KR100186875B1 - Rotary vane type compressor and vacuum pump - Google Patents

Abstract

Provided are a rotary vane type compressor and a vacuum pump which are compact and do not deteriorate in volumetric efficiency.

A vane 29 and 29 movable in a radial direction at a position biased to one side of the cylinder chamber by installing a cylinder chamber 23 having a pseudo-ellipse shape in the case 22 of the rotary vane type compressor 21 and the vacuum pump 51. Rotor 27 holding the rotor is freely installed, and the cylinder chamber 23 is provided by the rotor 27 with the compression chamber 30 of the large volume gas and the pump chamber 31 of the small volume liquid. The pressure seal liquid discharged from the discharge port 36 of the pump chamber 31 is supplied to the place which seal and lubrication of a compressor and a vacuum pump are needed.

Since a separate pump for pressurizing the sealant does not need to be provided, the compressor and the vacuum pump become compact and seal and lubricate with the pressurized solution, thereby preventing the drop in volumetric efficiency due to internal leakage.

Description

Rotary vane type hydraulic press

1 is a cross-sectional view of a gas compressor as a first embodiment of the present invention, and is broken by line A-A of FIG.

2 is a cross-sectional view taken along line B-B in FIG.

3 is a cross-sectional view of a vacuum pressure pump according to a second embodiment of the present invention, and is broken by the C-C line of FIG.

4 is a cross-sectional view taken along the line D-D in FIG.

5 is a longitudinal sectional view of a main portion of a known compressor.

6 is a cross sectional view of a main portion of a known compressor.

The present invention relates to a fluid pressure device such as a gas compression or vacuum pump, and more particularly to a rotating vane type fluid pressure device having a rotor having a smoothly moving vane.

One type of rotary vane type fluid compressor is a gas compressor. This is a rotor provided with a plurality of vanes moving smoothly in the radial direction in the cylinder chamber formed in the case freely rotated, the gas sucked into the cylinder chamber from the suction port by the rotation of the rotor. Is compressed by the vane and compressed by the vane and discharged from the discharge port.

In such a rotary vane type compressor, the gas compressed by the vane to high pressure tends to leak to the suction side of low pressure, and the leak tends to cause a decrease in volumetric efficiency. In addition, when the gas is compressed, the temperature rises and cooling is necessary. Therefore, in general, the sealing liquid is supplied to the rotary sliding portion of the compressor while providing sealing and lubricity and cooling.

As a means for supplying the above-mentioned sealing liquid, a method of using the discharge pressure of a compressor body is known conventionally. By the way, the method of using the discharge pressure sometimes causes the pressure of the gas in the compression chamber to be equal to or higher than the pressure of the sealing liquid, and this causes a problem that the sealing liquid is crushed to become a temporary sealing defect.

In order to solve this problem, it is also known to install a gear pump in the compressor so that the sealing liquid is forcibly supplied from the gear pump.

5 and 6 show an example of a rotary vane type compressor provided with such a gear pump. The rotary vane type compressor 1 is free to rotate in a position in which the rotor 5 having a plurality of vanes 4 which move smoothly in the radial direction in the cylinder chamber 3 formed in the case 2 is biased to one side. It arrange | positioned so that it may become free, and compresses the gas, such as air sucked in from the suction port 6 by the rotation of the rotor 5, for the said vane 4, and compresses the compressed gas into the valve hole 7 Discharged from the discharge port 8 and stored in the tank 9. The gas stored in the tank 9 is sent to a desired place as indicated by a solid arrow. 7) is provided with a backflow valve 7a that permits only the outflow of compressed gas to prevent backflow.

The gear pump 11 is attached to the gear case 10 attached to the case 2 described above. The suction port 12 of the gear pump 11 is connected to the bottom of the tank 9 by a pipe 13, and the discharge port 15 is connected to the port 17 of the case 2 by the pipe 16. The sealant is supplied from the port 17 to the rotary sliding portion of the compressor. Then, the sealing liquid supplied to the rotary sliding portion of the compressor 1 is discharged to the tank 9 together with the gas compressed in the vanes 4, and stored in the bottom of the tank due to the specific gravity difference.

Reference numeral 18 in FIG. 6 denotes an electric motor that rotates the rotor 5 and the gear pump 11.

The compressor 1 having such a gear pump 11 pressurizes the sealing liquid by the gear pump 11 and forcibly feeds it to the rotary sliding part of the compressor 1, thereby utilizing the discharge pressure of the compressor body. The supply of the sealing liquid is more secure than that, and the rotational sliding portion of the compressor is less likely to be a poor seal or a poor cooling. However, since the gear pump 1 must be incorporated separately, the compressor 1 is large as a whole. Moreover, there also existed a problem that the noise and vibration by gear meshing were also large.

This problem also applies to a rotary vane type vacuum pump that sucks and compresses and discharges gas by the rotation of the rotor holding the vanes.

The main object of the present invention is a rotary vane type which can be reliably supplied with a sealant without rotating a gear pump, has a low noise and vibration, and does not cause a decrease in volumetric efficiency due to leakage. To provide a fluid pressure device.

Another object of the present invention is to provide a reasonable design of the above-described fluid pressure device by combining a rotor for compressing gas and a pump function for pumping the sealant into the cylinder chamber.

In order to achieve the above object, according to the present invention, a rotor having a plurality of vanes moving smoothly in the radial direction is installed in a cylinder chamber formed in a case, and the rotor is freely disposed to rotate the rotor and the vanes. A rotary vane type fluid pressure device configured to suck gas from a suction port into a compression chamber, and to compress and discharge gas from a discharge port, wherein the cylinder chamber sucks and compresses gas by the rotor; It is provided that the pump liquid is partitioned into a pump chamber which sucks the sealant from the suction port and pressurizes it to discharge from the discharge port toward the rotary sliding portion.

According to the specific configuration state of this invention, the said cylinder chamber is substantially elliptical-shaped, and the said compression chamber and pump chamber are formed between the both ends of the ellipse in the constriction direction, and a rotor. In this case, it is preferable that the above-mentioned rotor is provided at a position biased to the pump chamber side in the cylinder chamber to one side, so that the volume of the pump chamber is smaller than that of the compression chamber.

According to one embodiment of the present invention, a separating means containing at least one of a filter or a cooler for separating the sealing liquid mixed into the compressor body is provided in the case.

The fluid pressure device of the present invention having the above-described configuration forms a pump chamber in a part of the cylinder chamber, sucks the sealing liquid into the pump chamber by rotation of the vane, pressurizes it, and feeds it to a desired place. Therefore, it is possible to effectively supply the sealant to a desired place by effectively using the rotor, vane and cylinder chamber for gas compression as a pump means for pumping the sealant without incorporating the conventional gear pump separately. As a result, leakage of gas can be reliably prevented, and a decrease in volumetric efficiency can be prevented.

In addition, by omitting the above-described gear pump, the compressor can be miniaturized as a whole, and the noise and vibration caused by the meshing of the gears can be eliminated, resulting in a low noise and low vibration compressor.

In addition, the rotor, the vane and the cylinder chamber also serve as a compression means for the gas and a pump means for pumping the sealant, so that the hydraulic pressure device can be made simple and reasonable in design.

Moreover, since the sealing liquid is actively pressurized and pumped by the vane, the flow of the sealing liquid is hardly influenced by the installation posture of the fluid pressure device. The unit can be installed.

1 and 2 show an example of a rotary vane type fluid pressure device according to the present invention, which shows a compressor for compressing a gas such as air, and the compressor 21 is hermetically connected to the case 22 by appropriate means. And a prime mover 25 (in the illustrated example, an electric motor).

The case 22 is composed of a first member 22a and a second member 22b that are hermetically coupled, and a cylinder chamber 23 is formed between these members 22a and 22b. This cylinder chamber 23 has a pseudo-ellipse shape, and the specific shape is that both halves of the major axis direction of the ellipse have a substantially semi-circular shape, and those semi-circular parts are connected to a circular arc-shaped part having a large curvature radius. .

In the cylinder chamber 23, a circular rotor 27 is disposed so as to be freely rotated. This rotor 27 is connected with the shaft 28 of the prime mover 25 by the key 27a, and is made to drive-drive rotation by this prime mover 25. As shown in FIG. On the outer circumference of the rotor 27, grooves with a plurality of vanes (two in the illustrated example) are radially formed at equal intervals in the circumferential direction, and vanes 29 are respectively provided in the grooves to which the vanes are attached. It is inserted so as to be movable in the radial direction. The rotor 27 is disposed in a position slightly biased to one side along the long axis of the ellipse in the cylinder chamber 23, whereby the volume for the cylinder chamber 23 to compress the gas is provided. A large compression chamber 30 and a pump chamber 31 with a small volume for conveying the sealing liquid are partitioned.

When the minimum allowable length of L is larger than the maximum allowable length of L so that the above-mentioned axial length L of the rotor 27 and the depth L of the cylinder chamber 23 can be fitted to the optimum dimensional accuracy. It is set in the length relationship therewith except for haptic.

Specifically, the allowable length of l is set to a length relation (gap feeling) slightly smaller than the minimum allowable length of L, or is set to a length relationship (middle fitting) which does not belong to any of the above length relationships (feeling and gap feeling), Among them, the length relation between the intermediate fittings is preferable. As a result, the above-described rotor chamber 27 maintains a small gap between the axially opposite side surfaces, the bottom surface of the cylinder chamber 23, and the inner surface of the second member 22b, respectively. 23) Rotation is freely arranged and mounted.

The vanes 29 and 29 are wall surfaces of the cylinder chamber 23 by means of adding a pressure such as the pressure of the sealant flowing into the attachment groove of the vane or a coil spring (not shown) installed in the groove. Is pressed towards.

In addition, the vanes described above are not limited to the illustrated two, and three or more vanes may be provided at equal intervals in the circumferential direction.

In the first portion 22a of the case 22, a suction port 33 for sucking gas, such as air, is provided at the inlet side of the compression chamber 30, and a vane (outside) of the compression chamber 30 is provided. A discharge port 34 for discharging the gas compressed at 29 and 29 is provided, and the discharge port 34 is connected to the discharge port 38 on the second member 22b by sandwiching the valve chamber 34a. Doing. In the valve chamber 34a, a check valve 37 for preventing the back flow of compressed gas is provided with a force applied to the spring 37a.

Further, the first member 22a of the case 22 is provided with a suction port 35 for suctioning a sealant made of water or oil toward the inlet side of the pump chamber 31 and the outlet of the pump chamber 31. A discharge port 36 for discharging the sealing liquid pressurized by the vanes 29 and 29 to the side is provided, and the discharge port 36 has a discharge port 42 on the second member 22b with the valve chamber 36a interposed therebetween. It is connected with. In the valve chamber 36a, the check valve 37 which prevents the backflow of the pressurized sealing liquid is provided with the force added to the spring 37a.

The port 27 between the discharge port 34 and the suction port 35 and between the discharge port 36 and the suction port 33, in other words, between the compression chamber 30 and the pump chamber 31. It is confidentially partitioned.

The suction port 33 of the gas communicates with the outside air, and the discharge port 38 of the compressor body is connected to the tank 40 by a conduit 39. In addition, the liquid intake port 35 of the sealing liquid is connected to the inner bottom of the tank 40 by the conduit 41, and the discharge port 42 of the sealing liquid is connected to the case 22 by the conduit 43. It is connected to the supply ports 44 and 45 formed from the plate 24, respectively. Said supply port 44 supplies a sealing liquid to the sliding surface between the shaft 28 and the case 22 by the flow path 46 formed by the case 22, The supply port 45 is a 2nd The sealing liquid is supplied to the cylinder chamber 23 side surface of the member 22a.

In addition, although description by the illustration was abbreviate | omitted, each said port 42,44,45 is provided in the case 22, and each of these ports is provided outside the compressor 21, and the said pipe line 43 is carried out. Instead of connecting in, the flow path for supplying the pressurized sealant to a place where sealing and lubrication or cooling is required may be formed directly inside the case 22. In this case, there is no trouble of external piping. The compressor 21 can be further miniaturized.

In addition, of course, when compressing gas other than air, the suction port 33 is connected with the gas source.

In addition, reference numeral 48 in FIG. 1 denotes a spring seat for the spring 37a which adds the force of the check valve 37, and FIG. 2 shows that the median protection 49 between the case 22 and the prime mover 25 is used. Sealing to seal.

In the compressor of the first embodiment described above, when the rotor 27 is rotated in the direction of the arrow in FIG. 1 by the oscillator 25, the vanes 29 and 29 protrude from the attachment grooves of the vanes by centrifugal force or the like. The tip is rotated together with the rotor 27 in a state of being pressed against the wall surface of the cylinder chamber 23. As a result, gas is sucked into the compression chamber 30 from the suction port 33 and is compressed by the rotation of the vanes 29. In the compression chamber 30, the gas compressed in the vanes 29 flows out from the discharge port 34, and supplies the check valve 37 with the force applied to the spring 37a to reach the discharge port 38. In this case, the pipe 39 is stored in the tank 40. The compressor body stored in the tank 40 is supplied to a suitable fluid pressure device, not shown.

In addition, a small amount of the sealing liquid supplied into the tank 40 before operation of the compressor 21 is sucked into the pump chamber 31 from the suction port 35 through the conduit 41 and the pump chamber 31. In the vanes (29). The pressurized sealing liquid is supplied to the supply ports 44 and 45 through the conduit 43 by supplying the check valve 37 with the force added to the spring 37a and discharging it to the discharge port 42. The compression chamber 30 is cooled while sealing and lubricating around the shaft 28 and the vanes 29 and 29.

The sealant, which seals and lubricates or cools the vanes 29 and 29, is introduced into the tank 40 with most of the sealant mixed with the compressed gas, and in the tank 40 due to the specific gravity difference. It is separated from the gas and stored at the bottom of the tank 40. The stored sealing liquid is sucked into the pump chamber 31 again from the suction port 35. In addition, a part of the sealing liquid circulates in the cylinder chamber 23 in accordance with the rotation of the rotor 27 and the vanes 29, and returns to the inlet side of the pump chamber 31 to be pressurized.

In this case, the separation function of the sealing liquid and gas can be further improved by incorporating a well-known oil separation filter or a cooler for cooling the discharged gas, or incorporating both of them.

In addition, although not shown, the case 22 may incorporate gas and liquid separation means such as an oil separation filter or a cooler into the case 22, and the compressor body may be supplied to the tank 40 through the separation means. The pipe 41 between the tank 40 and the suction port 35 can be omitted.

The compressor 21 having the above-described configuration divides the cylinder chamber 23 into the compression chamber 30 and the pump chamber 31 by the rotor 27, and vanes the sealing liquid sucked into the pump chamber 31. It is pressurized by 29) and supplied to the rotary sliding part which is the place where the seal | sticker and lubrication of the compressor 21 are needed, and a sealant can be reliably supplied to a desired place, without separately incorporating a gear pump like conventionally. Thereby, the fall of the volumetric efficiency by the leak of a gas can be reliably prevented by this. In addition, by omitting the above-described gear pump, the compressor can be miniaturized as a whole, and the noise and vibration caused by the meshing of the gears can be eliminated, resulting in a low noise and low vibration compressor.

In addition, since the sealing liquid is pressurized and pumped by the pump chamber 31, it is different from supplying the sealing liquid using the discharge pressure of the compressor body, and the pressure of the sealing liquid is high, which makes the sealing and lubrication reliable. And internal leakage can be reduced as much as possible.

In addition, since the amount of supply of the sealant is lower than that of the gas compressed in the compression chamber 30, the volume of the pump chamber 31 for pressurizing the sealant can be made smaller than that of the compression chamber 30. Since the chamber 23 is a pseudo-ellipse and the pump chamber 31 is installed in a part of the chamber 23, the size of the compressor 21 as a whole and the compression thereof can be obtained even when such a pump chamber 31 is provided in the compressor 21. The volume of the yarn hardly changes as compared with the absence of the pump chamber 31 described above.

3 and 4 show a vacuum pump as another example of the rotary vane type fluid pressure device according to the present invention. This vacuum pump 51 has a structure substantially the same as that of the compressor 21 of the first embodiment described above. The difference is that the suction port 33 is connected to the vacuum chamber 52 in the vacuum compressor. The discharge port 38 is opened to the atmosphere, and the suction port 35 is connected to the storage tank 55 of the sealing liquid.

In this vacuum pump 51, the gas in the vacuum chamber 52 is sucked from the suction port 33 and discharged to the outside from the discharge port 38, and the sealing liquid is transferred from the storage tank 55 to the suction port 35. Is inhaled.

Since the structure and operation | movement other than the above in the said vacuum pump 51 are the same as the said compressor 21, the same code | symbol is attached | subjected to the same principal place of drawing, and detailed description is abbreviate | omitted.

As described above, the fluid pressure device of the present invention forms a pump chamber in a part of the cylinder chamber, sucks the sealing liquid into the pump chamber by rotation of the vane, and pressurizes it to be pumped to a desired place. The sealing liquid can be reliably supplied to a desired place without incorporating the same gear pump separately, whereby leaking of the gas can be reliably prevented and a decrease in volumetric efficiency can be prevented.

In addition, by omitting the above-described gear pump, the compressor can be miniaturized as a whole, and the noise and vibration caused by the meshing of the gears can be eliminated, resulting in a low noise and low vibration compressor.

Moreover, since the sealing liquid is actively pressurized and supplied by the pump, the flow of the sealing liquid is hardly influenced by the installation posture of the fluid pressure device. Can be installed.

Claims (3)

Rotating vane type fluid pressure in which a rotor (27) having a plurality of vanes (29, 29) moving smoothly in a radial direction and disposed smoothly in a cylinder chamber (23) formed in a case (22) is disposed freely for rotation. In the apparatus, the cylinder chamber 23 is elliptical in shape, and gas is sucked from the suction port 33 by the rotation of the rotor 27 between the both ends of the long axis of the ellipse and the rotor 27. Suction chamber, the compression chamber 30 which compresses by the vanes 29 and 29, and discharges it to the discharge port 38, and the sealing liquid are sucked from the suction port 35, and pressurized by the vanes 29 and 29 A rotary vane type fluid pressure device, characterized in that divided into a pump chamber 31 for discharging toward the rotary sliding portion from the discharge port (42). 2. The pump chamber 31 according to claim 1, wherein the rotor 27 is provided at a position biased to one side on the pump chamber 31 side in the cylinder chamber 23, so that the volume of the pump chamber 31 is reduced. Rotating vane type fluid pressure device, characterized in that smaller than the volume. The rotating vane type according to claim 1 or 3, wherein the case (22) is provided with separating means containing one or more filters or coolers for separating the sealing liquid mixed into the compressor body. Fluid pressure equipment.