JPH08326677A - Hermetic compressor - Google Patents

Abstract

PURPOSE: To cool a rotor for a motor from the inside effectively by arranging an oil passage communicated with a compressing mechanism part while arranging, in a closed container, an oil supplying part for supplying lubricating oil in an oil sump part to the sliding parts of the compressing mechanism part and a motor mechanism part. CONSTITUTION: Lubricating oil 9 in an oil sump 10 is sucked from an oil guide 14 in association with rotation of a crankshaft 5, and the oil flows from the shaft end passage port 31 of the crankshaft 5 into an internal shaft passage 32a. The oil flows into the rotor 7a for a motor 7 passing through a radial direction passage 33a, and passes a circumferential direction passage 34a, an axial direction passage, and circumferential direction passage 34b in order. As a while, heat generated by the rotor 7a is absorbed in the lubricating oil 9 so as to cool the rotor 7a. After that, the oil flows into the passage 32b in the crankshaft 5 passing through a radial direction passage 33b, a main bearing 8, an auxiliary bearing 23, an eccentric bearing, and a thrust bearing are lubricated and cooled, and the oil is discharged from the oil discharging port 12 of a bearing parts 3.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hermetic compressor, such as a scroll compressor or a rotary compressor, which is used for commercial and domestic air conditioning.

[0002]

2. Description of the Related Art Electric hermetic compressors for refrigeration and air-conditioning include reciprocating compressors and rotary compressors, both of which are used in the air-conditioning field for home and business use. Up to now, they have grown by taking advantage of their respective characteristics in terms of performance and cost. Scroll compressors have been put to practical use by taking advantage of their characteristics of low noise and low vibration. Here, this scroll compressor will be described as an example.

FIG. 8 shows a vertical sectional view of a conventional scroll compressor. Inside the closed container 1, a compression mechanism 2 in which a fixed scroll 2a and a movable scroll 2b that makes a swivel motion with respect to the fixed scroll 2a are meshed, and a movable scroll 2b.
The thrust bearing 3a supporting the bearing and the bearing component 3 integrated with the thrust bearing 3a are provided on the upper portion. The shaft 2c of the movable scroll 2b is inserted into an eccentric bearing 6 having a substantially rectangular outer shape of a deformed hole 5b having a bottom surface provided at the end of the crankshaft 5. Then, the movable scroll 2b is caused to orbit by rotating the crankshaft 5.

The eccentric bearing 6 is constructed so as to be movable in the direction of reducing the turning radius, and is further urged by an iter spring (not shown) so as to keep the maximum turning radius r.
A rotor 7a of an electric motor 7 is attached to the crankshaft 5, and is disposed below the bearing component 3 together with a stator 7b that is shrink-fitted and fixed to the closed casing 1. The electrode 4 is
It is provided on the side surface of the closed container 1 and is connected to the stator 7b to supply electric power to the electric motor 7. The crankshaft 5 is supported by the main bearing 8 and the sub bearing 23 of the bearing component 3.
A gas suction pipe 11 is provided on the side of the closed container 1. The gas pressure on the suction side acts on the lower side of the spacer 22 inside the closed container 1, and the gas pressure on the compression side acts on the upper side of the spacer 22.

Reference numeral 15 is a discharge chamber provided at the upper portion of the fixed scroll, and 16 is a discharge pipe for discharging a compressed gas to the outside of the closed container 1. The fixed scroll 2a and the bearing component 3 are fastened with a bolt across the spacer 22. The spacer 22 is hermetically welded and fixed to the closed container 1 on the outer periphery thereof, and serves as a partition between a lower suction pressure portion and an upper compression pressure portion. Reference numeral 19 is a check valve for preventing the movable scroll 2b from reversing at the time of stop, 24 is a check valve guide for restricting the movement of the check valve, and 20 is for causing the movable scroll 2b to orbit with respect to the fixed scroll 2a. An Oldham ring 21 for preventing the rotation of the bearing 21 is a suction port provided in the bearing part 3 for sucking low-pressure gas into the compression mechanism 2.

An oil sump 10 for storing the lubricating oil 9 is provided at the lower bottom of the closed casing 1, and the lubricating oil 9 is sucked up from an oil guide 14 at the lower end of the crankshaft 5 to allow the crankshaft 5 to move.
Through the through hole 13 provided in each bearing, that is, the main bearing 8, the sub bearing 23, the eccentric bearing 25, and the thrust bearing 3a.
The lubricating oil 9 is supplied to the bearing parts 3, and then the lubricating oil 9 that lubricates and cools the bearings is discharged from the oil discharge port 12 provided in the bearing component 3.

Next, the operation of the compression mechanism having the above structure will be described. The low-pressure gas returns from the suction pipe 11 and is sucked into the compression mechanism 2. As the movable scroll 2b orbits with respect to the fixed scroll 2a, the sucked gas becomes high-pressure gas compressed by the compression mechanism 2 and once enters the discharge chamber 15. Then, it is discharged from the discharge pipe 16 to the outside of the closed container 1, and the low-pressure gas is circulated again to form a known compression cycle.

On the other hand, the lubricating oil 9 sucked up by the oil guide 14 rises in the through hole 13 of the crankshaft 5 to lubricate and cool the sub bearing 23, the eccentric bearing 6, the thrust bearing 3a and the main bearing 8. Then, the oil is discharged from the oil discharge port 12 to the upper portion of the stator 7b, passes through the cutout portion 18 of the stator 7b, and returns to the oil sump 10 to form a lubrication cycle.

[0009]

In order to increase the reliability and efficiency of the scroll compressor and the like, it is necessary to lower the temperature during operation of the electric motor so that the temperature of the electric motor is as high as possible. There is. However, the electric motor during operation tends to be heated to a high temperature due to Joule heat generated by itself, and is not the most efficient operation. This high-temperature operation not only lowers the efficiency, but also causes deterioration of the resin material normally used on the stator side, which causes lower reliability and efficiency. Normally, the heat generated by the electric motor is released to the low temperature and low pressure gas that has been sucked in and to the closed container to a certain extent to suppress the temperature rise of the electric motor. In other words, the refrigerating capacity is lost and limited, so that the temperature rise cannot be sufficiently suppressed.

An object of the present invention is to solve the above problems and provide a highly reliable and highly efficient hermetic compressor.

[0011]

According to a first aspect of the present invention, there is provided a stator fixed inside an airtight container, a rotor driven by the stator to rotate, and a crank to which the rotor is attached. An electric mechanism section including a shaft, a compression mechanism section driven by the driving force of the electric mechanism section via the crankshaft, an oil sump section for storing lubricating oil, the compression mechanism section and the electric mechanism. An oil supply part for supplying the lubricating oil of the oil sump part to the sliding part of the closed part is provided in the closed container,
The hermetic compressor is characterized in that it has an oil passage through which lubricating oil in the oil sump portion is supplied to the compression mechanism portion through a passage in the rotor that communicates with a passage in the crankshaft.

Further, the present invention according to claim 2 is composed of a stator fixed inside the closed container, a rotor driven by the stator to rotate, and a crankshaft to which the rotor is attached. Electric mechanism section, a compression mechanism section driven by the driving force of the electric mechanism section via the crankshaft, an oil sump section for storing lubricating oil, and sliding of the compression mechanism section and the electric mechanism section. An oil supply part for supplying lubricating oil to the oil sump part in the closed container, and the lubricating oil in the oil sump part flows through a passage in the rotor communicating with a passage in the crankshaft. The hermetic compressor is characterized by having an oil passage that is discharged into the hermetic container without being supplied to the compression mechanism section.

[0013]

According to the invention described in claim 1, since the rotor of the electric motor can be cooled from the inside by the lubricating oil, the temperature rise of the rotor and the stator can be efficiently suppressed, and the efficiency of the electric motor and the The reliability against deterioration of the resin used in the electric motor can be improved. Therefore, it is possible to realize a hermetic compressor having high reliability and high efficiency.

Further, according to the second aspect of the present invention, a lubricating oil passage is provided in the rotor in addition to the conventional lubricating oil passage for lubricating each bearing portion, and the stator is internally cooled. By not supplying oil to each bearing, it is possible to improve the efficiency and reliability of the electric motor, and it is possible to more reliably suppress the viscosity decrease due to the rise in the temperature of the lubricating oil supplied to each bearing. It is possible to realize a hermetic compressor with high reliability and efficiency.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is applied to a scroll compressor for air conditioning will be described below with reference to FIGS. It should be noted that the scroll compressor of the conventional example shown in FIG. 8 is almost the same as the vertical cross-sectional view except for the crankshaft, the rotor and the peripheral portion thereof.
The same numbers are assigned and detailed description is omitted.

First, a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a vertical sectional view of a scroll compressor to which the present invention is applied, and FIG. 2 is a transparent perspective view used for explaining a lubricating oil path.

In FIG. 1, inside a closed container 1, there is a compression mechanism 2 in which a fixed scroll 2a and a movable scroll 2b which makes a revolving motion with respect to the fixed scroll 2a are meshed,
A thrust bearing 3a that supports the movable scroll 2b, and a bearing component 3 that is integrated with the thrust bearing 3a are provided at the top. The shaft 2c of the movable scroll 2b is inserted into an eccentric bearing 6 having a substantially rectangular outer shape of a deformed hole 5b having a bottom surface provided at the end of the crankshaft 5. And crankshaft 5
The movable scroll 2b is caused to orbit by the rotation of.

The eccentric bearing 6 is constructed so as to be movable in the direction of reducing the turning radius, and is further biased by an iter spring (not shown) so as to keep the maximum turning radius r. A rotor 7a of an electric motor 7 is attached to the crankshaft 5, and is disposed below the bearing component 3 together with a stator 7b that is shrink-fitted and fixed to the closed casing 1. Crankshaft 5
Are supported by the main bearing 8 and the sub bearing 23 of the bearing component 3. A gas suction pipe 11 is provided on the side of the closed container 1. And the spacer 2 inside the closed container 1
The gas pressure on the suction side acts below 2 and the gas pressure on the compression side acts above the spacer 22.

Reference numeral 15 is a discharge chamber provided at the upper part of the fixed scroll, and 16 is a discharge pipe for discharging a compressed gas to the outside of the closed container 1. The fixed scroll 2a and the bearing component 3 are fastened with a bolt across the spacer 22. The spacer 22 is hermetically welded and fixed to the closed container 1 on the outer periphery thereof, and serves as a partition between a lower suction pressure portion and an upper compression pressure portion. Reference numeral 19 is a check valve for preventing the movable scroll 2b from reversing at the time of stop, 24 is a check valve guide for restricting the movement of the check valve, and 20 is for causing the movable scroll 2b to orbit with respect to the fixed scroll 2a. An Oldham ring 21 for preventing the rotation of the bearing 21 is a suction port provided in the bearing part 3 for sucking low-pressure gas into the compression mechanism 2.

An oil sump 10 for storing the lubricating oil 9 is provided at the bottom of the closed container 1. The oil guide 14 is provided at the lower end of the crankshaft 5, and the passages 32a, 32 not penetrated inside the shaft.
b is provided. Further, inside the rotor 7a, there are three passages communicating with the passages 32a and 32b inside the crankshaft 5.
3a, 33b, 34a, 34b, 35 are provided. In this configuration, the lubricating oil passages are 32a, 33a,
34a, 35, 34b, 33b, 32b are connected in this order. The outline of the path is shown in a transparent perspective view in FIG. The arrow in the figure indicates the direction in which the lubricating oil flows. Here, since the fitting surface 29 between the crankshaft 5 and the rotor 7a has a gap through which the lubricating oil 9 leaks,
The fitting surface 29 is sealed by an O-ring 30 so that the radial passages 43a and 43b do not communicate with each other through the gap of the fitting surface 29 and do not leak into the closed container.

Here, the operation of the lubricating oil in the above structure will be described. In the present embodiment shown in FIG. 1, the stator 7a and the like are cooled from the inside by a lubricating oil 9 in an oil sump 10 that is lower than the temperature of the electric motor 7 and each bearing.

The lubricating oil 9 of the oil sump 10 is sucked from the oil guide 14 as the crankshaft rotates, and flows from the passage opening 31 at the shaft end of the crankshaft 5 into the passage 32a in the shaft. Then, it flows from the crankshaft 5 into the rotor 7a through a passage 33a extending in the radial direction of the crankshaft, and passes through the circumferential passage 34a, the axial passage 35a, and the circumferential passage 34b in this order, and the lubricating oil 9 is fed between the rotor 9 and the rotor. The rotor 7a is cooled by absorbing the heat generated by 7a. After that, it further flows from the rotor 7a to the passage 32b in the crankshaft 5 through the radial passage 33b, and then to each bearing portion, that is, the main bearing 8, the sub bearing 23, the eccentric bearing 25, and the thrust bearing 3a. Then, the lubricating oil 9 that has lubricated and cooled each bearing portion is discharged from the oil discharge port 12 provided in the bearing component 3.

The form of the passage through which the lubricating oil 9 is supplied is shown in FIG.
As shown in (b), it may be constituted by a plurality of axial passages 35 and radial passages 33b. 2 (a) and 2 (b)
The number and position of the axial passages 35, the circumferential passages 34, and the radial passages 33 in FIG. 2 are not limited to those in FIG.
However, if a large number of passages are provided, the cooling effect of the rotor 7a may be improved, but the efficiency of the electric motor is reduced because the cross-sectional area of the rotor 7a is reduced, and the efficiency improvement due to the temperature rise suppression is offset. . Therefore, it is necessary to design in consideration of the balance between the two.

With this structure, the temperature rise of the stator is suppressed and the radiant heat to the stator and the like is also reduced, so that the temperature of other parts such as the stator can also be suppressed. Therefore, it is possible to solve the reliability and efficiency reduction due to the temperature rise of the electric motor, which has been a problem in the past, and to provide a highly reliable and efficient hermetic compressor such as a scroll compressor.

Next, a second embodiment will be described with reference to FIGS.

The difference from the first embodiment is that the lubricating oil 9 flowing from the rotor 7a into the crankshaft 5 through the radial passage 43b flows from the axial passage 42b to the radial passage 46b.
After passing through, the oil is discharged into the closed container 1 from the oil discharge port 47 provided in the auxiliary bearing 23. A groove 48 provided around the crankshaft 5 communicates with the radial passage 46, and serves to connect the passage 46 and the oil outlet 47 to each other while the crankshaft 5 is rotating. In this configuration example, the lubricating oil is 42a, 43a, 44a, 45, 44b, 42.
It flows in the order of b, 46, 48, 47. A schematic example of the path is shown in FIGS. 2A and 2B as a transparent perspective view. The design can be made based on a concept similar to that of the first embodiment. Further, the lubricating oil 9 discharged from the oil discharge port 47 falls on the rotor 7a and the stator 7b, and cools the rotor 7a and the stator 7b from the outer surface. Further, the lubricating oil 9 is supplied to each bearing by providing the crankshaft 5 with a through hole 13 similar to the conventional example of FIG.

With this configuration, in the first embodiment, the lubricating oil returned to the rotor or the crankshaft is heated by the heat taken from the rotor, and the lubricating performance and cooling effect for the viscosity-decreasing bearing are low. It is not good for the reliability and loss of bearings. However, according to this configuration, the lubricating oil 9 that has cooled the rotor 7a is discharged without returning to the bearing and returns to the oil sump 10, so there is no such concern.
Therefore, with the above configuration, it is possible to provide a hermetic compressor such as a scroll compressor having higher reliability and efficiency than the first embodiment.

Since the processing is more difficult and the cost is higher than that of the first embodiment, it may be better to use the first embodiment depending on the size of the compressor and the operating conditions.

Further, the second embodiment may have the configuration shown in FIGS. The difference from the embodiment of FIG. 3 is that the oil discharge port 5
6 configuration. That is, the oil discharge port 56 is provided at the compression mechanism 2 side of the stator 7a, that is, at the upper end. It is somewhat easier to process than the configuration of FIG. In this configuration example, 52
Lubricating oil is discharged from the oil discharge port 56 in the order of passages a, 53a, 54a, 55, 54b, 52b. FIG. 5 shows a schematic perspective view of the passage of the lubricating oil in a perspective view. FIG. 5B
Then, the passage of 53b is eliminated and it is possible to extend the 55 passages by 5
The 2b passage may be configured. This is easier to process.

Further, when it is advantageous in terms of loss that the lubricating oil discharged from the oil discharge port does not come into contact with the suction gas sucked from the suction port 11 as much as possible in terms of loss, the constitution shown in FIGS. The difference between this structure and the embodiment of FIG. 4 is that the oil discharge port 66 of the rotor 7a is provided on the opposite side of FIG. 4, that is, on the lower side. In this configuration example, 62a, 63a, 64
The lubricating oil flows from the oil discharge port 66 in the order of the passages a, 65, 64b, and 62b. With this configuration, the oil discharge port 62
The lubricating oil 9 released from b does not come into contact with the intake gas at a minimum, and thus the loss due to the intake gas being heated by the lubricating oil 9 can be suppressed. 7 (a),
FIG. 2B is a transparent perspective view schematically showing the lubricating oil passage.

With the above construction, it is possible to provide a hermetic compressor such as a scroll compressor having a reliability and efficiency equal to or higher than that of the second embodiment.

In all of the above-mentioned embodiments, the centrifugal pump using the oil guide sucks up the lubricating oil from the oil sump and supplies it to each part. However, the volumetric type such as a trochoid pump or other forced lubricating oil is supplied. It goes without saying that the use of such a pump makes it possible to realize a configuration that is easier and more effective than the above-described embodiments.

[0033]

As is apparent from the above description, according to the present invention, a hermetic compressor having higher reliability and efficiency than ever before,
For example, a scroll compressor can be realized and provided.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a scroll compressor according to a first embodiment of the present invention.

FIG. 2 is a transparent perspective view of a lubricating oil passage used in the first embodiment of the present invention.

FIG. 3 is a vertical sectional view of a scroll compressor according to a second embodiment of the present invention.

FIG. 4 is a vertical cross-sectional view showing another form of the second embodiment of the present invention.

FIG. 5 is a transparent perspective view of a lubricating oil passage used for explaining another mode of the second embodiment of the present invention.

FIG. 6 is a vertical sectional view showing another form of the second embodiment of the present invention.

FIG. 7 is a transparent perspective view of a lubricating oil passage used for explaining another mode of the second embodiment of the present invention.

FIG. 8 is a vertical sectional view of a scroll compressor in a conventional example.

[Explanation of symbols]

 1 Airtight container 2 Compression mechanism 3 Bearing 5 Crankshaft 6 Eccentric bearing 7 Electric motor 7a Rotor 7b Stator 8 Main bearing 9 Lubricating oil 10 Oil sump 30 O-ring 32-35 Lubricating oil passage

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Fumitoshi Nishiwaki 1006 Kadoma, Kadoma, Osaka Prefecture Matsushita Electric Industrial Co., Ltd. (72) Hideki Nakata, 1006 Kadoma, Kadoma City, Osaka Matsushita Electric Industrial Co., Ltd.

Claims (4)

[Claims] 1. A stator fixed inside an airtight container,
An electric mechanism unit having a rotor driven by the stator to rotate, and a crankshaft to which the rotor is attached, and a compression mechanism unit driven by the driving force of the electric mechanism unit via the crankshaft. An oil reservoir for storing lubricating oil; and an oil supply unit for supplying the lubricating oil of the oil reservoir to the sliding parts of the compression mechanism section and the electric mechanism section are provided in the closed container. A hermetic compressor having an oil passage through which a lubricating oil of a portion is supplied to the compression mechanism portion through a passage in the rotor communicating with a passage in the crankshaft. 2. A stator fixed inside a closed container,
An electric mechanism unit having a rotor driven by the stator to rotate, and a crankshaft to which the rotor is attached, and a compression mechanism unit driven by the driving force of the electric mechanism unit via the crankshaft. An oil reservoir for storing lubricating oil; and an oil supply unit for supplying the lubricating oil of the oil reservoir to the sliding parts of the compression mechanism section and the electric mechanism section are provided in the closed container. After the lubricating oil of the portion flows through the passage in the rotor that communicates with the passage in the crankshaft, it has an oil passage that is discharged into the closed container without being supplied to the compression mechanism portion. Characteristic hermetic compressor. 3. The compression mechanism portion of the rotor, after the lubricating oil in the oil sump portion flows through the passage in the rotor communicating with the passage in the crankshaft and is not supplied to the compression mechanism portion. The hermetic compressor according to claim 2, further comprising an oil passage through which the oil is discharged from the side end portion into the hermetic container. 4. The lubricating oil in the oil sump portion flows through a passage in the rotor that communicates with a passage in the crankshaft, and then is not supplied to the compression mechanism portion. The hermetic compressor according to claim 2 or 3, further comprising an oil passage through which the oil is discharged from the opposite end into the hermetic container.