JP2001041153A - Variable-displacement compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent abrasion due to a compressive reaction force or the like. SOLUTION: A hinge mechanism 50 is formed by a projecting part 51, a disc 52, a hole 53, a projecting piece 54 and a pin 55. A round hole 56 intersecting perpendicularly to a shaft is formed in the projection part 51 provided on the rear end face of a thrust flange 40, and the disc 52 is rotatably supported in the round hole 56. A hole 53 is formed in a position of the disc 52 offset from the central axis of the round hole 56, and a pin 55 suspended between a pair of projecting pieces 54 provided on the front end face of an oscillating plate is engaged with the hole 53 of the disc 52.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a variable displacement compressor.

[0002]

2. Description of the Related Art In a variable displacement compressor, the displacement is usually changed by changing the angle of inclination of an inclined rotating plate (such as a swash plate or a drive hub). The variable displacement compressor includes a hinge mechanism for changing the inclination angle of the inclined rotating plate.

FIG. 12 is a longitudinal sectional view showing the entire structure of a conventional rocking plate compressor.

[0004] A shaft 705 has a thrust bearing 733.
The thrust flange 740 supported on the inner wall surface of the front head 704 via the
Hinge ball 709 movable along shaft 705
The drive hub 741 is attached via the.

A rocking plate 710 is attached to a boss 743 of the drive hub 741 via a radial bearing 727 and a thrust bearing 728.

Thrust flange 740 and drive hub 7
The rotation of the shaft 705 is transmitted from the thrust flange 740 to the drive hub 741 via the link arm 742.

One end of the link arm 742 has a pin 755a
And the other end is connected to the drive hub 741 via a pin 755b. Link arm 742 and two pins 755a, 755
b constitutes a hinge mechanism.

The boss 743 of the drive hub 741 has
A rocking plate 710 is mounted via a radial bearing 727.

The drive hub 741 is inclined with respect to an imaginary plane orthogonal to the shaft 705. The inclination angle changes according to the pressure of the crank chamber 708, and the inclination of the rocking plate 710 changes according to the change. .

The swinging plate 710 makes a swinging motion about the hinge ball 709 as the drive hub 741 rotates, and this swinging motion is transmitted to the piston 707 via the connecting rod 711, and the piston 707 moves through the cylinder bore 706. Reciprocate linearly.

In this wobble plate compressor, the crank chamber 70
8, the inclination angle of the rocking plate 710 increases, and the stroke amount of the piston 707 becomes maximum,
The state becomes the maximum discharge amount state.

On the other hand, when the pressure in the crank chamber 708 increases, a part of the drive hub 741
Away from zero, the tilt angle of the swing plate 710 becomes smaller,
The stroke amount of the piston 707 becomes the minimum, and the state becomes the minimum discharge state.

FIG. 13 is a longitudinal sectional view showing the whole of a conventional variable displacement swash plate type compressor.

The conventional variable displacement type swash plate type compressor has a thrust flange 840 fixed to a shaft 805 and a thrust flange 840 mounted on a shaft 805 so as to be slidable and tiltable.
The swash plate 810 is connected to the swash plate 810 via a shoe 860 that relatively rotates on the sliding surface of the swash plate 810, and the piston linearly reciprocates in the cylinder bore 806 as the swash plate 810 rotates. 807.

Crank chamber 808 containing swash plate 810
The inclination angle of the swash plate 810 changes in accordance with the change in the pressure, and the stroke amount of the piston 807 changes.

The thrust flange 840 is connected to the thrust bearing 8.
33, it is rotatably supported on the inner wall surface of the front head 804. The cylinder bores 806 are formed in the cylinder block 801 at regular intervals on a circumference around the shaft 805.

The hinge mechanism 850 includes a bracket portion 843 provided on the flange-side end surface of the swash plate 810, a linear guide groove 844 provided on the bracket portion 843 and inclined with respect to the flange-side end surface, and a thrust flange 840. And a link pin 845 fixed to the swash plate side end surface. The spherical tip of the link pin 845 is the guide groove 8
44 is fitted so as to be relatively slidable.

The rotational force of the shaft 805 is transmitted from the thrust flange 840 to the swash plate 810 via the hinge mechanism 850, and the swash plate 810 rotates around the shaft 805. The rotation of the swash plate 810 causes the shoe 860 to move the swash plate 810.
Are relatively rotated, and the rotational force from the swash plate 810 is converted into a linear reciprocating motion of the piston 807.

[0019]

By the way, when the refrigerant gas is compressed by the piston, the compression reaction force of the refrigerant gas is transmitted from the drive hub to the thrust flange via the hinge mechanism.

In the case of the former compressor, the compression reaction force of the refrigerant gas due to the reciprocating motion of the piston 707 is applied to the thrust flange 7.
A pin 755a for connecting the link arm 742 with the link arm 742,
And the pin 755b connecting the drive hub 741 and the link arm 742.

In the case of the latter compressor, the compression reaction force of the refrigerant gas is received by the link pin 845 connecting the thrust flange 840 and the bracket 843.

The hinge mechanism receives a twisting moment generated around an axis perpendicular to the shaft 805 through the instantaneous center of rotation of the swash plate 810 (for example, point A in FIG. 13), in addition to the compression reaction force of the refrigerant gas.

Therefore, in the case of the former compressor, the thrust flange 740, the link arm 742, the drive hub 7
Edge contact occurs between the link arm 742 and the drive hub 741 or the pins 755a and 755b due to the tolerance between the pins 755a and 755b, and the pins 755a and 75 have a small contact area.
5b wears.

Similarly, in the case of the latter compressor, the link pin 845 having a small contact area is worn.

The present invention has been made in view of such circumstances, and an object thereof is to provide a variable displacement compressor capable of reducing wear caused by a compression reaction force of a refrigerant gas.

[0026]

According to a first aspect of the present invention, there is provided a fuel cell system comprising: a plurality of cylinder bores formed in a cylinder block; and a plurality of cylinder bores slidably accommodated in the plurality of cylinder bores. A piston, a rotating member fixed to the rotating shaft and rotating integrally with the rotating shaft, and having a center hole through which the rotating shaft passes, and an axial direction in a state inclined with respect to a virtual plane orthogonal to the rotating shaft. An inclined rotating plate slidably attached to the rotating shaft; and a connecting means disposed between the rotating member and the inclined rotating plate for connecting the inclined rotating plate to the rotating member so as to be capable of inclining. A variable displacement compressor in which a stroke amount of the piston changes in accordance with an inclination angle of the inclined rotating plate, wherein the connecting means includes a projection provided on a rear end surface of the rotating member; Department A disk rotatably supported by a circular hole, a hole formed in the disk, and located at a position offset from a center axis of the circular hole orthogonal to the rotation axis, and a front end surface of the inclined rotary plate. It is characterized by comprising a pair of protruding pieces provided, and a pin that extends between the protruding pieces and engages with the hole of the disc.

When the discharge capacity is reduced, the center axis of the pin moves downward as the inclination angle of the rotating plate decreases,
The disk rotatably supported by the round hole of the projection provided on the rotating member rotates clockwise. The compression reaction force of the refrigerant gas due to the reciprocating motion of the piston is received via the pin.

According to a second aspect of the present invention, in the variable displacement compressor according to the first aspect, the center axis of the pin is located on the rear side of the center axis of the disk, and the rotation axis of the rotary shaft at the time of minimum discharge. The distance from the center axis of the pin to the center axis of the pin is equal to or longer than the distance from the center axis of the rotation axis to the center axis of the disk.

FIG. 14 is an enlarged view of a disk rotatably supported by the round hole of the projection, and FIG. 15 is a view showing the relationship between the swash plate inclination angle and the top clearance in each quadrant shown in FIG. Note that each quadrant in FIG. 15 corresponds to each quadrant shown in FIG.

FIG. 14 shows the center axis of the pin at 30 ° in the first quadrant.
3 shows a case where the lens is positioned in a range 1A.

FIG. 15 shows that the center axis of the pin is the first axis.
When it is located in the quadrant A (1A in FIG. 14), it can be seen that the change in the top clearance (the distance between the piston head and the valve plate) is smallest.

According to a third aspect of the present invention, a plurality of cylinder bores formed in a cylinder block, a plurality of pistons slidably housed in the plurality of cylinder bores, and fixed to a rotating shaft, A rotating member that rotates integrally, and a center hole through which the rotating shaft passes, and an inclined rotation that is attached to the rotating shaft so as to be slidable in the axial direction while being inclined with respect to a virtual plane orthogonal to the rotating shaft. A plate, and a connecting means disposed between the rotating member and the inclined rotating plate, the coupling means for coupling the inclined rotating plate to the rotating member so as to be capable of inclining operation, according to an inclination angle of the inclined rotating plate. In the variable displacement compressor in which the stroke amount of the piston changes, the connecting means includes a pair of first protrusions provided on a rear end surface of the rotating member, and a spherical body between the protrusions. Pinched through A rolling element rotatably supported on a rear end face of the rotating member, a second projection provided on a front end face of the inclined rotating plate, and supported between the projections; And a pin engaged with the hole of the rolling element.

When the discharge capacity is reduced, the center axis of the pin moves downward as the inclination angle of the inclined rotating plate decreases, and is provided on the rotating member, and is pinched between the first projecting pieces via a spherical body. The rolling element thus rotated rotates clockwise. The compression reaction force of the refrigerant gas due to the reciprocating motion of the piston is received by the rear end face of the rotating member via the rolling element.

According to a fourth aspect of the present invention, a plurality of cylinder bores formed in a cylinder block, a plurality of pistons slidably housed in the plurality of cylinder bores, and fixed to a rotating shaft, A rotating member that rotates integrally, and a center hole through which the rotating shaft passes, and an inclined rotation that is attached to the rotating shaft so as to be slidable in the axial direction while being inclined with respect to a virtual plane orthogonal to the rotating shaft. A plate, and a connecting means disposed between the rotating member and the inclined rotating plate, the coupling means for coupling the inclined rotating plate to the rotating member so as to be capable of inclining operation, according to an inclination angle of the inclined rotating plate. In the variable displacement compressor in which the stroke amount of the piston changes, the connecting means is provided on a front end surface of the inclined rotating plate, and is provided around an intersection of a central axis of the piston and a central axis of the inclined rotating plate. A rotatable arm portion, a concave surface provided on a rear end surface of the rotating member, slidably supporting an arc-shaped tip surface of the arm portion, and a concave surface sandwiched between the rear end surface of the rotating member. A pair of protruding pieces provided, an elongated hole provided on the protruding piece, and extending along an arc having a radius smaller than the radius of the distal end surface of the arm section; A pin engaged with a long hole of the arm portion, and the distal end surface of the arm portion and the concave surface are shaped along an arc having substantially the same radius centered on the intersection.

When the discharge capacity is reduced, the arm slides on the concave surface of the rotating member and the pin moves along the elongated hole as the inclination angle of the inclined rotating plate decreases. At this time, the compression reaction force of the refrigerant gas due to the reciprocating motion of the piston can be received by the concave surface that slidably supports the arc-shaped tip portion of the arm portion. Further, the instantaneous center of rotation of the rotary motion of the inclined rotary plate coincides with the intersection of the central axis of the piston at the top dead center and the central axis of the swash plate.

According to a fifth aspect of the present invention, a plurality of cylinder bores formed in a cylinder block, a plurality of pistons slidably housed in the plurality of cylinder bores, and fixed to a rotating shaft, A rotating member that rotates integrally, and a center hole through which the rotating shaft passes, and an inclined rotation that is attached to the rotating shaft so as to be slidable in the axial direction while being inclined with respect to a virtual plane orthogonal to the rotating shaft. A plate, and a connecting means disposed between the rotating member and the inclined rotating plate, the coupling means for coupling the inclined rotating plate to the rotating member so as to be capable of inclining operation, according to an inclination angle of the inclined rotating plate. In the variable displacement compressor in which the stroke amount of the piston changes, the connecting means is provided on a front end surface of the inclined rotating plate, and is provided around an intersection of a central axis of the piston and a central axis of the inclined rotating plate. A rotatable arm portion, a concave surface provided on a rear end surface of the rotating member, slidably supporting an arc-shaped tip surface of the arm portion, and a concave surface sandwiched between the rear end surface of the rotating member. A pair of protruding pieces provided, a long groove provided on the protruding piece and extending along an arc having a radius smaller than a radius of a tip end surface of the arm, and sliding between the arm and the protruding piece. A spherical body provided so as to be capable of being provided, wherein the distal end surface of the arm portion and the concave surface have a shape along an arc having substantially the same radius around the intersection.

When the discharge capacity is reduced, the arm slides on the concave surface of the rotating member as the inclination angle of the inclined rotating plate decreases, and the spherical body moves along the long groove. At this time,
The compression reaction force of the refrigerant gas due to the reciprocating motion of the piston can be received by the concave surface that slidably supports the arc-shaped tip portion of the arm portion. Further, the instantaneous center of rotation of the rotary motion of the inclined rotary plate coincides with the intersection of the central axis of the piston at the top dead center and the central axis of the swash plate.

[0038]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a longitudinal sectional view showing the entire swinging plate compressor according to the first embodiment of the present invention.

This oscillating plate type compressor (variable capacity type compressor)
A rear head 3 is fixed to one end face of the cylinder block 1 via a valve plate 2, and a front head 4 is fixed to the other end face.

The cylinder block 1 is provided with a plurality of cylinder bores 6 at predetermined intervals in a circumferential direction around a shaft (rotating shaft) 5. These cylinder bores 6
A piston 7 is slidably accommodated therein.

A crank chamber 8 is provided in the front head 4.
A rocking plate 10 that swings around a hinge ball 9 in conjunction with the rotation of the shaft 5 is formed in the crank chamber 8.
And a thrust flange (rotating member) 40 are accommodated.

In the rear head 3, a discharge chamber 12 and a suction chamber 1 are provided.
3 are formed, and the suction chamber 13 is located around the discharge chamber 12. The inside of the discharge chamber 12 is partitioned by a baffle plate 14 into a discharge space 12a and a discharge section 12b, and the two discharge spaces 12a and 12b communicate with each other through a throttle hole 14a formed in the baffle plate 14.

The valve plate 2 is provided with a discharge port 16 for communicating the cylinder bore 6 with the discharge space 12a, and a suction port 15 for communicating the cylinder bore 6 with the suction chamber 13.

The discharge port 16 is opened and closed by a discharge valve 17, and the discharge valve 17 is fixed to an end face on the rear head side of the valve plate 2 by a rivet 19 together with a valve retainer 18. The suction port 15 is opened and closed by a suction valve 21, and the suction valve 21 is provided between the valve plate 2 and the cylinder block 1.

The cylinder block 1 has a suction chamber 13.
And a communication passage 31 for communicating the crank chamber 8 with the
A pressure regulating valve 32 is provided in the middle of the communication passage 31,
The suction chamber 13 and the crank chamber 8 are controlled by the pressure regulating valve 32.
Pressure adjustment is performed.

The front end of the shaft 5 is rotatably supported by a radial bearing 26 in the front head 4, and the rear end of the shaft 5 is rotatably supported by a radial bearing 24 and a thrust bearing 25.

The shaft 5 has a thrust flange 4
0 is fixed, and a drive hub (inclined rotating plate) 41 is attached via a hinge ball 9. The thrust flange 40 and the drive hub 41 are connected via a hinge mechanism (connection means) 50 described later, and the rotation of the shaft 5 is transmitted from the thrust flange 40 to the drive hub 41 via the hinge mechanism 50.

Thrust flange 40 and front head 4
A thrust bearing 33 is attached to the inner wall of the thrust bearing.

The swing plate 10 is attached to the boss 43 of the drive hub 41 via the radial bearing 27. A thread is provided on the outer peripheral surface of the tip of the boss 43, and a nut 34 is screwed to the thread via a balance weight 30.

The front end face of the oscillating plate 10 and the rear end face of the drive hub 41 face each other via a thrust needle bearing 28. The inclination angle of the drive hub 41 changes according to the pressure in the crank chamber 8, and the swing plate 10 is inclined integrally with the drive hub 41.

The connecting plate 11 is connected to the swinging plate 10.
One of the ball portions 11a is rotatably connected, and the other of the connecting rod 11 is connected to the piston 7,
The swing of the swing plate 10 causes the piston 7 to reciprocate linearly within the cylinder bore 6.

FIG. 2A is an exploded perspective view of the hinge mechanism, and FIG. 2B is a sectional view thereof.

The hinge mechanism 50 includes a projection 51 and a disc 5.
2, a hole 53, a projecting piece 54, and a pin 55.

The projection 51 has a round hole 56 extending in a direction perpendicular to the shaft 5. This projection 51
Are formed integrally with the rear end face 40a of the thrust flange 40.

The disk 52 is rotatably supported by the round hole 56. A hole 53 is formed in the disk 52 at a position offset from the center axis of the round hole 56.

The projecting piece 54 is formed integrally with the front end face 41 a of the drive hub 41. A pair of projecting pieces 5
4 are formed in parallel, and holes 57 for inserting the pins 55 are formed at opposing positions.

The pin 55 extends between the projecting pieces 54 via the holes 57 and engages with the holes 53 of the disk 52. Pin 5
5 is retained by a retaining ring 58.

The center axis of the pin 55 is located in the first quadrant A (1A) of FIG.

In this oscillating plate compressor, when the pressure in the crank chamber 8 decreases, the inclination angles of the drive hub 41 and the oscillating plate 10 increase, and the stroke of the piston 7 becomes maximum, so that the maximum discharge state is achieved.

On the other hand, when the pressure in the crank chamber 8 increases, a part of the drive hub 41 separates from the thrust flange 40, the inclination angles of the drive hub 41 and the swing plate 10 become small, and the stroke of the piston 7 becomes minimum. As a result, the state becomes the minimum discharge state.

When the discharge capacity decreases, the center axis of the pin 55 moves downward as the inclination angle of the swing plate 10 decreases, and the protrusion 51 provided on the thrust flange 40 is reduced.
The disc 52 rotatably supported by the circular hole 56 of FIG.

A large force (compression reaction force) is applied to the rear surface of the piston during the compression stroke. The compression reaction force acts on the pin 55 via the connecting rod 11 and the drive hub 41.

Since the center axis of the pin 55 does not move below the center axis of the disk 52, the change in the top clearance can be reduced.

According to the first embodiment, the pin 55 comes into surface contact with the protruding piece 54 and the hole 53 of the disk 52 and receives a compression reaction force over a wide area. Wear of the comparison pin 55 can be reduced.

Further, since the change in the top clearance is small, the volume efficiency can be improved.

Furthermore, unlike the conventional example, the number of components can be reduced without using two pins, so that productivity and assemblability are improved, and reliability is improved by simplification of the configuration.

The center axis of the pin 55 may be located in the first quadrant B (1B) of FIG. 14 as long as it is the first quadrant.

FIG. 3 is a longitudinal sectional view showing the whole of a wobble plate compressor according to a second embodiment of the present invention. The same parts as those in the first embodiment are denoted by the same reference numerals and the description thereof is omitted. .

This embodiment differs from the first embodiment in the hinge mechanism. Hereinafter, the hinge mechanism of this embodiment will be described.

FIG. 4A is an exploded perspective view of the hinge mechanism, and FIG. 4B is a sectional view thereof.

The hinge mechanism 150 includes a first protrusion 151
, Rolling element 152, second projecting piece 153, pin 15
4 is provided.

The first protrusion 151 is provided on the thrust flange 1.
40 are formed integrally with the rear end surface. The pair of protruding pieces 151 are formed in parallel, and concave portions 156a and 156b are formed at opposing positions so as to rotatably support a part of the balls (spherical bodies) 155a and 155b.

A columnar projection 1 is provided between the first projections 151.
57 is formed, and a concave portion 157a that supports a part of the ball 155c so as to be able to roll is formed at the tip of the protruding portion 157. These balls 155a, 155b, 1
The center of 55c is arranged on the same straight line. The balls 155a, 155b, and 155c have the same diameter, for example.

The rolling element 152 includes a rolling element body 158 and a pair of legs 159. A leg 159 formed at one end of the rolling element main body 158 has a substantially L-shape, and its distal end has an arc shape.

The leg 159 of the rolling element 152 and the projection 151
Are interposed between the protruding pieces 151 via balls 155a and 155b arranged between them.

A recess 152a is formed between the legs 159 of the rolling element 152 at a position facing the ball 155c to rotatably support a part of the ball 155c.

The other end of the rolling element main body 158 has a shaft 5
A hole 160 extending in a direction perpendicular to the direction is formed.

The second projection 153 is formed integrally with the front end surface 41 a of the drive hub 41. The pair of projecting pieces 153 are formed in parallel, and the pin 1
A hole 161 for inserting the hole 54 is formed.

The pin 154 is inserted through the hole 161 into the projection 15.
3 and engages with the hole 160 of the rolling element 152. The pin 154 is retained by a retaining ring 162. The pin 154 rotates about an axis passing through the centers of the balls 155a to 155c.

In this oscillating plate compressor, when the pressure in the crank chamber 8 decreases, the inclination angles of the drive hub 41 and the oscillating plate 10 increase, and the stroke amount of the piston 7 becomes maximum, so that the maximum discharge state is achieved.

On the other hand, when the pressure in the crank chamber 8 increases, a part of the drive hub 41 is moved to the thrust flange 140.
, The inclination angle of the drive hub 41 and the oscillating plate 10 becomes small, the stroke amount of the piston 7 becomes minimum, and a minimum discharge state is achieved.

When the discharge capacity is reduced, the center axis of the pin 154 moves downward as the inclination angle of the drive hub 41 and the swing plate 10 decreases, and the thrust flange 1
40, and the spherical body 155 is provided between the first protrusions 151.
The rolling element 152 pinched via a and 155b rotates clockwise in FIG.

The compression reaction force of the refrigerant gas due to the reciprocating motion of the piston 7 during the compression stroke is transmitted to the thrust flange 140 via the ball 155c supported by the recess 157a.

Further, the twisting moment is applied to the first projection 1
Balls 155a, 155 between 51 and rolling element 152
b, 155c through the thrust flange 14
0 is transmitted.

The driving torque is transmitted to the drive hub 41 via the ball 155a or 155b.

According to the second embodiment, the ball 155
c is in surface contact with the concave portion 157a and can receive a compressive reaction force in a wide area, and receives a twisting moment by any of the balls 155a to 155c, so that the force is dispersed, and the slidability and rolling property are improved. However, the wear of the ball can be reduced as compared with the conventional example.

Further, since no twisting occurs due to the balls 155a to 155c, the variable controllability in the link motion is improved.

FIG. 5 is a longitudinal sectional view showing the whole of a wobble plate compressor according to a third embodiment of the present invention. The same parts as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted. .

This embodiment differs from the first embodiment in the hinge mechanism. Hereinafter, the hinge mechanism of this embodiment will be described.

FIG. 6A is an exploded perspective view of the hinge mechanism, and FIG. 6B is a sectional view thereof.

The hinge mechanism 250 includes a first protruding piece 251.
, Rolling element 252, second projecting piece 253, pin 25
4 is provided.

The first projection 251 is provided on the thrust flange 2.
40 are formed integrally with the rear end surface. The pair of protruding pieces 251 are formed in parallel, and concave portions 256a, 256b that rotatably support a part of balls (spherical bodies) 255a, 255b are formed at opposing positions.

A concave portion 25 rotatably supporting the spherical portion 252a at one end of the rolling element 252 is provided between the first projecting pieces 251.
7a are formed. The center of curvature of the spherical portion 252a and the centers of the balls 255a and 255b are located on the same straight line.

The other end of the rolling element 252 is formed with a hole 260 extending in a direction perpendicular to the shaft 5.

The second projecting piece 253 is formed integrally with the front end face of the drive hub 41. The pair of protruding pieces 253 are formed in parallel, and holes 261 for inserting the pins 254 are formed at opposing positions.

The pin 254 is inserted through the hole 261 into the projection 25.
3 and engages with the hole 260 of the rolling element 252. The pin 254 is retained by a retaining ring 262. The pin 254 rotates about an axis passing through the centers of the balls 255a and 255b and the center of curvature of the spherical portion 257a.

According to the third embodiment, the same effects as in the second embodiment can be obtained. The rolling element 25
2 has a larger contact area between the spherical portion 252a at one end and the concave portion 257a than the contact area between the ball 155c and the concave portion 157a of the second embodiment. Is improved.

FIG. 7A is an exploded perspective view of a crank mechanism according to a modification of the third embodiment, and FIG. 7B is a cross-sectional view thereof. The description is omitted.

The drive hub 341 has one protrusion 35.
3 are formed, and a hole 361 through which the pin 354 is inserted is formed in the protruding piece 353.

At the other end of the rolling element 352, a protruding piece 353 is provided.
Are formed with a pair of holding pieces 364 sandwiching a groove 363 having a width substantially equal to the width of. A hole 360 extending in a direction perpendicular to the shaft 5 is formed in the holding piece 364 at the other end of the rolling element 352.

The pin 354 is inserted into the holding piece 36 through the hole 360.
4 and is engaged with the hole 361 of the protruding piece 353. The pin 354 is retained by a retaining ring 362. The pin 354 rotates about an axis passing through the centers of the balls 255a and 255b and the center of curvature of the spherical portion 257a.

According to this modification, the same effects as in the above embodiment can be obtained.

FIG. 8 is a longitudinal sectional view showing the entire swash plate type compressor according to a fourth embodiment of the present invention, and FIG. 9 is a sectional view of the hinge mechanism.

The cylinder block 50 of this swash plate type compressor
A rear head 503 is fixed to one end face of the device 1 via a valve plate 502, and a front head 504 is fixed to the other end face.

The cylinder block 501 is provided with a plurality of cylinder bores 506 at predetermined intervals in a circumferential direction around a shaft (rotating shaft) 505. A piston 507 is slidably accommodated in each of the cylinder bores 506.

A crank chamber 508 is formed in the front head 504, and a swash plate (inclination rotary plate) 510 is accommodated in the crank chamber 508 as the shaft 505 rotates.

A discharge chamber 512 and a suction chamber 513 located around the discharge chamber 512 are formed in the rear head 503.

The valve plate 502 has a cylinder bore 5
Port 516 for communicating the discharge chamber 512 with the discharge chamber 512
And a suction port 515 for communicating the cylinder bore 506 with the suction chamber 513.

The discharge port 516 is opened and closed by a discharge valve 517. The discharge valve 517 is fixed to a rear head side end surface of the valve plate 502 together with a valve retainer 518 by bolts 519. The suction port 515 is connected to the suction valve 521.
The suction valve 521 is opened and closed by the valve plate 502.
And the cylinder block 501.

The front end of the shaft 505 is rotatably supported by a radial bearing 526 in the front head 504, and the rear end of the shaft 505 is rotatably supported by a radial bearing 524 and a thrust bearing 525.

A thrust flange 540 is fixed to the shaft 505, and a bush 509 is provided.
The swash plate 510 is attached via the.

The thrust flange 540 and the swash plate 510 are connected via a hinge mechanism (connection means) 550, and the rotation of the shaft 505 is transmitted from the thrust flange 540 to the swash plate 510 via the hinge mechanism 550.

On the front end surface of the swash plate 510, the central axis of the piston 507 at the top dead center and the central axis of the swash plate (the axis passing through the center B of the bush 509 and parallel to the sliding surface 510a)
Arm portion 551 rotatable about the intersection P with the center is provided.

The distal end surface of the arm portion 551 is formed in an arc shape having a radius R1 about the intersection P. In addition, a hole 553 is formed in the arm 551 at the same radius as the long hole 546 (described later) with the intersection P as a center.

The rear end surface of the thrust flange 540 is provided with a concave surface 542 for slidably supporting the arc-shaped distal end surface 551a of the arm portion 551.

A pair of projecting pieces 545 are provided on the rear end face of the thrust flange 540 with the concave face 542 interposed therebetween. The protruding portion 545 is formed with an arc-shaped long hole 546 centered on the intersection P. This long hole 54
Numeral 6 regulates the inclination angle at the maximum discharge amount and the inclination angle at the minimum discharge amount.

Here, R1 is the radius of an arc centered on the intersection P, R2 is the radius of the front inner peripheral edge of the elongated hole 546 centered on the intersection P, and R3 is the elongated hole 5 centered on the intersection P.
46 shows the radius of the rear-side inner peripheral edge of each of them. Note that there is a relationship of R1>R2> R3 between the radii.

The drive hub 541 is provided between the projecting pieces 545.
The pin 555 is spanned between the protruding pieces 545 via the elongated holes 546 and engages with the holes 553 of the arm 551 in order to rotatably connect the thrust flange 540 and the thrust flange 540. Note that the pin 555 is retained by a retaining ring 558.

The hinge mechanism 5 includes the arm 551, the concave surface 542, the projecting piece 545, the long hole 546, and the pin 555.
50 are configured.

A bush 509 is attached to the shaft 505.
Are fixed by press fitting or the like.

This bush 509 is centered on the intersection P,
It has a shape along an arc of a radius R4 longer than the distance from the intersection P at the maximum discharge amount to the shaft 505, and is in contact with the inner peripheral surface of the center hole 541a formed in the drive hub 541.

A thrust bearing 533 is mounted between the thrust flange 540 and the inner wall surface of the front head 504.

A shoe 560 for supporting the spherical shape 511a at one end of the connecting rod 511 so as to be relatively rotatable is held by a retainer 563 on the sliding surface 510a of the swash plate 510. The retainer 563 is the boss 5 of the swash plate 510.
A retainer support plate 565 fixed to 43 supports the slide plate slidably relative to each other. Connecting rod 511
Is fixed to the piston 507.

The shoes 560 are connected to the connecting rod 5
A shoe body 561 for supporting the distal end surface of the spherical body 511a at one end of the connecting rod 5 in a relatively slidable manner;
And a washer 562 for supporting the rear end surface of the eleven spheres 511a so as to be able to relatively roll.

The rotation of the swash plate 510 causes the piston 507 to reciprocate linearly in the cylinder bore 506. The inclination angle of the swash plate (inclined rotating plate) 510 changes according to the pressure in the crank chamber 508.

In this swash plate compressor, when the pressure in the crank chamber 508 decreases, the inclination angle of the swash plate 510 increases,
The stroke amount of the piston 507 becomes the maximum, and the state becomes the maximum discharge state.

On the other hand, when the pressure in the crank chamber 508 increases, a part of the swash plate 510 separates from the thrust flange 540, and the inclination angle of the swash plate 510 decreases.
The stroke amount of 07 becomes the minimum and the state becomes the minimum discharge state.

When the discharge capacity is reduced, the swash plate 510
The arm 551 slides on the concave surface 542 of the thrust flange 540 and the pin 555 moves along the elongated hole 546 as the inclination angle of the armature 551 decreases. At this time, a large force (compression reaction force) is applied to the rear surface of the piston 507 during the compression stroke, but the compression reaction force of the piston 507 is slidably supported by the arc-shaped tip portion 551a of the arm portion 551. 54
2 and transmitted to the thrust flange 540.

Since the instantaneous rotation center of the rotational movement of the swash plate 510 coincides with the intersection P of the center axis of the piston 507 at the top dead center and the center axis of the swash plate, it is possible to make the fluctuation of the top clearance almost zero. it can.

According to the fourth embodiment, the piston 50
The reciprocating motion of the refrigerant gas caused by the reciprocating motion of the
Since the first arc-shaped tip portion is received by the concave surface 542 slidably supported, the force can be dispersed by receiving a compression reaction force over a wide area, and wear can be reduced.
The strength of the hinge mechanism 550 is improved.

Further, since the fluctuation of the top clearance becomes almost zero, the volume efficiency can be improved.

FIG. 10 is a longitudinal sectional view showing the whole of a swash plate type compressor according to a fifth embodiment of the present invention, and FIG. 11 is a sectional view of a hinge mechanism thereof. And the description is omitted.

This embodiment is different from the fourth embodiment in the hinge mechanism 650.

In this embodiment, the hinge mechanism 650 is
It comprises an arm 651, a concave surface 642, a protruding piece 645, a long groove 646, and a ball 655.

An arc-shaped long groove 646 centering on the intersection point P is formed on the protruding piece 645 formed on the rear end surface of the thrust flange 640.

The swash plate 610 and the thrust flange 640 are connected by a ball 655 supported by the concave portion 611 of the arm portion 651 and the long groove 646 of the projecting portion 645.
According to the inclination of the swash plate 610, the ball 655 is formed into the long groove 64.
6. Slide inside 6.

According to this embodiment, the same effects as in the fourth embodiment can be obtained.

In the second embodiment, the balls 155a to 155c having the same diameter are used. However, it is not necessary that all the balls have the same diameter.

[0140]

As described above, according to the variable displacement compressor according to the first aspect of the present invention, the pin is in surface contact with the projecting portion and the hole of the disk, and the compression gas of the refrigerant gas has a large area. Since the force is received, the force is dispersed, and wear can be reduced. Further, the number of parts is reduced, productivity and assemblability are improved, and reliability is improved.

According to the variable displacement compressor of the second aspect, the volume efficiency can be improved.

According to the variable displacement compressor of the third aspect of the present invention, the rolling element is in surface contact with the rear end projecting piece, receives a compression reaction force of the refrigerant gas over a large area, and receives the first projection. Since the torsion moment is received by the spherical body between the piece and the rolling element, the force is dispersed, the slidability and the rolling property are improved, and the wear can be reduced.

According to the variable displacement compressor of the invention described in claim 4 or 5, since the compression reaction force of the refrigerant gas is received by the concave surface slidably supporting the arc-shaped distal end of the arm, the compressor is wide. The force can be dispersed by receiving the compression reaction force of the refrigerant gas in the area, and wear can be reduced. Further, since the top clearance is constant, the volume efficiency can be improved.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing an entire swinging plate compressor according to a first embodiment of the present invention.

FIG. 2A is an exploded perspective view of a hinge mechanism, and FIG.
(B) is a sectional view thereof.

FIG. 3 is a longitudinal sectional view showing an entire swinging plate compressor according to a second embodiment of the present invention.

FIG. 4A is an exploded perspective view of a hinge mechanism, and FIG.
(B) is a sectional view thereof.

FIG. 5 is a vertical cross-sectional view showing an entire swinging plate compressor according to a third embodiment of the present invention.

FIG. 6A is an exploded perspective view of a hinge mechanism, and FIG.
(B) is a sectional view thereof.

FIG. 7A is an exploded perspective view of a crank mechanism according to a modification of the third embodiment, and FIG. 7B is a cross-sectional view thereof.

FIG. 8 is a longitudinal sectional view showing the entire swash plate type compressor according to a fourth embodiment of the present invention.

FIG. 9 is a sectional view of a hinge mechanism.

FIG. 10 is a longitudinal sectional view showing an entire swash plate compressor according to a fifth embodiment of the present invention.

FIG. 11 is a sectional view of a hinge mechanism.

FIG. 12 is a longitudinal sectional view showing the whole of a conventional swinging plate compressor.

FIG. 13 is a longitudinal sectional view showing the whole of a conventional variable displacement swash plate type compressor.

FIG. 14 is an enlarged view of a disk rotatably supported by a round hole of a projection.

FIG. 15 is a diagram showing a relationship between a swash plate inclination angle and a top clearance in each quadrant shown in FIG. 14;

[Explanation of symbols]

1,501 Cylinder block 5,505 Shaft (rotating shaft) 6,506 Cylinder bore 7,507 Piston 40,140,240,540 Thrust flange (rotating member) 50,150,250,550,650 Hinge mechanism (connecting means) 41 Drive hub (inclined rotating plate) 51 Projection 52 Disk 53,160,260 Hole 54,545,645 Projection 55,154,254,354,555 Pin 151,251 First projection 152,252 352 Rolling element 153, 253, 353 Second protruding piece 155a, 155b, 655 Ball (spherical body) 510 Swash plate (inclined rotating plate) 541a Center hole 542, 642 Concave surface 546 Long hole 551, 651 Arm portion 646 Long groove

Claims (5)

[Claims] A plurality of cylinder bores formed in a cylinder block; a plurality of pistons slidably accommodated in the plurality of cylinder bores; and a rotating member fixed to a rotating shaft and rotating integrally with the rotating shaft. An inclined rotating plate having a center hole through which the rotating shaft passes, and being attached to the rotating shaft so as to be slidable in the axial direction while being inclined with respect to an imaginary plane orthogonal to the rotating shaft; and the rotating member. And a connecting means disposed between the inclined rotating plate and the rotating member, for connecting the inclined rotating plate to the rotating member such that the inclined rotating plate can be inclined. The stroke amount of the piston according to the inclination angle of the inclined rotating plate. In the variable displacement compressor, the connecting means includes: a projection provided on a rear end surface of the rotating member; a disk rotatably supported by a round hole of the projection; Formed, A hole at a position offset from a center axis of the round hole orthogonal to the rotation axis, a pair of protrusions provided on a front end surface of the inclined rotating plate, and a bridge between the protrusions; And a pin engaged with the hole of the disc. 2. The center axis of the pin is located on the rear side of the center axis of the disk, and the distance from the center axis of the rotation axis to the center axis of the pin at the time of minimum discharge is smaller than the center axis of the rotation axis. The variable displacement compressor according to claim 1, wherein the distance is equal to or longer than a distance to a center axis of the disk. 3. A plurality of cylinder bores formed in a cylinder block, a plurality of pistons slidably housed in the plurality of cylinder bores, and a rotating member fixed to a rotating shaft and rotating integrally with the rotating shaft. An inclined rotating plate having a center hole through which the rotating shaft passes, and being attached to the rotating shaft so as to be slidable in the axial direction while being inclined with respect to an imaginary plane orthogonal to the rotating shaft; and the rotating member. And a connecting means disposed between the inclined rotating plate and the rotating member, for connecting the inclined rotating plate to the rotating member such that the inclined rotating plate can be inclined. The stroke amount of the piston according to the inclination angle of the inclined rotating plate. In the variable displacement type compressor, the connecting means is sandwiched between a pair of first protrusions provided on a rear end surface of the rotating member via a spherical body between the protrusions. The times A rolling element rotatably supported on a rear end face of the member; a second protruding piece provided on a front end face of the inclined rotary plate; and the rolling element supported between the protruding pieces. And a pin engaged with the hole of the variable displacement compressor. 4. A plurality of cylinder bores formed in a cylinder block, a plurality of pistons slidably housed in the plurality of cylinder bores, and a rotating member fixed to a rotating shaft and rotating integrally with the rotating shaft. An inclined rotating plate having a center hole through which the rotating shaft passes, and being attached to the rotating shaft so as to be slidable in the axial direction while being inclined with respect to an imaginary plane orthogonal to the rotating shaft; and the rotating member. And a connecting means disposed between the inclined rotating plate and the rotating member, for connecting the inclined rotating plate to the rotating member such that the inclined rotating plate can be inclined. The stroke amount of the piston according to the inclination angle of the inclined rotating plate. Wherein the connecting means is provided on a front end surface of the inclined rotating plate, and the arm is rotatable about an intersection of a central axis of a piston and a central axis of the inclined rotating plate. A concave surface provided on a rear end surface of the rotating member and slidably supporting the arc-shaped distal end surface of the arm portion; and a pair of concave surfaces provided on the rear end surface of the rotating member with the concave surface interposed therebetween. A protruding portion, a long hole provided in the protruding portion and extending along an arc having a radius smaller than the radius of the distal end surface of the arm portion; A variable displacement compressor comprising: a pin to be engaged; and a tip end surface of the arm portion and the concave surface are formed along an arc having substantially the same radius around the intersection. 5. A plurality of cylinder bores formed in a cylinder block, a plurality of pistons slidably housed in the plurality of cylinder bores, and a rotating member fixed to a rotating shaft and rotating integrally with the rotating shaft. An inclined rotating plate having a center hole through which the rotating shaft passes, and being attached to the rotating shaft so as to be slidable in the axial direction while being inclined with respect to an imaginary plane orthogonal to the rotating shaft; and the rotating member. And a connecting means disposed between the inclined rotating plate and the rotating member, for connecting the inclined rotating plate to the rotating member such that the inclined rotating plate can be inclined. The stroke amount of the piston according to the inclination angle of the inclined rotating plate. Wherein the connecting means is provided on a front end surface of the inclined rotating plate, and the arm is rotatable about an intersection of a central axis of a piston and a central axis of the inclined rotating plate. A concave surface provided on a rear end surface of the rotating member and slidably supporting the arc-shaped distal end surface of the arm portion; and a pair of concave surfaces provided on the rear end surface of the rotating member with the concave surface interposed therebetween. A protruding piece, a long groove provided on the protruding piece and extending along an arc having a radius smaller than a radius of a tip end surface of the arm, and slidably provided between the arm and the protruding piece. A variable displacement compressor including a spherical body, wherein a tip end surface of the arm portion and the concave surface are shaped along an arc having substantially the same radius centered on the intersection.