WO2005035981A1

WO2005035981A1 - Swash plate-type compressor

Info

Publication number: WO2005035981A1
Application number: PCT/JP2004/015048
Authority: WO
Inventors: Hiroshi Kanai; Hironobu Deguchi; Shunichi Furuya; Yukio Kazahaya
Original assignee: Valeo Thermal Systems Japan Corporation
Priority date: 2003-10-14
Filing date: 2004-10-13
Publication date: 2005-04-21
Also published as: JPWO2005035981A1

Abstract

A swash plate-type compressor capable of achieving sufficient durability against a compression load by increasing the strength of a rotation drive body and capable of being downsized. A swash plate-type compressor has a rotation drive body (16) and pistons (13), where discharge capacity of the compressor is regulated by varying the inclination angle of the rotation drive body (16). The rotation drive body (16) rotates in synchronous with the rotation of a drive shaft (6). The pistons (13) are placed at the peripheral edge of the rotation drive body (16), and as the rotation drive body (16) rotates, the pistons (13) reciprocally slide in cylinder bores (12) formed in a housing. The rotation drive body is inclinably connected to a shaft through at least one link pin. The link pin is provided on the shaft and has a head section in contact with the rotation drive body. The rotation drive body has at least one receiving section for slidably holding the head section.

Description

Specification

Swash plate compressor

Technical field

[0001] The present invention relates to a rotary drive housed in a crank chamber and rotating with the rotation of a shaft, and moored around the periphery of the rotary drive, and reciprocates in a cylinder bore with the rotation of the rotary drive. The present invention relates to a swash plate type compressor having a moving piston and controlling a discharge capacity by changing a tilt angle of a rotary driving body.

Background art

[0002] In this type of compressor, a vertically long opening is provided at the center of a rotary driving body, and a driving member that rotates together with a shaft is loosely fitted into the opening, and the rotary driving body and the driving member are separated from each other. One connected to a single link pin provided on the axis that serves as the tilting center of the rotary driving body and spanning the opening (Patent Document 1), or a drive member fixed to the shaft in a cup shape The driving member covers the rotary driving member, and the driving member and the rotary driving member are provided on an axis which is a tilting center of the rotary driving member and are provided on both sides of the rotary driving member. What is connected by a link pin is known (Patent Document 2) Patent Document 1: Japanese Patent Application Laid-Open No. 7-293435.

Patent Document 2: Japanese Patent Application Laid-Open No. 2002-147348

[0003] In these configurations, since the rotary driving body can be tilted about the link pin with respect to the driving member fixed to the shaft, the piston top clearance is reduced by the tilt angle of the rotary driving body. This makes it possible to keep the value constant irrespective of the fluctuation, and to improve the volumetric efficiency to substantially zero.

Disclosure of the invention

Problems to be solved by the invention

[0004] In the former configuration, a link pin serving as a tilting center is erected in the opening of the rotary driving body, and a driving member that rotates together with the shaft via the link pin is attached to the opening. Therefore, the opening provided in the rotary driver is driven via link pins. It is necessary that the moving member and the rotary driving body be formed to be vertically long enough to be connected. For this reason, the strength of the rotary driving body in the longitudinal direction of the opening is insufficient, and there is a concern that it is not possible to sufficiently secure durability against a compressive load. Further, in the latter configuration, since the driving member fixed to the shaft is formed in a cup shape so as to cover the rotary driving body, there is a disadvantage that it is difficult to reduce the size of the compressor.

[0005] In view of the above, the present invention has been made in view of the above-mentioned points, and while improving the strength of the rotary driving body while making the most of the advantages of the above-described compressor, the present invention has been made in view of the above. The main task is to provide a swash plate compressor that can ensure sufficient durability and that can be downsized.

Means for solving the problem

[0006] In order to achieve the above object, a swash plate type compressor according to the present invention includes a shaft penetrating through a crank chamber and rotatably supported by a housing, and an opening through which the shaft is inserted. A rotary driver arranged in a crank chamber and rotating in synchronization with the rotation of the shaft; and a reciprocating slide in a cylinder bore formed in the housing, moored at a periphery of the rotary driver, and rotated by the rotary driver. A piston that moves, and a suction chamber and a discharge chamber that selectively communicate with the cylinder bore by the forward and backward sliding of the piston. The discharge capacity is controlled by changing the inclination angle of the rotary driving body. In the configuration described above, the rotary driving body is tiltably connected to the shaft via at least one link pin, and the link pin is attached to the shaft. Having said rotational drive member which abuts against the head with the said rotary drive member is a least one receptacle for holding the head slidably, as characterized Rukoto! /

[0007] Therefore, the rotary driver and the shaft are connected so that the head of at least one link pin attached to the shaft is held by at least one receiving portion formed on the rotary driver. Unlike the conventional configuration, it is not necessary to secure a vertically long opening of the rotary driving body. Therefore, it is possible to reduce the opening of the rotary driver, and it is possible to suppress a decrease in the strength of the rotary driver.

[0008] Further, since the rotary driving body is connected via at least one link pin attached to the shaft inserted into the opening, the axial dimension of the shaft can be reduced. It works.

[0009] If there are a plurality of link pins or a single link pin for connecting the rotary driving body and the shaft, each link pin has a spherical head. A plurality of holding holes are formed from the outer periphery to the opening so as to accommodate the heads of the respective link pins in the rotary driving body, and at least the receiving portion is formed in a cylindrical shape. It is good to provide in one holding hole. In the configuration in which a plurality of link pins are provided, it is possible to disperse the load acting on the link pins and to prevent rotation against a twisting moment acting on the rotary driving body.

[0010] Here, the receiving portion may be provided in all the holding holes, or may be provided in some of the holding holes. The head of the link pin may be engaged with the corresponding receiving portion so that the rotary driver can rotate around the line connecting the centers.

When the receiving portion is provided only in one holding hole, the receiving portion is orthogonal to a plane including the center axis of the shaft and the portion corresponding to the top dead center of the rotary driving member that positions the piston at the top dead center, and The head of the link pin may be engaged with the receiving portion so that the rotary driver can rotate around a line passing through the portion. As described above, when the receiving portion is provided in some of the holding holes, the receiving portion may be provided only in the holding hole on the front side in the rotation direction.

[0012] In the case where the rotary driving body and the shaft are connected via a single link pin, the link pin is provided with a base attached to the shaft and a head extending vertically to the base. The direction in which the head of the link pin extends is orthogonal to the plane including the center axis of the shaft and the portion corresponding to the top dead center of the rotary drive that positions the piston at the top dead center; The head of the link pin is engaged with the receiving portion so that the rotary driving body can rotate around the central axis in the extending direction of the head. In the configuration in which the head extends perpendicularly to the base in this way, it is possible to disperse the load acting on the link pin and prevent rotation against a twisting moment acting on the rotary driving body. It is possible to do.

In the above-described configuration, the receiving portion is formed in the middle of a holding hole formed from the outer periphery of the rotary driver to the opening, and receives the head of the link pin from the opening. It may be formed. [0014] When there are a plurality of link pins, a line connecting the centers of the link pin heads is drawn to the top dead center-corresponding portion of the rotary driving member that positions the center axis of the shaft and the piston at the top dead center. If one link pin is preferable to be on a line perpendicular to the plane including the axis, the center of the head of the link pin should be positioned at the center axis of the shaft and the piston at the top dead center. It is preferable that the rotary driving body is positioned on a plane including the top dead center corresponding part.

[0015] Further, when there are a plurality of link pins, it is preferable that the line connecting the centers of the heads of the link pins be arranged so that the distance from the axis of the shaft is substantially equal to the pitch circle radius of the piston. When only one link pin is used, it is preferable that the center of the head of the link pin is set so that the distance from the axis of the shaft is substantially equal to the pitch circle radius of the piston.

[0016] Furthermore, in a swash plate type compressor having two column-shaped link pins whose heads are formed in a spherical shape, two holding members for accommodating the heads of the respective link pins in a rotary driving body. It is preferable to form a hole and set the clearance between the head and the inner surface of the holding hole smaller than the link pin on the rear side in the rotation direction.

In order to reduce torque reaction force, it is preferable that a contact portion for transmitting torque by contacting the rotary driving member is provided on the shaft on a side opposite to the link pin with respect to the shaft axis of the shaft. More preferably, the counterweight for the link pin is provided on the side opposite to the link pin with respect to the axis of the shaft in order to reduce the dynamic imbalance.

Further, the center of gravity of the rotary driving body is provided on the cylinder block side with respect to the center of the rotary driving body and on the side opposite to the link pin, thereby improving control stability at high speed. Is preferred. Further, a pin may be provided on the rotary driver so as to be movably engaged with the shaft in the axial direction, and an urging means for applying an urging force to the pin in the axial direction may be provided inside the shaft.

In the above configuration, in order to reduce the size of the compressor, the shaft is provided so as to pass through a boss formed by projecting the housing outward and inward, and is provided on the inner surface of the boss. Alternatively, it may be rotatably supported via a radial bearing and a thrust bearing provided at an end of the boss.

The invention's effect

[0020] As described above, according to the present invention, the number of rotary driving bodies in which the piston is moored around the periphery is reduced. In a swash plate type compressor that is tiltably connected to a shaft via at least one link pin, a link pin is attached to the shaft, and at least one slidably holds a head of the link pin on a rotary driving body. Since the receiving part is provided, the opening of the rotary driver connected to the shaft can be made smaller, and the strength of the rotary driver can be suppressed and sufficient durability against compressive load can be secured. It becomes. Further, since the rotary driving body is connected to the shaft inserted through the opening through the link pin, it is possible to reduce the axial dimension of the shaft and to reduce the size of the compressor. .

Brief Description of Drawings

FIG. 1 is a cross-sectional view showing a configuration example of a swash plate type compressor according to the present invention.

FIG. 2 is a cross-sectional view showing a shaft of the compressor shown in FIG. 1 and a rotary driving body connected to the shaft via a link pin.

[FIG. 3] FIG. 3 is an enlarged cross-sectional view of a part of a shaft of the compressor shown in FIG. 1 and a rotary driving body connected to the shaft via a link pin.

FIG. 4 is an enlarged cross-sectional view showing the vicinity of a thrust bearing provided at an end of a shaft on a cylinder block side.

FIG. 5 is a diagram showing another configuration example of the guide groove provided in the shaft.

FIG. 6 is a coordinate system for describing the position of the center of gravity of the rotary driving body.

FIG. 7 is a characteristic diagram showing a relationship between moments applied to a rotary driving body.

[FIG. 8] FIG. 8 is a characteristic diagram showing a relationship between moments applied to the rotary driver due to centrifugal force when the position of the center of gravity of the rotary driver is changed.

FIG. 9 is a diagram showing another configuration example of the rotary driving body.

[FIG. 10] FIG. 10 is a diagram for explaining a process of assembling a link pin for connecting a shaft and a rotary driving body. FIG. 10 (a) also shows a force in a direction perpendicular to the axis of the shaft. FIG. 10 (b) is a cross-sectional view of the shaft viewed in the axial direction.

FIG. 11 is a cross-sectional view showing a modification of the rotary driving body connected to the shaft of the compressor shown in FIG. 1 via a link pin.

FIG. 12 is a cross-sectional view showing another configuration example of the swash plate type compressor according to the present invention.

[FIG. 13] FIG. 13 shows the compressor shaft shown in FIG. 12 connected to the shaft via a link pin. It is sectional drawing which shows a rotation drive.

Explanation of symbols

[0022] 4 crankcase

5a, 5b Boss

6 shaft

6a Large diameter section

6d contact part

6f Counter weight

12 Cylinder bore

13 piston

15 Link pin

15c, 15e head

16 rotary drive

16a opening

16c Holding hole

16d receiver

20 Construction pins

26 Inhalation chamber

27 Discharge chamber

BEST MODE FOR CARRYING OUT THE INVENTION

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

1 to 3, the swash plate type compressor includes a cylinder block 1, a rear head 3 mounted on a rear side (right side in the drawing) of the cylinder block 1 via a knurl plate 2, and a cylinder block 1. And a front head 5 that is assembled so as to close the front side (the left side in the figure) of the cylinder block 1 and that defines a crank chamber 4. The block 1, the knurl plate 2, and the rear head 3 are fastened in the axial direction by fastening bolts, and constitute a compressor housing.

[0025] The crankcase 4, which is defined by the soga, go, and ¹ , has one end having a flange. A shaft 6 that protrudes from the front head 5 and to which a power transmission member (not shown) such as a pulley is fixed is housed. One end of the shaft 6 is provided so as to pass through boss portions 5a and 5b formed by projecting the center portion of the front head 5 outward and toward the cylinder block side, and is provided on the inner surface of the boss portion 5b. It is rotatably supported via the radial bearing 7 provided and a thrust bearing 8 provided at an end of the boss 5b.

The other end of the shaft 6 is rotatably supported by a recess 9 formed in the center of the cylinder block 1 via a radial bearing 10 and a thrust bearing 11. Here, as shown in FIG. 4, the thrust bearing 11 includes a panel seat 11a provided at the bottom of the concave portion 9, a sliding bearing member 1 lb abutting on the end of the shaft 6, and a panel seat 1 la. It is configured to have a panel member 11c elastically mounted between the sliding bearing member and 1 lb, and urges the shaft 6 in the thrust direction to prevent rattling of the shaft 6 and movement in the rear direction. I have to.

[0027] The cylinder block 1 is formed with the recess 9 in which the shaft 6 is supported and a plurality of cylinder bores 12 arranged at equal intervals on a circumference centered on the recess 9. In each of the cylinder bores 12, a single-headed piston 13 is inserted so as to be reciprocally slidable.

[0028] A rotary driver 16 is tiltably connected to the shaft 6 via two link pins 15, and protrudes into the crank chamber 4 via a pair of shoes 17 at a peripheral portion of the rotary driver 16. The tail 13a of piston 13 is moored. Therefore, when the shaft 6 rotates, the rotary driving body 16 rotates synchronously with the body, and this rotational movement 16 is converted into a reciprocating linear movement of the piston 13 via the shoe 17, and the reciprocating movement of the piston 13 causes The capacity of the compression chamber 18 formed between the piston 13 and the valve plate 2 in the cylinder bore 12 is changed.

[0029] The link pin 15 is provided on an enlarged diameter portion 6a formed integrally with an intermediate portion of the shaft 6 exposed in the crank chamber 4. The enlarged diameter portion 6a is formed so that the surface of the shaft, which is symmetrical with respect to the axis, protrudes in a direction perpendicular to the axis, thereby increasing the diameter at a predetermined portion having a phase difference of 180 degrees. A flat portion 6b having a flat surface parallel to the longitudinal direction of the enlarged diameter portion 6a is formed on both sides, and each link pin 15 is outwardly attached to one end of the enlarged diameter portion 6a in the longitudinal direction. (Approximately in the radial direction of the shaft). In this example, an attachment hole 6c for inserting the link pin 15 into one end in the longitudinal direction of the enlarged diameter portion 6a is formed in the enlarged portion. Two are formed symmetrically with respect to the longitudinal center line of the diameter portion 6a, and the link pin 15 is attached to the attachment hole 6c!

[0030] The link pin 15 includes a connecting portion 15a to be attached to the attachment hole 6c, a small-diameter portion 15b formed following the attaching portion 15a, and a small-diameter portion 15b formed at the free end. And a cylindrical pin having a head 15c having an enlarged diameter, and the surface of the head 15c following the small-diameter portion 15b is formed as a curved surface forming a part of a spherical surface.

[0031] The rotary driving body 16 is formed in a disk shape having a predetermined thickness, and has, in the center, a size capable of accommodating the enlarged diameter portion 6a of the shaft 6 with a predetermined clearance. An opening 16a is formed. The opening 16a is formed by enlarging a predetermined portion symmetrical with respect to the axis of the rotary driving body 16 in a direction orthogonal to the axis, and has flat surfaces parallel to the longitudinal direction of the opening on both sides. A flat portion 16b having a shape is formed. In addition, a holding hole 16c that extends in the longitudinal direction of the opening 16a at the peripheral edge of the rotary driving body 16 and that is also provided with the outer peripheral force of the rotary driving body 16 over the opening 16a to accommodate the head 15c of the link pin 15 is provided. Are formed at two locations symmetrical with respect to the longitudinal center line of the opening 16a.

[0032] In each holding hole 16c, a receiving portion 16d whose inner surface is formed as a curved surface forming a part of a spherical surface is formed in the middle, and the head portion 15c of the link pin 15 slides on each receiving portion 16d. It is kept accessible. The receiving portion 16d gradually decreases the diameter of the holding hole 16c toward the center of the rotary driving body 16 so as to hold the head 15c of the link pin 15 from the opening side of the rotary driving body 16. Is formed.

[0033] Therefore, the head 15c of the link pin 15 is engaged with the receiving portion 16d so that the rotary driving body can tilt about the center line A connecting the centers of the receiving portions 16d. It is attached to the shaft 6 substantially perpendicular to the core wire A. Since the surfaces of the head 15c of the link pin 15 and the receiving portion 16d that come into contact with each other are formed in a spherical shape, the rotary driving body 16 can smoothly tilt about the head 15c of the link pin 15 as a center. It is as follows.

[0034] A line connecting the centers of the heads 15c of the link pins 15 is a plane including the central axis of the shaft 6 and the portion corresponding to the top dead center of the rotary driving body 16 that positions the piston 13 at the top dead center. The line connecting the centers of the heads 15c of the link pins 15 is perpendicular to the top. Is set to be approximately equal to the pitch circle radius of the piston 13. Further, the clearance between the head 15c of the link pin 15 and the inner surface of the holding hole 16c is set smaller at the link pin 15 on the rear side in the rotation direction.

[0035] A mounting pin 20 erected so as to pass through the opening 16a in parallel with the center line A of the tilting center is loosely fitted to the rotary driving body 16 through an erection hole 16f. Passed past the center of shaft 6. The portion of the shaft 6 through which the erection pin 20 is inserted extends in the axial direction of the shaft 6 to form a guide groove 21 that allows the erection pin 20 to move in the axial direction of the shaft 6. A spring accommodating space 22 is formed inside the shaft 6 so as to extend in the axial direction across the erecting pin 20. The spring accommodating space 22 is provided in the axial direction of the shaft 5 with respect to the erecting pin 20. The spring (destroking spring 23, stroking spring 24) for applying an urging force is provided. In this example, the guide groove 21 is an elongated hole formed in parallel with the axial direction of the shaft 6, but as shown in FIG. 5, the center of the head 15 c of the link pin 15 ( It may be an arc-shaped long hole centered on the rotation center of the rotation driver 16).

Further, the enlarged diameter portion 6 a of the shaft 6 is provided with a contact portion 6 d which contacts the flat portion 16 b of the rotary driving body 16 and transmits the rotational torque, to the link pin 15 with respect to the central axis of the shaft 6. It is provided symmetrically on the flat portion 6b on the opposite side. In addition, the enlarged diameter portion 6a is provided with a meat steal 6e between the two link pins 15, and by forming the meat steal 6e, a counterweight 6f is provided on the opposite side of the shaft pin from the link pin 15. Is formed. Further, in this example, when the coordinate system of the rotary driver 16 is set as shown in FIG. 6, the center of gravity of the rotary driver 16 is located at a position corresponding to the fourth quadrant with respect to the center P of the rotary driver 16. That is, it is set at a position on the cylinder block side and opposite to the link pin 15.

[0037] The rear head 3 defines a suction chamber 26 and a discharge chamber 27 formed continuously around the suction chamber 26. The valve plate 2 includes a suction chamber 26, a compression chamber 18, And a discharge hole 29 that communicates the discharge chamber 25 and the compression chamber 18 with each other through a discharge valve (not shown). The rear head 3 is equipped with a pressure control valve (not shown) for controlling the communication between the discharge chamber 27 and the crank chamber 4 and the communication between the crank chamber 4 and the suction chamber 26 to control the crank chamber pressure. And this pressure control valve Therefore, the crank chamber pressure is controlled!

[0038] Therefore, when the shaft 6 rotates, the rotational power is transmitted to the rotary driver 16 via the head 15c of the link pin 15 and the contact portion 6d of the enlarged diameter portion 6a, and the rotary driver 16 is rotated. As the piston 13 rotates and the piston 13 reciprocates in the cylinder bore 12, the working fluid in the suction chamber 26 is sucked into the compression chamber 18 through the suction hole 28 during the descending stroke of the piston 13, and the piston 13 moves up and down during the ascending stroke. , The working fluid in the compression chamber is compressed and discharged to the discharge chamber 27 through the discharge hole 29.

When the pressure in the crank chamber 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 pressure difference between the crank chamber pressure and the spring force of the distroking spring 23 increases. The rotary driver 16 moves to the front side, and the rotary driver 16 rotates about the head 15 c of the link pin 15 to increase the inclination angle of the rotary driver 16 with respect to a plane perpendicular to the shaft 6, As the piston stroke increases, the displacement 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 spring force of the stroking spring 24 The rotary driver 16 moves toward the cylinder block 1 against the force, and the rotary driver 16 rotates about the head 15c of the link pin 15 to reduce the inclination angle of the rotary driver 16 and the piston strike. The smaller the stroke, the smaller the discharge capacity.

[0040] At this time, the rotational driving body 16 is a force that tilts around the head 15c of the link pin 15, and the position of the top dead center of the piston 13 is not different. Therefore, the piston top clearance is kept constant in the minimum state. This makes it possible to improve the volumetric efficiency regardless of the discharge capacity.

In the above-described configuration, since the link pin 15 is attached to the shaft 6 in a direction substantially perpendicular to the center line A serving as the tilt center of the rotary driver 16, the same tilt radius is formed. However, compared to a configuration in which the link pins are provided along the center line serving as the tilting center of the rotary driver, the longitudinal dimension of the enlarged diameter portion 6a can be reduced, and the opening 16a of the rotary driver 16 can be reduced. It becomes possible. For this reason, it is possible to suppress a decrease in the strength of the rotary driving body 16, and it is possible to sufficiently ensure durability against a compressive load. Further, the rotation driving body 16 has a link pin with respect to the enlarged diameter portion 6a housed in the opening 16a. Since the shaft 6 is connected via the shaft 15, the axial dimension of the shaft 6 can be suppressed, and the compressor can be reduced in size.

By the way, the tilt angle of the rotary drive 16 is actually changed by the tilt moment acting on the rotary drive 16, but this tilt moment is the moment due to the inertia force of the piston, It is determined by the sum of the moment due to the inertial force, the moment due to the eccentricity of the rotary driver, and the moment due to the spring force of the destroking spring, so that the rotary driver 16 is stabilized at the position where the tilting moment becomes zero. Has become.

However, in the conventional swash plate type compressor, as shown by the solid line in FIG. 7, only the moment due to the inertial force of the rotary driving body 16 and the moment due to the destroking spring are the inclination angles with respect to the plane perpendicular to the shaft. In the high rotation speed range, these downward-sloping moments (due to the inertia force of the piston) The moment and the moment due to the eccentric force of the conventional rotary driver), and the control may become unstable. Thus, in the above-described configuration, in order to cancel such a downward-sloping moment, the center of gravity of the rotary driving body is set at the position of the fourth quadrant to avoid such inconvenience. It is necessary to ensure stable control in the rotation speed range.

That is, when the center of gravity of the rotary driver 16 is set at the position of the fourth quadrant (on the cylinder block side with respect to the center of the rotary driver 16 and on the opposite side to the link pin 15), As shown by the broken line in FIG. 8, unlike the case where other quadrants are set, the characteristic of the moment caused by the centrifugal centrifugal force of the rotary driver 16 can be increased to the right, By using such a rotary driving body 16 (broken line in FIG. 7), it is possible to cancel the downward-sloping moment in the entire rotational speed range, and to obtain a stable control characteristic even in a high rotational speed range. It becomes possible.

When the center of gravity of the rotary driving body is set to the fourth quadrant in this way, the moment due to the eccentricity of the rotary driving body 16 is set such that the inclination angle is small, and in such a case, the inclination angle is increased. When the tilt angle is large, it can act in the direction of decreasing the tilt angle, so to maintain a small tilt angle, keep the crank chamber pressure somewhat higher than before. The tilt angle of the rotary driver changes excessively due to fluctuations in the crankcase pressure. Phenomenon can be reduced.

In the above-described compressor, the force required to connect the shaft 6 and the rotary driving body 16 so as to have a predetermined positional relationship via link pins is provided for convenience of assembly. Alternatively, as shown in FIG. 9, a discarding hole 16e may be provided on the side opposite to the holding hole 6c of the rotary driving body 16 to perform an assembling operation. In such a configuration, for example, as shown in FIG. 10, it is possible to perform an assembling operation using a jig 30 having a support 30a communicating with the disposal hole 16e.

[0047] That is, the jig is fixed to a plane in advance, the support 30a is erected, the shaft 6 is passed through the rotary driver 16, and the mounting hole 6c of the shaft 6 and the holding hole 16c of the rotary driver 16 are connected. The rotary drive 16 is placed on the jig so that the support 30a of the jig 30 is inserted into the discard hole 16e in this state, and the tip of the support 30a is applied to the shaft 6. Touch and fix. Here, the enlarged portion 6a (counter weight portion 6f) of the shaft 6 with which the tip portion of the column 30a abuts may be provided with a seat surface 16g orthogonal to the central axis of the attachment hole 6c. Then, in this state, the link pin 15 is inserted into the holding hole 16c from above, and the attachment portion 15a of the link pin 15 is press-fitted or screwed into the attachment hole 6c. The attachment work can be completed. Therefore, by providing such a disposal hole 16e, it is possible to improve the efficiency of the assembling work.

FIG. 11 shows another configuration example in which the rotary driving body and the shaft are connected via link pins. In this example, a holding hole extending in the longitudinal direction of the opening 16a on the peripheral edge of the rotary driver 16 and extending from the outer periphery of the rotary driver to the opening is a center line in the longitudinal direction of the opening 16a. It is the same as the above configuration example in that it is formed at two locations that are symmetrical with respect to, but the receiving portion 16d is formed only in the holding hole on the front side in the rotation direction, and the head of the link pin 15 is formed 15c is slidably held. The receiving portion 16d gradually decreases the diameter of the holding hole 16c toward the opening of the rotary driver 16 so that the head 15c of the link pin 15 also holds the opening-side force of the rotary driver 16. Is formed. The other holding hole is formed to have the same diameter from the outer periphery of the rotary driving body to the opening, and a receiving portion with which the head of the link pin 15 is engaged is formed.

[0049] In such a configuration, the rotation of the center axis of the shaft and the piston is positioned at the top dead center. The link pipe is provided so that the rotary driver 16 can rotate around a line B that is orthogonal to the plane including the portion corresponding to the top dead center of the driver and passes through the receiving portion 16d formed in the holding hole 16c on the front side in the rotation direction. The head 15c of the pin 15 is engaged with the receiving portion 16d, and the link pin 15 is attached to the shaft 6 substantially perpendicular to the line B. Since the surfaces of the head 15c of the link pin 15 and the receiving portion 16d that are in contact with each other are formed in a curved surface, the rotation driving body 16 can be smoothly tilted about the head 15c of the link pin 15 as a center. I'm familiar. Since other configurations are the same as those of the above configuration example, the same portions are denoted by the same reference numerals and description thereof will be omitted.

[0050] In such a configuration, the same operation and effect as those of the above-described configuration example are obtained, and the rotation driving body 16 is formed by only one of the link pins held by the contact portion 11 for transmitting the torque and the receiving portion 16d. Since the posture in the rotational direction is restricted, the rotational power of the shaft 6 is transmitted to the rotary driving body 16 through the head 15c of the link pin 15 and the contact portion 6d of the enlarged diameter portion 6a without any trouble.

[0051] In the above configuration, the link pin 15 is constituted by two cylindrical pins having a head portion 15c formed in a spherical shape, and the rotary driver 16 rotates around a line connecting the centers of the receiving portions 16d. Although the head 15c of the link pin 15 is engaged with the receiving portion 16d of the rotary driver 16 so as to be movable, the link pin 15 may be constituted by one link pin 15. In the case where one link pin 15 is used, the link pin 15 may be formed in a T shape as shown in FIGS. That is, the link pin 15 is constituted by a base 15d provided substantially perpendicularly to an axis serving as a tilt center of the rotary driving body 16, and a head 15e extending perpendicularly to the base 15d. The contact surface of the head 15e with the receiving portion 16d is formed into a curved surface that allows the rotary driver 16 to tilt, and the contact surface of the receiving portion 16d with the head 15e also allows the rotary driver 16 to tilt. It may be formed on a curved surface. The center of the head 15e of the link pin 15 is on a plane including the central axis of the shaft 6 and the position corresponding to the top dead center of the rotary drive 16 that positions the piston 13 at the top dead center. At the center of the head 15 e of the link pin 15, the axial force distance of the shaft 6 is set substantially equal to the pitch circle radius of the piston 13. Other configurations are the same as those of the above configuration example, and thus the same portions are denoted by the same reference numerals and description thereof will be omitted.

In such a configuration, in addition to the advantages described above, the number of link pins 15 can be reduced. Becomes possible. Incidentally, in order to facilitate the assembly of the link pin, the rotary driving body 16 may be provided with a discard hole at the peripheral edge opposite to the holding hole 16c with respect to the axis. Further, the enlarged portion 6a (counter weight portion 6f) of the shaft 6 may be provided with a seat surface orthogonal to the central axis of the attachment hole 6c.

Claims

The scope of the claims

[1] A shaft that penetrates a crank chamber and is rotatably supported by a housing, and a rotation drive that has an opening through which the shaft is inserted and is arranged in the crank chamber and rotates in synchronization with the rotation of the shaft. A body, a piston moored at a peripheral edge of the rotary driving body, and reciprocatingly sliding in a cylinder bore formed in the housing as the rotary driving body rotates. The swash plate compressor has a suction chamber and a discharge chamber that communicate with each other, and controls a discharge capacity by changing an inclination angle of the rotary driving body.

The rotary driving body is tiltably connected to the shaft via at least one link pin,

The link pin has a head attached to the shaft and abutting on the rotary driver.

The rotary driver has at least one receiving portion that slidably holds the head.

A swash plate type compressor characterized by the above-mentioned.

[2] The head has a plurality of cylindrical link pins formed in a spherical shape,

The rotary driving body has a holding hole formed from the outer periphery to the opening to accommodate the head of each link pin,

The swash plate compressor according to claim 1, wherein the receiving portion is provided in at least one holding hole.

[3] The receiving portion is provided in each holding hole,

The head of the link pin is engaged with the corresponding receiving portion so that the rotary driver can rotate around a line connecting the centers of the receiving portions. 2. The swash plate compressor according to 2.

[4] The receiving portion is provided only in one holding hole,

The rotary driver is orthogonal to a plane including the center axis of the shaft and the portion corresponding to the top dead center of the rotary driver that positions the piston at the top dead center, and around a line passing through the receiving portion. The head of the link pin is engaged with the receiving portion so as to be rotatable. 3. The swash plate type compressor according to claim 2, wherein

5. The swash plate compressor according to claim 4, wherein the receiving portion is provided only in the holding hole on the front side in the rotation direction.

[6] A link pin having a base attached to the shaft and a head extending perpendicular to the base is provided, and the extension direction of the head of the link pin is set to the above-described direction. A center axis of a shaft and a portion corresponding to the top dead center of the rotary driving body that positions the piston at the top dead center; The head is engaged with the receiving portion so as to be rotatable therearound.

The swash plate compressor according to 1.

[7] The receiving portion is formed in the middle of a holding hole formed from the outer periphery of the rotary driving body to the opening, and receives the head of the link pin on the opening side. The swash plate compressor according to claim 1.

[8] A line connecting the centers of the heads of the link pins is perpendicular to a plane including the center axis of the shaft and a portion corresponding to the top dead center of the rotary driving body that positions the piston at the top dead center. 3. The swash plate compressor according to claim 2, wherein the compressor is on a straight line.

[9] The center of the head of the link pin is located on a plane including a central axis of the shaft and a portion corresponding to a top dead center of the rotary driving member that positions the piston at a top dead center. The swash plate compressor according to claim 6.

10. The swash plate compressor according to claim 2, wherein a line connecting centers of heads of the link pins has a distance from an axis of the shaft substantially equal to a pitch circle radius of the piston.

11. The swash plate compressor according to claim 6, wherein the center of the head of the link pin has a distance from the axis of the shaft substantially equal to a pitch circle radius of the piston.

[12] The head has two cylindrical link pins formed in a spherical shape, and the rotary driving body is formed with two holding holes for accommodating the heads of the respective link pins. 3. The swash plate compressor according to claim 2, wherein the clearance between the head and the inner surface of the holding hole is set smaller at the link pin on the rear side in the rotation direction.

[13] The shaft has a contact portion for transmitting torque by contacting the rotary driving body. The swash plate type compressor according to claim 1, wherein the swash plate type compressor is provided on a side opposite to the link pin with respect to an axis of the swash plate.

14. The swash plate compressor according to claim 1, wherein a counterweight for the link pin is provided on a side opposite to the link pin with respect to an axis of the shaft.

15. The slant according to claim 1, wherein a center of gravity of the rotary driving body is provided on a cylinder block side with respect to a center of the rotary driving body and on a side opposite to the link pin. Plate compressor.

[16] The rotary driving body is provided with a pin that is movably engaged with the shaft in the axial direction, and is provided inside the shaft to apply a biasing force to the pin in the axial direction. 2. The swash plate compressor according to claim 1, further comprising a biasing means.

[17] The shaft is provided so as to pass through a boss formed by projecting the housing outward and inward, and a radial bearing provided on an inner surface of the boss and an end of the boss. The swash plate type compressor according to claim 1, wherein the swash plate type compressor is rotatably supported via an installed thrust bearing.