JPH048319Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a vane type rotary compressor.

In general, a vane type rotary compressor, as shown in FIGS. 1 and 2, includes a rotating shaft 1, a rotor 2 rotated via the rotating shaft 1, and a rotor 2 that is attached to the rotor 2 so as to be freely protrusive and retractable in a substantially radial direction. A cam ring 4 that accommodates a large number of vanes 3...3, a rotor 2 with the vanes 3...3 attached thereto, and front and rear sides that sandwich the cam ring 4 and form a pump chamber 5 on the inner periphery of the cam ring 4. The rotor 2 is made up of side plates 6 and 7, and a housing 8 that accommodates the side plates 6 and 7 and the rotor 2. In such a vane type rotary compressor, when the rotor 2 is rotated, the vanes 3...3 attached to the rotor 2 slide while being pressed against the inner peripheral surface of the cam ring 4, and each vane 3, 3 at that time slides. By changing the volume between them, a working gas (not shown) is introduced into the pump chamber 5 through the suction passage 9, pressurized, and discharged to the outside through the discharge passage 10. In addition, in this vane type rotary compressor, the oil 12 in the oil reservoir 11 connected to the discharge passage 10 is transferred to the rotor 2 through the throttle ring 13 and needle bearing 14 installed between the rotating shaft 1 and the side plate 7 by the gas discharge pressure. was introduced into the bottom of the vane receiving hole 2a, and by applying a predetermined back pressure to the vanes 3, the vanes 3...3 were pressed against the inner circumferential surface of the cam ring 4. Therefore, in such a conventional vane type rotary compressor, the gas discharge pressure in the pump chamber 5 is controlled by the throttle ring 13 through the oil 12.
After lowering the force by a certain amount, it was applied to the bottom of the vane 3, which caused the following problems. That is, in this compressor, the pressure in the pump chamber 5 is highest near the small arc of the cam ring 4 where the outer circumferential surface of the rotor 2 is closest to the inner circumferential surface of the cam ring 4. The pushing force acting on is maximized. Therefore, in this compressor,
When the ejecting force acting on the vane 3 is smaller than the pushing force, the tip of the vane 3 separates from the inner peripheral surface of the cam ring 4 and passes near a small arc of the cam ring 4, reducing the pushing force. It collides with the surface and generates noise. However, such problems can be solved by increasing the diameter of the aperture ring 13 and increasing the back pressure applied to the vane 3. However, in such a case,
Since a large back pressure is always applied to the vane 3, the ejecting force of the vane 3 becomes large, causing a problem that the vane 3 and the cam ring 4 are abnormally worn.

The present invention aims to provide a vane-type rotary compressor that prevents vanes and cam rings from being excessively worn out by suppressing the generation of vane collision noise that occurs near the position closest to the inner periphery of the cam ring. purpose.

As a means to achieve this purpose, the present vane type rotary compressor has a side plate that allows oil to flow into the side plate only at the bottom of the vane receiving hole located between the discharge side and the suction side of the pump chamber near the small arc of the cam ring. It is characterized in that an oil supply hole is provided to supply oil from the reservoir without going through the throttle ring.

Next, an embodiment of the present invention will be described in detail based on FIGS. 3 to 6.

The same parts as in the conventional example are given the same reference numerals, and the explanation thereof will be omitted. As shown in FIG. 5, between a pair of fan-shaped recesses 16 in the side plate 7, pairs of substantially arc-shaped long oil supply grooves 15a are formed independently (separated) from the fan-shaped recesses 16. Here, the pumping action of the pump chamber 5 having the suction side 5a and the discharge side 5b will be explained. When the rotor 2 is rotated in the direction of the arrow, the vanes 3 slide while being pressed against the inner peripheral surface of the cam ring 4, and due to the change in volume between each vane 3, working gas is sucked in from the suction port 9a and pressurized. After that, it is discharged from the discharge port 10a. At this time, each vane 3
The working gas sealed in between is compressed as it approaches the discharge port 10a, but this compression action exerts a pushing force on the vane 3 (a force that tries to push the vane 3 back into the rotor 2). It turns out. This pushing force becomes particularly large as the vane 3 moves from just before the discharge port 10a to the adjacent suction port 9a, and becomes larger than the ejecting force of the vane 3.

The oil supply long groove 15a is formed to correspond to a range in which the pushing force of the vane 3 is particularly larger than the ejecting force. That is, vane 3
From the location where the bottom of the vane receiving hole 2a in which the vane 3 is housed is located when it is located just in front of the discharge port 10a, to the location where the bottom of the vane receiving hole 2a is located when the vane 3 is located at the suction port 9a. It is formed over.

An oil supply hole 15 communicating with the oil supply long groove 15a is formed in the side plate 7 in which the oil supply long groove 15a is formed. As shown in FIG. 3, the oil supply hole 15 is formed in a portion of the side plate 7 that is spaced apart from a portion that contacts the aperture ring 13 and extends in the axial direction of the rotating shaft 13. The diameter of this oil supply hole 15 is the oil reservoir 1
It is formed to have a diameter that does not reduce the discharge pressure applied to the oil in the first oil. Further, a fan-shaped recess 16 is formed in the side plate 7, and this fan-shaped recess 16 distributes and supplies oil 12 that has entered through the aperture ring 13 to the bottom of the vane receiving hole 2a. The thrust bearing 17 is interposed between the rotor 2 and the front side plate 6, and a thrust race 17a (closing means) of the thrust bearing 17.
The other end of the vane receiving hole 2a near the small arc is closed by the oil supply long groove 15.
a), and is maintained independent from the other vane receiving holes 2a. Further, the annular groove 18 is provided in the front side plate 6, and communicates with the vane receiving hole 2a other than the vicinity of the small arc. In this embodiment, other needle bearings 19, seals 20, and oil drain holes 21 are provided.

In the vane type rotary compressor of the above embodiment, as described above, when the vane type rotary compressor is operated, the working gas sealed between each vane 3 is compressed as it approaches the discharge port 10a. A pushing force acts on the vane 3, and this pushing force becomes maximum immediately before the adjacent suction port 9a. on the other hand,
Immediately before the discharge port 10a, the vane 3 is rotated by the centrifugal force during rotation and the pressure of the oil 12 supplied to the bottom of the vane receiving hole 2a through the oil supply passage 15, the throttle ring 13, and the fan-shaped recess 16. 2
The flying force is acting to direct the object outward. The pushing force becomes larger than the flying force acting on the vane 3 as it approaches the adjacent suction port 9a from just before the discharge port 10a.

Therefore, the side plate 7 is provided with a vane receiving hole when the vane 3 further slides from the location where the bottom of the vane receiving hole 2a is located when the vane 3 is located immediately in front of the discharge port 10a and is located at the suction port 9a. An oil supply long groove 15a is formed extending to the location where the bottom of the hole 2a is located, and as described above, this oil supply long groove 15a
This corresponds to the range in which the pushing force acting on the ball is greater than the flying force. Therefore, in addition to the oil 12 supplied and sealed from the oil supply passage 15a via the throttle ring 13 to the vane receiving hole 2a in the range where the pushing force acts larger than the ejecting force, the pressure is reduced by the throttle ring 13. high pressure oil 1
2 is oil supply hole 15, oil supply long groove 15a
Supplied via. Therefore, the flying force is larger than the pressing force acting on the vane 3, and the vane 3 rotates without separating from the inner peripheral surface of the cam ring 4. Also, the vane 3 rotates without separating from the inner peripheral surface of the cam ring 4. Oil 12 from an oil reservoir 11 is supplied to the bottom via a throttle ring 13. Therefore, in this compressor, a low discharge pressure is applied to the bottom of the vane, and the oil 12 is returned to the oil reservoir 11 via the thrust bearing 17, annular groove 18, needle bearing 19, seal 20, and oil return hole 21. Ru. Therefore, according to the present invention,
When the sliding vane is located just in front of the discharge port,
In addition to the oil depressurized by the aperture ring,
High-pressure oil that is not depressurized by the throttle ring is supplied to the bottom of the vane receiving hole through the oil supply hole and the oil supply long groove, and this high-pressure oil is continuously supplied until the vane is located at the adjacent suction port. Therefore, it is possible to obtain a larger flying force than the pushing force, which increases as the vane approaches the suction port from just before the discharge port. As a result, the vane is prevented from separating from the inner circumferential surface of the cam ring over a wide range from just before the discharge port to the suction port, and collisions and vibrations caused by this separation can be prevented.

Furthermore, in this embodiment, high-pressure oil is supplied through the oil supply hole only to the bottom of the vane receiving hole near the small arc where the pushing force acting on the vane is maximum, thus preventing abnormal wear of the vane 3. There is an effect that can be done.

[Brief explanation of drawings]

Figure 1 shows a conventional vane type rotary compressor.
Figure 2 is a cross-sectional view taken along the line - - in Figure 1, Figure 3 is a cross-sectional view taken along the - line in Figure 4 showing the vane type rotary compressor of the present invention, and Figure 4 is the line sectional view taken in Figure 3. FIG. 5 is a front view of the rear side plate, and FIG. 6 is a front view of the front side plate. 1... Rotating shaft, 2... Rotor, 2a... Vane receiving hole, 3... Vane, 4... Cam ring, 5...
Pump chamber, 6, 7... side plate, 8... housing, 9... suction passage, 10... discharge passage,
11... Oil reservoir, 12... Oil, 13...
Aperture ring, 15...Oil supply hole.

Claims (1)

[Scope of utility model registration request] a rotating shaft; a rotor rotated via the rotating shaft; a large number of vanes attached to the rotor so as to be freely protrusive and retractable in a substantially radial direction; a cam ring housing the rotor to which the vanes are attached; The pump includes a side plate that holds a cam ring and forms a pump chamber on the inner periphery of the cam ring, and a housing that accommodates the side plate or the rotor, and is attached to the rotor when the rotor is rotated. The vanes slide while being pressed against the inner circumferential surface of the cam ring, and the change in volume between the vanes at that time introduces working gas into the pair of pump chambers through the suction port, pressurizes it, and connects it to the discharge port. At the same time, the oil in the oil reservoir connected to the discharge port is supplied to the fan-shaped recess through the aperture ring installed between the rotary shaft and the side plate by the discharge pressure. In a vane type rotary compressor that is adapted to be introduced into the bottom of the vane receiving hole of the side plate, when the sliding vane is located immediately in front of the discharge port, from the location where the bottom of the vane receiving hole is located. When the vane further slides and is located at the suction port, an oil supply long groove is formed independently from the fan-shaped recess and extends to a location where the bottom of the vane receiving hole is located. A closing means for closing the other end is provided, and an oil supply hole for supplying oil from the oil reservoir to the long oil supply groove is formed in a part of the side plate that is spaced apart from a part that contacts the aperture ring. Vane type rotary compressor.