JPH02215986A - Rotary compressor - Google Patents

Abstract

PURPOSE:To lessen a sliding loss as well as to making improvements in efficiency by setting up each roller bearing in the vicinity of an inner circumferential surface of a cylinder at the low pressure chamber side and also that at the side of an outer circumferential surface of the cylinder at the high pressure chamber side, respectively, at the wall of a vane groove part. CONSTITUTION:With compressive action, reaction forces F4, F5 act at a contact point between a vane 6 and a vane groove part 19a of a cylinder 19. Since a roller 21a in a roller bearing 22 rotates with reciprocating slide motion of the vane 6, a friction factor is lowered as compared with each slip sliding motion of metals themselves. Consequently, frictional force being produced in the vane groove part 19a so far caused for a sliding loss is reducible, so that such a compressor that is less in the sliding loss and excellent in efficiency can be thus secured.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a rotary compressor, and particularly to a rotary compressor intended to reduce sliding loss.

Conventional technology The conventional configuration will be explained using FIGS. 3 and 4.

1 is the sealed casing, 2 is the electric motor part, and shaft 3
via cylinder 4. Roller 6, vane 6, main bearing 7.
It is connected to a mechanical part main body 9 constituted by a sub-bearing 8. The shaft 3 is a main shaft 3a.

It consists of a subshaft 3b and an eccentric portion 3c. Further, 1o is an oil supply mechanism. Further, the vane 6 is housed in a vane groove 4a of the cylinder 4 so as to be able to slide back and forth.

Reference numeral 11 denotes a compression chamber formed within the cylinder 4, which is partitioned into a low pressure chamber 11a and a high pressure chamber 11b by a roller 6 and a vane 6 that is always in contact with the roller 5 by a spring 12.

13 is a suction pipe, and 14 is a discharge pipe.The suction pipe 13 directly communicates with the suction hole 16 of the cylinder 4 via the sub-bearing 8, and the discharge pipe 14 is open into the sealed casing 1. In addition, there are 16 discharge holes, and the compression chamber 11 is connected through the discharge valve 17.
The inside of the sealed casing 1 is communicated with the inside of the sealed casing 1. 18 is lubricating oil provided at the bottom of the sealed casing.

The operation of the compressor configured as above will be described below with respect to the flow of refrigerant gas.

The low-temperature, low-pressure refrigerant gas is passed through the suction pipe 13. It is guided through the suction hole 16 and reaches the compression chamber 11 inside the cylinder 4. The refrigerant gas that has reached the compression chamber is gradually compressed by the rotational movement of the shaft 3 as the motor section 2 rotates, and is continuously sent from the suction hole 14 to the discharge hole 16.

The compressed refrigerant gas is discharged through the discharge hole 16. It is discharged through a discharge valve 17. The discharged high-temperature, high-pressure refrigerant gas fills the inside of the sealed casing 1 and is guided to the outside via the discharge pipe 13.

In this compression action, the following load acts on the vane 6. First, a load F1 due to the differential pressure between the high pressure chamber 11b and the low pressure chamber 11a acts as a side load, and in the sliding direction of the vane 6, the internal pressure of the panel and sealed casing 1 and the low pressure chamber 1
A load F2 is applied due to the pressure difference between the pressure inside the high pressure chamber 1a and the high pressure chamber 11b.

As a result, the vane 6 receives a reaction force F3 from the roller 5, and also receives a reaction force F4''5 at the contact point between the vane 6 and the vane groove 4a.Here, the reaction forces F4 and F6 are:
This is a load generated by the resultant force of the load F1 and the component force F3a of the reaction force F3 in a direction perpendicular to the sliding direction of the vane 6.

Therefore, with the reciprocating sliding movement of the vane 6, the load F4
．． At the point of action of F6, there is a frictional force F6. F7 works.

As a result, the load F2. F
Component force F3b in the sliding direction of No. 3 - frictional force F6°F7 is balanced.

Problems to be Solved by the Invention However, in the above configuration, since the sliding contact between the vane and the vane groove of the cylinder is metal-to-metal sliding, the coefficient of friction is large and the frictional force F6. F7
As a result, there was a problem in that the sliding loss in the vane groove was large.

The present invention solves the above problems, and aims to provide a rotary compressor with high compression efficiency by reducing sliding loss.

Means for Solving the Problems In order to solve the above problems, the rotary compressor of the present invention provides a rotary compressor that has a wall surface of the vane groove of the cylinder, near the inner circumferential surface of the cylinder on the suction chamber side, and on the outer circumferential surface of the cylinder on the compression chamber side. A roller bearing was placed near the side.

Effect: With the above-described configuration, the present invention can reduce the coefficient of friction between the vane and the vane groove by the rolling motion of the rollers during the reciprocating sliding movement of the vane, and as a result, the sliding movement accompanying the reciprocating movement of the vane can be reduced. Since dynamic loss can be reduced, a highly efficient compressor can be provided.

EXAMPLE An example of the present invention will be described below with reference to FIGS. 1 and 2. In order to avoid duplication of explanation, the same parts as in the conventional example are given the same reference numerals and the explanation will be omitted.

19 is a cylinder, which has a vane groove 19a as in the conventional case.
The compression chamber 2o is partitioned into a low pressure chamber 20a and a high pressure chamber 20b by the roller piston 6 and the bezel 76.

Further, on the wall surface of the vane groove portion 19a, rollers 21&
, a shaft 21b, and a holder 21c.A roller bearing 22 is arranged.

The operation of the compressor configured as above will be explained below.

As in the conventional case, as the shaft 3 rotates, the refrigerant gas flows through the suction pipe 13 into the compression chamber 2Q, is compressed and discharged through the discharge hole 1e into the sealed casing 1, and then through the discharge pipe 14. led to the outside.

Due to this compression action, a reaction force F4 is generated at the contact point between the vane 76 and the vane groove 19a of the cylinder 19, as in the conventional case.
．． F6 works.

However, unlike the conventional case, since the rollers 21a in the roller bearing 22 rotate with the reciprocating sliding movement of the vane 6, the coefficient of friction is lower than that of sliding between metals, and the frictional force F8. F
9 is the conventional friction force F6. It is smaller than F7.

Therefore, the base groove 1, which was the cause of sliding loss,
9 & can be reduced, and as a result, an efficient compressor with less sliding loss can be provided.

Effects of the Invention As described above, the present invention comprises a cylinder, a main bearing and a sub-bearing fixed to both end surfaces of the cylinder, a roller rotating inside the cylinder, an electric motor section that rotates the roller, and an arc-shaped tip. It has a vane that partitions the inside of the cylinder into a low-pressure chamber and a high-pressure chamber by abutting the roller and reciprocating in a vane groove provided in the cylinder according to the rotation of the shaft. By arranging roller bearings near the inner circumferential surface and near the outer circumferential surface of the cylinder on the high pressure chamber side, an efficient compressor with less sliding loss can be realized.

[Brief explanation of the drawing]

FIG. 1 is an enlarged view of the main body of the mechanical part showing one embodiment of the present invention;
FIG. 2 is a side view of a roller bearing, FIG. 3 is a vertical cross-sectional view of a conventional compressor, and FIG. 4 is an enlarged view of the main body of the machine section taken along the line ■-■' in FIG. 3...Shaft, 6...Roller, 6.
Old...Vane, 7...Main bearing, 8.Old...Sub bearing, 19...Own...Cylinder, 19a...Vane groove, 20a...Low pressure room, 2 ob...
...High pressure chamber, 22... Roller bearing. Name of agent: Patent attorney Shigetaka Awano and 1 other person 3c
・-Shaft 1% π part 5---a-La piston 6-Hen 19--Syringe 19a--Vane groove 21G---Co 21b-m-Shaft port 1 Figure

Claims (1)

[Claims] A cylinder, a main bearing and a sub-bearing fixed to both end faces of the cylinder, a roller that rotates within the cylinder, an electric motor unit that rotates the roller, and an arcuate tip that abuts the roller. a vane that partitions the inside of the cylinder into a low pressure chamber and a high pressure chamber by reciprocating a vane groove provided in the cylinder according to the rotation of the shaft, and a wall surface of the vane groove on the low pressure chamber side A rotary compressor in which roller bearings are arranged near an inner circumferential surface of the cylinder and near an outer circumferential surface of the cylinder on the high pressure chamber side.