JPS60162092A - Oil feeding apparatus for rotary-vane type compressor - Google Patents

Abstract

PURPOSE:To prevent the compression disorder phenomenon by cutting-off an oil feeding passage which communicates to the bottom part of a vane groove from an oil reservoir for a certain time after the stop of operation and increasing the sectional area of the flow passage for a certain time after start and allowing the vane to be pressed sufficiently even on start when the pressure difference of a compressor is small. CONSTITUTION:When a compressor stops operation, a plunger 23 is shifted by the pressure difference of the compressor and an oil feeding passage 16 is cut off, and at the same time, a valve piece 27 shifts to allow an auxiliary passage 29 to communicate to the oil feeding passage 16. When the pressure difference lowers after a certain time, the plunger 23 shifts upward to separate a spherical body 20 from a valve seat 19, and the space in the vane bottom part is allowed to communicate to a high-pressure chamber 14 through the auxiliary passage 29 having a large sectional area and the oil feeding passage 16. When the compressor is started in this state, a sufficient amount of oil is supplied into the vane bottom part, and when the pressure difference increases after a certain time, a valve piece 27 contacts with a valve seat 28, and the feeding amount of lubricating oil is controlled to a proper value.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a lubricating device for a vane rotary compressor, and is particularly suitable for use in a vane rotary compressor used in an automobile air conditioner. It provides:

Conventional configuration and problems As is well known, in vane rotary compressors, high pressure is constantly applied to the bottom of the vane so that as the rotor rotates, the vane rotates and slides with its tip in contact with the inner wall of the cylinder. A structure that applies lubricating oil is used. Generally, the means to achieve all of this are the forced lubrication system, which uses a pump installed on the drive shaft of the compressor to forcibly supply lubrication, and the other, which utilizes the full pressure of the high-pressure fluid compressed by the compressor. Differential pressure lubrication systems that supply lubrication based on a 1F force difference between the height and the bottom are widely used.

However, with the forced lubrication type, the amount of lubrication increases as the rotation speed of the compressor increases, and the centrifugal force acting on the vanes causes the vanes to be pushed into excessive contact with the cylinder inner wall.
This has the disadvantage of causing increased wear on the vane tips and the inner wall of the cylinder and increased manpower for the compressor, resulting in poor durability and efficiency of the compressor.

On the other hand, with the differential pressure lubrication type, the above phenomenon can be completely alleviated by eliminating weekly lubrication, which causes the same drawbacks as in the case of the forced lubrication type described in -1-, and by installing a mechanism in the lubrication passageway that completely limits the amount of lubrication. However, in this case, even when the compressor is stopped after operation, the high-pressure side lubricating oil and high-pressure fluid are supplied to the bottom of the vane due to the pressure difference between the high and low pressures of the compressor, and the lubricating oil then flows inside the cylinder and continues to flow through the compressor. This can cause problems such as oil compression or reversing the compressor when starting the engine.

For this reason, in the conventional pictorial pressure oiling system, there is a box in the oiling 3ffi path.
It had a mechanism that completely shuts off the oil supply passage when the compressor is stopped and opens the oil supply passage when the compressor is in operation.

Figures 1 to 3 show the specific configuration of a vane rotary compressor having a conventional differential pressure oil supply system, in which 1 is a cylinder with a cylindrical inner wall, and 2 is a cylinder with a part of its outer periphery. A rotor forming a small gap with the inner wall; 3 a plurality of pages slidably inserted into a vane slot 4 provided in the rotor 2; 5 a plurality of pages formed integrally with the rotor 2 and rotatably supported; Drive shaft, 6 and 7 cylinders each
The front side plate and the rear side plate are completely closed at both ends to form the UJ chamber 8 inside, 9 is the suction port which communicates with the working chamber on the low pressure side, and 10 is the discharge port which communicates with the working chamber 8 on the high side. 1,11
12I''i is a discharge valve disposed at the discharge port 10, which communicates with the high pressure passage 13 and forms a high pressure chamber 14 therein, and is equipped with a screen 15 for separating and capturing lubricating oil in the compressed high pressure fluid. 16 is a supply passage connecting the oil reservoir below the high pressure chamber 14 and the vane bottom space 17;
18 is a passage that limits the amount of oil supplied; 19 is a spherical seat that is provided in the middle of the oil supply passage 16 and holds the spherical body 20; 21 has one end opened to the spherical valve seat 19 and the other end formed in a threaded portion of the plug body 22c; A joint UJ chamber 23 is slidably disposed in this sliding chamber and communicates with the high pressure side working aJ chamber 8 through the passage 22b and passage 22a. This is a plunger that controls the fluid pressure of the working chamber 8.

The operation of the vane rotary compressor oil supply system configured as described above will be described below. When the drive shaft 5 and rotor 2 rotate clockwise in FIG. 2 due to power transmission from a drive source such as an engine, low-pressure fluid flows into the working chamber 8 through the suction port 9. Rotor 2
The three bodies of high-pressure fluid compressed as the unit rotates push the discharge valve 11 up through the discharge port 10 and flow through the high-pressure passage 13 into the high-pressure chamber 14.
The lubricating oil is separated and captured by the screen 15 1, and the lubricating oil separated from the high pressure fluid flows into the high pressure chamber 14.
Stored downwards.

On the other hand, since the pressure in the working chamber 8 on the high-pressure side acts on the lower end surface of the plunger 23, the plunger 23 moves in one direction, overcoming the pressure on the negative end surface of the plunger 23, and moves the spherical valve seat 19 toward the spherical valve seat 19. is released and the oil supply passage 16 is allowed to run at full speed. Therefore, the lubricating oil stored below the high pressure chamber 14 is supplied from the passage 18 and the passage 16 to the vane bottom space 17 due to the differential pressure, and is used to press the vane 3.

Next, when the compressor stops, the pressure inside the working chamber 8 increases to the vane 3.
The pressure of the fluid on the E side rapidly decreases due to leakage from the longitudinal gap, so the force acting on the lower end surface of the plunger 23 is smaller than the force due to the pressure of the high pressure chamber 14 acting on one end surface. As a result, the plunger 23 moves downward, and the spherical body 20 is also held in close contact with the spherical valve seat 19, thereby blocking the oil supply passage 16. Therefore, no more hyperbaric chamber 1
Since the lubricating oil of the four blades is not supplied to the vane bottom chamber 17, the lubricating oil is spooled inside the sill 1 and the lubricating oil is not supplied to the vane bottom chamber 17.
The high-pressure lubricating oil and fluid flowing into the working chamber 8 are re-expanded without causing oil compression. There is no need to reverse the compressor.

However, when the compressor is started after a certain period of time has passed since the compressor stopped and the pressure of the fluid on the low-pressure side becomes equal to the pressure of the fluid on the high-pressure side, the conventional oil supply system described above 16 is shut off, lubricating oil is not supplied immediately after the compressor starts and during the time when the plunger 23 releases the sphere 20 from the sphere valve seat 19. Small aisle area 1
Since the supply from the lubricating oil supply from 3, the vane 3 becomes detached from the inner wall of the sill 1 and collides with it again, which is a well-known phenomenon, and the fluid is not compressed, resulting in poor compression.

OBJECTS OF THE INVENTION In view of the drawbacks mentioned above, the present invention has been developed to prevent vane malfunctions and poor compression phenomena even when the compressor is operated at full speed at low speed when there is no or small pressure difference between high and low pressures of the compressor, and to improve durability and durability. An object of the present invention is to provide an oil supply device for a vane rotary compressor that does not impair efficiency.

Composition of the Invention The present invention provides a lubricating device for supplying lubricating oil for pressing vanes in a vane rotary compressor from an oil reservoir in a high-pressure chamber to a vane bottom space, and includes a passage opening/closing means for disconnecting a lubricating passage, and a lubricating passage. passage area control means for controlling the communication area of the compressor to be large or small; When the pressure difference on the low-pressure side decreases with the passage of time and becomes smaller than a certain value, the oil supply passage is shut off, and in other cases, the oil supply passage is opened. When the pressure difference between high and low pressures is small during a certain period of time immediately after the compressor starts operating, the communication area of the oil supply passage is increased, and after a certain period of time after the compressor starts operation, the communication area of the oil supply passage is reduced. This is what I did.

With this configuration, even when the compressor is started at low speed when there is no or small pressure difference between the high and low pressures of the compressor, the oil supply passage from the high pressure chamber to the vane bottom space is initially in communication with the oil supply passage. Since the area control means operates so that the passage area becomes large, the necessary amount of lubricating oil can be supplied.
It has the unique effect of preventing vane malfunction and compression failure.

DESCRIPTION OF EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings.

FIG. 4 shows an enlarged cross-sectional view of the essential parts of the oil supply system for a vane rotary compressor according to an embodiment of the present invention, which is the same part as the oil supply system for the conventional vane rotary compressor. Components having the same functions and effects will be designated by the same reference numerals and will not be fully described.

In the figure, 26 is a valve body sliding chamber provided in a portion of the oil supply passage 16 communicating with the high pressure chamber 14 and in which the valve body 27 is slidably disposed, and 28 is a portion of the valve body sliding chamber 26 communicating with the oil supply passage 16. 29 is provided on the valve body 27, and when the valve body 27 comes into contact with the valve seat 28, an auxiliary passage which is cut off from the oil supply passage 16 and has a large passage area; 30 is an auxiliary passage provided on the valve body 27; Even if the valve body 27 is provided and comes into contact with the valve seat 28, the oil supply passage 1
6 and a passageway that limits the amount of oil supplied; 31 is a valve body 27;
32 is a spring that biases the plunger metal in a direction that releases the sphere 20 from the valve seat 19; 32 is a spring that fully controls the sliding of the valve body 27; be.

The entire operation of the vane rotary compressor oil supply system constructed as described above will be explained below.

During steady operation of the compressor, fluid pressure on the high pressure side acts on the lower end surface of the plunger 23, the sphere 2o is released from the spherical valve seat 19, the oil supply passage 16 is communicated, and the valve body 27 is filled with lubricating oil from the high pressure chamber 14. The spring 31 receives the flow resistance due to the flow K.
The lubricating oil stored below the high pressure chamber 14 is transferred from the passage 30 and the passage 16 to the bottom of the vane by overcoming the biasing force of the valve body 27, the weight of the valve body 27, and the sliding resistance of the valve body 27 and coming into contact with the valve seat 28. The fact that the oil is supplied to the space and used for suppressing the vanes is similar to the oil supply system of the conventional vane rotary compressor.

When the compressor stops operating, the pressure in the high pressure chamber 14 acting on one end of the plunger 23 overcomes the force acting on the lower end of the plunger 23 and the biasing force of the spring 33, and the plunger 23 ：Moving toward IJL Accordingly, the sphere 20 is also held tightly against the spherical valve seat 19, and the oil supply part W116 is shut off, which prevents oil compression or reverse rotation of the compressor at the time of starting the compressor. This is similar to the oil supply system for vane rotary compressors.

When the compressor stops and the oil supply passage 16 is blocked, the η heavy body 27 is moved by the biasing force of the spring 31 and the Ehi ring 32 is moved.
Therefore, the auxiliary passage 29 communicates with the oil supply passage 16. When a certain period of time passes after the compressor stops and the pressure difference between high and low pressures gradually decreases to below a certain value, the plunger y23 moves upward due to the biasing force of the spring 33 and pushes the sphere 20 onto the sphere valve seat 19. released from In this case spring 3
Refueling passage 1 by appropriately selecting the power of 3.
The difference between the high and low pressures at the time when 6 is connected can be set so that the problems of oil compression and reversal do not occur.

Therefore, if there is no pressure difference between the high and low pressures of the compressor, the sphere 20
Since the valve is separated from the spherical valve seat 19, the oil supply passage 16 communicates with the high pressure chamber 14 and the vane bottom space. In this state, start the compressor to 0J
Then, lubricating oil can be quickly supplied from the high pressure chamber 14 through the dog-shaped passageway of the passage area in response to pressure fluctuations in the bottom space of the vane, so that there is no shortage of vane pressure when starting the compressor. It is possible to prevent malfunctions and poor compression phenomena.

As the operation continues, the pressure difference between high and low pressures gradually increases, and the amount of lubricating oil supplied from the oil supply passage 16 to the bottom of the vane increases.
Since the compressor contacts the valve seat 28 against the urging force of the compressor, the durability and efficiency of the compressor will not be completely impaired by weekly refueling over a long period of time.

As described above, according to this embodiment, the lubricating oil for pressing the vanes in the vane rotary compressor is provided in the middle of the oil supply passage as a lubricating device that supplies lubricating oil from the oil reservoir of the high pressure chamber to the vane bottom space. A spherical valve seat that holds the entire sphere, a bracket @ J chamber that opens to the spherical valve seat at one end and communicates with the working chamber on the high pressure side at the other end, and a plunger that is slidably disposed within this sliding chamber. , a spring that exerts a biasing force in a direction in which the plunger releases the sphere from the spherical valve seat, a valve body sliding chamber provided in the high pressure chamber communication portion of the oil supply passage, and a sliding member in the valve body sliding chamber. A freely arranged valve body, a valve seat provided in the communication portion of the oil supply passage of the valve body sliding chamber, and when the valve body comes into contact with this valve seat, the area of the passage is cut off from the oil supply passage and becomes a dog. An auxiliary passage provided in the valve body with a metal plate, a passage provided in the valve body that communicates with the oil supply passage and restricts the oil supply section even when the valve body contacts the valve seat, and a passage that connects the valve body from the valve seat. By providing a spring that biases the valve in the direction of disengagement and a retaining ring that restricts the sliding of the valve body, even if the compressor is started at low speed when there is no or small pressure difference between the high and low pressures of the compressor, the high [The oil supply passage from the chamber to the bottom space of the vane is connected at the time of startup, and the passage area of the oil supply passage is also narrowed by the communication of the auxiliary passage, so the lubricating oil essential for pressing the vane can be quickly supplied. Furthermore, when the difference in high and low pressure becomes a dog and the differential pressure becomes sufficient to supply all the lubricating oil, the passage area can be reduced to limit the amount of lubricating oil and supply it to the space at the bottom of the vane, improving the durability and efficiency of the compressor. Vane malfunction and poor compression phenomena can be completely prevented without causing any damage.

Effects of the Invention As described above, the present invention is a lubricating device for supplying lubricating oil for pressing vanes in a vane rotary compressor from an oil reservoir in a high pressure chamber to a vane bottom space, and is capable of opening and closing a passage that disconnects and disconnects an oil supply passage. and an iM road area control means for restricting the communication area of the 1 m refueling road to a large or small one, and the passage opening/closing lower stage is controlled for a certain period of time from the time when the compressor stops operating, or after the compressor stops operating. Takada side and low pressure 1 inside the compressor
) When the pressure difference between the high and low levels decreases over time and becomes smaller than a certain value, the oil supply passage is shut off, and in other cases (arched, connected ω), the passage area is The control means increases the communication area of the oil supply passage when the pressure difference between high and low pressures is small within a certain period of time immediately after the compressor starts full operation, and decreases the communication area of the oil supply passage after a certain period of time has passed after the compressor starts operation. Even if the compressor is started with full rotation at low speed when there is no or small pressure difference between the high and low pressures of the compressor, the oil supply passage from the high pressure chamber to the bottom space of the vane is closed at the beginning.
The passage area control means of the oil supply passage is operated so that the area of the passage is small, so that the necessary giant lubricant can be quickly supplied, and as time passes, the pressure difference between the high and low pressures decreases. Thick enough for sufficient lubrication due to differential pressure 1t11f
: When the supply becomes available, the passage area control means operates to reduce the passage area, and the lubricant can be completely restricted and supplied to the vane bottom space, so vane malfunctions can be prevented without compromising the durability or efficiency of the compressor. and compression failure phenomena can be prevented.
Its practical effects are significant.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional view of a vane rotary compressor equipped with a conventional oil supply device, Fig. 2 is a sectional view taken along line X-X in Fig. 1, and Fig. 3 is a longitudinal sectional view of a conventional vane rotary compressor. FIG. 4 is an enlarged sectional view of the main part of the oil supply system for a vane rotary compressor in one embodiment of the present invention. 1... Shilling, 2... Loaf, 3...
... Vane, 4 ... Vane slot, 5.
...Kuri 1tM, e...Front side plate, 7...
...Rear side plate, 8...Made aJ room, 9...
...Suction port, 10...Discharge port, 11...
...Discharge valve, 12...High pressure case, 14...
・High pressure chamber, 16... Lubricating power m @ Figure 3?

Claims (1)

[Claims] A cylinder having a cylindrical inner wall, a rotor disposed inside the cylinder and having a part of its outer periphery forming a minute gap with the cylinder inner wall, and a slide a1 freely inserted into a bege slot provided in the rotor. a plurality of four vanes, a drive shaft formed integrally with the rotor and rotatably supported, and a front side plate and a rear side plate that close openings at both ends of the 0f1 sill to form a working chamber therein. , a suction passage and a discharge passage formed by communicating with the working chamber across a portion where the outer circumference of the loaf and the inner wall of the cylinder are close to each other, and a discharge valve disposed in the middle of the discharge passage communicating with the discharge passage. The case has a high pressure chamber that completely separates the lubricating oil in the compressed high pressure fluid and forms an oil reservoir in the lower part thereof, and the oil reservoir of the high pressure chamber is communicated with the vane slot to supply the lubricating oil. A refueling device for a vane rotary compressor comprising a refueling passage supplying oil into a bege slot, the refueling passage having a passage opening/closing means for disconnecting communication with the refueling passage and a passage for controlling the communication area of the refueling passage to be large or small. and area control means, and the passage opening/closing means controls the pressure difference between the high pressure side and the low pressure side inside the compressor for a certain period of time after the compressor is completely stopped, or after the compressor has stopped operating. The oil supply passage is shut off until the oil supply passage becomes smaller than a certain value and communicated otherwise, and the passage area control means is controlled to control the high and low pressure within a certain period of time immediately after the compressor starts operating. An oil supply device for a vane rotary compressor that increases the communication area of the oil supply passage when the difference is small, and reduces the communication area of the oil supply passage after a certain period of time has passed after the start of operation of the compressor.