JPH11125190A - Sliding vane type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent the occurrence of vane chattering phenomena and defective compression phenomena, which take place when an engine is started in a state that there exists the difference in pressure between a high pressure side and a low pressure side in a sliding vane type compressor. SOLUTION: The provision of a gas opening/closing means composed of two gas feeding passages 51a and 51b where one has a large cross sectional area and the other has a small cross sectional area, in the inside of a gas feeding passage communicating the portions of high pressure fluid with one another except a vane back pressure chamber and the oil basin of a high pressure chamber, thereby allows the occurrence of vane chattering phenomena and defective compression phenomena to be avoided by letting at least the passage 51a small in cross sectional area out of the aforesaid two gas feeding passages, be made to communicates with the back parts of vanes, even when the compressor is started regardless of the difference in pressure between a high pressure side and a low pressure side after the compressor has been suspended.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a sliding vane type compressor used for an air conditioner for an automobile or the like.

[0002]

2. Description of the Related Art As is well known, in a sliding vane type compressor, a high-pressure lubricating oil is applied to the rear end of the vane so that the vane makes a rotary sliding motion with the tip of the vane contacting the inner wall of the cylinder as the rotor rotates. Is widely used. Hereinafter, the above-described conventional sliding vane compressor will be described with reference to the drawings.

FIGS. 6 to 10 show a specific structure of a conventional sliding vane compressor of the differential pressure oil supply type. In the figure, 1 is a cylinder having a cylindrical inner wall, 2
Is a rotor whose part of its outer periphery forms a minute gap with the inner wall of the cylinder 1; 3 is a plurality of vane slots provided in the rotor 2; 4 is a plurality of vanes slidably inserted into the vane slot 4; Is a drive shaft integrally formed with the rotor 2 and rotatably supported, and 6 and 7 are cylinders 1 respectively.
Are a front side plate and a rear side plate in which both ends are closed to form a working chamber 8 therein.

A suction port 9 communicates with the low-pressure side working chamber 8.
10 is a discharge port communicating with the high-pressure side working chamber 8, 11 is a discharge valve arranged in the discharge port, 12 is a lubricating oil in a high-pressure fluid compressed by forming a high-pressure chamber 14 communicating with the high-pressure passage 13. This is a high-pressure case provided with a separator 15 for separating and trapping. Reference numeral 16 denotes a vane applying device main body disposed on the rear side plate, and supplies lubricating oil in an oil reservoir below the high pressure chamber 14 to the vane back pressure chamber 17.

Reference numeral 18 denotes an oil supply passage communicating between an oil reservoir below the high-pressure chamber 14 and the vane back pressure chamber 17, reference numeral 39 denotes an oil groove provided in the rear side plate 7 for communicating and blocking communication between the vane back pressure chamber 17 and the oil supply passage. Is a passage for restricting the amount of refueling by differential pressure, 20 is a first ball seat provided in the middle of the oiling passage, and 21 is a first ball seat 29.
A first sphere 22 that opens or abuts on the first ball seat 20 on the side opposite to the first sphere 21, and 23 denotes a first plunger chamber 2.
The first plunger 24 is slidably disposed in the inner chamber and is released from the first ball seat 20 when the first plunger 21 is moved to the first ball seat 29 side. A first communicating the plunger chamber 25 with the working chamber 8 immediately before the discharge valve;
A pressure introduction passage, 27 is a first gas supply passage having one end communicating with the vane back pressure chamber 17, 28 is a second gas supply passage having one end communicating with an upper portion of the high pressure chamber 14, 29 is a first gas supply passage A second ball seat 30 provided at a communication portion between the second gas supply passage 27 and the second gas supply passage 28 is free or in contact with the second ball seat 29 to cut off the communication between the first gas supply passage 27 and the second gas supply passage 28. A second sphere, 31 is a stopper for restricting the movement of the second sphere 30, and 33 is slidably disposed inside the second plunger chamber 32 and moves the second sphere 30 when moved toward the second sphere 29. A second plunger released from the second ball seat 29,
A spring 35 is provided in a second lower plunger chamber 34 at a lower end of the second plunger 33 and biases the second sphere 30 to be released from the second ball seat 29 via the second plunger 33. Second lower plunger chamber 34 at the lower end
Pressure introduction passage communicating with the intermediate pressure portion of the working chamber 8 and 3
7 denotes a first gas supply passage 27 communicating with the vane back pressure chamber 17.
The third ball seat 38 provided on the way is the first gas supply passage 2.
7 is a third sphere that restricts the flow of gas in only one direction and blocks the flow in the first gas supply passage 27.

[0006] The operation of the sliding vane type compressor constructed as described above will be described below. When the drive shaft 5 and the rotor 2 rotate clockwise in FIG. 7 upon receiving power transmission from a drive source such as an engine, a low-pressure fluid flows into the working chamber 8 from the suction port 9 with this.

The high-pressure fluid compressed with the rotation of the rotor 2 pushes up a discharge valve 11 from a discharge port 10 to form a high-pressure passage 13.
The lubricating oil flows into the higher-pressure chamber 14 and is separated and captured by the separator 15. On the other hand, since the over-compressed gas in the working chamber 8 having a pressure enough to overcome the pressure of the high-pressure fluid and push up the discharge valve 11 from the first pressure introduction passage 24 is supplied to the first upper plunger chamber 25, Plunger 2
3 moves to the first sphere 20 and releases the first sphere 21 from the first sphere 20.

The second gas supply passage 28 is connected to the high pressure chamber 14
The upper portion of the second pressure plunger 36 overcomes the pressure of the intermediate pressure of the working chamber 8 flowing into the second lower plunger chamber 34 from the second pressure introducing passage 36 and the urging force of the spring 35 to reach the position shown in FIG. 2 Holds the plunger 33.

That is, the second sphere 30 abuts the second sphere 31 and the first gas supply passage 27 and the second gas supply passage 28 are shut off. The third sphere 38 provided in the first gas supply passage 27 is connected to the vane back pressure chamber 1 of the first gas supply passage 27.
Since the pressure on the side 7 is high, it comes into contact with the third ball seat 37 and shuts off the first gas supply passage 27.

Accordingly, the lubricating oil stored in the oil reservoir below the high-pressure chamber 14 is supplied to the vane back pressure chamber 17 from the passage 19 and the oil supply passage 18 and is pressed against the vane 4 to be applied to the rotor 2 and the front side plate. It flows into the working chamber 8 through the gap between the rear panel 6 and the rear side plate 7 (FIG. 8).

When the compressor is stopped, the pressure in the working chamber 8 suddenly drops to the pressure of the low-pressure fluid, and the lower end of the first plunger 23 communicating with the first pressure introducing passage 24 opened in the working chamber 8. Is lower than the pressure at the upper end of the first plunger 23, the first plunger 23 moves to the lower plunger side, and the first sphere 21 contacts the first sphere seat 20.

Further, since the high pressure side in the refrigeration cycle and the inside of the compressor are partitioned by the first sphere 21, the pressure in the upper part of the high pressure chamber 14 is high, and the second plunger is held at the position shown in FIG. That is, the second sphere 30 abuts the second sphere 29, and the first gas supply passage 27 and the second gas supply passage 28 are shut off.

The pressure inside the compressor, that is, the pressure inside the working chamber 8 rapidly drops to the pressure of the low-pressure side fluid, so that the third sphere 38 is released from the third ball seat 37. Therefore, since the lubricating oil is not supplied after the compressor is stopped, the liquid compression at the time of starting the compressor, which is caused by the lubricating oil remaining in the working chamber 8, can be prevented.

When a predetermined time elapses after the compressor is stopped and the pressure difference between the high pressure side and the low pressure side reaches a predetermined value, the spring 35 moves the second plunger 33 to the second ball seat 29 side, so that the state shown in FIG. When the compressor is started from this state, the gaseous fluid instantaneously flows from the second gas supply passage 28 through the first gas supply passage 27 and the supply passage 18 to the vane back pressure chamber 17.
Supplied to

[0015]

However, in the above-mentioned conventional sliding vane type compressor, a certain time has elapsed since the compressor was stopped, and the pressure difference between the high pressure side and the low pressure side caused the second sphere to separate from the second sphere. When the compressor is started in a state slightly larger than the pressure difference between the high pressure side (high pressure chamber) and the low pressure side (low pressure chamber), particularly when lubricating oil is filled in the oil supply passage, the second sphere is moved to the second ball seat. The gaseous fluid is
Lubricating oil cannot be supplied from the gas supply passage to the vane back pressure chamber, but lubricating oil is supplied from the oil supply passage. However, the lubricating oil has high resistance at the beginning of flow due to its head, viscosity, and inertia. In such a case, a sufficient amount of lubricating oil cannot be supplied with respect to the volume fluctuation of the vane back pressure chamber generated at the time of the above.

For this reason, particularly when the rotation speed at the start of the compressor is low, the pressure in the back pressure chamber of the vane drops, and the well-known malfunctioning phenomenon in which the vane separates from the inner wall of the cylinder and collides again, and the poor compression phenomenon in which the fluid is not compressed occur. There was a problem that.

[0017] Therefore, there is a method of increasing the load of the spring in order to secure a pressure difference between the high pressure side and the low pressure side that lubricating oil can be sufficiently supplied from the oil supply passage to the vane back pressure chamber.
However, if the spring load is increased, gaseous fluid is always supplied to the vane back pressure chamber during steady operation at low load,
There was a problem that lubricating oil was not supplied at all and caused abnormal wear of the compressor.

[0018]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, a sliding vane type compressor according to the present invention is designed so that when a pressure difference between a high pressure side and a low pressure side fluid of a conventional compressor is equal to or less than a predetermined value, the sliding vane type compressor is used. A gas opening / closing means is provided for communicating two gas supply passages and communicating only when the gas supply passage has a smaller cross-sectional area when the gas supply passages are larger than a predetermined value.

[0019]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The invention according to claim 1 for solving the above-mentioned problem is a sliding vane type compressor in which when a pressure difference between a high-pressure side and a low-pressure side fluid is less than a predetermined value, two kinds of fluids are provided. By providing gas opening / closing means for communicating the gas supply passages and communicating only when the two gas supply passages have a smaller cross-sectional area when the gas supply passage is larger than a predetermined value, the pressure difference between the high-pressure side and the low-pressure side fluid is small. When the compressor is started, the gaseous fluid is supplied from the two gas supply passages to the vane back pressure chamber, and when the compressor is started when the pressure difference is larger than a predetermined value, the passage cross-sectional area of the two gas supply passages is reduced. By supplying a gaseous fluid from a smaller one, the gaseous fluid is released from the inner wall of the cylinder, and the well-known malfunctioning phenomenon and the poor compression phenomenon in which the fluid is not compressed can be prevented.

According to a second aspect of the present invention, the two gas supply passages having a small passage cross-sectional area are integrally provided in an outer case of a main body of the back pressure applying device. At the same time, costs can be reduced by reducing the number of parts and improving workability.

According to a third aspect of the present invention, the two gas supply passages having a small cross-sectional area are provided in a ball seat of a gas opening / closing means comprising a steel ball and a ball seat having the same configuration as a conventional sliding vane type compressor. Providing the protrusions has the effect of the invention of claim 2 as well as the effect of the invention of claim 1.

[0022]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS. In the figure, components having the same functions and effects as those of the conventional sliding vane type compressor are denoted by the same reference numerals and description thereof is omitted.

In the figure, reference numeral 50 denotes the first gas supply passage 27.
A third plunger 52 integrally formed with a third gas supply passage 51a having a small passage cross-sectional area and a third gas supply passage 51b having a large passage cross-sectional area is provided between the third gas supply passage 51a and the second gas supply passage 28. By contacting the plunger end face,
It is a seal seat surface that blocks the first and second gas passages.

The operation of the sliding vane compressor constructed as described above will be described below.

(Embodiment 1) In a steady operation state in which there is a sufficient pressure difference between the high pressure side and the low pressure side to refuel after a certain time has elapsed since the start of the compressor, the first pressure introduction passage 24 Since the over-compressed gas in the working chamber 8 having a pressure enough to push up the discharge valve 11 by overcoming the pressure of the high-pressure fluid is supplied to the first plunger chamber 25, the first plunger 23 moves to the first ball seat 20 side. And is released from the first sphere 20.

The second gas supply passage 28 is connected to the high pressure chamber 24
The upper portion of the second pressure plunger 36 overcomes the pressure of the intermediate pressure of the working chamber 8 flowing into the second lower plunger chamber 34 from the second pressure introducing passage 36 and the urging force of the spring 35 to reach the position shown in FIG. 2 Holds the plunger 33. That is, the lower end of the third plunger 50 abuts on the seal seat surface 52 to shut off the third gas supply passage 51b having a large passage cross-sectional area.

The third sphere 38 provided in the middle of the first gas supply passage 27 abuts against the third ball seat 37 because the pressure on the side of the vane back pressure chamber 17 of the first gas supply passage 27 is high. The supply passage 27 is shut off. Therefore, the third gas supply passage 51a communicates with the first and second gas supply passages 27 and 28, but has a very small passage cross-sectional area. Therefore, the third gas supply passage 51a is stored in the oil reservoir below the high pressure chamber 14 in the vane back pressure chamber 17. Lubricant is in passage 1
9. The oil is supplied from the oil supply passage 18 and is used to press the vane 4.

When the compressor stops, the pressure in the working chamber 8 rapidly drops to the pressure of the low-pressure side fluid, so that the pressure in the first lower plunger chamber 25 also drops to the pressure of the low-pressure side fluid and the lower end of the first plunger 23 Is lower than the pressure at the upper end of the first plunger 23, the first plunger 23 moves to the lower plunger chamber side, and the first sphere 21 becomes the first ball seat 20.
Abut.

The high pressure side in the refrigeration cycle and the inside of the compressor are separated by the first sphere 21 so that the high pressure chamber 14
The pressure in the upper part is high and holds the second plunger 33 at the position shown in FIG. That is, the lower end of the third plunger 50 abuts on the seal seat surface 52 to shut off the third gas supply passage 51b having a large passage cross-sectional area.

The pressure inside the compressor drops to the pressure of the low-pressure fluid, so that the third sphere 38 is released from the third ball seat 37. Therefore, the inflow of the lubricating oil into the working chamber 8 can be prevented as in the vane applying device of the conventional sliding vane type compressor. Even after a lapse of time after the stop, the third plunger 50 abuts on the seal seat surface 52 and the third gas supply passage 51b having a large passage cross-sectional area is blocked, but the third gas supply passage 51b having a small passage cross-sectional area is closed. Gas supply passage 5
Since 1a communicates with the first and second gas supply passages 28 and 27, a gaseous fluid can be instantaneously supplied to the vane back pressure chamber 17.

When the pressure difference between the high-pressure side and the low-pressure side decreases after a certain period of time after the compressor is stopped, the spring 35 moves the second plunger 33 to the seal seat side 52 as shown in FIG. When the compressor is started from, the gaseous fluid instantaneously flows from the second gas supply passage 28 to the vane back pressure chamber 17 via the third gas supply passages 51a and 51b, the first gas supply passage 27, and the oil supply passage 18. Supply.

Immediately thereafter, as the pressure in the high-pressure chamber 14 increases, the pressure overcomes the urging force of the spring 35 and the pressure of the second lower plunger chamber 34, that is, the third plunger 5
The lower end is in contact with the seal seat surface 52, and is switched to oil supply by shutting off the third gas supply passage 51b having a large passage cross-sectional area.

As described above, according to the present embodiment, when the pressure difference between the high-pressure side and the low-pressure side fluid is equal to or less than a predetermined value, the sliding vane-type compressor communicates with the two gas supply passages, When the pressure is equal to or greater than a predetermined value, by always integrally providing gas opening / closing means for communicating the two gas supply passages having a small passage cross-sectional area, any pressure difference between the high pressure side and the low pressure side after the compressor is stopped is reduced. Even in the state, since the high-pressure gaseous fluid is instantaneously supplied to the vane back pressure chamber, the well-known malfunctioning phenomenon in which the vane is released from the inner wall of the cylinder and collides again and the poor compression phenomenon in which the fluid is not compressed can be prevented. There is no loss in machine durability or efficiency.

(Embodiment 2) In Embodiment 1, the third gas supply passages 51a and 51b are integrally provided in the third plunger 50. However, since the third plunger 50 is made of an Fe-based material, the passage is formed. Third gas supply passage 5 having an extremely small cross-sectional area
Since the processing of 1a is very difficult, by changing to the back pressure applying device main body 16 (outer case side) which is generally made of an Al-based material, the effect of the invention of claim 1 and the workability can be improved. The cost can be reduced because the other components can be shared with the conventional components.

(Embodiment 3) In the conventional vane back pressure applying device, the third gas supply passage 51a is additionally processed on a part of the second ball seat 31, thereby achieving the effect of the first aspect and the second aspect. Of the invention described in the above.

Further, in the embodiment, the sliding vane type compressor has a perfect circular type having only one suction port 9 and one discharge port 10, but a type having a plurality of suction ports 9 and plural discharge ports 10 may be used. Although the number of vanes is three, the number of vanes may be any.

[0037]

According to the present invention, as is apparent from the above description,
The invention according to claim 1 for solving the above-mentioned problem is that in a sliding vane compressor, when a pressure difference between a high-pressure side and a low-pressure side fluid is equal to or less than a predetermined value, two gas supply passages are communicated, When the gas supply passage is larger than the predetermined value, the gas supply passage is provided integrally with a gas opening / closing means that communicates only when the passage cross-section is small. By supplying the gaseous fluid to the vane back pressure chamber from the gas supply passage having a small diameter, it is possible to prevent the well-known malfunctioning phenomenon that is released from the inner wall of the cylinder and collides again and the poor compression phenomenon that does not compress the fluid.

According to a second aspect of the present invention, the two gas supply passages having a small passage cross-sectional area are integrally provided in an outer case of the main body of the back pressure applying device, so that under any condition after the compressor is stopped. Even if the compressor is started, the gaseous fluid is supplied from at least the gas supply passage having a small cross-sectional area to the vane back pressure chamber, so that the well-known malfunctioning phenomenon that separates from the inner wall of the cylinder and collides again and the poor compression that does not compress the fluid. The phenomenon can be prevented, and the cost can be reduced by reducing the number of parts and improving the workability.

According to the third aspect of the present invention, the two gas supply passages having a small passage cross-sectional area are provided with recesses in the ball seat, so that the compressor can be started under any condition after the compressor is stopped. By supplying a gaseous fluid to the vane back pressure chamber from at least the gas supply passage having a small cross-sectional area, it is possible to prevent a well-known malfunction phenomenon and a poor compression phenomenon that does not compress the fluid, which are released from the cylinder inner wall and collide again. The cost can be reduced by reducing the number of parts and improving the workability.

[Brief description of the drawings]

FIG. 1 is an enlarged view of a main part of a vane back pressure applying device according to a first embodiment of the present invention (at the time of steady operation).

FIG. 2 is an enlarged view of a main part of the vane back pressure applying device in Embodiment 1 of the present invention (when stopped).

FIG. 3 is an enlarged view of a main part of the vane back pressure applying device according to the first embodiment of the present invention (at start-up).

FIG. 4 is an enlarged view of a main part of a vane back pressure applying device according to a second embodiment of the present invention.

5A is an enlarged view of a main part of a vane back pressure applying device according to a third embodiment of the present invention. FIG. 5B is an enlarged view of an arrow in FIG.

FIG. 6 is a longitudinal sectional view of a conventional sliding vane type compressor.

FIG. 7 is a sectional view taken along line XX of FIG. 6;

FIG. 8 is an enlarged view of a main part of the conventional vane back pressure applying device (at the time of steady operation).

FIG. 9 is an enlarged view of a main part of the conventional vane back pressure applying device (when stopped).

FIG. 10 is an enlarged view of a main part of the conventional vane back pressure applying device (at start-up).

[Explanation of symbols]

 Reference Signs List 1 cylinder 2 rotor 3 vane slot 4 vane 5 drive shaft 6 front side plate 7 rear side plate 8 working chamber 9 suction port 10 discharge port 11 discharge valve 12 high pressure case 13 high pressure passage 14 high pressure chamber 15 screen 16 vane back pressure applying device body 17 Vane back pressure chamber 18 Oil supply passage 19 Passage 20 First ball seat 21 First sphere 22 First plunger chamber 23 First plunger 24 First pressure introduction path 25 First upper plunger chamber 27 First gas supply path 28 Second gas supply Passageway 29 Second ball seat 30 Second ball 31 Stopper 32 Second plunger chamber 33 Second plunger 34 Second lower plunger chamber 35 Spring 36 Third pressure introduction path 37 Third ball seat 38 Third ball 50 Third plunger 51a, 51b Third gas supply passage 52 Seal seat surface

Claims (3)

[Claims] 1. A cylinder having a cylindrical inner wall, a rotor disposed inside the cylinder and having a part of an outer periphery forming a minute gap with the cylinder inner wall, and a vane slit provided in the rotor. A plurality of vanes slidably inserted into the rotor, a drive shaft provided on the rotor and rotatably supported, and a front side plate and a rear side plate closing both ends of the cylinder to form a working chamber therein. A suction port and a discharge port communicating with the working chamber with a portion where the outer periphery of the rotor and the inner wall of the cylinder are close to each other; a discharge valve provided at the discharge port; A high-pressure case that separates lubricating oil in a fluid and includes an oil reservoir at a lower portion thereof communicates with a vane back pressure chamber formed by the vane slot and a vane end, and an oil reservoir of the high-pressure chamber. Refueling passage and this An oil passage opening / closing means for interrupting the oil supply passage; a gas supply passage communicating with the vane back pressure chamber and a portion other than an oil reservoir in the high pressure case; Gas opening / closing means integrally provided with two gas supply passages, and when the pressure difference between the high-pressure side and the low-pressure side fluid is equal to or less than a predetermined value, the two gas supply paths are communicated with each other, and the high-pressure side and the low-pressure side A sliding vane-type compressor, wherein when the pressure of the fluid is higher than a predetermined value, only the two gas supply passages having a small cross-sectional area communicate with each other. 2. The sliding vane compressor according to claim 1, wherein the two gas supply passages each having a small passage cross-sectional area are provided on an outer case of the back pressure applying device main body. 3. The sliding vane compressor according to claim 1, wherein the two gas supply passages each having a small passage cross-sectional area are provided with a recess in a ball seat of a gas opening / closing means comprising a steel ball and a ball seat.