JPS5851425Y2 - Vane type rotary compressor - Google Patents

Description

[Detailed description of the invention] This invention relates to the improvement of a vane-type rotary compressor used in automobile air conditioners, etc. It prevents the generation of vane noise during high compression in the low rotation speed range, and provides quiet compression. The present invention provides an efficient vane type rotary compressor.

In general, vane-type rotary compressors suck and compress refrigerant through the rotation of the vanes, but when you want to perform high compression at low rotation speeds, such as during idle linking when cooling starts, the vanes are especially useful. There is a so-called dancing phenomenon in which the vane separates from the cylinder inner wall and comes into contact with the cylinder inner wall again when it reaches the compression stroke position. When this phenomenon occurs, a collision sound between the vane tip and the cylinder wall is generated, and the compression due to the vane tip dancing occurs. It is known that efficiency becomes extremely low due to refrigerant leaks.

Conventional solutions to these inconveniences include operating the vane at a high rotational speed of 1 minute to take advantage of its centrifugal force, or not increasing the compressed air temperature too high, or inserting a coil spring with sufficient pushing force into the bottom of the vane. Various countermeasures and treatments were considered.

As is well known, the refrigerant compressor for car air conditioners is driven by the car engine, so its rotational speed is 500R, P.
, M changes from around 600 OR, P, M, and the compression pressure also changes from around 1 OKt/iG to around 30 to 9/cJG.

In particular, regarding vane dance and vane noise, the compression pressure is 25 to 30 Ky/1 when the rotation speed is around 50 OR, P, and M.
This is likely to occur during yAG, and a concrete solution to this situation is to insert a coil spring into the bottom of the vane, but if the compressor is operated at around 600OR, P, and M, the durability of the spring may be affected. There are problems, and there are problems with impracticability.

In addition, for the same purpose, as shown in Japanese Patent Publication No. 49-26522, an annular groove is provided in the side plate of the compressor on the rotation locus at the bottom of the rotor knob groove, and the discharge refrigerant pressure is applied to this groove. A structure is known in which high pressure is applied to the bottom of the vane to prevent the vane from swinging.

However, in this structure, part of the annular groove is made thinner so that when the vane moves to the low pressure side as the rotor rotates, it does not suddenly protrude from the rotor, so it is difficult to supply lubricating oil between the rotor side surface and the side plate. There were problems such as insufficient sealing between the two, and a small amount of compressed gas leaking, so some kind of improvement measure was required.

The present invention eliminates the drawbacks of the conventional vane type rotary compressor.

Hereinafter, the present invention will be described with reference to the accompanying drawings showing one embodiment thereof.

In the figure, reference numeral 1 denotes a compression unit, which includes a cylinder 2 formed into a cylindrical shape so that the internal space has a circular cross section, side plates 3.4 that close the openings at both ends of the cylinder 20, and a cylinder 2 that is housed inside the cylinder 2 and that is located at both ends. The shaft portions 5a and 5b are connected to the side plate 3.
4 and a rotor 5 rotatably supported.

The rotor 5 has two vane grooves 6 parallel to each other in the diametrical direction.
is provided, and the tip of the vane groove 6 is always connected to the cylinder 2.
A vane 1 that comes into contact with the inner wall surface of the vane 1 is retractably provided.

Reference numeral 8 denotes a case that covers the cylinder 2 and forms an oil separation chamber 9 on the left side in the figure, and is provided with a high-pressure outlet 10.

11 is a suction port provided in the cylinder 2, 12 is a discharge port provided in the cylinder 2, and a discharge valve 13 and an insert 14 are provided on the discharge side thereof, respectively.

Here, the case 8 and the through hole 4a provided in the side plate 4 form a high pressure passage 15 communicating with the oil separation chamber 9.

Further, one side plate 3 is provided with a shaft sealing device 16 for supporting the shaft portion 5a of the rotor 5, and the other side plate 4 is provided with an oil passage 11 whose one end opens at the bottom of the oil separation chamber 9. ing.

18 is an annular oil supply groove provided on the inner surface of the side plate 4;
It communicates with the bottommost portion 6a of the vane groove 6 and also communicates with the other end of the oil passage 17.

This oil supply groove 18 is formed so that most of it is located on the rotation locus of the lowest part 6a of the vane groove 6, and the remaining part is formed so that the tip of the vane 7 is located at the minimum clearance point P between the rotor 5 and the cylinder 2. When the vane groove 6 reaches the vicinity of , it deviates from the width of the bottommost part 6a of the vane groove 6 and deviates from the rotation locus of the bottommost part 6a of the vane groove 6 toward the outer periphery of the rotor 5 so as not to communicate with the bottommost part 6a.

q indicates an outer rotation locus and an inner rotation locus of the bottommost portion 6a in the vane groove 6, respectively;
8 is formed so that its width falls within this range.

The operation of the above configuration will be explained.

When the rotor 5 and vane 7 rotate in the direction shown by the arrow in FIG.
The lubricating oil is compressed inside the refrigerant, pushes up the discharge valve 13, and reaches the oil separation chamber 9, where the lubricating oil is separated from the refrigerant.
2, the condenser (
(not shown).

The lubricating oil separated from the refrigerant here is pressurized by the pressure of the refrigerant in the oil separation chamber 9 and passes through the oil passage 17 into the oil supply groove 1.
Sent to 8th.

In FIG. 3, the rotor 5 and the base 7 are shown in the direction of the arrow.
7 is rotating, when the tip of vane I passes through the minimum clearance point P between rotor 5 and cylinder 2 and enters the suction state,
The lubricating oil is pumped from the oil supply groove 18 to the bottom 6 a of the vane groove 6 and pushes the vane 7 toward the cylinder 2 .

And 1. As the vane 7 continues to rotate and enters a compression stroke, the vane 1 is gradually pushed back against the rotor 5.

The force pushing back the vane 7 toward the rotor 5 is caused not only by the contact of the tip of the vane 7 with the cylinder 2 as the vane 7 rotates, but also by the pressure of the compressed refrigerant in the cylinder 2.

Therefore, the vane 7 is pressed against the cylinder 2 by the oil pressure from the oil supply groove 18, but if the tip of the vane 7 is close to the minimum clearance point P, the pressure inside the cylinder that the tip of the vane 7 receives and the vane The hydraulic pressure applied to the bottom becomes closer and the force pushing the vane 77 toward the cylinder 2 becomes weaker, but as the rotation of the vane 7 further progresses to the vane position indicated by R in FIG. 3, the bottom of the vane groove 6 6a and oil supply groove 1
Communication with 8 is cut off.

In this state, the lubricating oil present in the vane groove 6 as the vane 7 rotates pushes the vane 7 toward the cylinder 2 as a reaction force against the compressive force caused by the return movement of the vane 7 .

Therefore, since the pressure at the bottom of the vane 7 exceeds the refrigerant pressure at the tip of the vane, the tip of the vane does not come loose from the inner wall of the cylinder.

When the rotation of the vane 70 further progresses and the tip of the vane 1 passes near the minimum clearance point P, the oil supply groove 18 and the bottom 6a of the vane groove 6 communicate again, and the supply of oil pressure is instantly continued, and the vane 7 It contacts the cylinder wall and continues to rotate.

Therefore, in the rotational movement of the vane 70, when the tip of the vane 7 is in the refrigerant suction stroke, the bottom 6 of the vane groove 6
High-pressure lubricating oil is introduced into a, and this oil pressure brings the vane T into close contact with the cylinder 2. When the vane tip approaches the minimum clearance point P between the rotor 5 and cylinder 2 and begins to receive high compressed refrigerant pressure close to the lubricating oil pressure. , since the vane 7 is brought into close contact with the cylinder 2 by the self-pressure of the lubricating oil trapped in the bottom 6a of the vane groove 6, it is possible to reliably, inexpensively, and easily
A highly efficient and quiet vane type rotary compressor can be obtained.

Note that in the above embodiment, the oil supply groove 18 is located on one side plate 4.
Although only the lubricating oil reservoir portion communicating with the oil separation chamber 9, the oil passage 17, and the oil supply groove 1 have been described.
8 is also provided on the side of the other side plate 3 and the vane 7 is hydraulically pressed from both sides to obtain the same effect.

As is clear from the above embodiments, the vane type rotary compressor of the present invention includes a cylinder formed in a cylindrical shape and provided with a refrigerant suction passage and a discharge passage, and a vane provided inside the cylinder and extending diametrically. A cylindrical rotor with grooves,
a vane that is slidably housed in the vane groove and whose tip is always in contact with the inner surface of the cylinder; and a side plate that closes the opening groove of the cylinder and that constantly forms a space with a different volume in the cylinder by the vane. The compression unit is configured by: providing an annular oil supply groove on the inner surface of at least one of the side plates, the majority of which is located on the rotation locus of the bottom of the vane groove and communicating with the vane groove; The remaining portion of the vane is formed so that when the tip of the vane is located near the minimum clearance between the rotor and the cylinder, it deviates from the bottom of the vane groove and is outside the rotation trajectory near the outer periphery of the rotor, and the oil supply groove is This is connected to the lubricating oil reservoir in the oil separation chamber, and the tip of the vane is pressed against the inner wall of the cylinder by pressing the lubricating oil supplied into the vane groove from the oil supply groove. It also prevents the vane from separating from the cylinder, and prevents vane noise, vane damage, and refrigerant leaks caused by this.Furthermore, the tip of the vane, which has a great effect of separating the vane from the cylinder, minimizes the gap between the rotor and the cylinder. Regarding the part located at the point, the lubricating oil is trapped in the vane groove by cutting off the communication between the oil supply groove and the vane groove and suppressing the vane from sinking into the rotor. The oil supply groove communicates in an annular manner, and a part of it is located outside the rotation locus at the bottom of the vane groove and closer to the outer circumference of the rotor, so this part promotes lubrication of the rotor side surface. ) It has various advantages, such as being able to prevent refrigerant leakage between the two spaces and further improving compression efficiency.

[Brief explanation of drawings]

FIG. 1 is a sectional view of a vane type rotary compressor according to an embodiment of the present invention, and FIG. 2 is a sectional view taken along line A-A in FIG. 1.
FIG. 3 is an explanatory diagram of the operation of the vane type rotary compressor. 1...Compression unit, 2...Cylinder, 3. 4... Side plate, 5... Rotor,
6...Vane L6a...Bottom part, 1.
...Vane, 9...Oil separation chamber, 17...
...Oil passage, 18...Oil supply groove, P...
...Minimum gap point.

Claims (1)

[Scope of utility model registration request] A cylinder formed in a cylindrical shape and provided with a refrigerant suction passage and a discharge passage; a cylindrical rotor provided within the cylinder and provided with a vane groove in the diametrical direction; and a cylindrical rotor that is slidable within the vane groove. A compression unit is constituted by a vane which is housed and whose tip is always in contact with the inner surface of the cylinder, and a side plate which closes the open end of the cylinder and which always forms a space with a different volume in the cylinder by the vane, and at least one of the An annular oil supply groove is provided on the inner surface of the side plate, most of which is located on the rotation locus of the bottom of the vane groove and communicates with the vane groove. When the vane groove is located near the minimum clearance between the vane groove and the cylinder, the vane groove is formed so as to be out of the rotation locus near the outer periphery of the rotor, and the oil supply groove is formed in the lubricating oil reservoir of the oil separation chamber. A vane type rotary compressor connected to the