JPH06101640A - Variable-displacement swash plate compressor - Google Patents

Abstract

PURPOSE:To improve durability by suppressing the abrasion at a contact section between a swash plate and a rotation supporter limiting the maximum tilt angle of the swash plate. CONSTITUTION:The tilt angle of a swash plate 14 is controlled by the pressure in a crank chamber 5 to change the compression displacement, and the maximum tilt angle of the swash plate 14 is limited when a tilt face 14a formed on the back face of the swash plate 14 is brought into contact with a deterring face 30a formed on a rotation supporter 11. The rotation supporter 11 scoops the sealed oil in the crank chamber 5 as it is rotated, and oil guide paths (an oil guide groove, an oil guide hole 33b, and an oil guide fine groove) guiding and feeding the scooped oil into the deterring face 30a are bored. A contact section between the swash plate 14 and the rotation supporter 11 is lubricated by oil, and abrasion is suppressed.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable capacity swash plate compressor used in a vehicle air conditioner or the like.

[0002]

2. Description of the Related Art A conventional variable capacity swash plate compressor (hereinafter referred to as
(Hereinafter simply referred to as a compressor), JP-A-60-175783
The one disclosed in Japanese Patent Publication is known. In this compressor, a cylinder block having a plurality of cylinder bores is arranged in the center of a center housing, the front end of which forms a closed crank chamber and is closed by a front housing, and the rear end of which is a valve plate. It is closed by the rear housing via. The rear housing is provided with an intake chamber and a discharge chamber that communicate with the cylinder bore. A drive shaft is inserted into and supported by a central shaft hole of the cylinder block. The drive shaft supports a rotary support member in the crank chamber for synchronous rotation, and a sleeve for axial sliding. It has been inserted. A swash plate is connected to the rotary support through a hinge mechanism, and the swash plate is supported by the drive shaft by sliding contact with the sleeve by the inner surface of the spherical zone. In this way, the swash plate is capable of synchronous rotation with the drive shaft and displacement of the inclination angle via the hinge mechanism and the sleeve. A single-headed piston fitted in each cylinder bore is moored to the swash plate via a pair of shoes. The cylinder block is provided with a communication hole that connects the crank chamber and the suction chamber and is opened and closed by a control valve that controls the pressure in the crank chamber.

In this compressor, when the swash plate rotates in accordance with the drive of the drive shaft, the oscillating motion corresponding to the tilt angle of the swash plate is converted into the reciprocating motion of the piston through the shoe, so that the piston moves in the cylinder bore. Reciprocates inside. As a result, the refrigerant gas is sucked from the suction chamber into the cylinder bore, and the refrigerant gas is compressed and then discharged to the discharge chamber. The compression capacity of the refrigerant gas discharged into the discharge chamber is controlled by adjusting the pressure in the crank chamber by the control valve. That is, when the control valve opens the communication hole to communicate the crank chamber with the suction chamber, the back pressure acting on the piston is reduced, and the hinge mechanism and the sleeve operate to increase the inclination angle of the swash plate. This extends the stroke of the piston and increases the compression capacity.

On the contrary, when the pressure in the crank chamber is increased by blow-by gas due to the control valve closing the communication hole, the back pressure acting on the piston is increased and the inclination angle of the swash plate is decreased. This shortens the stroke of the piston and reduces the compression capacity.

[0005]

By the way, in the above compressor, the maximum inclination angle of the swash plate is such that the inclined surface formed on the back surface of the swash plate abuts against the stop surface formed on the inner end surface of the rotary support. Limited by During operation of the compressor, the pressure in the bore acts on the swash plate via the piston, but this pressure in the bore differs between the piston on the discharge side and the piston on the suction side. The pressure imbalance in the bore becomes large. Therefore, a non-uniform force due to the imbalance in the bore pressure acts on the abutting portion between the swash plate and the rotary support, causing uneven wear. Further, the abutting portion also wears due to repeated abutting of the swash plate and the rotary support.

The present invention has been made in view of the above circumstances, and aims to improve the durability by suppressing the wear at the contact portion between the swash plate and the rotary support, which limits the maximum inclination angle of the swash plate. Is a technical issue to be solved.

[0007]

According to the present invention for solving the above-mentioned problems, a cylinder bore is defined in a cylinder block, and a single-headed piston is housed in each of the cylinder bores so that the piston can reciprocate. A housing is joined to one end surface of the cylinder block so as to partition and form, and a rotary support is supported by the drive shaft housed in the crank chamber so as to be synchronously rotatable, and a hinge mechanism is formed between the drive shaft and the rotary support. And a swash plate is pivotally supported via a sleeve between the swash plate and the drive shaft, and the swash plate is reciprocally moved between the swash plate and the piston. A variable capacity swash plate compressor, in which a coupling mechanism for converting into a variable pressure valve is interposed, and the inclination angle of the swash plate is controlled by the pressure in the crank chamber to change the compression capacity. Has a new stop surface that abuts against the swash plate and limits the maximum inclination angle of the swash plate. It adopts a simple configuration.

[0008]

In the compressor of the present invention, the inclination angle of the swash plate changes based on the pressure difference between the pressure in the crank chamber and the suction pressure, and the maximum inclination angle of the swash plate is the stop in which the swash plate is formed on the rotary support. Limited by abutting the surface. As described above, the abutting portion is apt to be worn due to the non-uniform force due to the imbalance of the pressure in the bore from the piston or the repeated abutting of the swash plate and the rotary support. However, in the present invention, the oil guide passage formed in the rotary support scoops the enclosed oil in the crank chamber as the rotary support rotates, and guides it to the stop surface of the rotary support. For this reason, the contact portion between the swash plate and the rotary support is lubricated with oil, and wear is suppressed.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the present invention will be described below with reference to FIGS. In the figure, a front housing 2 is provided at a front end of a cylinder block 1 which is a main body of a compressor.
Is connected, and the rear housing 3 is connected to the rear end via the valve body 4. A crankshaft 5 formed by the cylinder block 1 and the front housing 2 accommodates a drive shaft 6 which is linked to an engine (not shown).
The drive shaft 6 is rotatably supported by bearings 7 and 8. The cylinder block 1 is provided with a plurality of cylinder bores 9 surrounding the drive shaft 6 and arranged in parallel, and each cylinder bore 9 has a single-headed piston 1
0 is inserted.

On the drive shaft 6 in the crank chamber 5, a rotary support 11 is fixed so as to be rotatable in synchronization with the drive shaft 6, and a sleeve 12 having a spherical bearing surface is fitted so as to be rotatable and slidable. Has been done. As shown in the front view of FIG. 2 and the bottom view of FIG. 3, the rotary support 11 has a central hole 11a fitted and fixed to the drive shaft 6 and a lower portion of the central hole 11a (see FIG. 1).
2) and a rectangular protrusion 30 that largely protrudes from the lower part of FIG. 2 to the rear side, and both sides of the rectangular protrusion 30 (both left and right sides in FIG. 2).
A pair of stepped portions 31, 32 protruding from the rear side to the rear side,
It has an arm 16 protruding rearward from an outer peripheral edge portion above the center hole 11a (upper side in FIGS. 1 and 2). Further, the tip end surface of the rectangular protrusion 30 is a substantially trapezoidal stop surface 30a. 2 is a front view seen from the rear side,
The rotary support 11 rotates counterclockwise in FIG.
The step portion 32 on the right side of FIG. 2 extends in an arc shape from the upper end surface located at the outer peripheral edge portion of the rotary support 11 toward the center, and has a depth corresponding to the protrusion of the step portion 32. An oil guide groove 33a is bored. That is, this oil guide groove 33a
Open toward the rotation of the rotary support 11. In addition, the rectangular protrusion 30 of the rotary support 11 linearly extends from the bottom of the right side surface (the right side in FIG. 2) toward the approximate center of the stopping surface 30a and opens at the stopping surface 30a. Further, an oil guide hole 33b communicating with the oil guide groove 33a is formed. Further, an oil guiding fine groove 33c linearly extending from the opening of the oil guiding hole 33b toward the left end (left side in FIG. 2) is also formed on the stop surface 30a of the rectangular protrusion 30. .
The oil guide groove 33a, the oil guide hole 33b, and the oil guide thin groove 3 are provided.
An oil guide passage is formed by 3c.

A counter spring 13 is interposed between the step portion of the drive shaft 6 and the sleeve 12 to bias the sleeve 12 in the rear direction, and on the sleeve 12, the spherical bearing surface is formed. A swash plate 14 having an inner surface of a spherical zone that fits with is tiltably supported. In the most contracted state of the counter spring 13 shown in FIG. 1, the inclined surface 14a formed on the lower rear surface of the swash plate 14 is formed on the inner end surface of the rectangular protrusion 30 of the rotary support 11. The maximum inclination angle of the swash plate 14 is limited because the swash plate 14 abuts the stop surface 30a. The piston 10 is moored to the disk surface formed on the outer peripheral portion of the swash plate 14 via hemispherical shoes 15 and 15 that form a connecting mechanism.

On the other hand, the tip of the arm 16 protruding from the outer peripheral edge of the rotary support 11 has a support shaft 17 in a direction perpendicular to the axis.
Is rotatably inserted. A guide pin 1 that penetrates the support shaft 17 in the radial direction with the arm 16 interposed therebetween.
Both guide pins 18 in which the base ends of 8 and 18 are fixed and extend
The front end portion of is slidably inserted into a joint portion 19 formed on the front surface side of the swash plate 14. A hinge mechanism K is constituted by the arm 16, the support shaft 17, the guide pin 18, and the joint portion 19.

The inside of the rear housing 3 is divided into a suction chamber 20 and a discharge chamber 21 by a partition wall, and a suction port 22 and a discharge port 23 are formed in the valve plate 4 so as to correspond to each cylinder bore 9. The suction port 22 and the discharge port 23 are opened and closed by a suction valve and a discharge valve 24 (not shown) in accordance with the reciprocating movement of the piston 10, and a control valve for adjusting the pressure of the crank chamber 5 is provided in the rear housing 3. , But detailed illustration and description thereof are omitted.

In the compressor configured as described above,
When the swash plate 14 rotates as the drive shaft 6 is driven, the swash plate 1
The oscillating motion corresponding to the inclination angle of 4 is converted into the reciprocating motion of each piston 10 via the shoes 15 and 15, whereby the refrigerant gas is sucked from the suction chamber 22 into the cylinder bore 9 and the refrigerant gas is compressed. Then, it is discharged into the discharge chamber 24. At this time, the compression capacity of the refrigerant gas discharged into the discharge chamber 24 is
It is controlled by adjusting the pressure in the crank chamber 5 by a control valve (not shown).

That is, for example, if the pressure in the crank chamber 5 is lowered by adjusting the pressure of the control valve, the back pressure acting on the piston 10 is lowered, and the tilt angle of the swash plate 14 is increased. That is, the sleeve 12 moves forward against the opposing spring 13, the swash plate 14 rotates in the depression direction along the bearing surface of the sleeve 12, and the articulation portion 19 of the hinge mechanism K rotates the spindle 17. Along with this, the slide pin 18 fluctuates in the inserting direction, and the inclination angle of the swash plate 14 increases. As a result, the stroke of the piston 10 is extended and the compression capacity is increased.

On the contrary, if the pressure in the crank chamber 5 is increased by adjusting the pressure of the control valve, the back pressure acting on the piston 10 is increased and the inclination angle of the swash plate 14 is decreased. That is,
The sleeve 12 is retracted by the urging force of the counter spring 13, the swash plate 14 is rotated in the upright direction along the bearing surface of the sleeve 12, and the articulation portion 19 of the hinge mechanism K is accompanied by the rotation of the support shaft 17. It fluctuates in the direction to remove the slide pin 18,
The inclination angle of the swash plate 14 becomes smaller. This allows the piston 1
The stroke of 0 is shortened and the compression capacity is reduced.

Here, in the compressor of this embodiment, the swash plate 14 is used.
The maximum inclination angle of the swash plate 14 is that the inclined surface 14a
It is limited by abutting against the stop surface 30a of the rectangular protrusion 30 of No. 1. Then, with the rotation of the rotary support 11, the enclosed oil in the crank chamber 5 is scooped into the oil guide groove 33a which is bored in the one step portion 32 and opened toward the rotation,
This oil is introduced into the oil guide groove 33a, the oil guide hole 33b, and the oil guide fine groove 33.
It is supplied to the stop surface 30a via c. Therefore, the contact portion between the swash plate 14 and the rotary support 11 is lubricated with oil, and wear is suppressed. The oil guide groove 33c is
2 extends to the left side of the restraining surface 30a in FIG. 2 because the portion of the restraining surface 30a on the left side in FIG. 2 is easily worn due to the pressure in the bore from the piston 10 in the compression stroke. Is. As described above, in the present embodiment, the wear of the abutting portion caused by the non-uniform force due to the imbalance of the pressure in the bore from the piston or the repeated contact between the swash plate and the rotary support is suppressed. Therefore, the durability of the rotary support 11 and the swash plate 14 can be improved.

[0018]

As described above in detail, in the compressor of the present invention, the oil enclosed in the crank chamber is scooped as the rotary support rotates, and the scooped oil is fed between the rotary support and the swash plate. Since the oil guide path for guiding to the abutting portion is bored in the rotary support, the lubricity of the abutting portion can be enhanced by oil to suppress wear. Therefore, the durability of the swash plate and the rotary support can be improved. Further, uneven wear of the abutting portion due to the non-uniform force exerted by the imbalance of the pressure in the bore from the piston is also suppressed, so that the obstruction of the capacity control due to this can be prevented. .

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view of a compressor according to an embodiment.

FIG. 2 is a front view of a rotary support according to the compressor of the embodiment.

FIG. 3 is a bottom view of the rotary support according to the compressor of the embodiment.

[Explanation of symbols]

1 ... Cylinder block 2 ... Front housing
3 ... Rear housing 5 ... Crank chamber 6 ... Drive shaft
9 ... Cylinder bore 10 ... Piston 11 ... Rotating support
12 ... Sleeve 14 ... Swash plate 15 ... Shoe (connecting mechanism)
K ... Hinge mechanism 14a ... Inclined surface 30a ... Stop surface
33a ... Oil guiding groove 33b ... Oil guiding hole 33c ... Oil guiding narrow groove

 ─────────────────────────────────────────────────── ─── Continuation of front page (72) Inventor Shoho Sonobe 2-chome, Toyota-cho, Kariya city, Aichi Stock company Toyota Industries Corp.

Claims (1)

[Claims] 1. A cylinder bore is defined in a cylinder block, and a single-headed piston is reciprocally housed in each of the cylinder bores. One end surface of the cylinder block is defined to define a crank chamber. A housing is joined, and a rotary support is supported by the drive shaft housed in the crank chamber such that the rotary support can rotate synchronously. A hinge mechanism is provided between the drive shaft and the rotary support, and a sleeve is provided between the drive support and the drive shaft. A swash plate is pivotally supported for tilt displacement, and a coupling mechanism for converting the swinging motion of the swash plate into the reciprocating motion of each piston is interposed between the swash plate and the piston. A variable displacement swash plate compressor configured to change the compression capacity by controlling the tilt angle of the swash plate by the pressure of A variable capacity swash plate compressor characterized in that a surface is formed, and an oil guide passage for guiding the oil enclosed in the crank chamber by the rotational movement thereof while guiding the oil to the stop surface is provided.