JPS61268893A - Rotating vane compressor - Google Patents

Abstract

PURPOSE:To decrease viscous resistance of the side end face of a vane and the inner surface of a side housing, so as to prevent seizure and wear between them by engraving concavities into the inner surface of the side housing which faces the side end face of the vane inserted in a rotor with free sliding movement. CONSTITUTION:A rotary compressor is equipped with a rotor 10 rotating at an eccentric position inside a center housing 22, a vane 16 inserted in the rotor 10, with free sliding movement, and an inlet opening 52 and discharge opening 42 provided through a rear side housing 23. And a large number of dimple-like concavities 35 are formed at the part facing the vane 16 on the inner surface of the rear side housing 23, radiately from the axial center of the rotor 10. This constitution creates turbulent flow of fluid filling spaces between both end sides of the rotor 10 and the inner surface of both side housings 21, 23 by means of the cancavities 35, thus having smaller viscous resistance of fluid than that by laminar flow. Therefore, seizure and wear between the vane 16 and both side housings 21, 23 can be avoided.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to improvements in vane rotary compressors used in superchargers of internal combustion engines and the like.

[Prior art] Vane rotary compressors used in internal combustion engine turbochargers, etc. are operated over a very wide range of rotation speeds, but at high speeds, seizure and wear on the rotor or vane end faces and the inner surface of the side housing can be a problem. become.

In order to improve the sealing effect while preventing direct contact between the rotor and the side housing, a groove is provided in either or both of the end face of the rotor and the part of the inner surface of the side housing that faces the rotor. issue,
Japanese Patent Application Publication No. 56-217789, Utility Model Application No. 13239-1982
Although it is disclosed in No. 3, the grooves are formed only on the inner surface of the side housing facing the rotor, so direct contact between the rotor and the side housing is prevented, but the vanes are not grooved. Since the inner surface of the side housing also slides, it is impossible to prevent seizure and wear caused by direct contact between the vane side end surface and the inner surface of the side housing.

[Problems to be Solved by the Invention] The present invention has been made to solve the above-mentioned problems, and its purpose is to facilitate the rotation of the rotor at high speeds and to improve the relationship between the vanes and the side housing. An object of the present invention is to provide a vane rotary compressor in which seizure and wear between the vanes are prevented.

[Means for Solving the Problems] In order to achieve the above object, the features of the present invention include the following:
A large number of recesses are formed on the inner surface of the side housing in a portion that is in contact with the vane side end surface to reduce the viscous resistance of the fluid between the side housing inner surface and the vane side end surface, and also to generate dynamic pressure between the vane side end surface and the side housing. This is because it prevents direct contact with the inner surface.

The recess may be provided in both the front side housing and the rear side housing, but since the vane tends to be closer to the rear side housing where the inlet and outlet are provided,
A recess is always formed on at least the inner surface of the rear side housing. The recesses are formed by electrolytic erosion (etching), and the depth of each recess is 0.005 to 0.05 mm, and the maximum width is smaller than the width of the vane side end face, so that the front and rear working chambers of the vane are It is desirable to prevent air from passing through the recesses, and it is preferable that the recesses are arranged regularly, especially radially, along the side end surface of the vane. Here, the recesses are defined as elongated grooves or Including dimple-like depressions.

[Function] When the rotor rotates at high speed, the resistance of the fluid between the rotor side end face and the inner surface of the side housing increases, but many recesses are formed in the inner surface of the side housing that faces the vane that includes the rotor facing part. Because of this, turbulent flow occurs and the viscous resistance of the fluid is smaller than in laminar flow. Therefore, there is no possibility that high-speed rotation of the rotor will be hindered by the viscous resistance of the fluid on the side surface of the rotor.

Furthermore, although the vanes move in and out in the radial direction, they also swing in the axial direction, so that their side end surfaces protrude from the side end surfaces of the rotor and approach either the front or rear side housing.

In particular, it tends to be closer to the rear side housing where the inlet and outlet are located. When the vane moves closer, the gap between the end face of the vane and the inner surface of the side housing on the closer side becomes extremely thin, but since there are many recesses cut into the inner surface of the side housing that faces the vane, dynamic pressure is generated. Prevents direct contact between the vane end face and the inner surface of the side housing.

[Example] As shown in FIGS. 1 and 2, which explain a compressor of the present invention based on an example shown in the drawings, a rotor 10 and a rotating shaft 1
4 is integrally formed, and a pulley 20 is attached to one end of the rotating shaft 14 to receive rotational transmission from the engine. Rotor 1
A vane 16 is fitted into the rotor 0 so as to be freely removable in the radial direction, and working chambers 43 and 53 are formed between the vane 16, the rotor 10, and the center housing 22. Suction side working chamber 53
Gas is sucked from the suction chamber 51 through the suction port 52, and after being compressed in the working chamber 43 on the compression side, it is discharged from the discharge port 42 to the discharge chamber 41 via the discharge valve 60. The center housing 22 is sandwiched between front and rear side housings 21 and 23, and a rear cover 24 in which a suction chamber 51 and a discharge chamber 41 are provided is attached to the rear side housing 23. A mechanical seal 11 and a bearing 13 are assembled into a front side housing 21, and a preload is applied to the bearing 13 in the axial direction via a collar 12 to regulate the position of the rotor IO. Therefore, the axial position of the rotor 1O, that is, the minute clearance between both ends of the rotor 10 and the front and rear side housings 21, 23 is kept constant. Center housing 22.
The front and rear side housings 21, 23 are made of aluminum alloy, the rotor is made of cast iron, and the vane 18 is made of carbon.

As shown in FIG. 3, a large number of dimple-shaped recesses 35 are formed on the inner surface of the rear side housing 23 in a portion facing the vanes.
are arranged radially from the rotor axis. The parts without recesses are the suction port 52, the discharge port 42, and the central vane bottom ventilation groove 58.
It is an annular part containing. After a recess 35 is formed on the inner surface of the rear side housing by electrolytic etching, it is anodized.

Although not shown, a recess is provided on the inner surface of the front side housing as well as on the rear side housing. In this case, since there is no suction port and no discharge port, a recess is also carved in that portion.

The compressor of this example was operated at high speed, for example 6000 r.

When rotating at speeds p and m, the fluid between both end faces of the rotor 10 and the inner surfaces of both side housings 21.23 produces turbulent flow due to the recesses 35, so the viscous resistance of the fluid is smaller than in a laminar flow state, and the rotor There is no problem with high-speed rotation. Furthermore, even if the vane 18 moves toward the rear side housing side, or even if the vane 18 moves toward the front side housing side due to the reaction, the dynamic pressure effect of the recess 35 on each inner surface prevents direct contact between the vane side end surface and the inner surface of the side housing. Therefore, seizure and wear of the vane and side housing are effectively prevented.
is prevented.

FIG. 4 shows the results of a comparative test showing the relationship between the wear of the recess and the vane, and the test was conducted using a compressor with a pump capacity (displacement amount) of 900 cc, which is the same as the embodiment shown in FIGS. 1 and 2. For comparison, three types of compressor front and rear side housings were prepared: one without a recess, one with a recess, and one with an anodized finish after the recess was carved. The vane was operated for 100 hours at a discharge pressure of 1.0 Kg/crn" (gauge), and the wear amount (mm) of the vane was measured. From this figure, the amount of wear of the vane was reduced by more than half when the recess was carved. It can be clearly seen that the wear is further reduced by providing an anodic oxide film on top of the anodic oxide film.

[Effects of the Invention] As described above, in the compressor of the present invention, a large number of recesses are carved in the inner surface of the side housing where the end surface on the vane side is in contact with the end surface, and the recesses are formed between the end surface on the rotor side including the vane and the inner surface of the side housing. This not only reduces viscous resistance by making the fluid a turbulent state, but also generates dynamic pressure when the vane approaches the side housing, thereby preventing direct contact between the vane side end surface and the inner surface of the side housing. Therefore, the rotor rotates smoothly even at high speeds, and seizure and wear of the vanes and side housing are prevented, which is an excellent effect.

[Brief Description of the Drawings] Figures 1 and 2 are a vertical cross-sectional view and a cross-sectional view of a compressor according to an embodiment of the present invention, Figure 11f53 is an enlarged internal view of the rear side housing, and Figure 4 is an internal view of the side housing. 3 is a graph showing the relationship between the concave portion and the wear amount of the vane. In the figure, reference numeral 10 is a rotor, 16 is a bevel, 21 is a front side housing, 22 is a center housing, 23 is a rear side housing, and 35 is a recess. Applicant Nippon Piston Ring Co., Ltd.

Claims (1)

[Scope of Claims] 1) A center housing, front and rear side housings that sandwich the center housing, a rotor that rotates at an eccentric position within the center housing, and a vane fitted into the rotor so as to be freely removable and removable. The compressor comprises an inlet port and a discharge port provided in the rear side housing, wherein a recess is carved in the inner surface portions of the front and rear side housings facing the side end surfaces of the vanes, or at least in the inner surface portion of the rear side housing. A vane rotary compressor, characterized in that viscous resistance of fluid between the side end surface of the vane and the inner surface portion is reduced. 2) The vane rotary compressor according to claim 1, wherein the width of each recess is narrower than the width of the side end surface of the vane. 3) The vane rotary compressor according to claim 1 or 2, wherein the recesses are regularly arranged. 4) The vane rotary compressor according to any one of claims 1 to 3, characterized in that an anodized film is formed on the inner surface portion in which the recesses are formed.