JPH065072B2 - Horizontal rotary compressor - Google Patents

Description

Description: FIELD OF THE INVENTION The present invention relates to a horizontal rotary compressor incorporated in a refrigerating device such as a refrigerator or an air conditioner.

[Background of the Invention]

The structure and problems of the conventional horizontal rotary compressor will be described below with reference to FIGS. 4 to 6. FIG. 4 is a vertical cross-sectional view of a conventional horizontal rotary compressor (hereinafter referred to as a compressor), in which a stator 1 of an electric element, a rotor 5, and a frame 6 having a compression element are housed in a case 1. Oil 17 is stored below. The rotating shaft 7 is arranged substantially horizontally, and the rotor 5
Roller 10 for eccentrically rotating the inner wall of cylinder 8
To drive. The oil 17 is sucked from the intake valve 11 by the oil supply pump using the back surface of the vane 15, and the oil supply pipe 1
2, the rotary shaft is refueled. From the oil groove provided on the rotary shaft 7, a part of the oil is discharged from the roller 10 and the crank pin portion 7.
It flows into the spaces 13 and 14 between d. As shown in FIGS. 5 and 6, the spaces 13 and 14 are eccentric with respect to the axial center, so that the rotation of the rotating shaft 7 causes centrifugal force to act on the oil 17 accumulated inside the spaces 13 and 14. And because hydraulic pressure is generated,
Axial thrust is generated on the crank pin portion 7d. Here, since the roller 10 and the cylinder 8 have a slight clearance in the axial direction, oil leaks from the spaces 13, 14 to the low pressure side inside the cylinder, and as a result, the spaces 13, 14 are leaked.
The oil pressure generated at the time fluctuates, and the shaft thrust also fluctuates, so that the rotating shaft 7 may rise in the axial direction from the thrust bearing to make a strong knocking sound of the thrust bearing 7a. The noise characteristic of the compressor at this time is shown in FIG. It occurred in a wide frequency band as shown in the figure.
Conventionally, as a countermeasure against this, a magnetic thrust acting on the rotor and the stator has been given by assembling the rotor 5 and the stator 4 by previously shifting the magnetic centers by a length δ in the axial direction.
In this case, there is a drawback that the efficiency of the motor is lowered, and when the stator 4 is displaced to the lid 2 side, since it comes close to the welding portion 3, the binding thread of the end coil 4a of the stator 4 is cut by welding heat. It had drawbacks. Furthermore,
When the number of rotations is increased, or in a large compressor, the hydraulic pressure generated in the spaces 13 and 14 increases, so that it is no longer possible to deal with it only by shifting the magnetic centers of the rotor 5 and the stator 4. Also had. As described above, in the case of the horizontal compressor, the weight of the rotor 5 does not act on the thrust bearing as in the vertical compressor, which is an unavoidable structural problem. Further, if such a knocking sound of thrust is continuously generated, abnormal wear of the thrust bearing may be caused, which is a problem in terms of reliability.

As an example of this type of compressor, US Pat. No. 3,130,9
There is specification No. 02.

[Object of the Invention]

An object of the present invention is to eliminate the above-mentioned drawbacks of the prior art and to provide a compressor with low noise and excellent reliability to the market.

[Outline of Invention]

According to the present invention, a space, which is covered by the crank pin portion, the roller, and the bearing end portion and is eccentric with respect to the shaft center, is provided on the anti-thrust side inside the roller, and the centrifugal force of the shaft rotation is applied to the oil accumulated in the space. The hydraulic pressure is generated, and the hydraulic pressure presses the shaft toward the thrust side to prevent the shaft from floating from the thrust and to prevent abnormal vibration of the shaft that causes thrust striking noise.

Example of Invention

An embodiment of the present invention will be described below with reference to FIGS. Inside the case 1, a stator 6 which is an electric element, a rotor 5, and a frame 6 having a compression element are housed, and oil 17 is stored in the lower part. The compression element includes a cylinder 8 fixed to the frame 6 and a rotating shaft 27 driven by the rotor 5, a roller 10 mounted on a crank pin portion 27d of the rotating shaft 27 and rotating along an inner wall of the cylinder 8, and a roller 10. The vane 15 reciprocates while being in contact with the outer circumference of the vane. The rotary shaft 27 has a thrust bearing 27a over substantially the entire end surface of the crank pin portion 27d on the frame 6 side.
And a space 13 that is covered with the inside of the roller 10, the end surface of the frame 6 and a part of the crank pin portion 27d.
Of the roller 1 and the crank pin portion 27d on the opposite side of the thrust bearing 27a.
Space 14 covered by the inside of 0 and the end surface of sub bearing 9
That is, the shape of the crank pin 27d of the rotary shaft 27, that is, the shape of the thrust bearing 27a on one end surface and the shape of the other end surface are unbalanced. .

The operation of the compressor of the present invention configured as described above will be described below. By the oil supply pump utilizing the reciprocating motion of the vane 15, the oil 17 stored in the bottom portion of the case 1 is sucked from the intake valve 11 and the oil supply pipe. The rotary shaft 27 is refueled with the oil 12. The oil 17 lubricates the oil of the crank pin portion 27d and the roller 10 through the oil supply hole 27b communicating from the inner diameter of the rotary shaft 27 to the crank pin portion 27d and the oil supply groove 27c.
Further, as shown in FIG. 3, the oil 17 flows into the space 14 covered with the crank pin portion 27d on the opposite side of the thrust bearing 27a, the inner diameter of the roller 10 and the end surface of the sub bearing 9, as shown in FIG. Since 14 is eccentric with respect to the shaft center, a centrifugal force acts on the oil 17 filled in the space 14 by the rotation of the rotating shaft 27. As a result, a hydraulic pressure is generated in the space 14, and the hydraulic pressure presses the crank pin portion 27d toward the thrust bearing 27a side, so that the rotary shaft 27 can perform stable rotation, and the conventional compressor generates. As described above, it is possible to eliminate the knocking sound due to the lift of the thrust bearing. Although the present embodiment shows an example in which the thrust bearing 27a is formed on the frame 6 side, the same effect can be obtained even when the sub bearing 9 side is formed as a thrust bearing.

〔The invention's effect〕

According to the present invention, since the thrust bearing can be prevented from rising and the tapping noise can be prevented from being generated, the operation noise of the compressor can be reduced as shown in FIG. 7, and the abnormal wear of the thrust can be avoided. . Further, in the conventional compressor, in order to prevent the generation of the thrust tapping noise, the magnetic centers of the stator and the rotor are displaced from each other, which causes a reduction in motor efficiency. Since there is no need to shift it, it is possible to improve the efficiency of the motor. Further, in the conventional large-sized model and the compressor having a high rotational speed, the thrust tapping noise is remarkably generated, but the present invention can expand the applications of the horizontal rotary compressor. As described above, the present invention has a large practical effect with almost no increase in cost, and thus has a large practical effect.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a horizontal rotary compressor of the present invention, FIG. 2 is a sectional view taken along line AA of FIG. 1, and FIG. 3 is taken along line BB of FIG.
Sectional drawing, FIG. 4 is a longitudinal sectional view of a conventional compressor, FIG. 5 is an AA sectional view of FIG. 4, FIG. 6 is a BB sectional view of FIG.
FIG. 7 compares the noise characteristics. 1 ... Case, 2 ... Lid, 3 ... Welded portion, 4 ... Stator, 4
a ... End coil, 5 ... Rotor, 6 ... Frame, 7 ... Rotating shaft, 7a ... Thrust bearing, 7c ... Refueling groove, 7
d ... Crank pin portion, 8 ... Cylinder, 9 ... Sub bearing, 10 ... Roller, 11 ... Intake valve, 12 ... Oil supply pipe,
13 ... Thrust side space, 14 ... Anti-thrust side space, 15
... vanes, 16 ... discharge valve, 17 ... oil, 27 ... rotary shaft of the present invention, 27a ... thrust bearing, 27b ... oil supply hole,
27c ... Refueling groove, 27d ... Crank pin part.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Shigetaro Tagawa 800 Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Hitachi Co., Ltd. Tochigi factory (72) Inventor Yozo Nakamura 502, Kamimachi-cho, Tsuchiura-shi, Ibaraki Hitate Co., Ltd. Machinery Research Laboratory of Manufacturing Co., Ltd. (56) References

Claims (1)

[Claims] 1. A part of an end surface of a crankpin portion of a rotary shaft is
In a horizontal rotary compressor in which a thrust bearing is configured by abutting either one of the frame and sub-bearing end faces that cover the cylinder from both ends, the inside of the roller, the frame end face, the sub-bearing end face, and both ends of the crankshaft pin Out of the two spaces on the thrust bearing side and the anti-thrust bearing side, which are covered with, the volume of the space on the anti-thrust bearing side is large and the volume of the space on the thrust bearing side is small. Compressor.