JPS62139991A - Scroll type compressor - Google Patents

Abstract

PURPOSE:To enable a static pressure thrust bearing having a high load capacity to be simply constituted by disposing an annular groove on a thrust receiving surfaces formed on the upper surface of an upper block and the back of a turning scroll and an annular seal member on the outer peripheral portion of said groove to supply high pressure fluid to the annular groove. CONSTITUTION:Thrust bearing surfaces 23a, 23b are provided on the upper surface of an upper block 21 opposed to the back of an end plate 1b of a turning scroll 1 and on the back of the turning scroll 1 respectively, and an annular groove 24 is disposed on the thrust bearing surface 23a. A seal groove 26 and an annular seal member 27 are disposed on the outer peripheral portion of said groove 24. And by supplying high pressure fluid to said annular groove 24 can be constituted a static pressure thrust bearing with high load capacity. Thus, the static pressure thrust bearing capable of supporting sufficiently uniformly a thrust load acting on the turning scrol 1 can be simply constituted, and the sliding resistance due to the turning motion of turning scroll 1 can be reduced to reduce a drive force and improve the durability and reliability.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a thrust bearing for a scroll compressor used in a refrigeration device such as an air conditioner.

Conventional technology Scroll compressors have fewer component parts than other types of compressors, and because the compression operation is continuous, there is less fluctuation in drive torque and vibration, and the relative speed of sliding parts is small. It is said to have an advantage in high speed.

An example of a conventional scroll compressor shown in FIG. 4 will be described below.

An orbiting scroll 1 having a spiral wrap 1b standing upright on an end plate 1&, and a fixed scroll 2 consisting of an end plate 2a and a lug 2b having substantially the same shape as the orbiting scroll 1.
A rotation preventing means called an Oldham ring 4 is provided between the orbiting scroll 1 and a frame 3 connected to the fixed scroll 2 at the outer peripheral portion thereof. An eccentric shaft 7 having an eccentric amount e is formed on the eccentric shaft 6 rotatably supported by a bearing 6 of the frame 3, and is rotatably engaged with the bearing portion 8 of the orbiting scroll 1. 6 is rotationally driven by an electric motor 9. Further, the eccentric shafts are provided with a balance member 10 for keeping rotational balance between the eccentric shaft 7 and the orbiting scroll 1 engaged therewith. The compression mechanism configured as described above is housed in a closed container 11. Lubricating oil 12 is sealed in the bottom of the closed container 11, and a suction pipe 14 leading to a compression chamber 13 and a high-pressure fluid are installed in the body. A discharge pipe 15 is provided for taking out the water.

The operation of the scroll compressor constructed as described above will be described below with reference to FIG. 6, which is a sectional view taken along the line xx in FIG. 4.

The fluid sucked from the suction pipe 14 flows through the orbiting scroll 1 (1
a, 1b) and a fixed frame 2 (2a.

The compression chambers 1sa and 13b located on the outer circumferential side of the compressor 13, which is a closed space formed by The fluid in the compression chamber moves to the center of both scrolls 1 and 2 while gradually reducing its volume, increases the pressure, and is discharged into the closed container 11 from the discharge hole 16 of the middle of the fixed scroll 2. Further, the high pressure fluid flows through the passage 17 to the lower part of the closed container 11 and flows from the discharge pipe 15 to an external device.

Furthermore, the lubricating oil 12 accumulated at the bottom of the closed container 11 rises in the oil supply hole 18 provided inside the eccentric shaft 6 by the discharge gas pressure of the compressor itself, and moves the orbiting scroll 1 between the eccentric shaft 7 and the oil supply hole 18 . The oil sump 19 formed between the orbiting scroll 1 and the frame 3 passes through the gap in the bearing section composed of
The Oldham ring 4 and the orbiting scroll 1 are
The sliding parts between the end plate 1a, the fixed scroll 2, and the frame 3 are supplied with oil and have a lubricating effect.

Problems to be Solved by the Invention However, in the above-described configuration, particularly in the method of supporting the orbiting scroll 1 on the outer periphery of the end plate 1a, the compression chamber 13
The thrust load due to the high pressure gas generated inside is several 100K.
g or 1ooOKf, so orbiting scroll 1
It is difficult to reliably support the thrust load on the sliding surface between the mirror plate 1a and the frame 3, and this causes problems such as abnormal wear and an increase in rotational torque.

In view of the above problems, the present invention provides a scroll compressor in which a static pressure type thrust bearing is configured using the compressor's own high pressure source.

Means for Solving the Problems In order to solve the above problems, the scroll compressor of the present invention has an annular groove communicating with the high pressure section formed on the upper surface of the stationary member opposite to the back surface of the end plate of the orbiting scroll. An annular seal member is disposed on the outer periphery to seal the gap between the back surface of the end plate and the upper surface of the stationary member, and fluid from the compressed high pressure section is conducted through the annular groove to constitute a hydrostatic thrust bearing. It is.

Effect The present invention has the above-mentioned structure, and the weight of
It is possible to realize a hydrostatic thrust bearing that can sufficiently and uniformly support the thrust load acting on the orbiting scroll, which can reach up to 100 kg, with a simple structure. The load can also be reduced.

Example Below, regarding a scroll compressor according to an example of the present invention,
This will be explained with reference to the drawings.

FIG. 1 is a longitudinal cross-sectional view of a scroll compressor according to an embodiment of the present invention, and FIG. 2 is a YY cross-sectional plan view of FIG. 1. In Figs. 1 and 2, the reference numeral 4 indicates the conventional example.
Components that are the same as those shown in the figures have the same functions, so detailed explanations thereof will be omitted.

Orbiting scroll 1 and fixed scroll 20, 2 tubes 1b
, 2b face each other and engage with each other, and the orbiting scroll 1 is engaged with an eccentric shaft 7 of a shaft 6 via a bearing portion 8. The fixed scroll 2 is connected to an upper block 21, which is a stationary member, at its outer circumference, and the upper block 2
Upper depression of 1? An Oldham ring 4 serving as rotation prevention means is provided between the upper block 21 and the orbiting scroll 1.

The upper surface of the upper block 21 is a thrust receiving surface 23a, and an annular groove 24 is formed on this surface, and a pressure supply path 25 for supplying fluid to the high pressure section in the closed container 11 is formed in the annular groove 24. Drill a hole. Further, a seal groove 26 is formed on the outer peripheral side of the annular groove 24, and the annular seal member 2 is inserted into the seal groove 26.
7 is inserted with a clearance that can be moved in the vertical direction, and the seal member 27 floats due to the pressure difference acting on the seal groove 26, and its upper surface is connected to the thrust receiver of the upper block 21 provided on the back surface of the orbiting scroll 1. The rotating thrust receiver corresponding to surface 23a is sized to be in contact with surface 23b.

A lower block 28 having a main bearing 6 that rotatably supports the shaft 6 is fixed to the lower part of the upper block 21,
A space 29 is formed between the upper and lower blocks 21, 28 in which a balance member 1o disposed on the shaft 6 and used to balance the rotational balance around the shaft 6 can rotate.

The discharge hole 1 is compressed in the compression chamber 13 and is connected to the annular groove 24 described above.
High-pressure fluid discharged into the closed container 11 from the fixed scroll 2 and upper block 21 is supplied from the fluid passage 30 provided between the fixed scroll 2 and the upper block 21 and the closed container 11 through the pressure supply path 26.

In addition, 9 is an electric motor that rotationally drives the shaft 6, 12 is lubricating oil collected at the bottom of the closed container 11, and 18 is the lubricating oil 12.
This is an oil supply hole provided in the shaft 6 to push up the oil by differential pressure.

Next, the pressure relationship in the main parts inside the compressor will be explained. Suction pipe 14
The low-pressure fluid that has been sucked moves from the outer circumferential side to the center in the compression chamber 13, which is closed between the wraps 1b and 2b of the orbiting scroll 1 and the fixed scroll 2, increasing the pressure, and increasing the pressure in the center of the fixed scroll 2. It is discharged from the discharge hole 16 and makes the entire inside of the closed container 11 high pressure. The lubricating oil 12 accumulated at the bottom of the closed container 11 is pushed up through the oil supply hole 18 in the shaft 6 by the high pressure.
It is depressurized by the minute gap and flows into the space 29.

On the other hand, the outermost chamber of the compression chamber 13 and the recess 22, which is the orbiting space of the orbiting scroll 1, communicate through an end plate gap 31, and further communicate with the space 29 through a low pressure passage 32. Therefore, the space 29 maintains a low pressure state substantially close to the suction pressure.

A part of the high pressure fluid discharged from the discharge hole 16 is transferred to the pressure supply path 2.
6, the thrust receiver of the upper block 21 flows into the annular groove 24 provided on the surface 23a, and the thrust receiver is evenly supplied to the minute gap between the surface 23a and the rotating thrust receiver surface 23b. The high pressure fluid then leaks into the aforementioned space 29. At this time, since the annular seal member 27 is provided on the outer peripheral side of the surface 23a of the thrust receiver and the surface 23b of the rotating thrust receiver, most of the high-pressure fluid leaks inward.

Based on the above pressure relationship, the principle of the thrust bearing will be explained in detail with reference to FIG. 3, which is a detailed view of the surface of the thrust bearing.

High-pressure fluid is supplied from the pressure supply path 26 to the annular groove 24 through the throttle 33, which is a small diameter hole. The high-pressure fluid spreads along the annular groove 24 between the thrust bearing surfaces 23a and 23b, flows into the seal groove 26 provided on the outer periphery of the annular groove 24, and floats the annular seal member 27 by the pressure. The high pressure fluid whose outer periphery is sealed leaks into the space 29 in the low pressure region through the gap 34 between the thrust receiver surfaces 23a and 23b.

At this time, the pressure distribution on the surfaces 23a and 23b of the thrust receiver becomes a distribution as shown by P in the figure. At this time, a thrust load W due to the compressed fluid acts on the orbiting scroll 1, and by pushing the orbiting scroll 1 downward, the clearance 34 between the surfaces 23a and 23b of the thrust receiver is reduced.
Because the amount of leakage of high-pressure fluid is reduced, the thrust receiver is
The pressure P generated at points a and 23b further increases. Note that even if the pressure P increases, the amount of backflow to the pressure supply path 26 due to the throttle 33 is small, so the pressure P acts as a force sufficient to maintain the thrust load W of the orbiting scroll 1.

Here, if the annular seal member 27 is not provided, the high-pressure fluid will flow through the thrust bearing surface 23a.

23b also leaks toward the outer circumference, and pressure P cannot be obtained as a large force.

As described above, according to this embodiment, the thrust receivers are provided on the upper surface of the upper block 21 and the back surface of the orbiting scroll 1 on the surfaces 23a and 2.
3b, the thrust receiver has an annular groove 24 on the surface 23a, a seal groove 26 and an annular seal member 27 on the outer periphery thereof, and supplies high-pressure fluid to the annular groove 24, thereby achieving a high load capacity static It becomes possible to configure a pressure thrust bearing.

In the above embodiment, the seal groove 26 and the annular seal member 27 are provided on the upper block 21, but they may be provided on the back side of the orbiting scroll 1.

Effects of the Invention As described above, the present invention enables a simple construction of a hydrostatic thrust bearing that can sufficiently and uniformly support the thrust load acting on the orbiting scroll, reduces sliding resistance due to the orbiting motion of the orbiting scroll, and improves drive performance. It can reduce force and improve durability and reliability.

[Brief explanation of drawings]

FIG. 1 is a longitudinal cross-sectional view of a scroll compressor according to an embodiment of the present invention, FIG. 2 is a YY cross-sectional plan view of FIG. 1, and FIG.
The figures are an enlarged sectional view of the main part of FIG. 1, FIG. 4 is a vertical sectional view of a conventional scroll compressor, and FIG. 5 is a sectional plan view taken along the line xx in FIG. 4. 1... Orbiting scroll, 1b... End plate, 21... Stationary member, 24... Annular groove, 26... Supply pressure path, 27...Annular seal member. Name of agent: Patent attorney Toshio Nakao and 1 other person27
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Claims (1)

[Claims] A fixed scroll consisting of an end plate and a spiral wrap standing upright thereon and an orbiting scroll are provided, both scroll members are engaged with each other with the wrap inside, and a rotation prevention means is provided between one of the orbiting scrolls and the stationary member, It is equipped with an eccentric shaft that makes the orbiting scroll orbit and a bearing means that supports it, and when the orbit scroll makes the orbit movement, the closed space formed by both scrolls moves while decreasing its volume, compressing the fluid. In a scroll compressor, an annular groove communicating with a high pressure section is formed on the upper surface of a stationary member opposite to the back surface of an end plate of an orbiting scroll, and a gap between the back surface of the end plate and the upper surface of the stationary member is sealed at the outer periphery of the annular groove. A scroll compressor characterized in that a hydrostatic thrust bearing is configured by disposing an annular seal member.