JP2000170652A - Variable displacement swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent abrasion and seizure of contact parts of a swash plate and a shaft as well as to improve controllability by smoothing the axial motion (the tilting motion) of the swash plate. SOLUTION: A link mechanism 41 for tiltably connecting a swash plate 10 to a thrust flange 40 and transmitting torque of the thrust flange 40 to the swash plat 10 is constituted of a bracket 10e provided on the front side end surface 10c of the swash plate 10, a pair of guide grooves 10f, 10g provided in parallel on the bracket 10e, a rod 43 screwed to the swash plate side end surface 40a of the thrust flange 40, and a pair of spherical parts 43a, 43b provided on the tip of the rod 43. Since a pair of spherical parts 43a, 43b of the link mechanism 41 are relatively slidably fitted to a pair of guide grooves 10f, 10g provided across the top dead center (t) of the swash plate 10, the rotation around the Y-axis of the swash plate 10 can be prevented.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable displacement type swash plate type compressor in which a stroke amount of a piston changes according to a change in an inclination angle of a swash plate.

[0002]

2. Description of the Related Art FIG. 11 is a longitudinal sectional view showing a conventional variable capacity swash plate compressor, and FIG. 12 is a diagram showing a swash plate, a thrust flange and a hinge mechanism.

This variable displacement swash plate type compressor has a plurality of cylinder bores 206 formed in a cylinder block 201.
A plurality of pistons 207 slidably housed in the plurality of cylinder bores 206, a thrust flange 240 fixed to the shaft 205 and rotating integrally with the shaft 205, and a center hole 209 into which the shaft 205 is inserted. A swash plate 210 slidable in the axial direction while being inclined with respect to an imaginary plane orthogonal to the shaft 205, and disposed between the thrust flange 240 and the swash plate 210. The swash plate 210 is connected to the swash plate 210 as the thrust flange 240 rotates.
Mechanism 241 for integrally rotating the shaft 20 and the shaft 20
5, a plurality of shoes 250 that relatively rotate on the sliding surface 210a of the swash plate 210 along with the rotation of the swash plate 210, a retainer 253 that is attached to the swash plate 210 so as to be relatively rotatable, and supports the plurality of shoes 250. And the retainer 25
And a retainer support plate 255 for supporting the slide 3 relatively slidably.

[0004] One end of the connecting rod 211 is rotatably connected to the shoe 250, and the other end of the connecting rod 211 is fixed to the piston 207.

[0005] The link mechanism 241 includes a bracket 210e provided on the flange-side end surface 210c of the swash plate 210,
A flange-side end surface 210 provided on the bracket 210e
and a rod 243 provided on a swash plate side end surface 240b of the thrust flange 240. The spherical tip 243a of the rod 243 is fitted into the guide groove 210f so as to be relatively slidable.

When the rotational force of an unillustrated vehicle-mounted engine is transmitted to the shaft 205, the rotational force of the shaft 205 is transmitted from the thrust flange 240 to the swash plate 210 via the link mechanism 241. To rotate. The rotation of the swash plate 210 causes the shoe 25 to rotate.
0 relatively rotates on the sliding surface 210a of the swash plate 210, and the rotational force from the swash plate 210 is converted into a linear reciprocating motion of the piston 207.

The link mechanism 241 shown in FIG. 11 has the following advantages.

When the load is low, a moment acts to reduce the inclination angle of the swash plate 210. When the inclination angle of the swash plate 210 decreases, the instantaneous rotation center (the rod 243) of the swash plate 210 decreases.
(The intersection between the axis of the swash plate 210 and the Y axis passing through the center of rotation of the swash plate 210) moves in a direction away from the axis of the shaft 205.
The moment applied to the swash plate 210 decreases, and the control is stabilized at an inclination angle at which the moment becomes zero. Further, the assembling is easy, and the spherical tip 243 of the rod 243 is provided.
a fits into guide groove 210f so as to be relatively slidable (point contact)
It is hard to be twisted.

[0009]

During the operation of the compressor, the swash plate 210 applies a compression reaction force P from the piston 207 to the swash plate 210.
And the tensile reaction force T pulled from the piston 207 always acts (see FIG. 12). In FIG. 12, the upper half of the swash plate 210 is a suction region, and the lower half of the swash plate 210 is a compression region, with the X axis passing through the shaft 205 in the axial direction as a boundary.

FIG. 13 is a sectional view taken along line XIII-XIII in FIG.

If the sum of the compression reaction force P in the compression region of the swash plate 210 and the sum of the tension reaction force T in the suction region of the swash plate 210 are equal to each other, they can cancel each other out and be balanced. Become.

However, the total of the compression reaction force P is the tensile reaction force T
, A torsional moment MT around the Y-axis (clockwise in FIG. 13) acts on the swash plate 210.

As a result, the edges L and R of the center hole 209 of the swash plate 210 hit the outer peripheral surface of the shaft 205.

However, when the torsional moment MT is large, the swash plate 210 cannot slide smoothly on the shaft 205, and the controllability deteriorates.
There is a problem that a contact portion between the shaft 205 and the shaft 205 is worn, and eventually seizure occurs.

SUMMARY OF THE INVENTION The present invention has been made in view of such circumstances, and an object thereof is to improve the controllability by smoothing the axial movement (tilting operation) of the swash plate, and to improve the controllability of the swash plate and the shaft. To prevent abrasion and seizure of the contact portion.

[0016]

According to a first aspect of the present invention, there is provided a variable displacement type swash plate type compressor having a plurality of cylinder bores formed in a cylinder block and sliding inside the plurality of cylinder bores. A plurality of pistons accommodated therein, 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,
A swash plate 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 connecting means disposed between the rotating member and the swash plate, for connecting the swash plate to the rotating member so as to be able to tilt, and for integrally rotating the swash plate with the rotation of the rotating member; A plurality of shoes that relatively rotate on the sliding surface of the swash plate with the rotation of the rotation shaft, and a retainer that is attached to the swash plate so as to be relatively rotatable and supports the plurality of shoes. One end of the connecting rod is relatively rotatably connected to the plurality of shoes, and the other end of the plurality of connecting rods is connected to the plurality of pistons. In a variable displacement type swash plate compressor in which a stroke amount of a piston is changed, the connecting means includes a pair of spherical portions provided on a rear end surface of the rotating member, and a swash plate on a front end surface of the swash plate. Dead center Provided Guyo, characterized in that it has a linearly pair parallel to each other for guiding the guide grooves the pair of spherical portions.

As described above, the pair of spherical portions of the connecting means are slidably fitted in the pair of guide grooves provided so as to straddle the top dead center of the swash plate. Rotation around the axis can be prevented. As a result, the edge of the center hole of the swash plate does not directly hit the outer peripheral surface of the rotating shaft, and the axial movement (tilting operation) of the swash plate becomes smooth.

According to a second aspect of the present invention, there is provided the variable displacement type swash plate type compressor according to the first aspect of the present invention, wherein a single rod is provided on a rear end surface of the rotating member. The pair of spherical portions are fixed to the tip of the rod.

As described above, one rod is provided on the rear end surface of the rotating member, and a pair of spherical portions is fixed to the tip of the rod. Therefore, the configuration is smaller than when two rods are used. Becomes easier.

According to a third aspect of the present invention, in the variable displacement type swash plate type compressor according to the first aspect, the swash plate is attached to the rotary shaft via a hinge ball. It is characterized by being.

As described above, since the intermediate portion (ridge line) of the inner peripheral surface of the center hole of the swash plate does not directly contact the outer peripheral surface of the rotating shaft, the axial movement of the swash plate becomes smoother.

[0022]

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

FIG. 2 is a longitudinal sectional view showing an entire variable displacement swash plate type compressor according to an embodiment of the present invention, and FIG.
FIG. 3 is a sectional view showing a part of the variable displacement type swash plate type compressor shown in FIG. 2 in which the inclination of the swash plate is minimum, and FIG. 4 is a view showing the variable displacement type swash plate type compressor of FIG. FIG. 5 is a cross-sectional view showing a state where the inclination of the swash plate is maximum, and FIG.
FIG. 6 is a view taken in the direction of arrow VI in FIG. 3, and FIG. 7 is a view taken in the direction of arrow VII in FIG.

A rear head 3 is fixed to one end face of a cylinder block 1 of this variable displacement type swash plate type compressor 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 5 (rotation axis). These cylinder bores 6
A piston 7 is slidably accommodated therein.

A crank chamber 8 is provided in the front head 4.
A swash plate 10 that rotates as the shaft 5 rotates is accommodated in the crank chamber 8. The sliding surface 10a of the swash plate 10 has a shoe 5 for supporting the spherical end 11a of the connecting rod 11 so as to be relatively rollable.
0 is held by the retainer 53. The retainer 53 is a retainer support plate 5 fixed to the boss 10b of the swash plate 10.
5 are slidably supported by each other. The other end 11 b of the connecting rod 11 is fixed to the piston 7.

The shoe 50 is connected to the connecting rod 11
A first supporting member 51 for supporting the distal end surface of the spherical end portion 11a of the connecting rod 11 in a relatively rotatable manner;
The second end for supporting the rear end face of the one end portion 11a so as to be relatively rollable.
And the supporting member 52.

In the rear head 3, a discharge chamber 12 is provided.
A suction chamber 13 located around the discharge chamber 12 is formed.

The valve plate 2 has a discharge port 16 for communicating the compression chamber of the cylinder bore 6 with the discharge chamber 12.
And a suction port 15 for communicating the compression chamber of the cylinder bore 6 with the suction chamber 13 are provided at predetermined intervals along a predetermined circumference centered on the shaft 5. The discharge port 16 is opened and closed by a discharge valve 17.
Is a valve retainer 18 on the end face of the valve plate 2 on the rear head side.
Also, they are fixed by bolts 19 and nuts 20.

The suction port 15 is opened and closed by a suction valve 21, and the suction valve 21 is disposed on the front end face of the valve plate 2. The high pressure refrigerant gas in the discharge chamber 12 is supplied to the bolt 19 with the radial bearing 24 and the thrust bearing 25.
A guide hole 19a is provided to lead to the front.

The radial bearing 24 and the thrust bearing 25 support the rear end of the shaft 5, and the radial bearing 26 rotatably supports the front end of the shaft 5.

A communication passage 31 is provided between the suction chamber 13 and the crank chamber 8, and a pressure regulating valve 32 is provided in the middle of the communication passage 31. And the pressure in the crank chamber 8 are adjusted.

A thrust flange (rotating member) 40 for transmitting the rotation of the shaft 5 to the swash plate 10 is fixed to the front end of the shaft 5.
Numeral 0 is rotatably supported on the inner wall surface of the front head 4 via a thrust bearing 33. Thrust flange 40
The swash plate 10 is connected to the swash plate 10 via a link mechanism (connection means) 41, and the swash plate 10 can be inclined with respect to a virtual plane perpendicular to the shaft 5.

The link mechanism 41 includes a bracket 10e provided on the front surface 10c of the swash plate 10, and a pair of guide grooves 10 provided in parallel with the bracket 10e.
f, 10 g and the swash plate side end surface 40 of the thrust flange 40
and a pair of spherical portions 48a and 48b provided at the distal end of the rod 43. The pair of spherical portions 48 a and 48 b are located on a virtual straight line orthogonal to the axis of the rod 43. Guide groove 10f, 1
The longitudinal axis of 0 g is inclined at a predetermined angle with respect to the front surface 10 c of the swash plate 10. Guide grooves 10f, 10g are swash plate 10
(See FIG. 1).
That is, as shown in FIG. 6, one guide groove 10f is located in the suction area i of the swash plate 10, and the other guide groove 10g is located in the compression area c of the swash plate 10. Spherical part 48
a and 48b are fitted into the guide grooves 10f and 10g so as to be relatively slidable.

The shaft 5 penetrates through the center hole 9 of the swash plate 10, and the swash plate 10 is attached slidably in the axial direction while being inclined with respect to an imaginary plane orthogonal to the shaft 5.
A winding spring 44 is provided between the swash plate 10 and the thrust flange 40.
Is mounted, and the swash plate 10 is urged toward the cylinder block 1 by the winding spring 44. A stopper 45 is fixed to the shaft 5, and a winding spring 47 is mounted between the stopper 45 and the swash plate 10. The swash plate 10 is urged toward the thrust flange 40 by the winding spring 47. .

During the operation of the compressor, a compression reaction force P from the piston 7 (see FIG.
) Acts, and a tensile reaction force T for pulling the piston 7 acts on the remaining substantially half of the swash plate 10 (suction area i). In FIG. 6, the left half of the swash plate 10 is a suction area i and the right half of the swash plate 10 is a compression area c with respect to the Y axis. In FIG. 1, the upper half of the swash plate 10 is a suction area i and the lower half of the swash plate 10 is a compression area c with respect to an X axis passing through the center of the shaft 5 in the axial direction.

Next, the operation of the variable displacement type swash plate type compressor will be described.

When the rotational power of a vehicle-mounted engine (not shown) is transmitted to the shaft 5, the rotational force of the shaft 5 is transmitted to the swash plate 10 via the thrust flange 40 and the hinge mechanism 41, and the swash plate 10 rotates.

The rotation of the swash plate 10 causes the shoe 50 to move to the swash plate 1.
Since the relative rotation is made on the zero sliding surface 10a, the rotational force from the swash plate 10 is converted into a linear reciprocating motion of the piston 7. The piston 7 reciprocates in the cylinder bore 6, and as a result, the volume of the compression chamber in the cylinder bore 6 changes, and the suction, compression, and discharge of the refrigerant gas are sequentially performed by the change in the volume. Of the high-pressure refrigerant gas having a predetermined capacity is discharged. In the suction stroke, the suction valve 21 opens, and low-pressure refrigerant gas is sucked from the suction chamber 13 into the compression chamber in the cylinder bore 6. In the discharge stroke, the discharge valve 17 opens, and the high-pressure refrigerant gas flows from the compression chamber to the discharge chamber 12. Is discharged.

When the heat load decreases and the pressure regulating valve 32 closes the communication passage 31 and the pressure in the crank chamber 8 increases, the swash plate 10 slides on the shaft 5 and the inclination angle of the swash plate 10 decreases. As a result, the stroke amount of the piston 7 decreases, and the discharge capacity decreases. At this time, the link mechanism 4
Spherical parts 48a, 48b located at the tip of one rod 43
Are relatively slid in the guide grooves 10f and 10g.
f, reaches one end of 10 g (see FIG. 3).

On the other hand, when the heat load increases and the pressure regulating valve 32 opens the communication passage 31, and the pressure in the crank chamber 8 decreases, the swash plate 10 slides on the shaft 5, and the swash plate 1
The inclination angle of 0 increases, and as a result, the stroke amount of the piston 7 increases, and the discharge capacity increases. At this time, the spherical portions 48a and 48b of the link mechanism 41 are
f and 10g relative to each other to reach the other ends of the guide grooves 10f and 10g (see FIG. 2).

During operation of the compressor, a compression reaction force P from the piston 7 is acting on the compression region c of the swash plate 10, and a tension reaction force T pulled from the piston 7 is acting on the suction region i. Since the sum of the compression reaction force P exceeds the sum of the tension reaction force T, the torsional moment MT around the Y axis acts on the swash plate 10, but the pair of spherical portions 48a and 48b Guide grooves 10 provided so as to straddle
f, 10g, so that they can be slid relative to each other.
Rotation around the zero Y axis can be prevented. As a result, the edges L and R of the center hole 62a of the swash plate 10 do not directly hit the outer peripheral surface of the shaft 5.

According to the variable displacement type swash plate type compressor of this embodiment, as described above, the edge L of the center hole 9 of the swash plate 10,
Since R does not directly hit the outer peripheral surface of the shaft 5, the swash plate 1
The movement in the axial direction of 0 (inclination operation) becomes smooth, controllability can be improved, and wear and seizure of the contact portion between the swash plate 10 and the shaft 5 can be prevented.

Since two spherical portions 48a and 48b are provided on the thrust flange 40 via one rod 43, the two spherical portions 48a and 48b are provided via two rods.
The link mechanism is simplified, the weight is reduced, and the cost can be reduced, as compared with the configuration in which the a and 48b are provided on the thrust flange 40.

FIG. 8 is a cross-sectional view showing a part of a variable displacement type swash plate type compressor according to another embodiment of the present invention, in which the inclination of the swash plate is minimum, and FIG. 9 is a sectional view showing the variable displacement type swash plate type. FIG. 10 is a cross-sectional view of a part of the compressor showing a state where the inclination of the swash plate is maximum, FIG. 10 shows a hinge ball, FIG. 10 (a) is a plan view, and FIG. FIG. 3C is a cross-sectional view along the line bb, and FIG. 3C is a cross-sectional view along the line cc in FIG. Portions common to the above-described embodiments are denoted by the same reference numerals, and description thereof is omitted.

In the above-described embodiment, the swash plate 10 is
Is mounted directly on the swash plate 1 in this embodiment.
10 was mounted on the shaft 5 via the hinge ball 60. The hinge ball 60 has a through hole 60a through which the shaft 5 penetrates, and a convex support surface 60b slidably fitted with the concave hinge ball receiving surface 109a of the swash plate 110. .

According to this embodiment, the inner peripheral surface of the center hole 109 of the swash plate 110 (eg, edges L, R, ridge line r, etc.) does not directly contact the outer peripheral surface of the shaft 5, so that the swash plate 110
In the axial direction becomes smoother.

In each of the above embodiments, the pair of spherical portions 48a, 48b is formed by connecting the thrust flange 40 to the swash plate side end surface 4a.
0a via the rod 43 has been described,
The pair of spherical portions 48a and 48b may be provided directly on the swash plate side end surface 40a of the thrust flange 40 without using the rod 43.

[0048]

As described above, according to the variable displacement type swash plate compressor of the first aspect of the present invention, the edge of the center hole of the swash plate does not directly contact the outer peripheral surface of the rotating shaft, so that the shaft of the swash plate is not rotated. The movement in the direction (inclination operation) becomes smooth, controllability can be improved, and wear and seizure of the contact portion between the swash plate and the rotating shaft can be prevented.

According to the variable displacement type swash plate type compressor according to the second aspect of the present invention, the structure is simplified, the number of parts is reduced, and the manufacturing operation is simplified as compared with the case where two rods are used. Can be.

According to the variable displacement type swash plate compressor of the third aspect of the invention, the axial movement of the swash plate becomes smoother.

[Brief description of the drawings]

FIG. 1 is a view taken in the direction of the arrow I in FIG.

FIG. 2 is a longitudinal sectional view showing the entire variable displacement swash plate compressor according to one embodiment of the present invention.

FIG. 3 is a sectional view showing a part of the variable displacement type swash plate type compressor shown in FIG. 2 and in which a swash plate has a minimum inclination.

FIG. 4 is a sectional view showing a part of the variable displacement type swash plate type compressor shown in FIG. 2 and in which a swash plate has a maximum inclination.

FIG. 5 is a view taken in the direction of the arrow V in FIG. 3;

FIG. 6 is a view taken in the direction of arrow VI in FIG. 3;

FIG. 7 is a view on arrow VII of FIG. 3;

FIG. 8 is a cross-sectional view showing a part of a variable displacement type swash plate compressor according to another embodiment of the present invention, in which a swash plate has a minimum inclination.

FIG. 9 is a cross-sectional view showing a part of the variable displacement type swash plate type compressor in which a swash plate has a maximum inclination.

FIG. 10 is a diagram for explaining a hinge ball.

FIG. 11 is a longitudinal sectional view showing a conventional variable displacement swash plate compressor.

FIG. 12 is a diagram showing a swash plate, a thrust flange, and a hinge mechanism.

FIG. 13 is a sectional view taken along the line XIII-XIII in FIG. 11;

[Explanation of symbols]

 Reference Signs List 5 shaft 6 cylinder bore 7 piston 9 center hole 10 swash plate 10c front surface of swash plate 10e bracket 10f, 10g guide groove 11 connecting rod 11a tip 11b rear end 40 thrust flange 40a thrust flange swash plate side end 41 link mechanism 43 Rod 48a, 48b Spherical part 50 Shoe 53 Retainer t Top dead center

Claims (3)

[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. A swash plate having a center hole through which the rotation shaft passes, and being attached to the rotation shaft so as to be slidable in the axial direction while being inclined with respect to an imaginary plane orthogonal to the rotation shaft; and A connecting means disposed between the swash plate and the swash plate, the swash plate being slidably connected to the rotating member, and a swash plate integrally rotating with the rotation of the rotating member; A plurality of shoes that relatively rotate on the sliding surface of the swash plate with the rotation of the swash plate, wherein the shoe intervenes between the swash plate and the piston, and the rotational movement of the swash plate causes the piston to rotate. Is converted to linear reciprocating motion of Also, in the variable displacement swash plate type compressor in which the stroke amount of the piston changes according to a change in the inclination angle of the swash plate, the connecting means includes a pair of spherical portions provided on a rear end surface side of the rotating member. A pair of parallel guide grooves that are provided on the front end surface of the swash plate so as to straddle the top dead center of the swash plate and guide the pair of spherical portions linearly. A variable displacement swash plate type compressor. 2. The variable capacitance type according to claim 1, wherein a single rod is provided on a rear end surface of the rotating member, and the pair of spherical portions are fixed to a distal end portion of the rod. Swash plate type compressor. 3. The variable displacement swash plate compressor according to claim 1, wherein said swash plate is attached to said rotary shaft via a hinge ball.