JPS63253189A - Scroll compressor - Google Patents

Abstract

PURPOSE:To optionally set a supply amount of oil, by forming a supply passage of oil for a thrust bearing by press work into a slit shape so that the supply passage of oil opens its one end to an internal peripheral edge side of the thrust bearing and blocks the other end in an optional position toward the outer in the diametric direction. CONSTITUTION:A thrust bearing 9 forms its supply oil passage 9a by press work and an depth D of the passage into a slit shape. The supply oil passage 9a opens its one end to an internal peripheral edge surface 9e of the thrust bearing and provides a final end part 9f in the other end in an optional plate communicating with a return oil hole 13 provided in a bearing support 10. Accordingly, the supply oil passage, being easily formed by press work, enables also a supply amount of oil to be optionally set.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a scroll compressor used for compressing refrigerant or air in refrigeration equipment, air conditioning equipment, etc.

[Conventional technology]

FIG. 15 is a sectional view of a conventional scroll compressor shown in, for example, Japanese Patent Application No. 59-64571, and is a specific example of applying the scroll compressor to a refrigeration system or an air conditioner. It is configured as a compressor for gases such as chlorofluorocarbons. In the figure, 1 is a fixed scroll, 1a is an end plate thereof, 1b is a spiral side plate such as an involute, 2 is an oscillating scroll, 2a is an end plate thereof, and 2b is a spiral side plate such as an involute. The compression chamber 5 is formed by assembling the side plates 1b and 2b eccentrically to each other. 6 is a suction chamber of the compression chamber 5, 7 is a suction hole provided on the outer periphery of the fixed suction pipe 1, 8 is a discharge pipe, 8 is the innermost peripheral chamber of the compression chamber 5,
4 is a discharge chamber; 9 is a thrust bearing that supports the lower surface of the end plate 2a; 10 is an upper bearing support that supports the main shaft via the main bearing 17; 18 is an oil return hole provided in the upper bearing support 10;
1 is a lower bearing support that supports the main shaft via the main bearing 18;
lla is a balancer chamber provided in the lower bearing support 11;
b is an oil return hole for discharging oil from the balancer chamber 11a.

The fixed scroll 1 and the bearing supports 10 and 11 are each coaxially combined by a pin (not shown) or a spigot part, and are fastened and fixed by a bolt (not shown) or the like. 12 is an Oldham joint which is an anti-rotation mechanism for preventing the rotation of the oscillating scroll 2 and causing it to revolve or oscillate, 14 is a crankshaft or main shaft that drives the oscillating scroll 2, and 16 is the axis of the main 1d114. The oil supply hole 16, which is eccentric to the center and penetrated in the axial direction, is a swing bearing that is provided eccentrically by a predetermined amount at the upper end of the main shaft 14, and the swing bearing 16 supports the shaft 2C. 17 is the upper bearing support lO
An upper main bearing 18 is fixed to the lower bearing support 11 by press fitting and rotatably supports the upper part of the main shaft 14, 19 is a lower main bearing fixed to the lower bearing support 11 by press fitting etc. and rotatably supports the lower part of the main shaft 14. The electric motor stator fixed to the lower main bearing 18 with bolts etc., 20 is the main 1llI14
Electric motor rotor fixed by press-fitting, shrink-fitting, etc.
1 is a first balancer fixed to the main shaft 14 by shrink fitting, etc.; 22 is a second balancer attached to the lower end of the motor rotor 2o;
The balancer 23 is a cylindrical oil pump fixed to the lower end of the main shaft 14 by shrink fitting or the like. Further, 24 is a lower shell that houses and fixes each of the above-mentioned members, and 25 is an upper shell that fits into the upper part of the lower shell 24 and seals the entire compressor by welding the fitting part. Each internal member is fixed by press-fitting or shrink-fitting the outer peripheral member of the lower bearing support H. 26 is a suction pipe provided on the side surface of the lower shell 24 and introduces suction gas from the lower part of the shell into the interior; 27 is oil stored at the bottom of the lower shell 24; 28 is provided above the oil 27 and is connected to the lower shell 24; A hole 28a for passing the main shaft 14 through the baffle plate is provided in the center of the baffle plate. 29 is a leg that supports the entire compressor and is fixed to the lower part of the lower shell 24 by welding or the like;
80 is a glass terminal fixed to the upper shell 25 by a ring projector or the like, and a lead wire (not shown) from the VD motive stator 19 is connected thereto.

When the scroll compressor configured as described above is energized, the main shaft 14 is rotated by the driving force generated in the electric motor stator 19 and the rotor 2o, and the swing bearing 16%
- Rotation is transmitted to the oscillating scroll 2 via. In response to this, the oscillating scroll 2 performs a so-called oscillating movement in which it moves while maintaining a constant angular number ζ relative to the upper bearing support 10, so that a compression action is performed. While such a compression action is being performed, gas is drawn into the compressor from the suction pipe 26 as shown by the dashed arrow, cools the upper part of the motor stator 19, and then flows through the passage around the outer periphery of the upper bearing support 1o (not shown). ) through the suction hole 7 of the fixed scroll 1.
and is inhaled into the suction chamber 6. After that, it is compressed and discharged W
It is discharged from 8.

During the movement of the compressor, the oil 27 in the lower shell 24 is sucked in from the tip of the oil pump 23, and the centrifugal force generated by the rotation of the main shaft 14 moves the shaft center a predetermined distance from the center of the main shaft 14. The oil rises within the oil supply hole 16 and the swing bearing 16 and the upper main bearing 17 are oiled. (This is a so-called centrifugal pump.) After this, the oil passes through the oil supply groove of the thrust bearing 9 and is discharged from the inner circumferential edge side of the thrust bearing 9 to the outer circumferential edge side. The oil is prevented from flowing out, falls into the balancer chamber 11a through the oil return hole 18, and is returned to the bottom of the lower shell 24 through the hole 28a of the baffle plate 28. In this way, during operation of the compressor, oil is continuously supplied to each bearing and the compressor is operated safely.

[Problem that the invention seeks to solve]

The restrust bearing 9 used in a conventional scroll compressor is provided with a radial or involute oil supply passage 9a from the inner peripheral edge side to the outer peripheral edge 9h side, as shown in FIGS. 16 to 19. is A1 alloy, P
Bearing layer 9 made of TFE (tetrafluoroethylene resin), etc.
b, and a degree Jr+'X9C made of a rolled steel plate that supports the bearing layer 9b by crimping or the like. At this time, generally i3 [distribution oil passage 9a is A1 alloy etc.
If it is within the depth range of the bearing layer 9b, it is generally formed by pressing, or if it is made of PTFE or the like, it is generally formed by cutting. First, let us consider a case in which the oil supply passage 9a is formed using a press. Generally, the bearing layer 9b has a thickness of about 0.6 to 0.9 ay at the time of crimping, and if this is surface-finished, the thickness of the bearing layer 9b can be reduced to 0.
．． It will be about 8 to 0.6 cm. Therefore, the depth D of the passage formed by the pressure I/S is considered to be about 0.8 to 0.6 bar.

By the way, as described in the oil supply path in a conventional scroll compressor, the oil 1 rising in the oil supply hole 15 is supplied to the swing bearing 16 and then reaches the upper main bearing 17 and the thrust bearing 9. At this time, it is clear that the amount of oil to be supplied should be set at the design stage so that sufficient oil can be supplied to each crest. At this time, if the oil supply passage 9a becomes narrow, it becomes difficult for oil to flow, resulting in a decrease in the amount of oil supplied. Especially the passage depth D
If it is 0.6 mm or less, it is necessary to widen the passage width W, shorten the passage length, or increase the number of passages. In such a state, the effective bearing portion (the area excluding the passage portion from the surface of the thrust bearing 9) 9
There is a problem in that d decreases and the surface pressure (load applied per unit area) increases, resulting in damage such as abnormal wear and seizure of the bearing.

Next, when forming the oil supply passage 9a by cutting,
Although the passage depth D can be set arbitrarily,
There are problems in that processing is time-consuming and deformation occurs due to processing.

Furthermore, in the conventional scroll compressor, as described above, the oil discharged from the inner circumferential edge side to the outer circumferential edge side of the thrust bearing oil supply passage 9a flows into the suction chamber 6 due to the minute gap between the oscillating scroll end plate and the Oldham joint 12. In this case, as shown in FIG. 20, in order to obtain the minute gap 81, the thickness of the thrust bearing 9, the height of the thrust bearing mounting surface 10a of the upper bearing support 10, and the Oldham coupling ring 12a
It is difficult to control the dimensions of the height, flatness, and even the height of the sliding surface 10b of the Oldham joint supporting the upper bearing (in particular, a great deal of effort was spent on grinding to obtain the flatness of the Oldham joint ring). ) As indicated by the solid line arrow in the figure, the oil could not be sufficiently prevented from flowing into the suction chamber 6 through the minute gap 81. According to experiments, when the minute gap 31 is narrowed to about 70 μm, the oil circulation amount (the weight ratio of oil to the refrigerant weight during refrigerant circulation during scroll compressor operation) can be reduced by 1%.
The flatness of the Oldham joint ring 12a can be made as follows,
High-precision processing such as thickness accuracy is required, which significantly increases costs. As a countermeasure against this, the thrust bearing oil supply passage 9a is closed at an arbitrary position from the inner circumferential edge side toward the radial outward, as shown in FIGS. It is conceivable to communicate with the oil return hole 13 provided in the. According to experiments, the gap between the thrust bearing sliding surface of the oscillating scroll end plate 2a and the thrust bearing 9 is filled with oil, and the thickness of the oil film is several μm.
It is. At this time, the oil circulation amount easily became 1% or less.

However, as mentioned above, the passage depth is 9 and the passage width W.

There is a limit to the setting of the passage length and the number of passages, and this has always caused problems in bearing reliability, processing methods, etc.

This invention was made to solve the above-mentioned problems, and it is possible to easily form an oil supply passage, and furthermore, the amount of oil supplied to the thrust bearing can be arbitrarily set. The objective is to obtain a reliable scroll compressor that can prevent excessive oil from flowing into the suction chamber and is free from seizure and damage.

[Means for solving problems]

In the scroll compressor according to the present invention, the oil supply passage of the thrust bearing is formed in the shape of a slit, one end of the oil supply passage is opened toward the inner peripheral edge of the thrust bearing, and the other end is opened radially outward. It is constructed so that it is closed by. Furthermore, a constriction part is provided near the closed part of the oil supply passage.

[Effect]

In the scroll compressor according to the present invention, the thrust bearing oil supply passage is formed by press punching and can be easily molded. A constricted portion is provided near the closed portion and communicates with an oil return hole that communicates with an oil reservoir at the bottom of the shell provided in the bearing frame. By doing so, the oil passes through the thrust bearing oil supply passage and is returned to the oil reservoir at the bottom of the shell through the oil return hole provided in the bearing frame.

[Embodiments of the invention]

An embodiment of the present invention will be described below with reference to FIG.

That is, only the parts that are different from the conventional device will be explained. 1st
The figure and FIG. 2 show a thrust III+h receiver 9 according to the present invention, and the oil supply passage 9a is formed by pressing. In this case, the passage depth D is equal to the plate thickness (thickness of the bearing layer 9b, thickness of the metal layer 9C)), which is a so-called slit shape, and the passage width W is within the pressable range (
In general, W≧1.5XD) is set, and the passage length can be decreased as desired. Further, as is clear from the figure, one end of the oil supply passage 9a opens at the inner circumferential side surface 9e of the thrust bearing.
The terminal end portion 9f at the other end is provided at an arbitrary location and communicates with an oil return hole 18 provided in the bearing support 10. .

Next, the flow of oil in the thrust bearing 9 in this embodiment will be described. In FIGS. 1 and 2, solid arrows indicate the flow of oil in the oil supply passage 9a, and the thrust bearing 9
The oil flows through the oil supply passage 9a from an opening provided on the inner circumferential side surface 9e and reaches the terminal end 9f. Here, the oil passes through the oil return hole 18 provided in the bearing support 10 and passes through the balancer chamber 1 shown in FIG.
1a, the oil is returned to the bottom of the lower shell 24 through the oil return hole ub. At this time, there is a small gap between the lower surface of the oscillating scroll end plate 2a and the opening of the effective bearing part of the thrust bearing, and although some oil flows there, it is a very small amount, and most of the oil flows into the lower shell. It is returned to the bottom in 24.

As mentioned above, the oil supply passage 9a has a passage depth of 1 passage width W.
The length of one passage and the number of passages can be arbitrarily selected, and specifications can be determined based on the amount of oil to be supplied to each of the bearings 16, 17, and 18.

In other words, when the passage depth D is shallow, the passage width W is comfortable, the passage length is long, and the number of passages is small, and the amount of supplied oil is small, the bearing will cause abnormal wear or seizure, then the passage depth D
It is possible to deepen the passage, widen the passage width W, shorten the passage length, or increase the number of passages. On the other hand, if the amount of oil to be supplied is large, you can perform the opposite operation. In addition, regarding the processing method, if the means for forming the passage is a press knife Roe,
The passage can be formed very easily.

Other embodiments are shown in FIGS. 8 to 6. The oil supply passage 9 is opened from an opening provided on the inner side surface 9e of the thrust bearing 9.
The flow of oil inside a is similar to the embodiment shown in FIGS. 1 and 2, but a throttle mechanism 9g is provided at the terminal end 9f. That is, the amount of oil supplied to the thrust bearing 9 can be arbitrarily set depending on the passage depth, passage width, and passage length of the throttle portion 9g. At this time, it is desirable to set the passage depth of the constricted portion 9g within the thickness of the bearing 849b by press molding, but it can also be easily formed by machining. The reason why the throttle mechanism 9g is provided is that, for example, when operating a scroll compressor with an inverter, etc., the amount of oil supplied by a centrifugal pump may decrease in the low-speed rotation range. This is because in the case of a passage shape, there is a possibility that the oil level will be lower than the passage depth, and it is necessary to control the oil supply to a sufficient amount of the bearing surface.

In addition, the oil supply passage 9a and the throttle mechanism 9g are shown in FIGS. 7 to 14.
Another specific example of the shape is shown below.

In FIGS. 7 to 10, the oil supply passage 9a is formed into a T-shape or an involute shape. In FIGS. 11 and 12, a throttling mechanism 9g which is an annular recess is provided in the oil supply passage 9a, and in this case, the terminal end 9f of the throttling mechanism 9g can be considered to be joined by the oil return hole 9h. can.

Further, the drawing mechanism 9g can be easily formed by pressing or turning.

13 and 14 show an arc-shaped throttle mechanism 9 in the oil supply passage 9a.
g is provided.

Note that it is clear that the oil supply passage 9a and the throttling mechanism 9g are not limited to the above-mentioned embodiments, and can be set arbitrarily.

〔Effect of the invention〕

As described above, according to the present invention, the oil supply passage of the thrust bearing can be easily formed using a press, and the amount of oil supply can also be set arbitrarily, so that the durability and reliability of the thrust bearing is increased and - Abnormality 1 (') A scroll compressor without wear and the like and with a reduced amount of oil circulation can be obtained.

[Brief explanation of drawings]

FIG. 1 is a plan view of a thrust bearing showing an embodiment of the present invention, FIG. 2 is a sectional view taken along I-1 in FIG. 4 is a cross-sectional view showing the O-μ cross section in FIG. 3, and FIG. 5 is a plan view of the thrust bearing showing another embodiment of the present invention. at-it
7 to 14 are plan views and sectional views of thrust bearing groove shapes showing other embodiments of the present invention; FIG. 15 is a sectional view showing a conventional scroll compressor; Fig. 16 is a plan view showing a conventional thrust bearing, Fig. 17 is a sectional view showing the IV-IV cross section in Fig. 16, Fig. 18 is a plan view showing another practical example of the conventional thrust bearing FIG. 19 is a sectional view showing the v-v section in FIG. 18, and FIG. 20 is a cross-sectional view θ showing the oil flow near the upper bearing support of a conventional scroll compressor. FIG. 21 is a plan view showing an improved example of a conventional thrust bearing;
Fig. 22 is a sectional view showing the VI-Vl section in Fig. 21, Fig. 23 is a plan view showing an improved example of the conventional thrust bearing, and Fig. 24 is the thrust d of the conventional scroll compressor.
,! This is a sectional view showing the flow of oil near the upper part of the Ih receiver when improvements are made to the Ih receiver. In the figure, 2 is a 1111m scroll and 9 is a thrust bearing. 10 is an upper bearing support, and 12 is an Oldham joint. In addition, in the figures, the same reference numerals indicate the same or equivalent parts.

Claims (2)

[Claims] (1) A fixed scroll and an oscillating scroll that have a spiral side plate such as an involute on one side of each end plate and form a compression chamber by combining the side plates with each other, and the oscillating scroll is oscillated. an Oldham joint for moving and a main shaft; a thrust bearing which is a plate-shaped body having an inner circumferential edge and an outer circumferential edge and includes an oil supply passage and supports the back surface of the oscillating scroll; and an Oldham joint for fixing the fixed scroll; , and accommodates the thrust bearing,
and a bearing support for supporting the main shaft, a shell for housing each of the above elements, an oil supply means for supplying oil stored at the bottom of the shell to an oil supply passage of the thrust bearing, an oil supply passage for the thrust bearing, and a bottom of the shell. In a scroll compressor equipped with an oil return hole that allows communication between A scroll compressor characterized by having a slit-like structure formed by press working. (2) A fixed scroll and an oscillating scroll that have a spiral side plate such as an involute on one side of each end plate and form a compression chamber by combining the side plates with each other, and the oscillating scroll is oscillated. an Oldham joint and a main shaft, a plate-shaped body having an inner circumferential edge and an outer circumferential edge, and having an oil supply passage, a thrust bearing supporting the back surface of the oscillating scroll, and fixing the fixed scroll;
a bearing support that accommodates the Oldham joint and the thrust bearing and supports the main shaft; a shell that accommodates each of the above elements; and an oil supply means for supplying oil stored at the bottom of the shell to the oil supply passage of the thrust bearing. In the scroll compressor, the oil supply passage of the thrust bearing is provided with an oil return hole that communicates the oil supply passage of the thrust bearing with the bottom of the shell, one end of which opens toward the inner peripheral edge of the thrust bearing, and the other end of which opens in the radial direction. 1. A scroll compressor characterized in that the scroll compressor is formed into a slit-like shape so as to be closed at an arbitrary position toward the outside, and a constricted portion is provided in a communication portion between the oil supply passage and the oil return hole.