JP2006161591A - Swash plate compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a swash plate compressor avoiding increase in whole length of a compressor and ensure smooth inclination of a rotary drive body. <P>SOLUTION: The swash plate compressor comprises: a shaft 6 passing through a crank chamber 4; the rotary drive body 16 having an opening part 16a in which the shaft 6 is inserted to be rotated in synchronization with the rotation of the shaft 6; and the piston 13 suspended on a peripheral edge of the rotary drive body 16 to reciprocate and slide in a cylinder bore accompanying the rotation of the rotary drive body 16. The swash plate compressor can change a stroke amount of the piston 13 by changing an inclination angle of the rotary drive body 16. The rotary drive body 16 is connected with the shaft 6 to be capable of being inclined through at least one support member (link pin 15), and is connected with a sliding member 23 sliding along the shaft 6. The sliding member 23 is columnar, is inserted to be slidable into a housing space 22 formed in the shaft, and is connected with the rotary drive body 16 through a drive pin 20 penetrating the shaft 6 and held to be capable of moving in a center axis direction of the shaft. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a rotary drive body that is housed in a crank chamber and rotates as the shaft rotates, and a piston that is anchored at the periphery of the rotary drive body and reciprocally slides in the cylinder bore as the rotary drive body rotates. In particular, the swash plate compressor controls the discharge capacity by changing the tilt angle of the rotary drive body, and in particular, the shaft and the rotary drive body are tiltably connected via at least one support member and connected to the shaft. The present invention relates to a compressor connected to a sliding member that slides along.

  As a conventional compressor of this type, a configuration of a swash plate compressor shown in Patent Document 1 described below is known. The swash plate compressor will be described with reference to FIGS. 9 to 12. The compressor has a shaft 102 that passes through the crank chamber 100 and is rotatably supported by the housing 101, and an opening through which the shaft 102 is inserted. 103a and a rotation driving body 103 that is arranged in the crank chamber 100 and rotates in synchronization with the rotation of the shaft 102, and is moored at the periphery of the rotation driving body 103. A piston 105 that reciprocates in a cylinder bore 104 formed in a cylinder block that forms part of the housing; and a suction chamber 106 and a discharge chamber 107 that selectively communicate with the cylinder bore 104 by reciprocating sliding of the piston 105; The discharge capacity is controlled by changing the inclination angle of the rotary drive body 103. In the plate compressor, a rotary drive body 103 is tiltably connected to a shaft 102 via a link pin (support member) 108, and protrudes into the crank chamber 100 via a pair of shoes 109 at a peripheral portion of the rotary drive body 103. The tail of the piston 105 is moored.

  The link pin 108 is provided in an intermediate portion 102a exposed to the crank chamber 100 of the shaft 102, and is fixed on a plane including the axis of the shaft 102, and is formed in the intermediate portion 102a. It has a base portion 108a fixed to the insertion hole 102c by press-fitting or the like, a small diameter portion 108b formed following the base portion 108a, and a head portion 108c formed in a spherical shape at the free end following the small diameter portion 108b. It is configured. The rotary drive body 103 has an engagement hole 103 a provided in the radial direction. The head 108 c of the link pin 108 is engaged with the engagement hole 103 a, and the shaft 102 is interposed via the link pin 108. The driving force is transmitted from.

  Further, a sliding member 110 is provided on the shaft so as to be slidably fitted in the axial direction. The sliding member 110 rotationally drives an arm portion 110 a extending in the radial direction via a support pin 111. The body 103 is configured to be spoke-like. Further, the sliding member 110 is formed with a long hole 110b through which the link pin 108 is inserted so as not to inhibit the sliding of the shaft 102 in the axial direction. The sliding member 110 is urged to the rear side by a spring 112 elastically mounted between the shaft 102 and the flange portion 102b, and is elastically mounted between a spring receiver provided on the rear side of the shaft. The spring 113 is biased toward the front side.

Therefore, when the shaft 102 rotates, the head portion 108c of the link pin 108 that rotates integrally with the shaft 102 presses the inner surface of the engagement hole 103a of the rotary drive body 103, and the shaft 102 is connected to the rotary drive body 103 via the link pin 108. Rotational power is transmitted. Further, when the rotary drive body 103 rotates around the support pin 111, the sliding member 110 is moved along the axis of the shaft 102, and the contact position of the head 108c of the link pin 108 is engaged. It is moved in the axial direction of the hole 103a. Further, the discharge capacity of the compressor is determined by the stroke of the piston 105, and this stroke is determined by the inclination angle of the rotary drive body 103 with respect to the plane perpendicular to the shaft 102. That is, the differential pressure between the pressure applied to the front surface of the piston (pressure in the cylinder bore) and the pressure applied to the back surface of the piston 105, that is, the pressure in the crank chamber, and the biasing force of the springs 112 and 113 biasing the sliding member 110 The inclination of the swash plate is determined at the balance, and the piston stroke is thereby determined.
Japanese Patent No. 3188716

  However, if the above-described configuration is applied to a compressor of a refrigeration cycle using carbon dioxide as a working fluid, the operating pressure is significantly higher than that of a conventional chlorofluorocarbon refrigerant, so that the rotary drive body acts from the piston. The compression reaction force becomes very large. For this reason, the spring that receives the sliding member also needs to have a correspondingly large spring constant. However, if a spring with a large wire diameter is to be installed, a long space is required in the axial direction of the shaft, and the spring is mounted around the shaft. In the above-described configuration, in order to secure a long space in the axial direction, there is an inconvenience that the entire length of the compressor must be increased.

  Further, the sliding member has a function of receiving a moment around an axis (Y axis) perpendicular to the axis of the shaft acting on the rotary drive body, and the moment around the Y axis (so-called torsional moment) is generated from the piston. This is due to the fact that the compressive reaction force acts at a position that is eccentric from the shaft with respect to the rotary drive body, so that it becomes very large when carbon dioxide is used as the refrigerant. For this reason, if the axial length relative to the diameter of the sliding member is not sufficiently secured, the reaction force of the torsional moment acting on both ends of the sliding member in the axial direction of the shaft increases, and a large friction between the sliding member and the shaft occurs. As a result, smooth sliding of the sliding member is hindered, and smooth tilting of the rotary drive body is hindered.

  The present invention has been made in view of such circumstances, and even when used in a high-pressure compressor, it avoids an increase in the overall length of the compressor, and smooth rotation of the rotary drive body. The main object is to provide a swash plate compressor that can be secured.

  In order to achieve the above object, a swash plate compressor according to the present invention includes a shaft that passes through a crank chamber and is rotatably supported by a housing, an opening through which the shaft is inserted, and the crank chamber. A rotary drive body that is arranged and rotates in synchronization with the rotation of the shaft, and a piston that is anchored on a peripheral edge of the rotary drive body and reciprocally slides in a cylinder bore formed in the housing as the rotary drive body rotates. And a suction chamber and a discharge chamber that selectively communicate with the cylinder bore by reciprocating sliding of the piston, and the discharge capacity is controlled by changing the inclination angle of the rotary drive body. The rotary drive body is connected to the shaft via at least one support member so as to be tiltable and is connected to a sliding member that slides along the shaft. The sliding member is formed in a columnar shape and is slidably inserted into an accommodation space provided in the shaft, and is movably held in the central axis direction of the shft through the shaft. It is connected with the said rotational drive body through the pin (Claim 1).

  Therefore, since the sliding member is formed in a columnar shape that is slidably inserted into the accommodation space in the shaft, the sliding member is not formed in the shaft even when the wire diameter of the spring biased by the sliding member is increased. Since there is no member that interferes with the spring, a large space in the shaft direction can be secured. In addition, since a sufficient length in the axial direction with respect to the diameter of the sliding member can be secured, it is possible to reduce the reaction force against the torsional moment acting on both ends of the sliding member in the shaft axial direction.

  In such a configuration, it is desirable that the rotational driving force from the shaft be transmitted to the rotational driving body via the drive pin (claim 2). As described above, when the accommodation space for accommodating the sliding member is formed inside the shaft, when it is configured to transmit the rotational power from the shaft via the link pin attached to the shaft as in the past, The link pin cannot be inserted sufficiently deep into the shaft, and it is difficult to form a strong mounting state. For this reason, there is a concern about a problem in terms of durability, such as a loosened wearing state over time.

  On the other hand, if the drive force is transmitted with a drive pin that penetrates the shaft as in this configuration, there is no need to worry about changes in the mounting state with the shaft over time, ensuring a stable connection state. Thus, it is possible to ensure the reliable transmission of the driving force.

  The sliding member has an axial length of 1.5 times or more the diameter of the sliding member in order to reduce the reaction force against the twisting moment of the rotary drive body and ensure smooth sliding. (Claim 3). Instead of such a configuration, or in addition to such a configuration, in order to ensure further smooth sliding, crowning is performed on both ends in the axial direction of the sliding member (claim 4), A coating film of a solid lubricant may be provided on the sliding contact surface of the sliding member with the shaft.

  As a specific example of the configuration described above, the housing space provided in the shaft is formed by forming the shaft into a bottomed cylindrical shape having a bottom at one end, and between the bottom of the housing space and the sliding member. In addition, the first spring may be mounted on the body (Claim 6), and in addition to this, a spring receiver is provided in the open portion of the storage space, and between the spring receiver and the sliding member of the storage space. The second spring may be elastically mounted (claim 7).

  Further, in order to ensure smooth sliding, lubricating oil can be introduced into the accommodation space together with the refrigerant (Claim 8). You may make it communicate through the communication part provided in the sliding member.

  Further, a holding hole for slidably holding the support member is formed in the rotary drive body, and the holding hole passes through the central axis of the shaft and rotates in a rotation direction with respect to a plane including the top dead center of the rotary drive body. Corresponding to this, the support member is offset to the front side in the rotational direction with respect to a plane passing through the central axis of the shaft and including the top dead center of the rotary drive. (Claim 11).

  Furthermore, even if the support member is formed integrally with the shaft (Claim 12), the drive pin passes through a central axis of the shaft and is on a plane including the top dead center of the rotary drive body. May be provided in the vertical direction (claim 13).

  As described above, according to the present invention, the rotary driving body that is arranged in the crank chamber and rotates in synchronization with the rotation of the shaft is tiltably connected to the shaft via at least one support member, In a swash plate type compressor connected to a sliding member that slides along a shaft, the sliding member is formed in a columnar shape and is slidably inserted into a housing space provided in the shaft, and passes through the shaft to be Since it is connected to the rotary drive body by a drive pin held so as to be movable in the direction, it is possible to secure a sufficient space in the axial direction for arranging a sliding member and a spring for applying a biasing force thereto. Even in a high-pressure compressor, there is no need to increase the overall length.

  In addition, since it is possible to ensure a sufficient length in the axial direction with respect to the diameter of the sliding member, it becomes possible to reduce the reaction force against the torsional moment of the rotary driving body acting on both ends of the sliding member in the shaft axial direction. The friction between the sliding member and the shaft can be reduced to ensure a smooth tilting of the rotary drive body.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS The best embodiment of the present invention will be described below with reference to the accompanying drawings.

  In FIG. 1, a swash plate compressor is used for a refrigeration cycle using carbon dioxide as a working refrigerant. A cylinder block 1 and a valve plate 2 on the rear side (right side in the figure) of the cylinder block 1 are provided. And a front head 5 that covers the cylinder block 1 and that is assembled so as to close the front side (left side in the figure) to define the crank chamber 4. The front head 5 and the rear head 3 are fastened in the axial direction by fastening bolts 35 to form a compressor housing. Even in the cylinder block 1 and the valve plate 2, the rear head 3 is fastened by fastening bolts (not shown). It is concluded to.

  A crank chamber 4 provided by the front head 5 and the cylinder block 1 accommodates a shaft 6 having one end protruding from the front head 5 and to which a power transmission member (not shown) such as a pulley is fixed. One end side of the shaft 6 is provided so as to pass through a boss portion 5 a that protrudes outward from the center portion of the front head 5, and the front side is interposed through a seal member 36 provided between the front head 5. A space between the head 5 is hermetically sealed, and a radial bearing 8 provided on the inner surface of the boss portion 5a and a thrust bearing 9 provided on the inner surface of the front head 5 via a thrust flange 7 provided on the outer peripheral surface. And is supported rotatably. Further, the other end of the shaft 6 is rotatably supported by a recess 10 formed in the center of the cylinder block 1 via a radial bearing 11.

  The cylinder block 1 is formed with the concave portion 10 for supporting the shaft 6 and a plurality of cylinder bores 12 arranged at equal intervals on a circumference centered on the concave portion 10. A single-head piston 13 is inserted into each cylinder bore 12 so as to be reciprocally slidable.

  As shown in FIGS. 2 to 5, the shaft 6 is connected to the rotary drive body 16 through a single link pin 15 as a support member so as to be tiltable. Further, a tail portion 13 a of the piston 13 projecting into the crank chamber 4 via a pair of shoes 17 is moored at the peripheral portion of the rotary drive body 16. Therefore, when the shaft 6 rotates, the rotary drive body 16 rotates integrally with the shaft 6, and this rotational motion is converted into the reciprocating linear motion of the piston 13 via the shoe 17. 12, the volume of the compression chamber 18 formed between the piston 13 and the valve plate 2 is changed.

  The link pin 15 is provided in an enlarged diameter portion 6 a formed at an intermediate portion exposed to the crank chamber 4 of the shaft 6. The link pin 15 has a diameter at a base portion 15c press-fitted into an insertion hole 6e formed in the enlarged diameter portion 6a, a small diameter portion 15b formed following the base portion 15c, and a free end following the small diameter portion 15b. It is constituted by a cylindrical pin having an enlarged head portion 15a. The head 15a of the link pin 15 has a spherical shape with a flat top, and the circumferential surface of the head 15a following the small diameter portion 15b is formed as a curved surface forming a part of a spherical surface. The flat portion is formed in a plane that is perpendicular to the central axis of the base portion 15 c of the link pin 15.

  The rotary drive body 16 is formed in a disk shape having a predetermined thickness, and is formed in the center so as to accommodate the enlarged diameter portion 6a of the shaft 6 with a predetermined clearance. An opening 16a is formed. The opening 16a is formed with a flat portion 16b having a flat surface parallel to both sides facing each other. In addition, a holding hole 16c that extends in parallel with the flat portion 16b and is drilled from the outer periphery of the rotary drive body 16 to the opening 16a and accommodates the head portion 15a of the link pin 15 is formed in the peripheral portion of the rotary drive body 16. It is formed on a plane that passes through the central axis of the shaft 6 and includes the top dead center of the rotary drive body 16. Therefore, the rotary drive body 16 can be smoothly tilted about the head 15a of the link pin 15.

  In addition, a drive pin 20 is installed in the rotation hole 16d formed in the flat portion 16b so as to pass through the shaft 16 and pass through the opening 16a. It is loosely fitted in a state in which the movement is restricted. That is, the drive pin 20 is provided in a direction perpendicular to a plane that passes through the central axis of the shaft 6 and includes the top dead center of the rotary drive body 16. The portion of the shaft 6 through which the drive pin 20 passes extends in the axial direction of the shaft 6 and constitutes a guide groove 6 b that allows the drive pin 20 to move in the axial direction of the shaft 6. A housing space 22 that extends in the axial direction across the front and rear of the drive pin 20 is formed inside the shaft 6. The housing space 22 is formed by opening a cylinder block side end of the shaft 6 and forming a bottomed cylinder with a bottom 6c formed at the end opposite to the shaft 6 side. To the vicinity of the boss 5a of the front head. The housing space 22 is elastically mounted between the sliding member 23 through which the drive pin 20 passes and the sliding member 23 and the bottom portion 6c, and applies an urging force to the sliding member 23 in the axial direction from the front side. The stroking which is elastically mounted between the destroking spring 24 to be performed and the sliding member 23 and the spring receiver 26 provided in the vicinity of the opening, and applies an urging force to the sliding member 23 in the axial direction from the cylinder block side. A spring 25 is accommodated.

  The sliding member 23 is formed in a columnar shape and has an insertion hole 23a formed in a radial direction through which the drive pin 20 is inserted in an intermediate portion, and is slidably inserted into the housing space 22. The axial length is set to 1.5 times the diameter or more. Further, in this example, an annular groove 20a having a reduced diameter is formed at the center of the drive pin 20, and a communication passage 27 that communicates from one end in the axial direction to the other end through the annular groove 20a at the center of the sliding member 23. Is formed so that the front and rear of the sliding member 23 in the housing space 22 communicate with each other in the axial direction. Furthermore, a communication path 6 d is formed in the bottom portion 6 c of the shaft 6 to communicate the housing space 22 with a shaft seal chamber 37 formed in front of the seal member 36 around the shaft.

  Further, the sliding member 23 is provided with crownings 23b having inclined peripheral edges in order to avoid stress concentration with the shaft at both ends in the axial direction. A coating is provided.

  The rear head 3 includes a suction chamber 30 and a discharge chamber 31 formed around the suction chamber 30. The valve plate 2 includes a suction valve (not shown) including the suction chamber 30 and the compression chamber 18. And a discharge hole 33 that connects the discharge chamber 31 and the compression chamber 18 via a discharge valve (not shown). The rear head 3 is equipped with a pressure control valve (not shown) for controlling the crank chamber pressure by controlling the communication state between the discharge chamber 31 and the crank chamber 4 and the communication state between the crank chamber 4 and the suction chamber 30. The crank chamber pressure is controlled by this pressure control valve.

  Therefore, when the shaft 6 rotates, the rotational power is transmitted to the rotational drive body 16 via the drive pin 20, the rotational drive body 16 rotates, and the piston 13 reciprocates in the cylinder bore 12. In the downward stroke, the working fluid in the suction chamber 30 is sucked into the compression chamber 18 through the suction hole 32, and in the upward stroke, the working fluid in the compression chamber is compressed and discharged into the discharge chamber 31 through the discharge hole 33. The Rukoto.

  When the crank chamber pressure is reduced by the pressure control valve, the pressure difference between the crank chamber pressure and the back pressure (compression chamber pressure) of the piston 13 increases, and the rotational drive is performed against the spring force of the destroking spring 24. The body 16 moves to the front side, and the rotation drive body 16 rotates around the head 15a of the link pin 15 to increase the inclination angle of the rotation drive body 16 with respect to the plane perpendicular to the shaft 6 and increase the piston stroke. As a result, the discharge capacity increases. On the other hand, when the crank chamber pressure is increased, the pressure difference between the crank chamber pressure and the back pressure (compression chamber pressure) of the piston 13 is reduced, and the rotary drive body 16 is resisted against the spring force of the stroking spring 25. The rotary drive body 16 moves to the cylinder block 1 side and pivots about the head 15a of the link pin 15, the inclination angle of the rotary drive body 16 decreases, the piston stroke decreases, and the discharge capacity decreases.

  At this time, the sliding member 23 connected to the rotary drive body 16 via the drive pin 20 is formed in a columnar shape that is slidably inserted into the housing space 22 that is long in the axial direction in the shaft 6. Increasing the axial dimension of the member 23 and increasing the wire diameters of the springs (destroking spring 24, stroking spring 25) biased to such an extent that it can be applied to the compressor for carbon dioxide refrigerant. (For example, 3 to 4 mm).

  Further, since the axial length with respect to the diameter of the sliding member 23 is set to 1.5 times or more, the reaction force against the torsional moment of the rotary driving body 16 acting on both ends of the sliding member 23 in the shaft axial direction is reduced. It becomes possible. As a result, friction between the sliding member 23 and the shaft 6 can be reduced, and a smooth tilting of the rotary drive body 16 can be ensured.

  In addition, crowning 23b is applied to both ends of the sliding member 23 in the axial direction. Furthermore, since the sliding contact surface of the sliding member 23 with the shaft 6 is provided with a solid lubricant garment, the sliding member 23 is smoother. It is possible to ensure a safe movement.

  Further, in the above-described configuration, the front and rear of the sliding member 23 of the accommodation space 22 are communicated with each other via the communication passage 27 formed in the sliding member 23 and also communicated with the shaft seal chamber 37. When the interior of the engine is used as a path for returning the lubricating oil or when used as a control bleed path for changing the crank chamber 4, the lubricating oil or the refrigerant can be surely flowed, and the sliding member 23, the shaft 6, Since the supply of the lubricating oil is ensured during this time, smooth movement between the sliding member 23 and the shaft 6 can be ensured.

  Further, in the above-described configuration, the rotational driving force of the shaft 6 is transmitted to the rotational driving body 16 by the drive pin 20 penetrating the shaft 6, so that a large load is not applied to the link pin 15, and the configuration as in this configuration. This configuration is suitable when the sliding member 23 is provided on the hollow shaft 6.

6 and 7 show another configuration example of the swash plate compressor according to the present invention.
In this example, the link pin 15 constituting the support member is formed integrally with the shaft 6. The link pin 15 extends perpendicularly to the axis of the shaft 6, and a head portion 15 a having a curved surface whose peripheral surface forms a part of a spherical surface is formed at an end portion.

  The shaft 6 is formed by a cylindrical first shaft member 60a pivotally supported on the front head 5 and the cylinder block by radial bearings 8 and 11, and by press-fitting so as to close a front side end portion of the first shaft member 60a. And a second shaft member 60b that is fitted and protrudes from the front head 5 and to which a power transmission member (not shown) such as a pulley is fixed. The first and second shaft members 60a and 60b provide a cylinder block side inside the shaft. A housing space 22 is formed, and the bottom portion 6c is configured by the second shaft member 60b.

  The housing space 22 is elastically mounted between the sliding member 23 through which the drive pin 20 penetrates and the sliding member 23 and the bottom portion 6c so as to apply an urging force to the sliding member 23 in the axial direction from the front side. A straw that is elastically mounted between a destroke spring 24 to be applied and a sliding member 23 and a spring receiver 26 provided in the vicinity of the opening to apply an urging force to the sliding member 23 in the axial direction from the cylinder block side. A king spring 25 is accommodated.

Here, the sliding member 23 has an insertion hole 23a that is formed in a columnar shape and is pierced in the radial direction through which the drive pin 20 is inserted, and is slidably inserted into the accommodation space 22. The length in the axial direction is set to 1.5 times the diameter or more. Similarly to the configuration example, an annular groove 20a having a reduced diameter is formed at the center of the drive pin 20, and the center of the sliding member 23 is connected from one end in the axial direction to the other end through the annular groove 20a. A communication path 27 is formed to communicate the axial direction of the sliding member 23 in the space 22.
Further, the second shaft member 60b constituting the bottom portion 6c of the shaft 6 has a longitudinal hole 6d-1 drilled in the axial direction of the shaft 6 and a radial direction of the shaft 6 connected to the longitudinal hole 6d-1. A communication passage 6d is formed, which is formed by a horizontal hole 6d-2 drilled in the shaft and communicates between the housing space 22 and a shaft seal chamber 37 formed in front of the seal member 36 around the shaft.

Furthermore, in this example, the diameter is formed to be somewhat smaller at the central portion of the sliding member 23, and the reduced diameter portion 23 c prevents contact with the inner wall of the accommodation space at the central portion of the sliding member 23. Further, crowning 23b having an inclined peripheral edge is applied to both ends in the axial direction of the sliding member 23 in order to avoid stress concentration with the shaft, and a solid lubricant is applied to the sliding contact surface with the shaft 6. The coating is provided.
The thrust flange 7 that is externally mounted on the outer peripheral surface of the shaft 6 does not need to be fixed by press-fitting the shaft 6, but is loosely fitted to the shaft 6, and is a flange portion 38 provided on the shaft 6. The axial position of the shaft 6 may be positioned. Other configurations are the same as those in the above configuration example, and thus the same portions are denoted by the same reference numerals and description thereof is omitted.

Even in such a configuration, the same effects as the above configuration example can be obtained, and even when the housing space 22 is formed inside the shaft 6, the link pin 15 is integrated with the shaft 6 to provide sufficient strength. In addition, since the shaft 6 is composed of two bodies of the first shaft member 60a and the second shaft member 60b, it is easy to manufacture the shaft 6 having the accommodation space 22, and It becomes possible to improve processing accuracy.
In addition, it is within the design requirement that the shape of the link pin 15 has a curved surface for avoiding interference with the rotary drive body 16 and avoiding stress concentration.
Furthermore, in this example, since the reduced diameter portion 23c is provided at the center of the sliding member 23, the friction of the sliding member 23 is reduced, and the durability can be increased.

  In any of the above configuration books, the holding hole 16c for slidably holding the link pin 15 passes through the central axis of the shaft 6 and is formed on a plane including the top dead center of the rotary drive body 16. Correspondingly, the link pin 15 also passes through the central axis of the shaft 6 and on a plane including the top dead center of the rotary drive body 16 (through the central axis of the shaft 6 and the drive pin 20 As shown in FIG. 8, the holding hole 16 c formed in the rotary drive body 16 passes through the central axis of the shaft 6 and the top dead center of the rotary drive body 16. Correspondingly to the plane including the point (with respect to the plane passing through the central axis of the shaft 6 and perpendicular to the drive pin 20), the link pin 15 is provided in the same way. May be offset in the direction .

  In such a configuration, since the axis of the link pin 15 and the plane passing through the center of the shaft 6 and including the top dead center of the rotary drive body 16 are shifted, the drive pin 20 of the rotary drive body 16 is shifted. It is possible to reduce the rotational moment (torsional moment) about the axis that is perpendicular to the axis.

  In the above-described configuration, the case where one link pin 15 is used as a support member for connecting the shaft 6 and the rotary drive body 16 is shown. However, the shaft 6 and the shaft 6 can be rotated using two or more link pins. The driver 16 may be connected.

FIG. 1 is a sectional view showing a swash plate compressor according to the present invention. FIG. 2 is an enlarged cross-sectional view showing a connected state of the shaft, the sliding member, the rotary drive body, and the piston of the swash plate compressor shown in FIG. FIG. 3 is a perspective view showing the connected state of FIG. FIG. 4 is an exploded perspective view showing the connecting elements of the shaft, the sliding member, and the rotary drive body of the swash plate compressor according to the present invention. FIG. 5 is a cross-sectional view of the connected state of the shaft, the sliding member, and the rotary drive body of the swash plate compressor according to the present invention as seen from the axial direction of the shaft. FIG. 6 is a cross-sectional view showing another configuration example of the swash plate compressor according to the present invention. FIG. 7 is an enlarged cross-sectional view showing a connected state of the shaft, the sliding member, the rotary drive body, and the piston of the swash plate compressor shown in FIG. FIG. 8 is a cross-sectional view showing a modified example of the connected state of the shaft, the sliding member, and the rotary drive body of the swash plate compressor according to the present invention. FIG. 9 is a cross-sectional view showing the overall configuration of a conventional swash plate compressor. FIG. 10 is a perspective view showing a connected state of the shaft, the sliding member, and the rotary drive body of the swash plate compressor shown in FIG. FIG. 11 is a cross-sectional view showing a conventional configuration showing a connection state of a shaft, a sliding member, and a rotary drive body of a conventional swash plate compressor, viewed from a direction perpendicular to the shaft center. . 12 is a cross-sectional view taken along line XX in FIG.

Explanation of symbols

4 Crank chamber 6 Shaft 6c Bottom 12 Cylinder bore 13 Piston 15 Link pin 16 Rotating drive body 16c Holding hole 20 Drive pin 22 Housing space 23 Sliding member 23b Crowning 24 Destroking spring 25 Stroke spring 26 Spring receiver 27 Communication path

Claims (13)

A shaft that passes through the crank chamber and is rotatably supported by the housing, and a rotary drive body that has an opening through which the shaft is inserted and that is disposed in the crank chamber and rotates in synchronization with the rotation of the shaft; A piston moored at the periphery of the rotary drive and reciprocatingly slides in a cylinder bore formed in the housing as the rotary drive rotates, and a suction selectively communicating with the cylinder bore by the reciprocating slide of the piston In the swash plate type compressor having a chamber and a discharge chamber, and controlling the discharge capacity by changing the inclination angle of the rotary drive body,
The rotary drive body is connected to the shaft via a at least one support member so as to be tiltable and is connected to a sliding member that slides along the shaft,
The sliding member includes a drive pin that is formed in a columnar shape and is slidably inserted into a housing space provided in the shaft, and is movably held in the central axis direction of the shaft through the shaft. And a swash plate compressor connected to the rotary drive body. 2. The swash plate compressor according to claim 1, wherein the rotary drive body is one to which rotational power from the shaft is transmitted through the drive pin. The swash plate compressor according to claim 1, wherein the length of the sliding member in the axial direction is 1.5 times or more the diameter of the sliding member. 2. The swash plate compressor according to claim 1, wherein both ends of the sliding member in the axial direction are crowned. The swash plate compressor according to claim 1, wherein a coating film of a solid lubricant is provided on a sliding contact surface of the sliding member with the shaft. The housing space provided in the shaft is formed by forming the shaft into a bottomed cylindrical shape having a bottom at one end, and a first spring is formed between the bottom of the housing space and the sliding member. The swash plate compressor according to claim 1, wherein the swash plate compressor is mounted. 7. A swash plate type compression according to claim 6, wherein a spring receiver is provided at an end of the shaft that opens the housing space, and a second spinning is elastically mounted between the spring receiver and the sliding member. Machine. The swash plate compressor according to claim 1, wherein lubricating oil can be introduced into the housing space together with the refrigerant. 2. The swash plate type compression according to claim 1, wherein the housing space is separated into two spaces by the sliding member, and the two spaces communicate with each other via a communication portion provided in the sliding member. Machine. A holding hole for slidably holding the support member is formed in the rotation drive body, and the holding hole passes through a central axis of the shaft and is on a plane including a top dead center of the rotation drive body. 2. The swash plate compressor according to claim 1, wherein the compressor is offset to the front side in the rotational direction. The swash plate compressor according to claim 10, wherein the support member is offset forward in the rotational direction with respect to a plane that passes through a central axis of the shaft and includes a top dead center of the rotary drive body. . The swash plate compressor according to claim 1, wherein the support member is formed integrally with the shaft. 2. The swash plate compressor according to claim 1, wherein the drive pin is provided in a direction perpendicular to a plane passing through a central axis of the shaft and including a top dead center of the rotary drive body. .

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