JPS5847195A - Oil feeding structure for movable-vane type rotary compressor - Google Patents

Abstract

PURPOSE:To prevent generation of seizure and abnormal high-temperature on the surface of a rotor in high-speed revolution by forming oil feeding grooves in the direction of the tangential sealing part on the rear and the front side plates and allowing said grooves to communicate to a back-pressure oil feeding hole through a bearing. CONSTITUTION:The pressurized oil equivalent to the discharge pressure flows into the back- pressure oil feeding hole 12 on the rear side plate 5 on one side of a cam ring 3, and said pressurized oil flows into the thrust needle bearing 14 which supports a rotor 6 from the hole 12 through a passage 13, and a vane 8 is allowed to spring-out to the outer periphery of the rotor 6 by said pressurized oil, and further the oil is gushed onto the rear side slidable surface of the rotor 6 through the passage 16 communicated to the point immediately after the compression cycle from the gap formed with a radial needle bearing 7, and forced to divengently flow into the front side plate 4 from the hole 12 through a passage 17. As a cicumferential oil groove 19 and an oil groove 22 in tangential direction are formed on the plate on the outer periphery of the bearing 14, the pressurized oil which flows into the groove 19 is always gushed onto the both edge surfaces of the rotor 6 and in the direction of the tangential sealing part by a centrifugal force, and lubrication films are formed on the both edge surfaces of the rotor and in the vicinity of the tangential sealing part, and thus the rotor 6 is guarded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a movable vane type rotary compressor used in a carnier conditioner. The present invention relates to a movable vane type rotary compressor characterized in that it is disposed on a moving member.

In general, the bearing structure of a movable vane rotary compressor uses thrust needle bearings between both end faces of the rotor and the front and rear plates to avoid surface contact between the rotor and the front and rear plates. In order to position the rotor in the thrust direction, and to support the radial force resulting from the refrigerant compression action, the front and rear plates are mounted.

Equipped with a shear needle bearing.

One of the conventional problems with such movable vane rotary compressors is that they operate in the high-speed rotation region (compressor rotation speed of 600 rpm).
Orpm), the discharge temperature may rise abnormally (over 150'CC) due to overcompression heat, vane sliding friction heat, recompression heat due to internal leakage, etc.
This method causes thermal deformation in each sliding member and causes seizure and burnout on the outer periphery of the rotor and both end surfaces of the rotor, which has the disadvantage of significantly reducing durability.

SUMMARY OF THE INVENTION An object of the present invention has been made to eliminate the above-mentioned drawbacks of the conventional technology. It is an object of the present invention to provide a durable movable vane type rotary compressor, which is characterized in that seizing and burning out of the outer periphery of the rotor is avoided.

The above purpose is to replace part of the vane back pressure oil supply with differential pressure.
The oil flow is divided into the oil supply passages provided on the front and rear plates, and the oil supply passages are further filled with Freon) 1! +1 and the outer periphery of the bearing box arranged on the rear plate, and the oil supply hole or oil groove that communicates with the outer periphery of the bearing box is connected to the front and rear plate slides by the number of compression chambers (the number of tangential seals). This is achieved by placing it on the moving surface.

Hereinafter, one embodiment of the present invention will be described in more detail with reference to the accompanying drawings.

FIGS. 1 and 2 show the main body of a compressor equipped with an embodiment of the present invention, and the compressor includes a compressor cover 1 with an open end that surrounds the compressor cover, and a compressor cover 1 that surrounds the compressor cover. The main body A includes a cam ring 3 and a front side plate 4 fastened to both sides of the cam ring 3.
and the rear side plate 5, and these three members form a new cam ring chamber B.
Inside, the rotor 6 has a front side plate 4 and a rear side plate 5.
It is rotatably housed by a radial needle bearing 7 disposed in the radial needle bearing 7.

A vane 8 is slidably installed on the rotor 6, and the vane 8 divides the inside of the cam ring xf3 into a plurality of working chambers (in the example in FIG. 2, a 3 compression chamber 5 vane system).
, suction compression is performed by rotating the rotor 6 in the direction of the arrow.

To describe the flow and operation of the refrigerant in the compressor, after flowing into the low pressure chamber C inside the front cover 2 in the direction of the arrow from the suction port 9 formed in the front cover 2, the refrigerant flows through the front plate. Suction holes 10 provided (3 locations in Figure 2)
From there, it flows into the cam ring chamber B through the suction port D in the direction of the arrow. The refrigerant is supplied to a discharge port E provided in the rotor 6.
and when flowing through the oil separation device (not shown in FIG. 1) provided in the compressor cover l through the discharge valve 11,'
The oil is separated from the refrigerant, stored in the inner bottom of the compressor cover 1, and is supplied to the back of the vane and the bearing box, including the back pressure oil supply hole 12 arranged in the rear side plate 5. The lubricating oil is supplied by the differential pressure and returned to the inner bottom of the compressor cover 1 as lubricating oil. Furthermore, the passage configuration from the back pressure oil supply hole 12 to the inside of the bearing box and the outer periphery of the thrust needle bearing in the bearing box, according to an embodiment of the present invention, will be explained using FIGS. 1 and 3. explain. Pressure oil equivalent to the discharge pressure flows into the back pressure oil supply hole 12 arranged on the rear side plate 5, and a conduction path 13 is connected from the back pressure oil supply hole 12 to the bearing box arranged on the rear side plate 5. After the pressure oil flows into the outer periphery of the rear thrust needle bearing 14 in the bearing box as shown by the arrow, it reaches the rear part 15 of the vane and has the effect of causing the vane 8 to protrude toward the outer periphery of the rotor 6. A part of the pressure oil that has reached the box passes through the gap formed by the rear radial needle bearing 7 in the bearing box, and is led to the rear sliding surface of the U-Taro immediately after the compression stroke. Passage 1
6 as shown by the arrow, and due to the differential pressure, the rear 1 of the rotor 6
It is reflected onto the sliding surface. Also, a part of the pressure oil that has flowed into the front pressure oil supply hole 12 is communicated with the outer periphery of the front thrust needle bearing 14 in the bearing box disposed on the front side. and outside the cam ring
The oil is supplied to a conduction path 17 provided through it as shown by the arrow. Further, the vane backpressure oil passes through M between the vane slits, flows out to the front side sliding surface of the rotor 6, and flows through the gap in the bearing box provided on the front side plate 4 as shown by the arrow. A part of the pressure oil that has reached the shaft seal chamber F flows through a conduction path 18 provided in the front plate 4 that communicates with the front sliding surface of the rotor 6. As a result, the lubricating oil is injected with a differential pressure onto the front sliding surface of the rotor 6.Finally, the lubricating oil leaked between the rotor end face and the front side 4 and rear side plates 5 is released to the cam ring chamber B.

Next, FIG. 3, FIG. 4, FIG. 5, and FIG. Using 1. This will be explained more specifically.

The feature of the present invention is that the pressure oil flowing into the back pressure oil supply hole 12 shown in FIG.

Due to the passage structure, it reaches the outside and vicinity of the thrust needle bearings 14 in the bearing boxes disposed on the front side 4 and rear side plates 5, and is disposed on the plate sliding surface shown in FIGS. 4 and 5. Circumferential oil groove 19 or semicircular oil supply hole 2
1 through a conductive path 20 (FIG. 6).

That is, in FIG. 4, a circumferential oil groove 19 is provided on the rear plate 5 on the outer periphery of the rear thrust needle bearing 14, and the oil groove branching from the circumferential oil groove 19 is arranged in a circumferential manner. The injection direction in the oil groove follows the rotational direction (arrow direction) of the coater 6. A tangential oil groove 22 is provided in the tangential direction.
The end of the rotor external line indicated by i and the broken line
The terminal position of the upper oil groove 22 in the tangential direction is intersected with the fulcrum of the cam cylinder curve (tangential seal part a) at angular intervals corresponding to the number of compression chambers (tangential seal part a) (see Fig. 4). If it is a 3-compression chamber type, the oil supply grooves will be arranged at 120° intervals (Arrangement 1-B).

Therefore, with the above oil supply groove configuration, the circumferential upper reservoir located on the outer periphery of the rear side streak needle bearing 14: l'+19
The pressure oil that has flowed into the cylinder flows out toward the outer periphery of the cylinder 4 due to the force of the hydraulic fluid, while rotating in the rotational direction of the rotor 6 within the upper cylinder 4 in the tangential direction.
22, and is constantly scattered in the vicinity of the tangential/ru portion, so that a good lubricating film is always formed on the front side and rear sliding body of the rotor, and the oil film especially near the tangential seal portion is Increase the strength and reduce internal leakage from the discharge 11]1] to the intake side.

In addition, in FIG. 5, which is an example of a +g light, a semicircular oil supply hole 21 is located from the outer part of the rear thrust needle bearing 14 to the tangential seal portion on the sliding surface of the rear plate.
The conduction passage 20 shown in Fig. 6 is arranged on the rear plate, and the positions of the semicircular oil supply holes 21 are arranged at angular intervals corresponding to the number of compression chambers (the number of tangential seals) (3 in Fig. 5). If it is a compression chamber type, the oil supply holes are arranged at 120° intervals.

Therefore, with the oil supply hole configuration described above, the pressure oil that has reached the external part of the rear thrust needle bearing 14 flows into the conduction path 20 and is constantly injected from the oil supply hole 21 to the vicinity of the tangential seal portion by centrifugal force. Similar to the example (Figure 4),
In particular, the strength of the oil film near the tangential seal portion is increased to reduce internal leakage from the discharge side to the intake side.

As described above, according to the present invention, oil supply grooves or oil supply holes are provided in the direction of the tangential seals on the sliding surfaces of the front and rear plates, and pressure oil is constantly supplied to both end surfaces of the rotor and the tangential seals. Since the oil is sprayed in the direction of the rotor, a good lubricating film is always formed on both end faces of the rotor and near the tangential seal, which has the effect of preventing abnormal overheating of the rotor surface, even in high-speed rotation areas. The increase in discharge temperature is suppressed, and it is possible to avoid seizure and burnout occurring on the sliding member surface, thereby providing a durable movable vane rotary compressor.

[Brief explanation of the drawing]

Figure 1 is a sectional view of the movable vane rotary compressor main body, Figure 2 is a sectional view taken along I-4 in Figure 1, Figure 3 is an enlarged explanatory view of the oil supply passage, and Figures 4 and 5 are the main body of the rotary compressor. An explanatory diagram for explaining the invention in detail, FIG. 6 is a sectional view taken along line X-X in FIG. 5. 3... Cam ring, 6... Rotor, 7... Radial needle bearing, 12... Vane back pressure oil supply hole, 14
...Thrust needle bearing, 19...Circumferential oil groove,
21... Half figure S

Claims (1)

[Scope of Claims] (1) A cam ring chamber is formed by a cam ring and front and rear plates fastened to both sides of the cam ring, and a rotor is rotatably suspended horizontally in the cam ring chamber; In a movable vane type rotary compressor in which vanes are arranged between vane slits 3 so as to be slidable in the radial direction, a bearing box is provided in a convex space formed in the front side and rear side plates, and a bearing box is provided in the convex space formed in the front side and rear side plates. A radial needle bearing and a thrust needle bearing are arranged, and the back pressure oil supply hole arranged in the rear side plate is communicated with the vicinity of the outer periphery of the thrust needle bearing in the rear side bearing box. A refueling structure for a movable vane rotary compressor, characterized in that a refueling passage communicating with the vicinity of the outer periphery of a thrust needle bearing in a front bearing box is provided in a cam ring and a front plate. 2. Claim 1: 1. A circumferential oil groove is provided on the sliding surface of the rear plate near the outer periphery of the rear thrust needle bearing, and the oil groove is branched from the circumferential oil groove. is provided in the tangential direction of the oil groove on the circumference according to the rotational direction of the rotor, and the end of the upper oil groove in the tangential direction is located toward the tangential seal portion of the cam ring, while the oil supply end position is located in the direction of the number of compression chambers (the tangential direction). A refueling structure for a movable vane rotary compressor, characterized in that the oil supply structure is arranged on the rear sliding surface at angular intervals corresponding to the number of seals (number of seals). 3. In claim 1, there is provided a conduction path that connects from the outer circumference of the rear thrust needle bearing to the semicircular oil supply hole located in the direction of the cam ring tangential seal on the sliding surface of the rear plate. A movable airfoil shape characterized in that the semicircular oil supply holes are arranged on the sliding surface of the rear plate at angular intervals corresponding to the number of compression chambers (the number of tangential seals). Oil supply structure for a rotary compressor. 4. A patented airfoil according to claims 2 and 3, characterized in that the oil supply structure is also provided on the sliding surface of the front plate at the same time or in combination. Rotary compressor oil supply structure.