JPS6244107B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an oil supply mechanism that does not use an oil pump in a rotary swash plate compressor for compressing refrigerant.

A rotating swash plate compressor is configured so that a piston reciprocates within a cylinder bore as the swash plate, which is fixedly mounted at an angle to the drive shaft, rotates, and performs compression in cooperation with the suction and discharge valves. has been done. The drive shaft is rotatably supported along with the swash plate by a thrust bearing and a radial bearing, and a mechanical seal is provided on the protruding side of the drive shaft, and an oil supply is provided to supply lubricating oil to each of these parts. A mechanism is provided.

Conventionally, this lubrication mechanism has been equipped with an oil pump installed at the end of the drive shaft to forcibly suck up lubricating oil from the oil reservoir below the swash plate chamber as the drive shaft rotates, and supply the lubricating oil to each part. Pump type has been adopted. However, since oil pumps are relatively expensive and require power to drive, so-called differential pressure type oil supply mechanisms have recently been adopted.

The differential pressure oil supply mechanism uses the rotation of the swash plate to splash the lubricating oil stored in the oil reservoir below the swash plate chamber into oil mist, and transfers the refrigerant in the swash plate chamber mixed with this oil mist to the swash plate chamber. It attempts to supply various parts by utilizing the pressure difference between the low pressure chamber and the low pressure chamber. However, this pressure difference between the swash plate chamber and the low pressure chamber is caused by blow-by gas that enters the swash plate chamber through the gap between the piston and cylinder bore during the discharge process of the piston, so the amount of this blow-by gas is insufficient. When this is not the case, that is, at the initial stage of driving or during low-speed operation, a sufficient pressure difference cannot be obtained, resulting in a lack of lubricating oil. For the thrust bearing, a lubrication hole is formed that communicates the swash plate chamber with the shaft insertion hole, and a lubrication passage is formed from the swash plate chamber through this lubrication hole to the thrust bearing. A refrigerant containing lubricating oil can be supplied to the swash plate chamber by the centrifugal force generated by the rotation of the plate. Therefore, even with these improvements, the problem that still remains is the lack of lubricating oil in the radial bearings. It has been difficult to stably supply sufficient lubricating oil to the

Therefore, in this invention, in order to solve the above problems, the radial bearing is reached from the swash plate chamber through the oil supply hole that communicates the swash plate chamber and the shaft insertion hole, and further between the shaft insertion hole and the valve plate. A refueling passage is provided that opens into the suction hole through a suction hole communicating with the suction hole, and an edging effect is produced by a jet flow of refrigerant sucked from the low pressure chamber into the compression chamber through the suction hole of the valve plate. The present invention aims to provide a rotary swash plate compressor that can secure stable oil supply by powerfully supplying refrigerant containing lubricating oil in the swash plate chamber to the radial bearings using the suction force generated by the swash plate chamber.

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

1 and 2, an embodiment of the present invention is shown, in which a pair of cylinder blocks 1a and 1b are shown.
front and rear cylinder heads 3a, 3b are fixedly sealed with valve plates 2a, 2b in between. cylinder block 1
A, 1b and the valve plates 2a, 2b have a shaft insertion hole and center holes 4a, 4b formed in their centers, and a drive shaft 5 is inserted into the shaft insertion hole 4 and center holes 4a, 4b with a gap therebetween. ing. Although not shown, the drive shaft 5 is not inserted through the center hole 4b on the rear side;
The diameter may be smaller than that of the shaft insertion hole 4. This drive shaft 5
The front side of the cylinder protrudes so that rotation of the compressor can be transmitted thereto, and a mechanical seal 6 is provided between the cylinder head and the front cylinder head 3a for sealing.

The swash plate 7 is fixed to the drive shaft 5 and arranged in a swash plate chamber 8 formed in the cylinder blocks 1a and 1b. The swash plate 7 and the drive shaft 5 are connected to the swash plate 7.
It is rotatably supported with respect to the silling blocks 1a and 1b by thrust bearings 9a and 9b provided on both sides of the boss portion 7a and radial bearings 10a and 10b provided near both ends of the shaft insertion hole 4. There is.

The double-acting piston 11 has a central portion hollowed out so as to straddle the periphery of the swash plate 7, and a ball 12
The swash plate 7 is sandwiched between the cylinder blocks 1a and 12b and the shoes 13a and 13b, and is fitted into cylinder bores 14 formed in the cylinder blocks 1a and 1b.
Therefore, when the drive shaft 5 is rotated, the swash plate 7 swings and rotates, and the piston 11 reciprocates within the cylinder bore 14 accordingly.

A partition wall 15a is formed between the front cylinder head 3a and the valve plate 2a to form a high pressure chamber 1.
6a and a low pressure chamber 17a, and this low pressure chamber 17
The mechanical seal 6 is arranged at a. On the other hand, like the front cylinder head 3a, the rear cylinder head 3b is partitioned by a partition wall 15b so that in addition to a high pressure chamber 16b and a low pressure chamber 17b, a chamber 18 separated from the low pressure chamber 17b communicates with the shaft insertion hole 4. It is formed. The high pressure chambers 16a, 16a and 16a of the front and rear cylinders 3a, 3b, respectively,
16b and the low pressure chambers 17a, 17b are communicated with each other via a refrigerant passage (not shown) formed in the cylinder blocks 1a, 1b, and are connected to a suction pipe 28 and a discharge pipe (not shown) provided in the rear cylinder head 3b. Refrigerant is sucked in and discharged from the

A high pressure chamber 16 is provided in the valve plates 2a and 2b.
a, 16b and the compression chamber 19 in the cylinder bore 14
a suction hole (not shown) that communicates with
Suction holes 20a, 20b are formed to communicate the low pressure chambers 17a, 17b and the compression chambers 19a, 19b. The discharge hole is connected to the valve plate 2.
The suction holes 20a, 20b are closed by discharge valves (not shown) provided in the valve plates 2a, 2b and the cylinder blocks 1a, 1b.
It is closed by a suction valve 23 integrally formed with gaskets 22a and 22b sandwiched between the two. The diameter of the inlet side of the suction holes 20a, 20b is narrowed by gaskets 21a, 21b on the cylinder head 3a, 3b side. Therefore, when the piston 11 reciprocates within the cylinder bore 14, the volume of the compression chambers 19a and 19b changes, and a compression action is performed in cooperation with the suction valve 23 and the discharge valve.
During the suction stroke, the suction refrigerant from the low pressure chambers 17a, 17b passes rapidly through the suction holes 20a, 20b.

An oil reservoir 24 is formed below the swash plate chamber 8 and extends to the front and rear cylinder heads 3a, 3b, and the peripheral edge of the swash plate 7 is immersed in the lubricating oil stored in the oil reservoir 24. Therefore, when the swash plate 7 is rotated, the lubricating oil in the oil reservoir is thrown up and turned into oil mist.

The oil supply holes 25a, 25b are for thrust bearings 9a, 9b and radial bearings 10a, 10.
b, and is formed in the cylinder blocks 1a, 1b, communicating the swash plate chamber 8 and the shaft insertion hole 4.

The suction holes 26a and 26b are connected to the valve plate 2.
The center holes 4a, 4b formed in the shaft insertion holes 4a, 2b communicate with the suction holes 20a, 20b.

Therefore, as shown in FIG. 2, the swash plate chamber 8 reaches the radial bearings 10a, 10b through the oil supply holes 25a, 25b, the gap between the drive shaft 5 and the cylinder blocks 1a, 1b, and then the center hole 4.
An oil supply passage A is formed which opens from a, 4b to the suction holes 20a, 20b through the suction holes 26a, 26b. Further, from the swash plate chamber 8, the oil supply holes 25a, 25b, the drive shaft 5 and the cylinder block 1 are connected.
Through the gap between a and 1b, the thrust bearing 9
A refueling passage B is formed that extends to a and 9b.

In the above configuration, when the drive shaft 5 is rotated,
The swash plate 7 swings and rotates, the piston 11 reciprocates within the cylinder bore 14, and a compression action is performed in cooperation with the suction valve 23 and the discharge valve (not shown). Since several percent of lubricating oil is mixed in the suction refrigerant, when this enters the front side low pressure chamber 17a, it lubricates the mechanical seal 6 and the compression chamber 1.
9a and 19b to lubricate the piston 11 through the gap between the piston 11 and the cylinder bore 14. The lubricating oil in the refrigerant that has entered the swash plate chamber 8 through the gap between the piston 11 and the cylinder bore 14 is separated from the refrigerant and temporarily stored in the oil reservoir 24 because the swash plate chamber 8 has a large volume. Along with the above effects,
As the swash plate 7 rotates, the lubricating oil stored in the oil reservoir 24 is thrown up and becomes oil mist.
This oil mist is transferred to the radial bearing 10 through the oil supply passages A and B together with the refrigerant in the swash plate chamber 8.
a, 10b and thrust bearings 9a, 9b to lubricate them.

That is, in the oil supply passage A, since one end of the passage A opens to the suction holes 20a and 20b, an edging effect is produced by the jet flow of refrigerant generated in the suction holes 20a and 20b during the suction stroke.
As a result, a suction force is generated from the swash plate chamber 8 to the suction holes 20a, 20b, and the radial bearings 10a, 1
0b is refueled. On the other hand, in the oil supply passage B, centrifugal force is generated by the rotation of the swash plate 7, which generates a suction force in the direction of the thrust bearings 9a, 9b, and the thrust bearings 9a, 9b are lubricated, and the swash plate chamber 8 is refilled. be returned. Such actions are performed continuously to automatically supply sufficient lubricating oil to each part.

It should be noted that in addition to the above embodiments, the following embodiments are also applicable to this invention.

First, regarding the suction holes 26a and 26b, in the above embodiment, the valve plate 2
It is formed by drilling holes a and 2b, but as shown in Figures 3 and 4.
As shown in the figure, it may be configured by a groove 27 having a semicircular cross section formed in the valve plate 2a and a gasket 21a, whereby the suction hole 26a,
26b can be easily formed.

Second, the suction holes 2 of the valve plates 2a, 2b
0a and 20b, in the above embodiment, the diameter is narrowed by the gasket 21a, but as shown in FIG. 26a may be opened, thereby further increasing the speed of suction refrigerant.

Thirdly, the shaft insertion hole 4 and the low pressure chamber 1 on the rear side
7b, in the above embodiment, it is done by the partition wall 15b of the rear cylinder head 3b, but as shown in FIG. 6, it is done by the gasket 21b on the side of the rear cylinder head 3b. Of course, it is also a good thing. In addition, a bulkhead similar to that on the rear side is provided on the front cylinder head 3a.
A mechanical seal chamber separated from 7a may be provided.

As described above, according to the present invention, in a rotary swash plate compressor that does not use an oil pump, at least the oil supply passage that opens from the swash plate chamber through the radial bearing to the suction hole of the valve plate is provided, so that the suction refrigerant Utilizing the edging effect caused by the jet flow, it is now possible to forcibly guide the refrigerant containing oil mist in the swash plate chamber to the radial bearings, making it possible to supply oil to each part in a well-balanced and stable manner. can improve reliability.

[Brief explanation of the drawing]

Fig. 1 is a sectional view showing a rotary swash plate compressor which is an embodiment of the present invention, Fig. 2 is an enlarged sectional view of the main part of the same as above, and Figs. 3 and 4 are for suction in other embodiments. 3 is a sectional view taken in the vertical direction, FIG. 4 is a sectional view taken in the horizontal direction, and FIG. 5 is a sectional view showing the vicinity of the suction hole in another embodiment, FIG. 6 is a sectional view showing the vicinity of the rear radial bearing in still another embodiment. 1a, 1b... cylinder block, 2a, 2b
... Valve plate, 4 ... Shaft insertion hole, 5 ... Drive shaft, 7 ... Swash plate, 8 ... Swash plate chamber, 24 ... Oil reservoir, 25a, 25b ... Oil supply hole, 26a,
26b... Suction hole, A... Oil supply passage.

Claims (1)

[Claims] 1. A shaft insertion hole 4 is formed in the cylinder blocks 1a, 1b, and center holes 4a, 4b are formed in the valve plates 2a, 2b provided on both sides of the cylinder blocks 1a, 1b. Insertion hole and center hole 4a of at least front valve plate 2a
In a rotary swash plate type compressor, a swash plate 7 is fixed to a drive shaft 5 inserted into the cylinder block 1a, 1b, and the swash plate 7 is disposed in a swash plate chamber 8 defined in the cylinder blocks 1a, 1b. The oil supply holes 25a and 25b that communicate the plate chamber 8 and the shaft insertion hole 4 are connected to the cylinder block 1.
a, 1b, and the center holes 4a, 4
a suction hole 26 that communicates between the suction holes 20a and 20b formed in the valve plates 2a and 2b;
a, 26b are provided, and the oil supply holes 25a, 25b are provided from the swash plate chamber 8, the radial bearings 10a, 10b that rotatably support the drive shaft, the center hole 4a,
4b, and the suction holes 20a, 2 of the valve plates 2a, 2b through the suction holes 26a, 26b.
A rotary swash plate compressor characterized by having an oil supply passage that opens at 0b. 2 Suction holes 20a of valve plates 2a, 2b,
2. The rotary swash plate compressor according to claim 1, wherein the suction holes 20a and 20b are constricted near the center thereof. 3. The rotary swash plate compressor according to claims 1 and 2, wherein the suction holes 26a and 26b are formed by boring the valve plates 2a and 2b. 4. The suction holes 26a, 26b are constituted by grooves 27 formed in the valve plates 2a, 2b and gaskets 21a, 21b on the cylinder head side. The rotary swash plate compressor described in .