JPS6120315Y2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vane-type compressor used to compress refrigerant gas and the like, and particularly relates to an improvement in the structure of the vane.

BACKGROUND OF THE INVENTION Examples of conventional vane type compressors include those shown in FIGS. 1 to 4, for example. In FIG. 1, a cam ring 2 is disposed within a case 1, and a rotor 5 is disposed within a chamber constituted by the inner wall of the cam ring 2 and the inner walls of side wall members 3 and 4 attached to both sides of the cam ring 2. A plurality of grooves 6 are formed in the radial direction of the rotor 5, and vanes 7 are fitted into the grooves 6. When the drive shaft 8 to which the rotor 5 is fixed is rotated, the rotor 5 is rotated. 5 is rotated, and this rotation causes the cam ring 2 to rotate.
, the inner walls of the side wall members 3 and 4, and the adjacent vanes 7 expand or contract, and after suction, the space is pressurized, and the pressurized fluid flows through a pump flow (not shown). The cam ring 2 via the outlet
Then, it temporarily accumulates in the discharge pressure chamber 10 formed between the rear side wall member 4 and the case 1, and is discharged from the discharge port 16.

In such a conventional vane type compressor, the vane 7 is formed into a substantially rectangular thin flat plate as shown in FIG. 2, and when it is slidably inserted into the groove 6 of the rotor 5, , side wall members 3 arranged on both sides of the cam ring 2, as shown in FIG.
Both side end surfaces are in sliding contact with the inner surface of the rotor 5 to seal the front and rear chambers of the vane 7, which are partitioned by the portion of the vane 7 that protrudes toward the outer circumferential side of the rotor 5.

However, in such a conventional vane type compressor, the vane 7 is simply formed into a thin flat plate, and the side end surfaces of the portion of the vane 7 that protrudes toward the outer circumferential side of the rotor 5 and the side wall members 3 and 4 are connected to each other. Since the length L in the rotational direction of the rotor 5 of the sealing allowance between the inner surface and the inner surface is small, as shown by the two-dot chain arrow in FIG. This has the disadvantage that leakage from the compressor to the suction chamber tends to occur, deteriorating the volumetric efficiency and compression efficiency.

An object of the present invention is to eliminate the above-mentioned conventional drawbacks and provide a vane type compressor with good volumetric efficiency and compression efficiency.

In the present invention, enlarged side wall portions are formed at both end portions of the vane over the entire longitudinal direction thereof, and the sealing margin between the both end surfaces of the portion of the vane that protrudes toward the rotor outer circumferential side and the inner circumferential wall of the side wall member is reduced. The rotor is characterized by an increased length in the rotational direction.

An embodiment of the present invention will be described with reference to FIGS. 4 to 7.

4 to 7, a vane type compressor of this invention is shown, in which a cylindrical cover 1a is fixed to a front head 1b, forming a case 1 as a whole. Case 1 arranged horizontally
A cam ring 2 having an endless cam surface 2a with an elliptical cross section is arranged inside. A pair of side wall members 3 and 4 are attached to both ends of the cam ring 2 to form a pump housing together with the cam ring 2. A discharge pressure chamber 10 is formed between the rear side wall member 4 and the cover 1a. A rotor 5 is disposed in a chamber 13 defined in the pump housing by the cam ring 2 and the inner walls of the side wall members 3 and 4, and the rotor 5 has a rotating shaft 8 passing through the front head 1b and the front side wall member 3. are fitted into and fixed to the thrust bearing 2, respectively.
It is in sliding contact with the side wall members 3 and 4 via 7 and 28. A plurality of grooves 61 opening approximately in the radial direction are formed at equal intervals in the circumferential direction on the circumferential surface of the rotor 5.
Vanes 71 are fitted into these grooves 61 so as to be movable in the radial direction. Further, as shown in FIG. 5, a pump inlet 14 and an outlet 15 are formed on the peripheral wall of the cam ring 2, and communicate with the compressor inlet 9 and the discharge outlet 16 via a discharge pressure chamber 10, respectively. are doing. A fluid guide plate 2 is provided on the peripheral wall of the cam ring 2.
9 and a discharge valve assembly 30 are attached. In addition, a cover 1a forming the upper wall of the discharge pressure chamber 10
A lubricating oil inlet/outlet 24 is formed in the portion.

Incidentally, between the cam ring 2 and the case 1, rod-shaped seal members 12 made of rubber are disposed at, for example, four locations to maintain an airtight state.

Here, when the rotating shaft 8 connected to the drive shaft of a prime mover (not shown) rotates, the rotor 5 rotates, and the centrifugal force generated by this rotation pushes the vanes 71 supported on the rotor 5 outward in the radial direction.
While being pressed against the endless cam surface 2a of the cam ring 2, it slides on the cam surface 2a.

Each time each vane 71 passes through the inlet 14 formed in the cam ring 2, fluid is sucked into the chamber 13 defined by the vane 71, the following vane 71, the cam ring 2, and the rotor 5. . In the suction stroke, the volume of the chamber 13 changes from the minimum to the maximum to suck in fluid, and in the discharge stroke, the volume changes from the maximum to the minimum and pressurized fluid is discharged from the outlet 15,
This action is repeated to produce a pump action.

In this vane type compressor, the vane 71 is formed into a short substantially shaped steel shape as shown in FIG. That is, the main body 72 of the vane 71 has a rectangular flat plate similar to the conventional vane 7 shown in FIG. are integrally formed in a direction perpendicular to the longitudinal direction (left-right direction) of the main body portion 72. The center portion of each enlarged side wall member 73 is located at the end corresponding to the main body portion 72, the width _L1 thereof is constant over the entire length, and the shape of the tip edge is curved. It has a radius of curvature that does not interfere with the endless cam surface 2a over the entire range.

On the other hand, the groove 61 into which the vane 71 is inserted is formed in a groove shape as shown in FIG. 7 so as to correspond to the vane 71. That is, the groove 61
The main body part 62 has an elongated rectangular cross section similar to the conventional groove 6 shown in FIG. They are each formed in a perpendicular direction. Each enlarged groove portion 63 has a central portion that is connected to the main body portion 6.
2, and its width is approximately equal to the width of the side wall portion 73 of the vane over its entire length. Each enlarged groove portion 62 is formed at both ends of the rotor 5 and is open to the outer circumferential surface of the corresponding end of the rotor 5 .

The vane 71 is slidably inserted into the groove 61. That is, the main body portion 72 of the vane 71 is fitted into the main body portion 62 of the groove 61, and both enlarged side wall portions 73 of the vane 71 are fitted into the enlarged groove portion 63 of the groove 61, respectively. In this state, the outer surfaces of both enlarged side wall portions 73 of the vane 71 are in sliding contact with the inner surfaces of the opposing side wall members 3 and 4, respectively. Since both enlarged side wall portions 73 have sufficient width, the vane 7
The rotor 5 rotational direction length L ₁ of the sealing margin between both end surfaces of the portion of the rotor 5 protruding toward the outer circumferential side of No. 1 and the inner surfaces of the side wall members 3 and 4 is larger than that of the conventional vane 7. The amount of leakage is extremely small because the refrigerant is difficult to leak from the compressor to the suction chamber or from the front-stage compression chamber to the rear-stage compression chamber through this. Therefore, this vane type compressor has improved volumetric efficiency and compression efficiency, and the improved volumetric efficiency allows the vane type compressor to be made smaller. The amount of work can be reduced and labor can be saved.

As explained above, according to the present invention, enlarged side wall portions are formed at both ends of the vane over the entire longitudinal direction thereof, and both enlarged side wall portions are brought into sliding contact with the inner surfaces of the front and rear side wall members, respectively. As a result, the length of the sealing distance in the rotor rotational direction between the end surfaces of the portion of the vane that protrudes toward the rotor outer circumferential side and the inner surfaces of the front and rear side wall members becomes longer, and leakage from between the vane and the side wall member increases. can be prevented. Also,
Since the distal end edge of the enlarged side wall portion is curved, the enlarged side wall portion does not interfere with the cam surface of the cam ring.

[Brief explanation of the drawing]

Fig. 1 is a cross-sectional view of a conventional vane compressor, Fig. 2 is a perspective view showing a conventional vane, Fig. 3 is a partial sectional view of a rotor equipped with vanes, and Fig. 4 is an implementation of the present invention. A vertical sectional view of a vane type compressor showing an example, FIG. 5 is a sectional view taken along the - line of FIG. 4, and FIG. 6 is a perspective view showing a vane in an embodiment of the present invention.
FIG. 7 is a sectional view taken along the - line in FIG. 4. 1...Case, 2...Cam ring, 3, 4...
Side wall member, 5... Rotor, 8... Rotating shaft, 9...
Suction port, 10...Discharge pressure chamber, 61...Groove, 63...
...Enlarged groove portion, 71...Vane, 73...Enlarged side wall portion.

Claims (1)

[Scope of utility model registration request] a cam ring having an endless cam surface; side wall members disposed on both sides of the cam ring; a rotor rotating and disposed within a chamber formed by an inner circumferential wall of the cam ring and inner walls of the both side wall members; A vane type compressor comprising a plurality of grooves formed in the radial direction on the circumferential surface of a rotor, and a vane that is fitted into each of these grooves so as to be able to move forward and backward, and whose tip can slide into contact with the inner circumferential wall of the cam ring. , forming enlarged groove portions in which the groove width is enlarged along the circumferential direction of the rotor at both ends of each of the grooves on both end faces of the rotor; Enlarged side wall portions extending in a direction perpendicular to the advancing and retreating direction of the vane are respectively formed, and these enlarged side wall portions are slidably fitted into the enlarged groove portion, and the outer surfaces of these enlarged side wall portions are The cam ring is disposed in sliding contact with the inner surfaces of both side wall members, and the distal end edge of the enlarged side wall portion is curved with a curvature that does not interfere with the endless cam surface of the cam ring over the entire range. Vane type compressor.