JPS61164095A - Rotary compressor - Google Patents

Abstract

PURPOSE:To make sufficient cooling for lubricating oil performable, by installing at least a part of a lubricating oil passage ranging from an oil sump to a lubricating object in a casing wall adjacent to an empty chamber existing in a suction stroke. CONSTITUTION:At a position being a bottom part of a casing 1 of a rotary compressor and being offset so as to be approximated to the side of a suction chamber (a), there are provided with three lubricating oil passages 43 as being paralleled with each other along the axial direction. At this part, these lubricat ing oil passages are exposed to low temperature directly, cooling lubricating oil inside the passage. Since these lubricating oil passages 43 are interconnected to a shaft seal 16 and a bearing 7 via an interconnecting passage 45 while to a vane groove bottom part via an interconnecting passage 47, respectively so that these sliding members are efficiently lubricated by the low temperature lubricating oil.

Description

DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to a rotary compressor, and more particularly to a rotary compressor having a suitable cooling structure for lubricating oil.

<Prior Art> In rotary compressors such as vane type compressors, lubricating oil may be circulated to lubricate rotor bearings, supply back pressure to vane members, etc. Conventionally, lubricating oil is supplied to, for example, a bearing using the discharge pressure of a compressor, the lubricating oil that lubricates the bearing is sent to a high pressure chamber together with the discharged gas, and the lubricating oil is separated from the discharged gas in the high pressure chamber. A lubrication structure in which the fI lubrication is reused for fI lubrication is known. This type of rim structure has the advantage of not requiring a separate pump for lubricating oil supply. However, the lubricating oil becomes high in temperature due to frictional heat in the bearing or heat generated due to gas compression, so it is necessary to cool the lubricating oil.

Conventional rotary compressors are cooled simply by natural heat radiation from passages or pipes that supply lubricating oil, but there is a risk that a sufficient cooling effect may not always be obtained. Therefore, it is conceivable to separately provide a cooling device such as an oil cooler, but this has the disadvantage of increasing manufacturing costs and requiring a large space.

<Problems to be Solved by the Invention> In view of these drawbacks of the prior art, the main object of the present invention is to provide a rotary compressor that can suitably cool lubricating oil with a simple cooling structure. There is a particular thing.

Means for Solving the Problems According to the present invention, such an objective is to provide a rotary compressor in which lubricating oil is separated from discharged gas, collected in an oil sump, and reused. By providing a rotary compressor, at least a part of the lubricating oil passage from the oil reservoir to the object to be lubricated is provided in a casing wall adjacent to a cavity in the suction stroke. achieved. Especially cold l
It is preferable that the lubricating oil path for lubricating oil is made up of a plurality of parallel passages.

Effect> As described above, by providing the cooling oil passage near the empty space in the suction stroke, the lubricating oil can be suitably cooled. In particular, if such a cooling lubricating oil passage is formed by a plurality of parallel passages, a large heat transfer area can be obtained and the cooling effect can be further improved.

<Example> FIGS. 1 and 2 show a vane type rotary compressor based on the present invention. This rotary compressor includes a cylindrical casing 1, a front plate 2 attached to its front end,
Rear plate 3 attached to the rear end of the casing 1
and a rear casing 4 attached to the further rear end of the rear plate, and mounting holes ia and 4a for mounting bolts are provided in the casing 1 and the rear casing 4, respectively. An 0-tar 5 is rotatably and eccentrically received inside the casing 1. That is, rotor 5
The rotor shaft 6 of the front plate 2 and the rear plate 3
They are rotatably supported by roller bearings 7.8 provided therein.

A flange 9 is screwed onto the front end of the rotor shaft 6, and an annular clutch member 11 is attached to the outer periphery of the flange via a leaf spring member 10. On the other hand, a pulley 13 is rotatably attached to the outer circumference of the front plate 2 via a ball bearing 12, and the front surface of the pulley faces the clutch member 11 with a small gap therebetween.

An annular recess 13a is provided in the rear surface of the pool 913 over the entire circumference □, and the electromagnet 14 is fixed to the front plate 2 so as to be located within the recess.

The electromagnet 14 is selectively magnetized by the current supplied from the leads 1111 and 4a, and the clutch member 11 is selectively engaged with the front surface of the pulley 13, so that the pulley 13 and the rotor shaft 6 □ constitutes a clutch device that connects and disconnects power transmission between and.

7 A mechanical seal structure is provided on the outer periphery of the rotor shaft 6 between the flange 9 and the bearing 7, and the bearing 7 is connected to I11.
Prevents floating lubricating oil from leaking to the outside.

It consists of a fixing member 15 fixed to the side of the mechanical seal rate, and a zero rotation part 16 that rotates integrally with the rotor shaft 6 and is biased by a boiling spring 17 and slides into liquid-tight contact with the fixed part 15. ing.

As clearly shown in No. nil, vane grooves 18 consisting of three axial grooves are cut at equal intervals in the circumferential direction on the outer periphery of the rotor 5. A member 19 is fitted. These vane members 19 divide the inside of the casing 1 into a suction chamber a', a compression chamber and a discharge chamber C, and as the volumes of these chambers increase and decrease as the rotor 5 rotates, working fluid such as refrigerant is pumped. It's pressurized.

The fluid to be compressed is introduced from the suction port 20, passes through the filter 21 and the suction path 22, and is introduced into the suction chamber a from the recess 23 formed in the inner peripheral surface of the housing 1. The fluid is further pressurized and pressurized in the compression chamber, and is discharged from the recess 24 formed in the inner circumferential surface of the housing 1 to the discharge passage 25 via the discharge chamber C. A reed valve 27 is provided between the discharge passage 25 and the discharge chamber 29, and its maximum opening is regulated by a one-piece retainer 26 screwed with a bolt 28.

The pressurized fluid discharged toward the discharge chamber 29 flows through the discharge passage 30
The lubricating oil is introduced into the high pressure chamber 31 defined in the rear casing 4, and the lubricating oil mixed therein is separated by an oil separator (not shown), and then passed through the discharge passage 32 to the discharge port 3.
It will be discharged from 3. The lubricating oil separated by the oil separator is collected in an oil sump 34 at the bottom of the high pressure chamber 31.

Next, the m-slide system of this embodiment will be explained.

An annular depression 36 is formed in the lower part of the rear surface of the rear plate 3, which is located below the lubricating oil level 35 when the oil reservoir 34 is stopped, and an annular protrusion 38 is defined in the center thereof. . An oil return passage 39 is provided at the center of the annular protrusion 38.
has been defined.

A valve retainer 37 is fitted into the opening of the annular recess 36 facing the oil reservoir 34, and a filter 40 is attached inside the valve retainer.
is held in a biased state toward the rear casing by a compression coil spring 42. A notch 41a is provided on the outer periphery of the valve body 41, and the oil reservoir 34 and the annular recess 36 are always communicated with each other regardless of whether the valve body 41 is opened or opened.

In this embodiment, three lubricating oil passages 43 are provided in parallel to each other along the axial direction at positions offset from each other in the bottom of the casing 1 and close to the suction chamber a. these! vI oil passing passages 43 - are gathered at the front and rear ends of the thing 1 so as to communicate with each other through arcuate grooves 43b and 43a. The groove 43a communicates with the annular recess 36, and the other groove 43b communicates with the fixed part 1 of the mechanical seal through an oil jet 44 and a lubricating oil passage 45.
5 and the rotating portion 16 and is supplied to the sliding contact portion of the mechanical seal to lubricate and cool the sealing surface between the rotor shaft 6 and the rotor shaft 6.

Furthermore, the vane groove 18 that receives the vane member 19 passes through the lubricating oil passage 47 and the arcuate groove 5a recessed in the front end surface of the rotor.
This applies a back pressure to each vane member 19 that urges the vane 19 in the projecting direction. Furthermore, lubricating oil is supplied to the rear end of the rotor shaft 6 from a lubricating oil passage 48 provided in the rear end plate 3 via a vane groove 18 and an arcuate groove 5b provided on the back surface of the rotor 5 similar to that described above. The oil is supplied to the bearing 8 to lubricate it.

The lubricating oil that lubricates and cools these parts is finally discharged through the gap between the vane member 19 and the vane groove 18 or the gap between the sliding surfaces at the front and rear ends of the rotor 5 into the suction chamber a, which has a particularly low pressure, and is then pumped. It mixes with the pressurized gas and is discharged together with the discharged gas into the high pressure chamber 31, and is returned to the oil reservoir 35 by the oil separator as described above.

An oil return passage 39 provided at the center of the annular protrusion 38 opens at the bottom of the compression chamber, and the open end of the oil return passage 39 on the high pressure chamber side, that is, the rear end of the annular protrusion 38, is slightly opened. It faces the valve body 41 with a gap therebetween. This is because lubricating oil accumulates in the compression chamber when the rotary compressor stops operating, and when the rotary compressor is started again, there may be a lack of lubricating oil in various parts, or the compressor may become incompressible. This is to avoid damage to the vane members etc. when trying to compress the lubricating oil.

That is, when the compressor is in operation, the pressure in the high pressure chamber 31 is higher than the internal pressure of the compression chamber, so the valve body 41 resists the spring force of the compression coil spring 32 and presses against the open end of the annular protrusion 38. Although the oil return passage 39 is closed by pressure contact, when the operation of the rotary compressor is stopped, the pressure in the high pressure chamber 31 gradually decreases, and the valve body 41 eventually closes the annular protrusion 3 due to the restoring force of the compression coil spring 42.
Separate from the open end of 8. Therefore, the compression chamber b1. The remaining lubricating oil is collected into the oil sump 34 from the three oil return passages mainly by gravity, and is used to pressurize the incompressible fluid as described above. This makes it possible to avoid the situation.

Furthermore, a valve unit 51 is provided at the center of the back surface of the rear end plate 3 to protrude into the high pressure chamber 31 for promoting the supply of lubricating oil to the vane groove 18 when the compressor is started. This valve unit 51 has a cylindrical casing 52 screwed onto the rear end plate 3 so as to be coaxial with the rotor 5, and a piston 55 slidably received in the inner hole of the casing. The front end of the piston 55 has an enlarged diameter head 55a, which abuts against the shoulder of the casing 52 to prevent the piston 55 from being pulled out rearward. Further, a spring retainer 54 is fixed to the rear end of the piston 55 by a snap ring, and a compression coil spring 53 installed between the spring retainer 54 and a step on the outer periphery of the casing 52 keeps the piston 55 rearward at all times. It is energized towards.

A passage 57 is formed in the intermediate portion of the piston 55 and includes a portion extending in the diametrical direction and a portion extending from the portion toward the front end of the piston 55 and opening toward the cavity 58. This cavity 58 defined at the front end of the piston 55 communicates with the bearing 8, which in turn communicates with the vane groove 18 via the lubricating oil passage 48 and the arcuate groove 5b of the rotor 5. A plurality of labyrinth grooves 56 are provided around the outer periphery of the piston 55 rearward of the passage 57 to enhance the sealing effect.

When the piston 55 is in the rear position shown in the figure due to the biasing force of the compression coil spring 53, the lubricating oil in the oil reservoir 34 flows through the annular recess 36 provided in the rear end plate 3, the lubricating oil passage 49, and the casing 52. The piston 5 passes through the mW1 oil passage 50 and throttle passage 50a provided in part
The oil is supplied to an arm oil passage 57 bored inside the tank 5. However, when the piston 55 is displaced to the forward position, communication between the throttle portion 50a and the lubricating oil passage 57 of the piston 55 is established, and lubricating oil is supplied from the oil reservoir 34 to the lubricating oil passage 57 of the piston 55. It becomes impossible to do so.

In the above-described configuration, lubricating oil is supplied to the vane groove 18 at the time of starting the compressor through the cooling lubricating oil path 43. ff1
This is provided in view of the fact that if the back pressure is supplied only through the ifl oil passage 45 and the mechanical seal, the supply of back pressure to the vane member 19 at the time of starting the compressor will be insufficient, and the noise caused by chattering by the vane member 19 will become a problem. It is something that By providing the pulp unit 51, when the pressure in the high pressure chamber 31 rises to a certain extent when the compressor is started, the lubricating oil in the oil reservoir 34 flows through the lubricating oil passage 49, 50 and the throttle portion 50a to the piston 55. B! lWi oil road 57
The air is supplied from the empty space 58 and the bearing 8 to the vane groove 18 relatively quickly. When the pressure in the high pressure chamber 31 further increases, the piston 55 moves forward due to the pressure balance between the empty chamber 58 and the pressure chamber 31, and the supply of lubricating oil to the lubricating oil path 57 in the piston 55 is stopped, and the vane Groove 1
Back pressure is supplied to the lubricating oil passage 47 exclusively through the mechanical seal.

As explained above, according to the present invention, all of the II lubricant oil supplied to the mechanical seal, the bearing 7.8 of the rotor shaft 6, or the vane groove 18 during normal operation is supplied to the cooling lubricant oil path 4.
3, and since the cooling lubricating oil passage consists of a plurality of parallel passages, its heat dissipation area is large, and these passages are provided at positions offset to the suction chamber side of the casing 1. Therefore, the lubricating oil is suitably cooled by the relatively low-temperature suction fluid, and excellent cooling efficiency can be obtained. In addition, these parallel cooling lubricating oil passages 43 are gathered together in the groove 43b and then are supplied to each part after being throttled by the jet 44, so mW4 oil is distributed equally to each of these cooling myn oil passages 43. Since the water is distributed over the air and flows at a relatively low speed, the cooling can be carried out even more efficiently.

<Effects> As described above, according to the present invention, the lubricating oil passage can be provided so as to have a large heat dissipation area in a relatively low-temperature part without having to route the lubricating oil passage specially for cooling. Suitable cooling performance can be obtained without complication. Therefore, without complicating the structure of the compressor,
Since the oil can be suitably cooled, the reliability and performance of the compressor can be improved without increasing the manufacturing cost of the compressor.

[Brief explanation of drawings]

FIG. 1 is a sectional view II of a rotary compressor according to the present invention. FIG. 2 is a sectional view taken along line I-II in FIG. 1. 1... Casing 1a... Mounting hole 2... Front end plate 3... Rear end plate 4... Rear casing 4a... Mounting hole 5... Rotor 5a, 5b... Arc-shaped groove 6 ...Rotor shaft 7.8...Bearing 9...7 Lunge
10... Leaf spring member 11... Clutch member 12.
...Ball bearing 13...Pulley 13a...Annular groove 14...Electromagnet 15...Fixed part 16.
・Rotating part 17 ・Compression coil spring 18 ・・
・Vane groove 19...Vane member 20...Suction port 21...Filter 22...Suction path
23.24... Depression 25... Discharge passage 26
... Single presser □27 ... Reed valve 28
···screw. 29...Discharge chamber 30...Discharge passage 31...
・High pressure chamber 32...Discharge path 33...Discharge port
34...oil sump 35...r! U lubricant level 3
6... Annular depression 37... Pulp retainer 38...
Annular protrusion 39...Return passage 40...Filter 41...Valve body 42...Compression coil spring 4
3...Cooling ram oil passages 43a, 43b...
Groove 44...Jet 45...Lubricating oil path 47~
50...n Clean oil passage 50a... Restricted oil passage 51-...Pulp unit 52...Casing 53...Compression coil spring 54...Spring retainer 55-...Piston
55a... Enlarged diameter head 56... Labyrinth groove 57
...Lubricating oil path 58...Empty room

Claims (2)

[Claims] (1) Separate the lubricating oil from the discharged gas and collect it in an oil sump.
In a rotary compressor that reuses the oil, at least a part of the lubricating oil path from the oil reservoir to the object to be lubricated is provided within a casing wall adjacent to a vacant space in the suction stroke. A rotary compressor featuring: (2) the lubricating oil passage portion consists of a plurality of parallel passages;
Claim 1, characterized in that a throttle is provided between the downstream gathering portion of the parallel passage and the object to be lubricated.
The rotary compressor described in section.