JPH02218888A - Compressor - Google Patents

Abstract

PURPOSE:To prevent the shortage of lubricating oil in the compressor internal part in high-speed operation by introducing a lubricating oil reached to the outlet of a main bearing to a sub-bearing through the internal part of a compression mechanism, and returning a part of the lubricating oil from the sub-bearing to an oil sump, with the remainder being recirculated to a lubricating passage. CONSTITUTION:A centrifugal pump built in a shaft 26 is operated by the rotation of a rotor 25 in an electric motor 23 to force feed a lubricating oil 41. Namely, in a main bearing 28, the lubricating oil fed from an oil hole 34 is raised to an oil channel 37 to conduct lubrication. When reached to a notch 38 on the upper end of the main bearing 28, the lubricating oil 41 is transferred to a sub-bearing 30 through a plurality of lubricating oil passages 36a-36c. In the sub-bearing 30, the lubricating oil fed from an oil hole 35 is combined with the lubricating oil from the lubricating oil passage 36c. Thereafter, a part of the lubricating oil is introduced to an oil channel 40 and fed to the sub bearing 30 to conduct lubrication. The remainder is introduced into a gap between the shaft 26 and a second end plate 31 to lubricate a piston 32 and the shaft 26.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a compressor used in an air conditioner or the like.

2. Description of the Related Art Conventionally, this type of compressor is described in Japanese Patent Application Laid-open No. 174177/1983 and is constructed as shown in FIG.

This will be explained below with reference to the drawings.

In the figure, a roller 6 fitted to an eccentric portion 5 of a shaft 4 is disposed inside a cylindrical compression chamber 3 provided in a cylinder 2 of a hermetic compressor 1, and a vane 7 is fitted to the cylinder 2. are combined. An upper bearing 8 and a lower bearing 9 are fixed to the cylinder 2. Lubricating oil 11 is stored in the lower part of the container 10. At the bottom of the N hole 12, there is an oil supply device 1.
3 is press-fitted and protrudes downward from the shaft 4, and the lubricating oil 11
is immersed in. When the shaft 4 rotates, the lubricating oil 11 present near the inner wall of the oil supply device 13 receives an upward force due to centrifugal force and viscosity, and is pushed up. Twisted plate 1 in which pushed up lubricating oil 11 is inscribed in vertical hole 12
4, the lubricating oil 11 ascends the wave path formed by the twisting temporary 14 and the vertical hole 12, reaches the horizontal holes 15, 16, 17 of the shaft 4, and clears the clearances 18, 19.
．． 20 is refueled.

Problems to be Solved by the Invention However, in the above-described configuration, the amount of oil supplied increases rapidly during high-speed operation, but due to the rotation of the shaft 4 at the outlet of the upper bearing 8, atomization of the lubricating oil 11 begins, causing the oil to flow outside the compressor. The amount of lubricating oil discharged to the tank also increases.

As a result, there has been a problem in that the amount of lubricating oil inside the compressor is insufficient, the lubricating oil is insufficiently supplied to the sliding parts, and wear of the sliding parts increases due to metal contact and the like.

In view of the above problems, the present invention provides a highly reliable compressor that can prevent a shortage of lubricating oil inside the compressor during high-speed operation.

Means for Solving the Problems In order to solve the above problems, the compressor of the present invention includes a cylinder, a first end plate fixed to an end face of the cylinder on the electric motor side, and having a main bearing that pivotally supports a drive shaft. , a second end plate fixed to an end surface of the cylinder opposite to the first end plate and having a sub-bearing that pivotally supports the drive shaft; the first end plate, the cylinder and the second end plate; lubricating oil provided on the second end plate, having one end opened to the lubricating oil outlet part of the main bearing of the first end plate, and the other end opening to the lubricating oil outlet part of the sub bearing of the second end plate; It consists of a passageway.

According to the above structure, the present invention guides the lubricating oil that has reached the outlet of the main bearing through the inside of the compression mechanism to the sub-bearing, returns part of the lubricating oil from the sub-bearing to the oil reservoir outside the compression mechanism, and removes the remaining lubricating oil. This recirculates the lubrication path.

Therefore, it is possible to prevent the lubricating oil from being atomized at the outlet of the main bearing due to the rotation of the rotor or shaft of the electric motor, and it is possible to ensure a sufficient amount of lubricating oil inside the compressor even during high-speed operation.

EXAMPLE Hereinafter, a compressor according to an example of the present invention will be described with reference to the drawings.

FIG. 1 shows a longitudinal sectional view of a compressor in a first embodiment of the present invention.

In the figure, a compressor 21 is constructed by incorporating an electric motor 23 in the upper part of a closed container 22 and a compression mechanism 24 in the lower part. The rotor 25 of the electric motor 23 and the compression mechanism 24 are connected by a shaft 26. The compression mechanism 24 includes a cylinder 27;
A first end plate 29 has a main bearing 28 fixed to the upper end surface of the cylinder 26 and pivotally supports the shaft 26, and a second end plate 29 has a sub bearing 30 fixed to the lower end surface of the cylinder 27 and pivotally supports the shaft 26.
The end plate 3I of the cylinder 27 is inserted into the eccentric part of the shaft 26.
It is comprised of a piston 32 that eccentrically rotates inside, and a vane 33 whose tip always contacts the outer peripheral surface of the piston 32 and divides the inside of the cylinder 27 into a suction chamber and a compression chamber. The shaft 26 has a built-in centrifugal pump (not shown), and an oil tank 34 serves as a lubricating oil supply port to the main bearing 28 and sub-bearing 30.
．． 35 are open.

36 is a lubricating oil passage, which connects the first @ plate 29 and the cylinder 2.
7 and 36a, 36b, 36c in the second end plate 31
It is made up of. Lubricating oil passage 3 of first end plate 29
6a has one end opened to a notch 38 at the outlet of the oil groove 37 at the upper end of the main bearing 29, and the other end opened to the lubricating oil passage 36b. Note that a lid 39 is fixed to the upper part of the notch 38 of the first end plate 29.

On the other hand, one end of the lubricating oil passage 36c of the second end plate 31 is
It opens at the lubricating oil inlet of the sub-bearing 30, that is, at the oil entry 35 position of the shaft 26, and the other end opens into the lubricating oil passage 36b.

Further, the gap between the lid 39 and the shaft 26 is set to be larger than the bearing gap of the main bearing 28 and sufficiently smaller than the passage area of the lubricating oil passage 36. In addition, the oil groove 4 of the secondary bearing 30
The passage area of 0 is set larger than the lubricating oil road 36. Note that 41 is lubricating oil, which is stored around the compression mechanism 24.

The operation of the compressor configured as described above will be explained below using FIG. 1.

First, in the main bearing 29, the lubricating oil supplied from the oil filler 34 flows into the bearing gap while ascending the oil groove 37, and lubricates the main bearing 28. Thereafter, the lubricating oil reaches the notch 38 at the upper end of the main bearing 28 and flows into the lubricating oil passage 36a, which has a sufficiently low passage resistance compared to the gap between the lid 39 and the shaft 26. Then, the secondary bearing 3 passes through the lubricating oil passages 36b and 36c.
0 to the lubricating oil inlet.

Next, in the secondary bearing 30, the lubricating oil supplied from the oil filler 35 merges with the inflowing lubricating oil from the lubricating oil passage 36c, a part of which flows into the oil groove 40, and enters the secondary bearing 30 from the bearing gap. At the same time, the lubricating oil supplied to the main bearing 28 is returned to the oil storage section at the bottom of the sealed container 22. After lubricating the shaft 26, the lubricating oil reaches the inlet of the main bearing 28 and is recirculated.

As explained above, since the lubricating oil flowing out from the main bearing 28 passes through the inside of the compression mechanism 24 and is returned to the oil storage section at the bottom of the closed container 22, atomization of the lubricating oil by the rotor 25 and shaft 26 occurs. do not.

As a result, during high-speed operation, lubricating oil is not discharged to the outside of the compressor, and sufficient lubricating oil can be secured within the compressor, thereby improving reliability. In addition, since some of the lubricating oil is recirculated, the piston 3, which tends to be insufficient during low-speed operation,
The oil supply to the upper and lower end surfaces of the air conditioner 2 is sufficient, the sealing performance is improved, and the efficiency in low-speed operation is high.As a result, the annual power consumption of the air conditioner can be significantly reduced.

Note that the amount of recirculation can be determined by providing a notch in the second end plate 31 or the thrust surface of the shaft 26, so that the inner side of the piston 32 and the secondary bearing 30
It can be adjusted appropriately by communicating with the lubricating oil inlet of.

Next, a second embodiment of the present invention will be described.

During high-speed operation, a large amount of air bubbles are generated in the lubricating oil behind the vane due to the intense reciprocating motion of the vane, and this lubricating oil is supplied to the vane, resulting in poor lubrication due to lack of lubricating oil in the vane. This has the problem of increased wear, which is undesirable in terms of service life.

The present invention provides a highly reliable compressor that can not only prevent a shortage of lubricating oil inside the compressor during high-speed operation, but also prevent poor lubrication of vanes.

FIG. 2 shows a longitudinal sectional view of a compressor in a second embodiment of the invention. Here, the same parts as those in the first embodiment are given the same reference numerals and the description thereof will be omitted.

In the same figure, 36b° is a lubricating oil passage provided in the cylinder 27, which is formed by an oil groove 43 cut into a vane groove 42 that accommodates the vane 33 of the cylinder 27 and a side wall of the vane 33, and has one end connected to a side wall of the vane 33. Lubricating oil passage 36 of end plate 29 of 1
a, and the other end is connected to the lubricating oil passage 36c of the second end plate 31.
The lubricating oil passage 36 is formed as a whole.

In the above configuration, the lubricating oil passage 36 has one end connected to the main bearing 28.
The first embodiment has an opening in a notch 38 at the upper end which is the lubricating oil outlet of the bearing, and an oil hole 35 of the shaft 26 which is the lubricating oil inlet of the sub bearing 30 at the other end. The same action and effect can be obtained. Further, a portion of the lubricating oil flowing into the lubricating oil passage 36b comes into contact with the vane 33, flows into the gap between the vane 33 and the vane groove 42, and is used for lubrication, and the rest flows into the lubricating oil passage 36c. However, since the lubricating oil in the lubricating oil passage 36b is supplied from the lower part of the oil reservoir and does not contain air bubbles, sufficient lubricating oil can be supplied to the vanes even during high-speed operation, and lubrication failure will occur. do not.

Therefore, vane wear can be prevented and a highly reliable compressor can be realized. Further, since fluid lubrication can be ensured by sliding between the vane and the vane groove, power loss due to sliding is small, and a highly efficient compressor can be provided.

Furthermore, since the speed can be increased, it is possible to obtain a large compressor during capacity control.

Furthermore, a third embodiment of the present invention will be described.

During defrosting operation, especially when starting defrosting or returning to heating, lubricating oil forms inside the compressor and a large amount of lubricating oil temporarily flows out of the compressor. Poor lubrication occurred in the surrounding areas, which was undesirable in terms of service life.

In particular, the above-mentioned phenomenon is remarkable in high-speed operation, and is the cause of not being able to shorten the defrosting time.

The present invention provides a highly reliable compressor that can not only prevent a shortage of lubricating oil inside the compressor during high-speed operation, but also prevent poor lubrication during defrosting operation.

FIG. 3 shows a longitudinal sectional view of a compressor in a third embodiment of the present invention. Here, the same parts as those in the first embodiment are given the same reference numerals and the description thereof will be omitted.

In the figure, 36b'' is an oil reservoir provided in the cylinder 27, and 42 is a throttle, which is press-fitted into the entrance of the lubricating oil passage 36c.
The lubricating oil passage 36a of i29 is connected to the lower part of the lubricating oil passage 36c of the second end plate 31 via a throttle 36c, thereby forming the lubricating oil passage 36 as a whole.

In the above configuration, the lubricating oil passage 36 has one end connected to the main bearing 28.
The first embodiment has an opening in a notch 38 at the upper end which is the lubricating oil outlet of the sub-bearing 30, and an opening at the oil filler position 35 of the shaft 26 which is the lubricating oil inlet of the sub-bearing 30. The same action and effect can be obtained. Furthermore, during heating operation, the compressor operates at high speed, and the oil reservoir 36b'' is filled with lubricating oil supplied via the lubricating oil passage 36a by a centrifugal pump built into the shaft 26.

When defrosting begins, the pressure inside the compressor 21 is rapidly reduced, and a portion of the lubricating oil 41 forms and flows out of the compressor 21. At this time, the pressure inside the oil reservoir 36b'' is also reduced, but the path connecting to the space inside the compressor 21 has a large passage resistance due to the lubricating oil passage 36c having the throttle 42 at the entrance and the oil groove 40 of the sub-bearing 30. The rate of pressure reduction is slow and the time required for pressure to equilibrate is long.

Also, due to the gentle forming of the lubricating oil in the oil sump 36b', the lubricating oil in the oil sump 36b'' passes through the lubricating oil passage 36a to the inside of the main bearing 28 and the piston 32, and passes through the lubricating oil passage 36c to the sub bearing 30 and the piston. 32.

Therefore, the area around the shaft 26 can be lubricated by the lubricating oil in the oil reservoir 36b'' until the lubricating oil that has flowed out from the compressor 21 returns, and lubrication failure around the axis 26 does not occur when defrosting starts. The same applies after returning.

Therefore, poor lubrication around the shaft 26 during defrosting operation can be solved, and a highly reliable compressor can be realized.

In addition, high-speed defrosting is simply possible, the defrosting time can be shortened, and the size can be reduced during indoor temperature fluctuations, and annual power consumption as an air conditioner can be reduced and comfort can be improved.

Furthermore, the above-mentioned functions and effects can also be obtained at the time of startup, and the temperature rise performance of the air conditioner can also be improved due to high-speed startup. Further, the above-mentioned functions and effects can be further ensured by using a porous material, that is, a bush that can be impregnated with oil, for the main bearing 28 and the sub-bearing 30.

Effects of the Invention As described above, the present invention includes a cylinder, a first end plate fixed to an end face of the cylinder on the electric motor side and having a main bearing that pivotally supports a drive shaft, and the first end plate of the cylinder. a second end plate having a sub-bearing that is fixed to an end surface opposite to the drive shaft and pivotally supports the drive shaft; It consists of a lubricating oil passage that opens at the lubricating oil outlet of the main bearing of the first end plate and the other end opens at the lubricating oil inlet of the sub-bearing of the second end plate, and the efficiency in the low speed range is improved. This not only provides an expensive and highly reliable compressor, but also has the effect of significantly reducing the annual power consumption of air conditioners.

[Brief explanation of the drawing]

FIG. 1 is a vertical cross-sectional view of a compressor according to a first embodiment of the present invention, FIG. 2 is a vertical cross-sectional view of a compressor according to a second embodiment of the present invention, and FIG. A vertical cross-sectional view of the compressor in the embodiment, and FIG. 4 is a vertical cross-sectional view of a conventional compressor. 23...Electric motor, 26...Shaft, 28.
Old...Main bearing, 29...First end plate, 30...
...Secondary bearing, 3I...Second end plate, 36.
...Lubricating oil passage, 36a...Lubricating oil passage of first end plate, 36b...Lubricating oil passage of cylinder, 36b"......Lubricating oil passage of vane groove Oil groove, 36b-・
...Oil sump, 36c...Lubricating oil passage in the second end plate. Name of agent: Patent attorney Shigetaka Awano (Figure 36)

Claims (4)

[Claims] (1) A cylinder, a first end plate fixed to the end face of the cylinder on the motor side and having a main bearing that pivotally supports the drive shaft, and fixed to the end face of the cylinder opposite to the first end plate. a second end plate having a sub-bearing that pivotally supports the drive shaft; and a second end plate provided on the first end plate, the cylinder and the second end plate, with one end connected to the main end plate of the first end plate. A compressor comprising a lubricating oil passage opening at a lubricating oil outlet of a bearing and having the other end open at a lubricating oil inlet of a sub-bearing of the second end plate. (2) A compressor according to claim (1), wherein a part of the lubricating oil passage is provided in a vane groove of the cylinder. (3) Claims (1) in which an oil reservoir is provided in the lubricating oil passage
) The compressor described in item 2. (4) A compressor according to claim (1), wherein an oil reservoir is provided in the lubricating oil passage, and a throttling device is provided in the lubricating oil passage that connects the oil reservoir and the lubricating oil inlet of the sub-bearing.