JP3018801B2 - Reciprocating compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a reciprocating compressor suitable for use in vehicle air conditioning.

[0002]

2. Description of the Related Art Conventionally, each piston reciprocates in a plurality of bores formed in a cylinder block in parallel with a drive shaft, as in a swash plate compressor described in Japanese Patent Application Laid-Open No. Sho 59-145378, for example. Compressors that compress refrigerant gas are known. In this type of compressor, a drive shaft is fitted and supported in a central shaft hole of a cylinder block, and each piston is linked to a swash plate in a crank chamber that cooperates with the drive shaft to move directly in each bore. A housing is joined to the end surface of the cylinder block via a valve plate, and a suction chamber for supplying refrigerant gas into the bore and a discharge chamber for discharging refrigerant gas compressed by a piston in the bore are formed in the housing. Is formed. The suction of the refrigerant gas from the suction chamber into the bore is performed by moving the piston to the bottom dead center position, and by setting the suction port formed in the valve plate and the pressure in the bore provided on the bore side of the suction port. And a suction valve that opens a suction port in response to the pressure. Further, the discharge of the refrigerant gas from the bore to the discharge chamber is performed by moving the piston to the top dead center position, the discharge port formed in the valve plate, and the discharge port provided on the discharge chamber side of the discharge port inside the bore. This is performed via a discharge valve that opens a discharge port according to pressure.

[0003]

However, in the conventional compressor, the suction valve is configured to overcome its own elastic force acting in the direction of maintaining the valve closed state and to open the valve. Is big. This pressure loss leads to a decrease in volumetric efficiency. Therefore, the present applicant has filed Japanese Patent Application No. Hei.
No. 31853 proposed a reciprocating compressor having excellent volumetric efficiency. In this compressor, a conduction path that radially communicates each bore with the central shaft hole is formed, and a rotary valve is coupled to the drive shaft via a key as a torque transmitting member so as to be able to rotate synchronously. The rotary valve is formed with a suction passage that sequentially connects the passage of each bore in the suction stroke and the suction chamber. In the proposed compressor, the rotary valve rotates in synchronization with the drive shaft via the key, so that the refrigerant gas in the suction chamber is sequentially sucked into each of the bores. The pressure loss is extremely reduced because it is continued stably. Thus, this compressor can maintain sufficient volumetric efficiency regardless of whether it has a fixed capacity or a variable capacity.

However, in this compressor, if the axis of the drive shaft and the axis of the rotary valve are not concentrically aligned due to tolerances of the drive shaft, rotary valve, cylinder block, etc. In order to prevent caulking from occurring in the central shaft hole of the block, it is necessary to allow the radial valve to move to some extent in the radial direction. For this reason, in the above proposal, minute gaps are positively provided between the drive shaft and the key and between the key and the rotary valve, thereby absorbing the tolerance. On the other hand, if the gap is too large, the synchronous rotation of the rotary valve will be impaired. For this reason, in this compressor, it was very difficult to achieve both the absorption of the tolerance and the synchronous rotation of the rotary valve.

[0005] It is an object of the present invention to solve the above problem while maintaining sufficient volumetric efficiency and achieving both tolerance absorption and synchronous rotation of a rotary valve.

[0006]

SUMMARY OF THE INVENTION In order to solve the above problems, a reciprocating compressor according to the present invention has a cylinder block having a plurality of bores around an axis, and a bearing fitted into a shaft hole of the cylinder block. A drive shaft, a piston linked to a swash plate in a crank chamber cooperating with the drive shaft, and linearly moving in the bore, a suction chamber communicating with the shaft hole, and an outer region of the suction chamber. A reciprocating compressor having a discharge chamber and a housing for closing an end face of the cylinder block, wherein a conduction path is formed between each of the bores and the shaft hole. A rotary valve having a suction passage that sequentially connects the passage of each bore in the suction stroke and the suction chamber through a torque transmission member via a torque transmission member is connected to the drive shaft so as to be synchronously rotatable, and the drive shaft and the torque transmission member are connected to each other. Means that movement in one of the radial directions is allowed Coupled Te, it employs a novel configuration that movement in the other direction that intersects with the direction of the radial direction and the torque transmitting member and the rotary valve is coupled allowed.

[0007]

In the reciprocating compressor of the present invention, the rotary valve rotates in synchronization with the drive shaft via the torque transmitting member, so that the refrigerant gas in the suction chamber is in the suction passage and the suction stroke of the rotary valve. Inhaled into each bore sequentially through the bore passage,
Since the suction operation of the refrigerant gas is smoothly and stably continued in each bore, the pressure loss is extremely reduced.

Further, in this compressor, the drive shaft and the torque transmitting member are allowed to move in one of the radial directions, and the torque transmitting member and the rotary valve are allowed to move in the other direction of the radial direction. Is acceptable. The one direction and the other direction intersect with each other, and the rotation of the rotary valve is not impaired. For this reason, even if there is a tolerance in the drive shaft, the rotary valve, the cylinder block, and the like, the torque transmission member functions as an Oldham coupling, and the tolerance is absorbed. Here, if the rotary valve can also move in the axial direction, the torque transmitting member functions as a universal joint. For this reason, even when the axis of the drive shaft and the axis of the rotary valve are not concentrically aligned due to tolerance, the rotary valve does not generate caulking in the center shaft hole of the cylinder block. It rotates synchronously with the drive shaft.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments 1 and 2 embodying the present invention will be described below with reference to the drawings. (Embodiment 1) In FIGS. 1 and 2, reference numeral 1 denotes a cylinder block having a central shaft hole 1a penetrating in the axial direction and six bores 1A to 1F. 2 and a rear housing 4 is joined to the other end surface via a ring-shaped valve plate 3. In the crankcase 5 in the front housing 2,
A drive shaft 6 made of an iron-based metal is inserted into the front housing 2 and is inserted into a center shaft hole 1a of the cylinder block 1 and is rotatably supported. A rotor 7 is fixed on the drive shaft 6, and a long hole 8 a penetrates a distal end of a support arm 8 extending to the rear side of the rotor 7. A pin 8b is slidably fitted into the elongated hole 8a, and a swash plate 9 is slidably connected to the pin 8b.

A sleeve 10 is loosely fitted on the drive shaft 6 adjacent to the rear end of the rotor 7 and is always urged toward the rotor 7 by a coil spring 11 and protrudes from the left and right sides of the sleeve 10. A pivot 10a (only one is shown) is fitted into an engagement hole (not shown) of the swash plate 9, and the swash plate 9 is supported so as to be able to swing around the pivot 10a. A rocking plate 12 is supported on the rear side of the swash plate 9 via a thrust bearing or the like.
The rotation of the rocking plate 12 is restricted by a notch (not shown). In addition, six connecting rods 14 are moored at equal intervals on the outer edge of the swing plate 12, and each connecting rod 14 has a bore 1A to 1A.
It is moored with the piston 15 in 1F. Therefore,
The rotational movement of the drive shaft 4 is converted into forward and backward swing of the swing plate 12 by the intervention of the rotor 7 and the swash plate 9, and each piston 15 reciprocates in the bores 1 </ b> A to 1 </ b> F. The stroke of the piston 15 and the tilt angle of the rocking plate 12 are changed in accordance with the pressure difference from the suction pressure. The pressure in the crank chamber 5 is controlled by a control valve (not shown) provided in the rear housing 4 based on the cooling load.

The rear housing 4 is provided with a suction chamber 17 which is opened at the rear end face at the center and communicates with the central shaft hole 1a of the cylinder block 1. A discharge chamber 18 is provided outside the suction chamber 17. Are formed. Valve plate 3
Has a discharge port 3 communicating with the head of each of the bores 1A to 1F.
a, and a retainer 21 is interposed between the discharge port 3a and the discharge chamber 18 via a discharge valve 20.

As shown in FIG. 2, the cylinder block 1 has radially extending conductive paths 2A to 2F between the bores 1A to 1F and the central shaft hole 1a. And
As shown in FIG. 3, the end of the drive shaft 6 extending into the central shaft hole 1 a is interposed via a disc spring and a liner 23 as a torque transmitting member. A cylindrical rotary valve 22 made of an aluminum-based metal that slides with the cylinder is mounted.

In this liner 23, as shown in FIG.
An elongated first engagement opening 23b extending in the x-direction from the substantially disk-shaped substrate 23a is provided. Further, a sleeve 23d extends in the y direction orthogonal to the first engagement opening 23b in the substrate 23a of the liner 23.
A second engaging opening 23e that opens on both sides in the y-direction is provided through the second engaging opening 23e. The liner 23 is manufactured by extracting and bending a steel plate from the z direction in the drawing.

On the other hand, at the end of the drive shaft 6, an opposing flat surface having a width equal to the width in the y direction of a side wall 23c protruding from the first engagement opening 23b of the liner 23 toward the rotary valve 22 is provided. An engagement shaft portion 6a having a length shorter than the width in the x direction of the side wall 23c and having a substantially rectangular cross section is provided to protrude in the z direction. In addition, rotary valve 2
2 has a flange 22c protruding in the axial direction, and a notch 22d of the flange 22c is provided with a sleeve 23 of the liner 23.
The spring pin 22a which accommodates the first housing d and is slidable in the second engagement opening 23e is fixed. Further, in the center of the end portion of the rotary valve 22, a concave portion 2 in which the outer width of the side wall 23c of the liner 23 and the engaging shaft portion 6a of the drive shaft 6 can be sufficiently loosely fitted.
2b is recessed.

As shown in FIG. 1, the rotary valve 22 has an opening formed at a predetermined angle communicating with the inner surface, and the opening and the inner surface define a suction passage 25 communicating with the suction chamber 17. I have. The rear side of the rotary valve 22 is supported on the inner wall of the suction chamber 17 via a thrust bearing. The compressor configured as described above is disposed in a circuit as a vehicle air conditioning refrigeration apparatus and is used.

When the compressor is operated and the drive shaft 6 rotates, the swash plate 9 swings while rotating together with the drive shaft 6, and the swing plate 12 rotates in a state where the rotation of the swing plate 12 is regulated with respect to the swash plate 9. Only the oscillating motion is performed, so that the piston 15
Reciprocate in 1F. When the piston 15 starts moving from the top dead center toward the bottom dead center in the bores 1A to 1F, the bores 1A to 1F enter a suction stroke. Also, bore 1A
If the piston 15 starts moving from the bottom dead center toward the top dead center within 1F, the bores 1A-1F enter the compression / discharge stroke.

Here, as shown in FIG.
The torque in the direction is transmitted from the engagement shaft portion 6a of the drive shaft 6 to the liner 23 by the side wall 23c of the first engagement opening 23b,
The torque in the M direction of the liner 23 is transmitted to the rotary valve 22 from the second engagement opening 23e by the spring pin 22a. In this way, when the rotary valve 22 rotates in the direction shown by the arrow in FIG. 2 in synchronization with the drive shaft 6 via the liner 23, the bores 1A to 1F in the suction stroke cause the conduction passages 2A to 2F to move through the suction passages 2A to 2F. The refrigerant gas in the suction chamber 17 communicates with the passage 25 and is sucked into each of the bores 1A to 1F sequentially through the suction passage 25 and the conduction passages 2A to 2F.

Thereafter, if the rotation of the rotary valve 22 causes each of the bores 1A to 1F to be in the compression / discharge stroke, their conduction paths 2A to 2F do not communicate with the suction path 25, and It is closed. At this time, the pressure in the bores 1A to 1F during the compression stroke is still lower than the pressure in the discharge chamber 18, and the discharge valve 20 is closed. Also, the bores 1A to 1F in the discharge stroke do not communicate with the suction passage 25 in the conduction passages 2A to 2F, and are closed by the seal portion of the rotary valve 22. However, at this time, the pressure in the bores 1A to 1F in the discharge stroke becomes higher than the pressure in the discharge chamber 18, and the discharge valve 20 is opened.

In this way, the respective bores 1A to 1F sequentially repeat the suction, compression and discharge strokes via the rotary valve 22 which rotates in synchronization with the reciprocating movement of the piston 15. At this time, the bores 1A to 1F in the suction stroke are communicated with the suction chamber 17 through the conduction paths 2A to 2F and the suction passage 25, and the suction operation of the refrigerant gas is continued smoothly and stably. Is made very small. Therefore, in this compressor, sufficient volumetric efficiency can be maintained.

Further, in this compressor, as shown in FIG. 4, the engagement shaft 6a of the drive shaft 6 is movable along the side wall 23c of the first engagement opening 23b of the liner 23. The liner 23 is allowed to move in the x direction with respect to the drive shaft 6. Also, the second engagement opening 23 of the liner 23
Since the spring pin 22a of the rotary valve 22 is movable along e, the rotary valve 22 is allowed to move in the y direction with respect to the liner 23. Here, since the concave portion 22b of the rotary valve 22 sufficiently loosely fits the side wall 23c of the liner 23 and the engagement shaft portion 6a of the drive shaft 6, the movement of the drive shaft 6 and the liner 23 in the x direction and the liner 23 And the rotation valve 22 are not prevented from moving in the y direction. In addition, z of the rotary valve 22
The movement in the direction is possible within a range against the urging force of the disc spring. The x direction and the y direction are orthogonal to each other, and the rotation of the rotary valve 22 is not impaired. For this reason, even if there is a tolerance in the drive shaft 6, the rotary valve 22, the cylinder block 1, and the like,
The liner 23 functions as a universal joint and absorbs such a tolerance. For this reason, even if the axis of the drive shaft 6 and the axis of the rotary valve 22 are parallel, refracted, or separated from each other due to tolerance, the rotary valve 22 can be mounted on the central shaft hole 1 of the cylinder block 1.
a, and rotates in synchronism with the drive shaft 6 without fail. For this reason, the rotation valve 22 does not align the axis of the drive shaft 6 and the axis of the rotation valve 22 concentrically due to tolerance,
Even if the rotary valve 22 is bent or separated, the rotary valve 22 rotates in synchronism with the drive shaft 6 without forming caulking in the central shaft hole 1a of the cylinder block 1.

Accordingly, in this compressor, sufficient volumetric efficiency can be maintained, and both absorption of tolerance and synchronous rotation of the rotary valve 22 can be achieved. Further, in this compressor, the liner 23 can be manufactured relatively easily, so that the manufacturing cost can be reduced. Further, in this compressor, since the drive shaft 6 is made of an iron-based metal, the strength at the time of torque transmission is secured. Since the rotary valve 22 is made of an aluminum-based metal, the weight is reduced.
Is relatively lightweight, and the sum of the rotary valve 22 and the liner 23 does not increase so much, so that the weight of the compressor can be reliably reduced.

In this compressor, a disc spring may be provided on the rear housing 4 side. (Embodiment 2) This compressor employs a liner 24 and a rotary valve 26 shown in FIG. Another configuration is the first embodiment.
Therefore, the same components are denoted by the same reference numerals, and the description of the same configurations and operations will be omitted.

In the liner 24, similarly to the first embodiment, an engagement opening 24b extending in the x-direction from the substantially disk-shaped substrate portion 24a and aligned with the engagement shaft 6a is opened. A side wall 24c is formed around 24b. Also,
In the substrate portion 24a of the liner 24, a pressing surface 24d facing the rotation direction of the drive shaft 6 is bent so as to extend in the y direction orthogonal to the engagement opening 24b. The liner 24 is also manufactured by extracting and bending a steel plate from the z direction in the drawing.

On the other hand, the notch 22d on the rotation direction side of the flange 22c protruding from the end of the rotary valve 26 is
Is pressed against the pressing surface 24d. Also in this compressor, as shown in FIG.
The drive shaft 6 and the liner 24 are allowed to move in the x-direction because the engagement shaft portion 6a of the drive shaft 6 is movable along the side wall 24c. Also, the pressing surface 2 of the liner 24
Since the notch 22d of the rotary valve 26 is movable along 4d, the rotary valve 26 is allowed to move in the y direction with respect to the liner 24.

Therefore, also in this compressor, the same operation and effect as in the first embodiment can be obtained.

[0026]

As described in detail above, the reciprocating compressor of the present invention employs the configuration described in the claims, so that sufficient volumetric efficiency is maintained, and tolerance absorption and rotation are achieved. The synchronous rotation of the valve can be compatible.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a compressor according to a first embodiment.

FIG. 2 is a cross-sectional view of the compressor according to the first embodiment.

FIG. 3 is an exploded perspective view of a main part of the compressor according to the first embodiment.

FIG. 4 is a sectional view of a main part of the compressor according to the first embodiment.

FIG. 5 is an exploded perspective view of a main part of the compressor according to the second embodiment.

FIG. 6 is a sectional view of a main part of the compressor according to the second embodiment.

[Explanation of symbols]

1: Cylinder block 1a: Central shaft hole 1A
~ 1F ... Bore 3 ... Valve plate 4 ... Rear housing 6 ...
Drive shaft 5 ... Crank chamber 9 ... Swash plate 15
... Piston 17 ... Suction chamber 18 ... Discharge chamber 2A
２2F: conduction path 22, 26: rotary valve 23, 24: liner (torque transmitting member) 25: suction path x direction: one direction y direction: other direction

──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Ei Hirota 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation (58) Field surveyed (Int. Cl. ⁷ , DB name) F04B 27 / 08 F04B 39/10

Claims (1)

(57) [Claims] A cylinder block having a plurality of bores around an axis, a drive shaft fitted and supported in a shaft hole of the cylinder block, and a swash plate in a crank chamber cooperating with the drive shaft. And a housing having a suction chamber communicating with the shaft hole and a discharge chamber formed outside the suction chamber to close an end face of the cylinder block. In the reciprocating compressor, a conduction path is formed between each of the bores and the shaft hole, and a conduction path of each of the bores in a suction stroke is formed on the drive shaft via a torque transmission member. A rotary valve having a suction passage sequentially communicating with the suction chamber is coupled so as to be synchronously rotatable,
The drive shaft and the torque transmitting member are coupled while being allowed to move in one direction of the radial direction, and the torque transmitting member and the rotary valve are moved in the other direction intersecting the one direction in the radial direction. A reciprocating compressor characterized by being permitted and coupled.