JPH09287584A - Rotary compressor - Google Patents

Abstract

(57) [Abstract] [PROBLEMS] In a rotary compressor used for a refrigerator-freezer or an air conditioner, instability behavior such as sliding of a roller and a vane, which are components of a compression mechanism, and vane dance and disengagement, is solved.
It is an object of the present invention to provide a rotary compressor which is reliable and has a long life. A compression mechanism unit having a vane 3 having an R-shaped tip and a roller 4 revolving in the cylinder 2 and an electric motor unit for driving the compression mechanism unit are provided, and a roller groove portion 13 is formed on a part of the outer periphery of the roller 4. The tip of the vane 3 is slidably arranged in the roller groove portion 13, and the tip of the vane 3 is provided in the roller groove portion 13.
And at least two surfaces are in contact with each other. As a result, even when the force for pressing the vane 3 against the roller 4 is weak such as at the time of start-up, the lateral force for pushing the tip of the vane 3 back toward the center of the roller groove portion 13 is large, and the vane 3 causes the roller groove portion 13 to move. It is stably held inside, and it is possible to make it difficult for the vane 3 to dance or come off.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor used in a refrigerator / freezer, an air conditioner or the like.

[0002]

2. Description of the Related Art Rotary compressors are widely used for refrigerators and air conditioners because of their compactness and simple structure. The compression mechanism parts such as vanes and roller pistons (hereinafter referred to as rollers), which are the main components of the compressor, are described in, for example, Kawahira, Closed Refrigerator (1993) 14th.
Page, Figure 6.1.

The operation of the conventional rotary compressor will be described below with reference to FIG. In an airtight container (not shown), a compression including a crankshaft 1 having an eccentric portion, a bearing (not shown) supporting the crankshaft 1, a cylinder 2, a vane 3, and a roller 4 eccentrically rotating in the cylinder 2. The vane 3 having a circular arc tip constitutes a mechanical part and reciprocates in the groove 5 of the cylinder 2. The tip of the vane 3 is driven by the spring force of the spring 6 and the pressure difference between the inside and the outside of the cylinder 2. Is pressed against the outer peripheral surface of the roller 4
The inside of the cylinder 2 is divided into a suction chamber 7 and a discharge chamber 8 by sliding in contact with the outer peripheral portion of the cylinder.

[0004] O is the center of the cylinder 2 and the crankshaft 1,
The crankshaft 1 has an eccentric portion (hereinafter referred to as a crankpin) 9 centered on P which is eccentric from the center O by e, and a roller 4 is fitted to the crankpin 9 by an electric motor (not shown). When the crankshaft 1 rotates and the roller 4 revolves in the cylinder 2, the refrigerant gas is sucked from the suction port 10 and sent to the discharge port 11 while being compressed. Discharge port 1
The refrigerant gas No. 1 is sent to the refrigeration cycle side through the discharge valve 12, passes through the condenser, the expansion valve, and the evaporator, and then returns to the suction port 10 of the compressor again.

[0005]

However, in the above-described conventional configuration, the tip of the vane 3 has an arcuate curved surface,
Since the outer peripheral surface of the roller 4 is also a circular curved surface (cylindrical surface),
The contact state between the vane 3 and the roller 4 is equivalently a contact between the small cylinder and the large cylinder. Therefore, the contact state is a line contact state, the contact area becomes small, the load per unit area, that is, the contact stress becomes large, and the contact sliding condition of the vane 3 and the roller 4 becomes severe.

The rotation number of the roller 4 is determined by the difference between the sliding resistance between the inner peripheral surface of the roller 4 and the crank pin 9 and the sliding resistance between the outer peripheral surface of the roller 4 and the tip of the vane 3. Therefore, the rotation speed of the roller 4 is also very unstable (generally, the rotation speed of the roller is about several tens to several hundreds rpm when the rotation speed of the crankshaft 1 is 3500 rpm).

Therefore, the sliding surface of the tip of the vane 3 and the sliding surface of the roller 4 becomes an unstable sliding motion in which the sliding speed changes depending on the conditions and the oil film thickness also changes. From the above, there has been a problem that it is necessary to severely limit the usage conditions of the compressor, especially in the flow of the alternative refrigerant which is said to be extremely severe in the sliding state in recent years. . As one conventional example for solving this problem, for example, Japanese Utility Model Laid-Open No. 57-84.
There is an example described in Japanese Patent No. 384, etc. in which a groove is provided in the roller 4 to reduce the load on the sliding portion (FIG. 6).

However, in this method, the load on the sliding portion can be reduced, but as shown in FIG. 6, the force for pressing the vane 3 working near the point A against the roller 4 especially at the time of startup with a small difference in high pressure and low pressure. When Fp is weak, the restraining force against the rotation of the roller 4 around the center P is also weak, and an abnormal noise (chattering noise) is generated in the groove due to the vane 3 coming off the roller groove 13 or dancing in the roller groove 13. There was a problem of scratching, which was a major obstacle to practical use (generally, in the closed container of the compressor, there are many types in which the pressure is high, and during normal operation, the vane 3 is pressed against the roller 4 due to the pressure difference. Exist).

Therefore, the present invention solves the above-mentioned conventional problems by reducing the load on the sliding portion between the vane 3 and the roller 4, and preventing the roller 4 and the vane 3 from coming off and dancing.
It is an object of the present invention to provide a rotary compressor which is reliable and has a long life.

[0010]

According to the present invention for solving this problem, a crank shaft having a crank pin, a bearing for rotatably supporting the crank shaft, and the crank pin are provided. A cylinder to be inserted, a roller piston located between the crank pin and the cylinder and moving in the cylinder while being driven by the crank pin, and all or a part of the tip is R-shaped, and the tip is The vane, which is in pressure contact with the outer peripheral surface of the roller piston and reciprocates in conjunction with the movement of the roller piston, and the tip of the vane in the outer peripheral surface of the roller piston, are formed in pressure contact, and the tip of the vane is formed. And a recessed portion that is in contact with at least two locations.

The recess may be R-shaped, and a small groove may be further formed in the center of the recess.

The recess may be R-shaped, and the R dimension of the center of the recess may be smaller than the R dimension of the tip of the vane.

All or part of the recess may be V-shaped.

Further, the center of the tip of the vane may not be R-shaped, and the rest of the tip other than the center may be R-shaped.

According to a sixth aspect of the present invention, there are provided a crankshaft having a crankpin, a bearing rotatably supporting the crankshaft, a cylinder into which the crankpin is inserted, a crankpin and the cylinder. Located in between
A roller piston that moves in the cylinder while being driven by the crankpin, and a vane whose tip contacts a recess formed in the outer peripheral surface of the roller piston and reciprocates in conjunction with the movement of the roller piston, A rotary compressor provided with a vane spring having a pressing force that presses the vane into the recess in a startable range at the time of starting when the pressure acting on the front and rear ends of the vane is small.

The crankpins of claims 1 and 2 are:
It was used to identify the crank part,
The crank pin pin vocabulary does not limit its shape.

[0017]

Embodiments of the present invention will be described below with reference to the drawings.

The configuration of the rotary compressor according to the embodiment of the present invention is substantially the same as that of the conventional example described in FIG. 7 except for a part such as a roller groove portion. The same components as those described in the example are designated by the same reference numerals, and the description thereof will be omitted.

(Embodiment 1) Hereinafter, a first embodiment of the present invention will be described with reference to FIG.

As shown in FIG. 1, an R-shaped roller groove portion 13 is provided in a part of the roller 4, the tip of the vane 3 having substantially the same curvature is slidably arranged in the roller groove portion 13, and the roller groove portion 13 is formed into two. A small groove portion 14 is provided at a certain angle from the center of the roller groove portion 13 so as to be divided. (The angle is determined in consideration of the swinging angle of the roller 4 around the tip of the vane 3 and the magnitude of the force that presses the vane 3 against the roller 4.) With such a configuration, the crankshaft As the roller 1 (not shown) rotates, the roller 4 moves to the crank pin 9
Although the cylinder 2 revolves (eccentric oscillating motion) as it moves, even if the force of pressing the vane 3 against the roller 4 is weak such as at start-up, as is apparent from the figure, the conventional contact is made around the point A. In the present invention, what has been done is B
The points F and C come into contact with each other, and forces F1 and F2 around the center P of the large roller 4 tend to push the tip of the vane 3 back toward the center of the roller groove portion 13. Therefore, the vane 3 is stably held in the roller groove portion 13, and it is possible to prevent the phenomenon such as the vane 3 from dancing or coming off. In addition, foreign matter and abrasion powder generated in the sliding portion are not affected by the small groove portion 1.
There is also an effect that it becomes difficult to be caught in the sliding portion by flowing into 4, and the lubricating state is improved.

In the present embodiment, the roller groove portion 13
R of the vane 3 has substantially the same curvature as the tip R of the vane 3, but it does not necessarily have to have the same curvature, and the small groove portion 14
The shape is not limited to a round groove, but may be a triangular groove, a square groove, or the like, and it goes without saying that the cross-sectional shapes of the roller groove portion 13 and the small groove portion 14 do not have to be the same in the longitudinal direction.

(Second Embodiment) A second embodiment of the present invention will be described below with reference to FIG.

In FIG. 2, the curvature of R of the roller groove portion 13 is made smaller than the curvature of the tip R of the vane 3. Even if the small groove portion is not provided, as in the first embodiment, B is the same.
The contact is made at the points C and C, the lateral force for pushing back the tip of the vane 3 toward the center of the roller groove portion 13 is large, and the vane 3 is stably held in the roller groove portion 13, It is possible to make it difficult for the dance of the vane 3 and the deviation phenomenon to occur.

In FIG. 2, the points B and C are changed from line contact to surface contact due to familiarity, but it is needless to say that they may be processed to be surface contact from the beginning.

(Third Embodiment) A third embodiment of the present invention will be described below with reference to FIG.

As shown in FIG. 3, the roller groove portion 13 has a V-groove shape, and like the first embodiment, the roller groove portion 13 comes into contact at the points B and C, and the tip of the vane 3 is connected to the roller groove portion 13.
The lateral force to push back toward the center of the vane is large, and the vane 3 is stably held in the roller groove portion 13,
It is possible to make it difficult for the dance of the vane 3 and the deviation phenomenon to occur.

Although the small groove portion 14 is shown in the drawing, the second groove
Similar to the embodiment described above, it is not always necessary to provide it.

Further, in FIG. 3, the points B and C change from line contact to surface contact due to familiarity, but as in the second embodiment, it may be processed so as to be surface contact from the beginning. That is of course.

(Embodiment 4) Hereinafter, a fourth embodiment of the present invention will be described with reference to the drawings.

As shown in FIG. 4, the tip of the vane 3 is slidably arranged in the roller groove portion 13, and the tip R of the vane 3 is divided into two in the sliding direction.
Even with such a configuration, the same effect as that of the above embodiment can be obtained.

Although the tip of the vane 3 is cut flat in FIG. 4, it is needless to say that it may have another shape.

(Fifth Embodiment) Hereinafter, a fifth embodiment of the present invention will be described with reference to the drawings.

As shown in FIG. 5, the tip of the vane 3 is slidably installed in the roller groove portion 13, and there is almost no pressure difference between the tip and the rear end of the vane 3 at the time of start-up (the inside of the closed container is of a low pressure type). In the case of the type, during normal operation), the R portion at the tip of the vane 3 is composed of a spring 15 having a pressing force sufficient to constantly contact both side portions of the roller groove portion 13 with a margin. Unlike the conventional specification in which the line contact is made, the surface contact has a margin in the allowable surface pressure of the contact portion, so that the spring force of the spring 15 can be increased to such an extent that the starting is not hindered.
With such a configuration, the two
Since a large lateral force that tries to push the tip of the vane 3 back toward the center of the roller groove portion 13 on the surface is constantly generated, the vane 3 is stably held in the roller groove portion 13,
It is possible to suppress the dance and the deviation phenomenon of the vane 3.

It should be noted that, as can be said with respect to all of the above-mentioned embodiments, the contact portion does not necessarily have to be bilaterally symmetrical, and one sliding length is increased depending on the R shape and the sliding load state. Of course, asymmetrical shapes may be used.

The roller groove portion corresponds to the concave portion of the present invention.

[0036]

As is apparent from the above description, according to the present invention, there is provided a compression mechanism section including a vane having an R-shaped tip and a roller revolving in the cylinder, and an electric motor section for driving the compression mechanism section. A recess is provided in a part of the outer circumference of the roller, the vane tip is slidably arranged in the roller recess, and the vane tip is in contact with the roller recess on at least two surfaces. .

In this structure, even when the force for pressing the vane against the roller is weak such as at the time of starting, the lateral force for pushing back the tip of the vane toward the center of the roller groove portion is large, and the vane moves in the roller groove portion. It is held stable and can prevent the vane from dancing and coming off.

Further, there is also an effect that foreign matter and abrasion powder generated in the sliding portion flow into the small groove portion and become difficult to be caught in the sliding portion, and the lubricating state is improved.

As described above, the load on the sliding portion between the vane and the roller can be reduced, and the vane can be prevented from slipping out of the roller groove or dancing to realize a highly reliable and long-life rotary compressor. is there.

[Brief description of drawings]

FIG. 1 is a side view of essential parts showing a configuration of vanes and rollers of a rotary compressor according to a first embodiment of the present invention.

FIG. 2 is a side view of a main part showing a configuration of vanes and rollers of a rotary compressor according to a second embodiment of the present invention.

FIG. 3 is a side view of essential parts showing the configuration of vanes and rollers of a rotary compressor according to a third embodiment of the present invention.

FIG. 4 is a side view of essential parts showing a configuration of vanes and rollers of a rotary compressor according to a fourth embodiment of the present invention.

FIG. 5 is a side view of essential parts showing a configuration of vanes and rollers of a rotary compressor according to a fifth embodiment of the present invention.

FIG. 6 is a side view of essential parts showing a configuration of vanes and rollers of a conventional rotary compressor.

FIG. 7 is a side view of a main part of a compression mechanism portion of a conventional rotary compressor.

[Explanation of symbols]

 1 Crankshaft 2 Cylinder 3 Vane 4 Roller 9 Crankpin 13 Roller Groove 14 Small Groove

Front page continuation (72) Inventor Fumitoshi Nishiwaki 1006 Kadoma, Kadoma City, Osaka Prefecture Matsushita Electric Industrial Co., Ltd. Person Hideki Nakata 1006 Kadoma, Kadoma City, Osaka Prefecture, Matsushita Electric Industrial Co., Ltd. (72) Inventor, Hiroshi Hasegawa 1006 Kadoma, Kadoma City, Osaka Prefecture, Matsushita Electric Industrial Co., Ltd. Takada Hondori 4-2-5 Matsushita Cold Machinery Co., Ltd.

Claims (6)

[Claims] 1. A crankshaft having a crankpin, a bearing rotatably supporting the crankshaft, a cylinder into which the crankpin is inserted, and a crankpin located between the crankpin and the cylinder. A roller piston moving in the cylinder while being driven, and all or part of the tip has an R shape, and the tip presses against the outer peripheral surface of the roller piston, and reciprocates in conjunction with the movement of the roller piston. And a recess formed in a portion of the outer peripheral surface of the roller piston where the tip of the vane is in pressure contact with the tip of the vane and contacting at least two points. 2. The rotary compressor according to claim 1, wherein the recess is R-shaped, and a small groove is further formed in the center of the recess. 3. The rotary compressor according to claim 1, wherein the recess is R-shaped, and the R dimension of the center of the recess is smaller than the R dimension of the tip of the vane. 4. The rotary compressor according to claim 1, wherein all or part of the recess is V-shaped. 5. The rotary compressor according to claim 1, wherein the center of the tip of the vane is not R-shaped, and the rest of the tip other than the center is R-shaped. 6. A crankshaft having a crankpin, a bearing rotatably supporting the crankshaft, a cylinder into which the crankpin is inserted, and a crankpin located between the crankpin and the cylinder. A roller piston that moves in the cylinder while being driven, a vane whose tip contacts a recess formed on the outer peripheral surface of the roller piston, and reciprocates in conjunction with the movement of the roller piston, and a vane before and after the vane. The pressure acting on the edge is small at startup,
A rotary compressor, comprising: a vane spring having a pressing force that presses the vane into the recess in a startable range.