JPS60132089A - Rotary compressor - Google Patents

Abstract

PURPOSE:To force a vane to fly out and improve the starting characteristic of a sliding vane compressor, by providing a pin, which can be extended and retracted by a spring, in a side surface of the vane and a groove, with which the pin engages, on one side of a side plate. CONSTITUTION:The center Og of a guide groove 21 provided on a side plate 4 is placed in a position between the center Or of a rotor 5 and the internal diametric center Oc of a cylinder 1. Then a vane 7 provides in its side surface a hole 23 in which a pin 22, extensibly and retractably engaged by a compression spring 24, is provided. Accordingly, a compressor, even when it is started, ensures the vane to smoothly act by forcing the vane to be extended and retracted by the guide groove.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to improving the restartability of a sliding vane rotary compressor used in car coolers and the like.

Conventional Structure and Problems Before explaining the present invention, a two-page explanation will be given of a sliding vane type rotary compressor for a car cooler.

As shown in FIGS. 1 and 2, a general sliding vane compressor includes a cylinder 1 having a cylindrical space inside, and a blade chamber 2 fixed to both sides of the cylinder 1, which is the internal space of the cylinder 1. It is composed of a rear side plate 3 and a front side plate 4 that are sealed on the side surfaces, a rotor 6 that is eccentrically arranged inside the cylinder 1, and a bay 77 that is slidably engaged with a slit 6 provided in the rotor 5. . 8 is a suction hole formed in the cylinder 1, 9 is a discharge hole also formed in the cylinder 1, 10 is a reed valve that prevents the compressed gas discharged from the discharge hole 9 from flowing back, and 11 is a reed valve 1o. It is a protective presser plate. The vanes 7 are projected outward by centrifugal force as the rotor 6 rotates, and their tips slide on the inner wall surface of the cylinder 1, compressing gas. Furthermore, as shown in FIGS. 3 and 4, a ring-shaped oil groove 12 is provided in the rear plate 3 at a position corresponding to the rear end of the slit 6 on the side surface of the rotor 5. The oil 14 is filled into the oil groove 12 through the nozzle 16 and the oil hole 162"-:' by its own discharge pressure, and the rear end surface of the vane γ is pressurized from the rear end of the slit 6, so that the tip of the vane 7 is connected to the rotor. 5 and the adjacent portion 17 of the cylinder 1, a part of the oil groove 12 is blocked in order to seal the oil chamber at the rear end of the vane 7 and prevent jumping of the vane 77 due to overcompression.

However, the above configuration has the following problems. Normally, the vane 7 is often made of a lightweight material in order to reduce sliding resistance during high-speed rotation. Therefore, sufficient centrifugal force cannot be obtained in a low speed rotation range such as when the engine is idling, and the viscous force of the oil existing in the gap between the vane 7 and the slit 6 often prevents the bee 77 from being ejected reliably. . Furthermore, in the method of pushing the vanes 7 using the discharge pressure described above, there is almost no compression difference when the compressor is started, and on the contrary, negative pressure is generated when the vanes 77 pop out due to centrifugal force, which further prevents the vanes 77 from popping out. Therefore, when the compressor is started (when it is started after being stopped for a long time), the compressor function provided by the vanes 7 cannot be obtained. .

OBJECTS OF THE INVENTION The present invention eliminates the drawbacks of the conventional sliding vane type rotary compressor, and aims to ensure startability by forcibly protruding the vanes.

Structure of the Invention The present invention is a sliding vane type rotary compressor, which consists of a guide groove provided in an annular shape on the rotor contact surface of the front plate, and a pin housed in a hole on the side surface of the vane so as to be able to move in and out by means of a spring. The pin then engages with the guide groove and pushes the vane toward the outer circumference along the slit, making it possible to reliably start compression even at startup, thereby improving startup performance.

DESCRIPTION OF EMBODIMENTS The present invention will be described below with reference to FIGS. 6 and 7 showing one embodiment thereof.

First, in FIG. 6 and FIG.
It is between r and the cylinder's inner diameter center 0c and 4 pcm. Reference numeral 22 denotes a pin that is removably engaged by a hole 23 provided in the side surface of the vane 7 and a compression spring 24 inserted therein. Further, the vanes 7 are slidably engaged with the slits 6 provided in the rotor 6 as in the conventional example, and are slidably rotated along the inner surface of the cylinder 1 as the rotor 5 rotates.

As shown in FIG. 6, the guide groove 21 has an inclination θ with respect to the plane of the front plate 4, and a part of its circumference coincides with the blocking position of the oil groove 12 of the rear plate 3 of the conventional example. Does not form grooves. That is, the effect of preventing jumping when the vane 7 passes through the rotor 6 and the adjacent portion 17 of the cylinder 1 is achieved by trapping oil at the rear end of the vane 7.

The inclination θ of the guide groove 21 is still such that the pin 22 is in the guide groove 2.
This is also necessary from the point of view of smooth entry into and exit from the guide groove 21 from the non-formed portion of the guide groove 21.

In order to obtain the same effect, most of the guide groove 21 may be made to have a constant depth, and only the both ends required for entry and escape may be made smooth, but it is easier to provide the slope θ around the entire circumference as described above from the viewpoint of processing. It is.

Page 6 Next, in FIG. 7, the position of the pin 22 provided on the vane 77 is outside (from the shortest distance position from the center Or of the rotor 6) when the vane is fully inside the slit 6 of the rotor 6. The side where vane 7 comes out) is better. and rotor 6
The locus 26 of the pin 22 drawn by the movement of the vane 7 in and out as it rotates is not a perfect circle, but roughly elliptical.
It is desirable that the shape of the guide groove 21 (especially the shape on the inner diameter side) corresponds to the locus 25 of the pin 22. However, from the standpoint of actual machining, a perfect circle 26 that approximates the locus 26 may also be used.

In other words, the guide groove 21 has radii Ri and Ro, which are the sum of the radius of the pin 220 and the radius of the pin 220 on the inner diameter side having the minimum radius and the outer diameter side having the maximum radius of the locus 26 of the pin 22, respectively.

At this time, the center oq of the guide groove 21 should be selected so that the outer diameter side of the guide groove 21 does not come out from the outer diameter of the rotor 6 and the inner diameter side does not interfere with the rotor bearing hole. Necessary to prevent leakage of compressed gas.

Therefore, the center 0q of the guide groove 21 is defined as the position between the rotation center Or of the rotor 5 and the inner diameter center 0c of the cylinder 61'--1, where the eccentricity with respect to the rotor wheel center Or is maximum.

In the compressor configured as described above, the pin 22 provided on the side surface of the vane 7 rotated by the rotor 6 slides into the guide groove 21 provided in the front plate 4, and as the rotor 5 rotates, the center of the rotor 6 The distance of the pin 22 from Or increases, and therefore the vane 7 protrudes toward the outer circumference along the slit 6 of the rotor 6.

The suction gas is compressed by the protrusion of the bay 77 and is discharged from the discharge hole 9, and the pressure increases to the oil 1 in the case 13.
4 and push the rear end of the vane 7 through the oil groove 12 of the rear side plate 3 to promote the pop-out of the vane 7.

Therefore, the functions of the pin 22 and the guide groove 21 are necessary at the time of starting the rotation, and there is no problem in durability since there is no large force during normal rotation. Compression can be reliably started when the compressor is started.

Effects of the Invention As is clear from the above embodiments, the rotary compressor of the present invention operates the sliding vane without relying on centrifugal force or discharge pressure.
The guide groove and the pin feed ensure that it pops out more reliably, and the structure is simple and its operation is reliable.

[Brief explanation of the drawing]

Figure 1 is a cross-sectional view of a conventional sliding vane type rotary compressor, Figure 2 is a vertical cross-sectional view of the same rotary compressor, Figure 3 is a longitudinal cross-sectional view of the rear part of the same rotary compressor, and Figure 4 is a vertical cross-sectional view of the rotary compressor. FIG. 5 is a plan view of the rear plate of the rotary compressor as viewed from the cylinder side, FIG. 5 is a plan view of the front plate of the rotary compressor showing an embodiment of the present invention as viewed from the cylinder side, and FIG. FIG. 7 is a longitudinal cross-sectional view of the central part of the rotary compressor, and a plan view of the front plate showing the shape of the guide groove of the rotary compressor. 7...Vane, 4...Front side plate (side plate)
, 21... Guide groove, 22... Pin,
24... Spring. Name of agent: Patent attorney Toshio Nakao and 1 other person No. 1
Figure 2, :j5214 31!1 Figure 4 Figure 5

Claims (2)

[Claims] (1) Rotary compression with a pin on the side of the vane that can be moved in and out by a spring, and a guide groove that engages with the pin on one side of the side plate that is fixed to both sides of the cylinder to form a compression chamber and rotatably receives the rotor. Machine. (2) The rotary compressor according to claim 1, wherein the guide groove is generally ring-shaped and has no groove in part.