JP2000170677A - Rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce surface pressure by making a main vane part in a main vane groove part and a guide vane part in a guide vane groove part in such a way as to receive forces acted on a vane by differential pressure between an intake chamber and a compression chamber, and to increase a sliding loss by both ends supporting the vane to prevent partially abutting. SOLUTION: A compressing system part composed of a crankshaft 2, a main bearing 3, an auxiliary bearing 4, a cylinder 5, a vane 19, and a roller 7, is provided in a closed container, and the vane 19 is provided in a vane groove 20 of the cylinder 5 so as to freely reciprocate. In this case, the vane groove 20 is composed of a main vane groove part 21 provided on the cylinder 5 and a guide vane groove part 22 provided on the main bearing 3, and the vane 19 is composed of a main vane part 23 and a guide vane part 24. Forces acted on the vane 19 by differential pressure between an intake chamber and a compression chamber is received with the main vane part 23 in the main vane groove part 21 and the guide vane part 24 in the guide vane groove part 22 to reduce surface pressure and decrease the possibility of partially abutting of the vane 19.

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 for a refrigerator or an air conditioner.

[0002]

2. Description of the Related Art Rotary compressors, which are typical rotary fluid machines, are compact and have a simple structure.
It is often used for refrigerators and air conditioners. The compression mechanism such as vanes and rollers, which are main components of the compressor, are described in, for example, Kawahira, Hermetic Refrigerator (1993, Japan Refrigeration Association), page 14, FIG. 6.1.

[0003] The operation of the conventional rotary compressor will be described below with reference to FIGS. 8 and 9.

FIG. 8 is a longitudinal sectional view of a conventional rotary compressor, and FIG. 9 is a transverse sectional view of an AA portion (cylinder center portion) thereof. In a closed container 1, a compression mechanism unit including a crankshaft 2 having an eccentric portion, a main bearing 3 supporting the crankshaft 2, an auxiliary bearing 4, a cylinder 5, a vane 6, and a roller 7 eccentrically rotating in the cylinder 5 is provided. Make up. The arc-shaped vane 6 reciprocates in the vane groove 8 of the cylinder 5, and its tip is formed on the outer peripheral surface of the roller 7 by the spring force of the spring 9 and the force due to the pressure difference between the inside and outside of the cylinder 5. While being pressed against and sliding in contact with the outer peripheral portion of the roller 7, the inside of the cylinder 5 is moved into the suction chamber 10 and the compression chamber 1.
It is divided into 1.

[0005] A point O is the center of the cylinder 5 and the crankshaft 2, and the crankshaft 2 has an eccentric portion (hereinafter referred to as a crankpin) 12 centered on a point P eccentric from the center O by an eccentric amount e.
The roller 7 is fitted to the crank pin 12, and the electric motor composed of the stator 13 and the rotor 14 rotates the crank shaft 2 in the direction of the arrow B so that the roller 7 revolves in the cylinder 5. Then, the refrigerant gas is sucked from the suction port 15 and sent to the discharge port 16 while being compressed. The refrigerant gas coming to the discharge port 16 is sent from the discharge valve 17 to the refrigeration cycle side through the discharge pipe 18 through the inside of the closed vessel 1. In this manner, the refrigerant gas is compressed.

[0006]

However, in the above-mentioned conventional construction, the force generated by the pressure difference between the suction chamber 10 and the compression chamber 11 of the vane 6 is applied to the vane groove 8.
Therefore, a large force was applied to the end of the vane groove 8 in order to hold the cantilever. In particular, the contact and sliding conditions between the vane 6 and the vane groove 8 at the end portion C of the vane groove 8 become severe, and there is a problem that abrasion easily occurs and sliding loss increases.

Further, since the tip of the vane 6 has an arc curve and the outer peripheral surface of the roller 7 is also a circular curved surface (cylindrical surface), the contact state between the vane 6 and the roller 7 is equivalently equivalent to a small cylinder and a large cylinder. The convex surfaces of the cylinder are in contact with each other. Therefore, the contact state is a line contact state, and the suction chamber 10 and the compression chamber 11 are partitioned, so that it is difficult to sufficiently seal, and gas leakage from the compression chamber 11 to the suction chamber 10 occurs, thereby affecting the performance.

The number of rotations of the roller 7 is also determined by a difference in sliding resistance between the inner peripheral surface of the roller 7 and the crankpin 12 and a sliding resistance between the outer peripheral surface of the roller 7 and the tip of the vane 6. The rotation speed of the roller 7 is very unstable (generally, when the rotation speed of the crankshaft 2 is 3500 rpm, the rotation speed of the roller is about several tens to several hundreds rpm). Therefore, the sliding speed of the tip of the vane 6 and the sliding surface of the roller 7 changes depending on conditions, resulting in unstable sliding sliding. And there is a problem that wear is easily generated and a sliding loss is increased. Also, R134a, R410
When using an HFC refrigerant containing no chlorine such as A,
Since the lubricating performance is inferior to that of the conventional refrigerant R22, relaxation of sliding conditions has been a problem. Further, when carbon dioxide or the like is used as the refrigerant, the pressure range of the operating conditions is 10
In some cases, the sliding conditions are even harsher than in the prior art, and relaxation of the sliding conditions has become a problem.

In the conventional configuration, the cylinder 5, the main bearing 3 and the sub-bearing 4 are separately machined. Therefore, the joining surfaces of the respective parts need to be polished with high precision in order to prevent leakage. In addition, when assembling the components integrally, a step of centering the components is required, which has a problem of increasing the cost.

In view of the above-mentioned problems of the conventional rotary compressor, the present invention reduces the load and leakage of the sliding portion at the vane groove and the tip of the vane, and provides a high reliability and a long service life. It is an object of the present invention to provide a rotary compressor that achieves higher efficiency and lower cost.

[0011]

The present invention comprises a cylinder, a main bearing and a sub bearing located at both ends of the cylinder, and an eccentric portion rotatably housed between the main bearing and the sub bearing. A roller fitted to a crank rotation shaft and eccentrically rotating within the cylinder; a guide vane provided in at least one of a main bearing groove and at least one of a main bearing and a sub bearing provided in the cylinder in communication with the main vane groove. A compression mechanism unit having a vane groove formed of a groove and a vane that reciprocates in the vane groove and abuts on the roller to divide the cylinder; an electric drive unit that drives the compression mechanism unit; A rotary compressor including a hermetically sealed container that houses a compression mechanism section and an electric drive section.

[0012]

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

The configuration of the rotary compressor according to one embodiment of the present invention is substantially the same as that of the conventional example described with reference to FIGS. 8 and 9 except for a part of a vane groove and a roller groove. In one embodiment, the same components as those described in the above-described conventional example are denoted by the same reference numerals, and description thereof will be omitted.

The rotary compressor according to the present embodiment uses a refrigerant that does not contain chlorine, such as HFC134a, R410A, or hydrocarbon (HC), or a refrigerant, such as carbon dioxide, in a refrigeration and air conditioning cycle device. belongs to.

First Embodiment A first embodiment of the present invention will be described with reference to FIGS.

FIG. 1 is a longitudinal sectional view of a main part of a rotary compressor according to a first embodiment of the present invention, and FIG.
FIG. 3 is a cross-sectional view of a D portion (for convenience of explanation, a crankshaft, rollers, and vanes are omitted). FIG. 3 is a perspective view of the vane. FIG. 3A shows the vane used in the example of FIG. 1, and FIG. 3B shows another embodiment.

As shown in FIGS. 1 to 3, in the present embodiment, the vane groove 20 has a main vane groove 21 provided in the cylinder 5 and a guide vane groove 22 provided in the main bearing 3.
, And the vane 19 is composed of a main vane portion 23 and a guide vane portion 24. In the vane 19 of FIG. 1, the main vane portion 23 inserted in the main vane groove 21 and the guide vane portion 24 inserted in the guide vane groove portion 22 reciprocate in the respective grooves as the crankshaft 2 rotates.

As shown in FIG. 3, the length W2 of the guide vane portion 24 of the vane 19 is longer than the length W1 of the main vane portion 23 by W3. This is to prevent the refrigerant in the compression chamber or the suction chamber from leaking from near the tip of the vane 6 to the guide vane groove 22. It is considered that the difference W3 in the vane length is preferably long, but if it is too long, interference with the crankshaft 2 occurs, and the vane 19 itself becomes heavy and the inertia force increases. . Therefore, it is convenient in terms of configuration if the tip of the guide vane portion 24 is determined to be slightly outside the inner diameter of the roller 7. Here, W3 is slightly shorter than the thickness tr of the roller 7 (the difference between the outer radius and the inner radius of the roller 7) (however, in a third embodiment described later,
Considering the roller groove depth Hm formed in the roller 7, W3
Is slightly shorter than tr-Hm). FIG. 3 (b)
Is an example in which guide vanes 24 are provided on both sides of the main vane 23.

According to this configuration, the force acting on the vane 19 due to the differential pressure between the suction chamber 10 and the compression chamber 11 shown in FIG. 9 is applied to the main vane section 23 in the main vane groove section 21 and the guide vane groove section 22.
Since it can be received by the guide vane portion 24 inside, the surface pressure is lower than in the conventional configuration, and the vane 19 is not cantilevered, so that it is difficult to hit one side, and the sliding condition is eased. Therefore, the reliability can be improved as compared with the related art, and the sliding loss can be reduced and the efficiency can be improved.

Embodiment 2 Next, a second embodiment of the present invention will be described with reference to FIGS. FIG. 4 is a longitudinal sectional view of a main part of a rotary compressor according to a second embodiment of the present invention, and FIG. 5 is a transverse sectional view of an FF section (for convenience of explanation, explanation of a crankshaft). , Rollers, and vanes are omitted).

In this embodiment, a vane groove 20 having a main vane groove 21 and a guide vane groove 22 is provided in a cylinder bearing block 25 in which the cylinder 5 and the main bearing 3 in the first embodiment of FIG. It is configured.

According to this configuration, the number of parts is reduced, and the highly accurate centering and assembling process of aligning the center of the cylinder 5 with the center of the main bearing 3, which has been conventionally performed, becomes unnecessary.
The number of assembling steps can be reduced.

Further, in the first embodiment, the vane groove 20 cannot be cut to the outer periphery of the cylinder 5 as shown by an arrow G in FIG. Although it is necessary to process the relief portion, in the present configuration shown in FIG. 5, the vane groove 20 can be cut to the outer periphery as shown by the arrow H, so that the processing is facilitated. Further, in the case of the first embodiment, the main vane groove 21 and the guide vane groove 22 shown in FIG. 1 are separately processed, but since the cylinder 5 and the main bearing 3 are integrated,
The main vane groove 21 and the guide vane groove 22 can be formed collectively, so that the process time can be reduced and the processing accuracy of both vane grooves 21 and 22 can be improved. In addition, since there is no step at the joint between the main vane groove 21 and the guide vane groove 22 by forming them all at once, it is possible to prevent leakage of the refrigerant and one-sided contact.

Therefore, the reliability and efficiency can be improved as compared with the first embodiment, and the cost can be further reduced.

(Embodiment 3) Next, a third embodiment of the present invention will be described with reference to FIGS. FIG. 6 is a longitudinal sectional view of a main part of a rotary compressor according to a third embodiment of the present invention, and FIG. 7 is an explanatory diagram of a roller groove.

This embodiment is different from the first embodiment shown in FIG. 1 in that the reliability and efficiency are further improved.
The outer peripheral portion of the roller 7 in the first embodiment of FIG.
As shown in FIG. 7B, a roller 26 having a roller groove 27 formed in parallel with the axial direction of the crankshaft 2 is provided on the roller 26, and as shown in FIG. It is configured to be fitted. The vane groove 20 and the vane 19 are the same as in the first embodiment.

According to the above configuration, when the crankshaft 2 rotates, the vane 19 reciprocates in the vane groove 20 with the tip end inserted in the roller groove 27, and the roller 26
9 Swing around the center of the arc at the tip.

Referring to the sliding at the roller groove 27, the tip of the vane 6 and the outer periphery of the roller 7 are in line contact with each other in the first embodiment of FIG. In this case, as shown in FIG. 7A, the groove surface of the roller groove 27 comes into surface contact with the arc surface at the tip of the vane 19, so that the surface pressure of the sliding portion can be reduced. Further, the sliding speed of the roller 26 can be made smaller than the conventional one because the amplitude of the swinging motion of the roller 26 is as small as about twice the eccentricity e in FIG. As described above, since the surface pressure and the sliding speed can be reduced, the sliding conditions can be relaxed, and the reliability can be improved.

Further, according to the above configuration, the leakage of the refrigerant gas from the compression chamber 11 partitioned by the vane 19 to the suction chamber 10 increases the contact area between the tip of the vane 19 and the roller groove 27, and the sealing length is reduced. The longer the length, the less likely it is to leak, the higher the performance, and the higher the rate.

Therefore, according to the present embodiment, the first
In this embodiment, the reliability and efficiency can be further improved.

Further, in addition to the configuration of the third embodiment shown in FIG. 6, a configuration using a cylinder bearing block 25 (see FIG. 4) in which the cylinder 5 and the main bearing 3 are integrated is adopted. The reliability and efficiency can be improved as compared with the third embodiment, and the cost can be reduced similarly to the above-described second embodiment.

By adopting the structure of the above-described first to third embodiments, even when the operating condition is such that carbon dioxide having a high pressure of about 10 MPa is used as the refrigerant, the sliding condition at the tip of the vane 19 and the side surface of the vane is conventionally higher. Can be reduced, so that efficiency and reliability can be improved. Since the high pressure acts on the rear end of the vane 19, the vane 19
It is effective to reduce the thickness of the vane 19 in order to suppress the force acting on the sliding portion at the tip of the vane. At this time,
According to the configuration of the above embodiment, since there are many support points with the guide vane portion, it is advantageous in terms of strength, and the vane can be made thinner than before.

In the first to third embodiments, the fluid handled in the rotary compressor of the present invention is described as a chlorine-free refrigerant such as HFC134a or a refrigerant such as carbon dioxide. However, the present invention is not limited to this.

In the first to third embodiments, the guide vane groove 22 is provided on the main bearing 3. However, a configuration in which the guide vane groove 22 is provided on the auxiliary bearing 4 side is also possible, and the same effect as described above can be obtained.

Further, as shown in FIG. 3B, guide vanes 24 are formed on both sides of the main vane 23,
By configuring the guide vane groove portion 22 in both the main bearing 3 and the sub bearing 4, the above effects can be obtained.

In the first embodiment shown in FIG. 3A, the thickness t1 of the main vane portion 23 and the thickness t2 of the guide vane portion 24 are the same, but it goes without saying that they may be different. No. Further, the widths h2 and h2 ′ of the guide vanes 23 on both sides shown in FIG. 3B may be different, and the same effect as described above can be obtained.

The inner end side of the guide vane groove portion 22 near the shaft 2 (the M portion indicated by the arrow in FIG. 2) is the same as the outer diameter of the shaft 2 as indicated by the N portion indicated by the arrow in FIG. When the groove is continuous to the sliding surface of the bearing 3, the processing of the guide vane groove 22 is further facilitated, and the cost can be reduced.
Further, lubricating oil can be easily supplied to the main bearing 3 and the vane groove, and the reliability can be improved. Of course, secondary bearings
The same applies to the four sides.

[0038]

As apparent from the above description, according to the present invention, the force acting on the vane due to the pressure difference between the suction chamber and the compression chamber is controlled by the main vane in the main vane groove, Because it can be received by the guide vane in the vane groove, the surface pressure is lower than the conventional configuration,
Since the vane is not cantilevered, it is difficult to hit the cantilever, and the sliding conditions are greatly eased. Therefore, even when HFC134a or the like, which does not contain chlorine in the refrigerant itself and has poor lubricity, is used as the refrigerant, the reliability of the rotary compressor can be improved and the sliding loss can be reduced and the efficiency can be improved. Is what you can do.

According to the second aspect of the present invention, since a vane groove having a main vane groove portion and a guide vane groove portion is formed in a cylinder bearing block in which a cylinder and a main bearing are integrally formed, machining and assembly are easier than before. And the accuracy is also improved. Therefore, the reliability and efficiency of the rotary compressor can be improved, and the cost can be further reduced.

According to a third aspect of the present invention, a vane having a guide vane portion is used, and a roller groove for fitting the vane tip is provided on the outer periphery of the roller. Gas leakage can be prevented and reduced. Therefore, the efficiency of the rotary compressor can be further improved.

According to a fourth aspect of the present invention, a cylinder bearing block in which a cylinder and a main bearing are integrally formed is used, and a roller groove for fitting a tip end of a vane having a guide vane portion is provided on the outer periphery of the roller. In addition, the sliding conditions at the tip of the vane can be reduced, the leakage of the refrigerant gas at the tip of the vane can be reduced, and machining and assembly can be made easier with the cylinder bearing block.

Therefore, the reliability and efficiency of the rotary compressor can be further improved, and the cost can be significantly reduced.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a rotary compressor according to a first embodiment of the present invention.

FIG. 2 is a cross-sectional view of a DD section of FIG.

FIG. 3 is a perspective view of a vane according to the first embodiment of the present invention.

FIG. 4 is a sectional view of a main part of a rotary compressor according to a second embodiment of the present invention.

FIG. 5 is a transverse cross-sectional view taken along a line FF in FIG. 4;

FIG. 6 is a cross-sectional view of a main part of a rotary compressor according to a third embodiment of the present invention.

FIG. 7 is an enlarged view of a roller groove portion according to a third embodiment of the present invention.

FIG. 8 is a longitudinal sectional view of a conventional rotary compressor.

FIG. 9 is a cross-sectional view taken along the line AA of FIG. 8;

[Explanation of symbols]

 2 Crankshaft 3 Main bearing 4 Secondary bearing 5 Cylinder 6, 19 Vane 7, 26 Roller 8, 20 Vane groove 21 Main vane groove 22 Guide vane groove 23 Main vane part 24 Guide vane part 25 Cylinder bearing block

 ──────────────────────────────────────────────────の Continuing on the front page (72) Inventor Fumitoshi Nishiwaki 1006 Kadoma Kadoma, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd.

Claims (8)

[Claims] 1. A cylinder, a main bearing and a sub-bearing located at both ends of the cylinder, and rotatably housed between the main bearing and the sub-bearing, the cylinder being fitted to a crank rotation shaft having an eccentric portion. A roller that rotates eccentrically inside,
A main vane groove provided in the cylinder and a vane groove formed of a guide vane groove provided in communication with the main vane groove in at least one of the main bearing and the sub-bearing, and reciprocating in the vane groove. A compression mechanism unit having a vane that abuts the roller and divides the inside of the cylinder;
A rotary compressor, comprising: an electric drive unit that drives the compression mechanism unit; and a sealed container that houses the compression mechanism unit and the electric drive unit. 2. The rotary compressor according to claim 1, wherein one of the main bearing and the sub-bearing and the cylinder are formed integrally. 3. The rotary compressor according to claim 1, wherein a concave groove on which the tip of the vane is disposed is provided on an outer periphery of the roller. 4. The roller according to claim 1, wherein a concave groove portion is provided on an outer periphery of the roller, where the tip of the vane is disposed in contact with the roller, and one of the main bearing and the sub-bearing and the cylinder are formed integrally. The rotary compressor according to claim 1, wherein 5. The vane portion reciprocating in the guide vane groove protrudes longer than the vane portion reciprocating in the main vane groove. Rotary compressor. 6. The bearing according to claim 1, wherein at least the guide vane groove provided in the main bearing or the sub bearing is formed so as to communicate with a bearing sliding surface of the main bearing or the sub bearing. The rotary compressor according to any one of the above. 7. The rotary compressor according to claim 1, wherein the rotary compressor is operated using a refrigerant containing no chlorine as a fluid. 8. The rotary compressor according to claim 1, wherein the rotary compressor is operated using a refrigerant containing carbon dioxide as a main component as a fluid.