plate 101 is biased in the axial direction of the shaft 100 but also a rotational torque that only overcomes the negative torque described above. Therefore, the drive hole 111 and the drive pin 102 can always maintain a contact state similar to that during rotational driving, and the generation of abnormal noise during torque fluctuation can be prevented. Thereby, even if the minimum capacity operation of the compressor is performed in a specific rotation speed range (abnormal noise generation rotation speed range NL to NH) in which the torque fluctuation becomes larger than a certain level, generation of abnormal noise is suppressed.

  For this purpose, the swash plate 101 and the lug plate 110 are provided with locking portions 101a and 110a for locking the end portions of the front springs 150, respectively. According to this, it is necessary to apply the rotational torque of the front side spring 150 twisted and assembled between the swash plate 101 and the lug plate 110 reliably and continuously.

(Second Embodiment)
FIG. 3 is a schematic view of a hinge portion in the second embodiment of the present invention. The main part of the present invention will be described. Between the drive hole 111 and the drive pin 102, the drive hole 111 and the drive pin 102 constituting the hinge mechanisms 102 and 111 are always in a contact state similar to that at the time of rotational drive. An elastic member 112 such as a spring is disposed on the top.

  According to this, by inserting the elastic member 112, the drive hole 111 and the drive pin 102 can always maintain a contact state similar to that at the time of rotational drive, and noise generation at the time of torque fluctuation can be prevented. it can. Thereby, even if the minimum capacity operation of the compressor is performed in a specific rotation speed range (abnormal noise generation rotation speed range NL to NH) in which the torque fluctuation becomes larger than a certain level, generation of abnormal noise is suppressed.

  Further, a groove shape 113 is provided as a holding shape portion for holding the elastic member 112 on the surface of the driving hole 111 that faces the surface on which the driving pin 102 abuts. According to this, it is necessary to keep the inserted elastic member 112 continuously. However, the groove shape is not limited to that shown in FIG. Further, as shown in FIG. 3, when there are two hinge portions, the elastic member 112 may be provided only on one side.

(Third embodiment)
FIG. 4 is a schematic view of a hinge portion in the third embodiment of the present invention. The main part of the present invention will be described. A split groove 103 is provided on the distal end side of the drive pin 102 so that the clearance between the drive hole 111 and the drive pin 102 constituting the hinge mechanisms 102 and 111 is narrowed, thereby forming a split pin shape. In addition, the drive pin 102 is lightly press-fitted into the drive hole 111.

  According to this, since the drive pin 102 has a split pin shape and is lightly press-fitted into the drive hole 111, the clearance between the drive hole 111 and the drive pin 102 is reduced and there is no play, so noise is generated when torque changes. Can be prevented. Thereby, even if the minimum capacity operation of the compressor is performed in a specific rotation speed range (abnormal noise generation rotation speed range NL to NH) in which the torque fluctuation becomes larger than a certain level, generation of abnormal noise is suppressed.

  In addition, an R shape is applied to the groove bottom of the split groove 103. According to this, it is possible to prevent the drive pin 102 from being cracked due to stress concentration. However, the shape of the dividing groove 103 is not limited to that illustrated in FIG.

  The variable displacement swash plate compressor described above is driven without a magnet clutch. According to this, all of the variable displacement swash plate compressors of the above-described embodiments are suitable for use in a clutchless compressor that is operated with a minimum discharge capacity even when the compression is stopped.

(Other embodiments)
In the above-described embodiment, the locking portions 101a and 110a that lock the ends of the front-side springs 150 provided on the swash plate 101 and the lug plate 110 have a protruding shape, but the present invention is not limited to this. Instead of a thing, the hole shape etc. which insert the line end of a spring may be sufficient.

1 is a cross-sectional view of a variable capacity swash plate compressor according to a first embodiment of the present invention. It is sectional drawing which shows the time of the maximum capacity | capacitance driving | operation of the compressor of FIG. It is a schematic diagram of the hinge part in 2nd Embodiment of this invention. It is a schematic diagram of the hinge part in 3rd Embodiment of this invention. It is a graph showing an example of the relationship between the rotational speed of an engine, and the torque fluctuation level added to a compressor. It is a graph showing the state at the time of the torque fluctuation large applied to the conventional compressor.

Explanation of symbols

DESCRIPTION OF SYMBOLS 100 ... Shaft 101 ... Swash plate 101a ... Locking part 102 ... Drive pin (swash plate side pin part, hinge mechanism)
103 ... Split groove 110 ... Lug plate (plate)
110a: retaining portion 111 ... driving hole (plate side hole, hinge mechanism)
DESCRIPTION OF SYMBOLS 112 ... Elastic member 113 ... Holding shape part 130 ... Rear housing (housing)
131 ... Cylinder 132 ... Piston 133 ... Front housing (housing)
150 ... Front side spring 151 ... Rear side spring θ ... Inclination angle

Claims (7)

A housing (130, 133) with a cylinder (131);
A shaft (100) rotatably supported relative to the housing (130, 133);
A plate (110) provided to be rotatable integrally with the shaft (100) in the housing (130, 133);
A swash plate (101) which is operatively connected to the plate (110) by inserting the shaft (100) through the housing (130, 133) and swingable around the shaft (100);
A piston (132) disposed in the cylinder (131) and operatively connected to the swash plate (101) so as to reciprocate within the cylinder (131) by swinging of the swash plate (101);
The plate (110) and the swash plate (101) are coupled so that the inclination angle (θ) formed by the rotation axis of the shaft (100) and the central axis of the swash plate (101) can be changed and can be integrally rotated. Hinge mechanism (102, 111);
A front-side spring (150) disposed in an outer peripheral position of the shaft (100) in the housing (130, 133) and biasing the swash plate (101) in a direction in which the inclination angle (θ) decreases. A rear side spring (151) for urging in a direction in which the inclination angle (θ) increases,
In the variable displacement swash plate type compressor in which the tilt angle (θ) is varied by varying the swing center position of the swash plate (101) and the compression capacity of the piston (132) is varied,
The front-side spring (150) so that the plate-side hole portion (111) and the swash plate-side pin portion (102) constituting the hinge mechanism (102, 111) are always in contact with each other as in the case of rotational driving. The variable capacity swash plate compressor is arranged between the swash plate (101) and the plate (110) by twisting it around the central axis.   The locking portion (101a, 110a) for locking the end portion of the front side spring (150) is provided on each of the swash plate (101) and the plate (110). The variable capacity swash plate compressor described. A housing (130, 133) with a cylinder (131);
A shaft (100) rotatably supported relative to the housing (130, 133);
A plate (110) provided to be rotatable integrally with the shaft (100) in the housing (130, 133);
A swash plate (101) which is operatively connected to the plate (110) by inserting the shaft (100) through the housing (130, 133) and swingable around the shaft (100);
A piston (132) disposed in the cylinder (131) and operatively connected to the swash plate (101) so as to reciprocate within the cylinder (131) by swinging of the swash plate (101);
The plate (110) and the swash plate (101) are coupled so that the inclination angle (θ) formed by the rotation axis of the shaft (100) and the central axis of the swash plate (101) can be changed and can be integrally rotated. Hinge mechanism (102, 111),
In the variable displacement swash plate type compressor in which the tilt angle (θ) is varied by varying the swing center position of the swash plate (101) and the compression capacity of the piston (132) is varied,
The plate side hole (111) is configured so that the plate side hole (111) and the swash plate side pin (102) constituting the hinge mechanism (102, 111) are always in contact with each other in the same manner as in rotational driving. ) And the swash plate side pin portion (102), an elastic member (112) is disposed.   A holding shape portion (113) for holding the elastic member (112) is provided on a surface of the plate side hole portion (111) opposite to a surface with which the swash plate side pin portion (102) contacts. The variable capacity swash plate compressor according to claim 3. A housing (130, 133) with a cylinder (131);
A shaft (100) rotatably supported relative to the housing (130, 133);
A plate (110) provided to be rotatable integrally with the shaft (100) in the housing (130, 133);
A swash plate (101) which is operatively connected to the plate (110) by inserting the shaft (100) through the housing (130, 133) and swingable around the shaft (100);
A piston (132) disposed in the cylinder (131) and operatively connected to the swash plate (101) so as to reciprocate within the cylinder (131) by swinging of the swash plate (101);
The plate (110) and the swash plate (101) are coupled so that the inclination angle (θ) formed by the rotation axis of the shaft (100) and the central axis of the swash plate (101) can be changed and can be integrally rotated. Hinge mechanism (102, 111),
In the variable displacement swash plate type compressor in which the tilt angle (θ) is varied by varying the swing center position of the swash plate (101) and the compression capacity of the piston (132) is varied,
In order to reduce the clearance between the plate side hole (111) constituting the hinge mechanism (102, 111) and the swash plate side pin portion (102), it is divided to the tip side of the swash plate side pin portion (102). A variable capacity swash plate type in which a groove (103) is provided to make a split pin shape and the swash plate side pin portion (102) is lightly press-fitted into the plate side hole portion (111). Compressor.   6. The variable capacity swash plate compressor according to claim 5, wherein the groove bottom of the split groove (103) has an R shape.   The variable displacement swash plate compressor according to any one of claims 1 to 6, wherein the variable displacement swash plate compressor is driven without a magnet clutch.

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