JPH01219377A - Scroll compressor - Google Patents

Abstract

PURPOSE:To improve the extent of abrasion resistance by installing a race, which rotates in response to turning motion of a turning scroll, in each end face of the turning scroll, where a ball is slidden in contact, and a block. CONSTITUTION:A ringlike, turning scroll side race 24 is installed at the opposite lap side back of a turning scroll 5 free of rotational motion, and a ringlike, block side race 25 is installed in an end face of a block 3 being opposed to the turning scroll side race 24 free of rotational motion as well. With this constitution, the maximum load of thrust force being produced by compressive action is no longer imposed on the same part of balls 26a-26x and the races 24, 25, and thereby it is uniformly supported by all the circumference, so that local wear in these races 24, 25 and consequent separation and wear in these balls 26a-26x are all brought to nothing, thus abrasion resistance is improved.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to scroll compressors used in refrigeration cycles and the like, and particularly relates to improving the reliability of thrust slide bearings.

Conventional technology A conventional configuration will be explained with reference to FIGS. 3 to 6.

1 is a sealed casing, 2 is! This is the motive part, and the block 3. Fixed Souflo 1v4. Rotating Nucrow IV
5. A mechanical part main body 7 constituted by an anti-rotation mechanism 6 is fixed. The fixed flow /l/4 is composed of an end plate 4a and an involute standing upright on the end plate 4a, or a wrap 4b having a thickness similar to a curve similar to an involute, and is fixed to the block 3 by the end plate 4a. or,
The rotating suflow/I/6 stands upright on the end plate 6a and the m-plate 6a, and is constructed with a wrap 6b having the same curve as the wrap 4b of the fixed suflow/I/4.
The 1v4 end plate 4a and the block 3 are sandwiched and supported with a clearance A, and are restrained by an anti-rotation mechanism 6 called an Oldham mechanism. The fixed flow A/4 and the orbiting scroll 6 are arranged in each lap 4b, s.
Winding end 4b' of b.

They are combined with es b' shifted by a certain angle.

8 is a discharge hole, 9 is a suction hole, the discharge hole 8 is provided in the center of the involute of the fixed flow A/4, and the suction hole 9 is provided at the outer edge of the end plate 4a of the involute of the fixed flow A/4. It is being Reference numeral 10 denotes a protrusion provided on the surface of the swirling flow lv6 opposite to the lug 5b, and is concentric with the center of the involute of the wrap 5b. Reference numeral 11 denotes a shaft supported by the block 3 via a thrust bearing 12, and a boss portion 11a provided at the end of the main body 7 of the machine section and eccentric from the center of the shaft houses the projection 1o of the swing flow/I/6. By doing so, the electric motor part 2 and the rotating flow)
V5 is connected. In addition, an oil supply hole 11b penetrates through the center of the shaft 11, and a boss portion 1 of the shaft 11 is provided.
1a and the shaft storage space 13 formed by the protrusion 1o of the rotating flow/L'5 and the lower part of the sealed casing 1 are communicated with each other. Reference numeral 14 denotes a back pressure chamber formed on the back surface of the rotating flow 1%/6, and the wrap Sb side of the rotating flow/I15 communicates with the low pressure section through the clearance A of the head plates 5a and 4a.

15 is a bolt 16 on the back side of the orbiting scroll 6 on the opposite side.
Annular orbiting scroll side fixed at
, 1" tri It is an annular block side race fixed to the end face of the block 3 opposite to the orbiting scroll side race 15 with a port 18.

19a to 19I are a plurality of balls arranged between the orbiting scroll side race 16 and the block side race 17, and the holes 20a to 20x have the same number as the holes 19a to 19x.
They are held by a retainer 20 so as not to come into contact with each other. Further, the retainer 20 has the above-mentioned rotating flow/I
/6 rotational movement in response to the turning movement.

21 is a suction pipe communicating with the suction hole 9, and 22 is a discharge pipe. Further, 23 is lubricating oil accumulated in the lower part of the sealed casing 1.

Next, the compression mechanism of the scroll compressor will be explained. The rotational motion of the shaft 110 accompanying the rotation of the electric motor section 2 is transmitted to the orbiting scroll A 15 via the boss section 11& and the projection section 10, but due to the action of the rotation prevention mechanism 6, the orbiting scroll 6 does not rotate on its own axis and moves to the fixed scroll A15. It rotates around the center of the /4 involute as the center of rotation. At this time, the winding end cs of the wrap 6b of the rotating flow/I15
Inhalation is complete when b' is in contact with the wrap 4b of the fixed spflow/I/4 and the winding end 4b' of the wrap 4b of the fixed spflow/I/4 is in contact with the wrap 6b of the rotating spflow/115. The pressure in the compression space S increases as the two contact points between the wrap 4b and the flop b approach the center of the involute due to the revolution of the rotating flow/L15.

By the compression mechanism of this scroll compressor, the refrigerant sucked in through the suction pipe 21 and the suction hole 9 is compressed and once discharged into the sealed casing 1 through the discharge hole 8, and then through the discharge pipe 22. At this time, as the pressure in the compression space S increases, a thrust force is generated between the stationary flow /L/4 and the rotating flow /L15 to pull them apart in the axial direction. Conventionally, this thrust force is partially maintained by the low pressure introduced into the back pressure chamber 14 on the back surface of the orbiting scroll 6 through the clearance A, and most of it is maintained by the orbiting scroll 6/l.
The retainer 20 (7) hole 2 is disposed between the end plate 6a of /6 and the block 3 in response to the turning movement of the turning flow A15.
0 a~2 Balls 19a~19x that move freely in Ox
(e.g., U.S. Pat. No. 3,600)
, No. 114).

Problems to be Solved by the Invention Since the above-mentioned thrust force acts on the thrust bearing of a scroll compressor as an eccentric load, and this eccentric load fluctuates during one revolution of the shaft, The maximum load will be applied to the thrust bearing at that position.

At this time, the balls do not move freely in the direction provided on the retainer, but rotate together with the retainer, so the balls take the maximum load one after another. Therefore, there is no possibility that some of the balls will wear out due to the large load acting on them.

However, in the above configuration, the race aimed at improving wear resistance is fixed to the end face of the orbiting scroll and block that slide in contact with the balls, so the variable load mentioned above acts on the race, and the maximum load is It acts on a fixed position. Therefore, despite aiming for wear resistance, the race wears out, and with this wear, the balls also wear out and peel off.

In view of the above problems, the present invention provides a scroll compressor with excellent wear resistance of a thrust bearing that receives an eccentric load.

Means for Solving the Problems In order to solve the above problems, the scroll compressor of the present invention includes a race that rotates in response to the orbiting movement of the orbiting scroll on the end face of the orbiting scroll and the block on which the port slides in contact. It is prepared.

Function: With the above-described configuration, the present invention can eliminate local wear of the thrust bearing on which eccentric loads are applied, and can provide a highly reliable scroll compressor.

EXAMPLE An example of the present invention will be described below with reference to FIGS. 1 and 2. Incidentally, the same parts as in the conventional example are given the same reference numerals, and the description thereof will be omitted.

Reference numeral 24 denotes an annular orbiting flow /L/4A loose provided on the rear surface of the orbiting scroll 6 on the opposite side of the lap, and is not fixed to the orbiting flow /L15, but is provided so as to be freely rotatable. Reference numeral 25 denotes an annular block-side race provided on the end face of the block 3 facing the orbiting scroll-side race 24, and is not fixed to the block 3 but is provided so as to be freely rotatable.

26a~26! A plurality of balls are arranged between the orbiting scroll side race 24 and the block side race 26, and the holes 27a to 27 have the same number as the ports 1v26a to 26x.
They are held so as not to come into contact with each other by retainers 27 having an angle x, and the retainers 27 are provided without being fixed so as to rotate in response to the orbiting motion of the orbiting scroll 6.

Next, we will discuss the operation.

When the scroll compressor starts compression, the above-mentioned thrust force is generated, and most of this thrust force is generated by the po/I/2 that freely moves inside the holes 27a to 27χ of the retainer 27.
6a to 26x.

At this time, the retainer 27 receives force from the balls 26a to 26x that freely move within the holes 27a to 27x, and rotates on the block side race 26 together with the ports/I/26a to 26x.

In addition, since the orbiting scroll side race 24 and the block side race 26 contact and slide with the balls 26a to 26x, a slight frictional force is generated between them and the balls 26a to 26x.
This friction force causes the orbiting scroll side race 24 and the block side race 25 to rotate.

That is, when the rotating suflow/T'S performs a rotational movement and compression is performed, the retainer 27 responds to this rotational movement.
．． Beau/L'26a~26x, rotating suflo ° -μ side race 24. The block side race 25 will move in rotation.

Under such operation, the scroll compressor's 7
As mentioned above, the last bearing has a rotating flow/I/
The maximum load is applied when the position of 6 is reached, but among the elements that make up the thrust bearing, the thrust force is applied to the ports 4/26a to 26I, the orbiting scroll side race 24.
Since the block side race 26 rotates in response to the orbiting motion of the orbiting scroll 6, the maximum load is not applied to the same part9, and the P/L/26a to 26
The maximum load is evenly applied to all the numbers x, the entire circumference of the turning neck race 24 and the block side race 25.

Therefore, unlike in the past, the race does not wear locally and the ball also does not wear out or peel off due to this wear.
Wear resistance is improved.

Furthermore, since the ball and race rotate together, their relative speeds are reduced, resulting in the secondary effect of reduced sliding loss and improved efficiency.

Effects of the Invention As is clear from the above description, the present invention includes a retainer for holding the balls so that they do not contact each other and rotate in response to the orbiting motion of the orbiting scroll, and the balls contact and slide. Since the orbiting scroll and the end face of the block are equipped with a race that rotates in response to the orbiting motion of the orbiting scroll, the maximum load of the thrust force generated by the compression action is not applied to the same part of the ball and race, and is evenly distributed. Since the bridge is held all around the circumference, local wear of the race and accompanying peeling and wear of the bow are eliminated, improving wear resistance. Additionally, since the relative speed between the bow and the race is reduced, it also has the secondary effect of reducing sliding loss.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal cross-sectional view of a scroll compressor showing an embodiment of the present invention, Fig. 2 is an enlarged view of the thrust bearing section of Fig. 1, Fig. 3 is a longitudinal cross-sectional view of a conventional scroll compressor, and Fig. 4 is a cross-sectional view taken along the IV-1r line in Fig. 3;
The figure is an enlarged view of the thrust bearing section in FIG. 3. 3...Block, 4...Fixed flow μ, 6...Orbiting scroll, e...Rotation prevention mechanism, 24...... Orbiting scroll side race, 26...Block side race, 26a~2
6x...Ball, 27...Retainer. Name of agent: Patent attorney Toshio Nakao and 1 other person 2nd
Figure Otsu 5 Do6m 27. , (Figure 3 Z3 t tb

Claims (1)

[Claims] two mutually interlocking orbiting and fixed scrolls having wraps standing upright on end plates, a block for fixing the fixed scrolls, an anti-rotation mechanism for preventing rotation of the orbiting scrolls and performing orbiting motion, and an anti-wrap for the orbiting scrolls. a plurality of balls disposed between the side surface and the block; and a retainer that holds the balls so that the balls do not contact each other and rotate in response to the orbiting movement of the orbiting scroll; A scroll compressor, wherein a race is provided on the end face of an orbiting scroll and a block that slide in contact with each other, and the race is arranged to be rotatable in response to the orbiting movement of the orbiting scroll.