JP6812230B2 - Compressor - Google Patents

Description

The present invention relates to a compressor and particularly relates to a compressor including an oil drain pipe that returns lubricating oil from a compression mechanism to an oil sump at the bottom of a closed container.

A compressor such as a scroll compressor provided with an oil drain pipe for returning lubricating oil from a compression mechanism to an oil sump at the bottom of a closed container is described in Japanese Patent No. 4433184 (Patent Document 1). There is. Patent Document 1 describes an oil drain pipe that returns lubricating oil that lubricates a main bearing or the like that supports a rotary drive shaft from an oil drain passage formed in a frame of a compression mechanism to the bottom of a closed container. .. This oil drain pipe vibrates as the motor rotates, and hits the inner wall surface of the closed container, which is one of the causes of generating abnormal noise. Therefore, in Patent Document 1, the movement of the oil drain pipe is restrained and vibration is suppressed by bringing a part of the oil drain pipe into contact with the inner wall surface of the closed container and the outer peripheral surface of the motor. ..

Japanese Patent No. 4433184

Although the one described in Patent Document 1 has a certain effect of suppressing the vibration of the oil drain pipe, consideration is not given to the noise caused by the resonance of the oil drain pipe itself generated by the propagation of the vibration of the motor. It wasn't enough.

Normally, noise caused by vibrations with a high frequency of 1000 Hz or higher can be easily reduced by attaching a soundproof cover, etc., but noise caused by vibrations with a low frequency of less than 1000 Hz can be reduced by using a soundproof cover, etc. It is difficult.

An object of the present invention is to obtain a compressor capable of reducing noise caused by low frequency vibration.

In order to achieve the above object, the present invention has a compression mechanism portion, a drive portion for driving the compression mechanism portion via a rotating shaft, and an oil reservoir in a closed container, and a sliding portion of the compression mechanism portion. In a compressor provided with an oil drain pipe that returns the oil supplied to the oil reservoir, the oil drain pipe has a connecting portion connected to the compression mechanism portion and a linear oil guide that guides the oil to the oil reservoir. It is characterized in that the portion is provided, and the outer diameter of at least the central portion of the oil conducting portion is larger than the outer diameter of the other portion of the oil drain pipe.

Another feature of the present invention is that a frame fixed in a closed container, a fixed scroll fixed to the upper part of the frame, and the frame and the fixed scroll are provided and meshed with the fixed scroll. A compression mechanism unit including a swirling scroll forming a compression chamber, a drive unit arranged below the compression mechanism unit to drive the compression mechanism unit via a rotation shaft, and a bottom portion in the closed container are formed. In a compressor having an oil sump and a drainage pipe for returning the oil supplied to the sliding portion of the compression mechanism portion to the oil sump, the oil drainage pipe is connected to the compression mechanism portion. It is provided with a portion and a linear oil guide portion that guides oil to the oil sump, and the outer diameter of at least the central portion of the oil guide portion is configured to be larger than the outer diameter of the other portion of the oil drain pipe. is there.

According to the present invention, there is an effect that a compressor capable of reducing noise due to low frequency vibration can be obtained.

It is a vertical sectional view which shows Example 1 of the compressor of this invention. It is a perspective view which shows the oil drainage pipe in a conventional compressor. It is a perspective view explaining the state of deformation when the conventional oil drainage pipe shown in FIG. 2 vibrates at its natural frequency. It is a perspective view explaining the structure of the oil drainage pipe in Example 1 shown in FIG. It is a perspective view explaining the structure of the oil drain pipe in Example 2 of the compressor of this invention. It is a perspective view explaining the structure of the oil drain pipe in Example 3 of the compressor of this invention.

Hereinafter, specific examples of the scroll compressor of the present invention will be described with reference to the drawings. In each figure, the parts with the same reference numerals indicate the same or corresponding parts.

The "natural frequency" used in the description of the present invention includes both the natural frequency in the fundamental vibration and the natural frequency in the n times vibration (n is an integer of 2 or more).

Example 1 of the compressor of the present invention will be described with reference to FIGS. 1 to 4. FIG. 1 is a vertical cross-sectional view showing the compression chamber of the first embodiment, FIG. 2 is a perspective view showing an oil drainage pipe in a conventional compressor, and FIG. 3 is a natural frequency of the conventional oil drainage pipe shown in FIG. FIG. 4 is a perspective view for explaining the state of deformation when vibrating, and FIG. 4 is a perspective view for explaining the structure of the oil drain pipe according to the first embodiment shown in FIG.

First, the overall structure of the scroll compressor as the compression chamber of the first embodiment will be described with reference to FIG.
The scroll compressor (compressor) 1 is configured by accommodating a compression mechanism unit 2 and a drive unit 3 for driving the compression mechanism unit in a closed container 4.

The compression mechanism portion 2 includes a frame 20 fixed to the closed container 4, a fixed scroll 21 attached to the upper portion of the frame 20 and provided with a spiral wrap on a base plate, the frame 20 and the fixed scroll 21. A swirl scroll 22 or the like is provided between the base plates and is meshed with the fixed scroll 21. The swivel scroll 22 is meshed with the fixed scroll 21 to form a compression chamber 23, and the working fluid is taken into the compression chamber 23 and compressed.

The drive unit 3 is composed of a motor 30 composed of a stator 31 and a rotor 32, a rotating shaft (crankshaft) 33 inserted in the center of the rotor 22 and fixed integrally, and the like. ..
The upper side of the rotating shaft 33 is supported by a main bearing 24 arranged on the frame 20, and the lower side thereof is supported by an auxiliary bearing 6 attached to a lower frame 5 fixed to a closed container 4. ..

The upper end of the rotating shaft 33 is a crank portion (eccentric shaft portion) 33a, and the crank portion 33a is interposed in a swivel boss portion 22a provided in the center of the back surface of the swivel scroll 22 via a swivel bearing 25. It has been inserted. Reference numeral 26 denotes an old dam ring that engages with both the back surface of the end plate of the swivel scroll 22 and the frame 20 to prevent the swivel scroll 22 from rotating and to cause a swivel motion.

Therefore, when the rotor 32 of the drive unit 3 rotates, the swivel scroll 22 swivels through the rotation shaft 33, and the compression chamber 23 formed by the fixed scroll 21 and the swivel scroll 22 has a volume. Compresses while decreasing, and moves to the center side.

Reference numeral 7 denotes a suction pipe connected to a suction chamber provided on the outer peripheral side of the fixed scroll 21, and reference numeral 21a is a discharge port provided at the center of the end plate of the fixed scroll 21. When the rotating shaft 33 rotates to rotate the swivel scroll 22, a working fluid such as a refrigerant in the refrigeration cycle is sucked from the suction pipe 7 into the compression chamber 23 via the suction chamber. Then, after undergoing the compression stroke by the compression operation, the working fluid in the compression chamber 23 is compressed and discharged from the discharge port 21a of the fixed scroll 21 to the discharge space 8 formed in the upper part of the closed container 4. .. The working fluid discharged into the discharge space 8 passes through a passage (not shown) formed between the closed container 4, the outer peripheral surface of the fixed scroll 21 and the outer peripheral surface of the frame 20, and the driving unit. It flows into the space where 3 is arranged, and then is supplied from the discharge pipe 9 to the refrigerant pipe or the like of the refrigeration cycle.

On the other hand, a refueling passage 33b penetrating in the axial direction is formed in the rotating shaft 33, and a refueling pump 10 is provided on the lower end side of the rotating shaft 33, and the refueling pump 10 is the rotating shaft 33. As it rotates, oil (lubricating oil) is sucked up from the oil sump 11 formed at the inner bottom of the closed container 4 and supplied to the oil supply passage 33b.

A part of this oil is supplied to the auxiliary bearing 6 to lubricate the auxiliary bearing 6. Other oil supplied to the oil supply passage 33b is supplied from the upper end of the crank portion 33a into the swivel boss portion 22a to lubricate the swivel bearing 25, and then some oil is supplied to the frame 20 and the swivel scroll. It flows into the intermediate pressure chamber 27 formed between the 22 and the intermediate pressure chamber 27. The oil that has flowed into the intermediate pressure chamber 27 lubricates the sliding portions such as the old dam ring, and also flows into the compression chamber 23 to lubricate the sliding portions of the fixed scroll 21 and the swivel scroll 22. This oil also has a function of preventing the working fluid in the compression chamber 23 from leaking to the low pressure side.

Most of the other oil after lubricating the swivel bearing 25 flows to the main bearing 24 to lubricate the main bearing 24, and then drains from the through hole 20a formed in the frame 20 to the through hole 20a. It is returned to the oil sump 11 via the oil pipe 12.

In the scroll compressor 2 of the present embodiment shown in FIG. 1, the oil drain pipe 12 is L-shaped, and the connection portion (insertion portion) 12a on the upper end side of the oil drain pipe 12 is placed on the lower side surface of the frame 20. The structure is such that it is inserted into the formed through hole 20a and fixed. If the outer periphery of the lower side surface of the frame 20 has a structure close to the inner wall of the closed container 4, a through hole is provided on the outer peripheral side of the lower end surface of the frame 20, and a linear oil drainage hole is provided in the through hole. It may be configured to connect pipes.

The oil drain pipe 12 is made of a metal pipe such as iron, and the oil drain pipe 12 passes through a gap formed between the closed container 4 and the stator 31 of the motor 30. The structure extends to the oil sump 11 side at the bottom of the closed container 4. Further, the lower end side of the oil drain pipe 12 penetrates the lower frame 5 and is fixed by the oil drain pipe support member 13 provided in the lower frame 5. In this embodiment, the lower end side of the oil drain pipe 12 is fixed by the oil drain pipe support member 13, but for example, a part of the oil drain pipe 12 is brought into contact with the inner wall surface of the closed container 4 to support it. It may be used as another support structure.

Here, the configuration of the conventional oil drainage pipe 12 will be described with reference to FIG. 1 with reference to FIG. As shown in FIG. 2, the conventional oil drain pipe 12 is formed in an L shape, and is formed on the upper connecting portion (inserting portion) 12a to be inserted into the through hole 20 of the frame 4 and the inner wall surface of the closed container 4. It is composed of a linear oil guide portion 12b extending downward along the line and a bent portion 12c connecting the connection portion 12a and the oil guide portion 12b.

The conventional oil drain pipe 12 as shown in FIG. 2 is composed of pipes having substantially the same diameter over the entire length, and the oil guide portion 12b having a length of about 250 mm constitutes the oil guide portion. The outer diameter of the pipe is 7 mmφ (thickness 0.7 mm) and is generally used. As described above, since the conventional oil drain pipe 12 has a thin and long shape, when the scroll compressor is operated by supporting both ends of the oil drain pipe 12, the oil drain pipe 12 is as shown in FIG. It was found that the vibration that deforms most near the center of the oil guide portion 12b occurs, and the natural frequency thereof is about 560 kHz.

For this reason, in the conventional scroll compressor, noise of low frequency vibration of less than 1000 Hz is generated, and it is difficult to reduce the noise of vibration of low frequency like this even if a soundproof cover is used. Met.

Therefore, in the scroll compressor of this embodiment, the oil drain pipe 12 has the configuration shown in FIG. The oil drain pipe 12 shown in FIG. 4 has the same configurations of the connecting portion 12a and the bent portion 12c as those shown in FIG. 2, but the configurations of the oil guiding portion 12b are different. In this embodiment, the cylindrical reinforcing member 12d is inserted into the oil conducting portion 12b of the oil draining pipe 12 by means such as press fitting or shrink fitting, and is integrally fixed. As a result, the outer diameter of the oil guide portion 12b of the oil drain pipe 12 is increased (larger), and the rigidity of the portion having the lowest rigidity, that is, the vicinity of the center (center portion) of the oil guide portion 12b is increased, and the oil drain pipe is discharged. The natural frequency of 28 is increased.

The portion of the oil guide portion 12b for increasing the outer diameter may be at least a section from the upper part to the lower part of the stator 31.

In this embodiment, as shown in FIG. 1, the reinforcing member 12d is provided from the upper part of the stator 31 of the motor 30 to the lower frame 5 in the oil guiding portion 12b, the outer diameter of which is 12 mmφ, and the inner diameter of the guide. The outer diameter of the oil portion 12d is 7 mmφ, which is the same as the outer diameter. Therefore, the wall thickness of the reinforcing member 12d is 2.5 mm, and the total wall thickness including the wall thickness of the oil guide portion 12b of 0.7 mm is 3.2 mm.

By configuring the oil drain pipe 12 in this way, even if the scroll compressor is operated, the deformation of the oil guide portion 12b in the oil drain pipe 12 can be suppressed and the vibration can be suppressed, and the natural frequency thereof can be up to 1035 kHz. I was able to make it higher. As described above, according to the present embodiment, the natural frequency of the oil drain pipe 12 can be easily set to 1000 Hz or higher, and the generation of low vibration noise having a frequency lower than 1000 Hz can be significantly suppressed. Further, since the vibration amplitude of the oil drain pipe 12 can be significantly suppressed, the generation of noise can also be suppressed.

That is, since the natural frequency of the oil drain pipe 12 can be set to 1000 Hz or higher, the frequency of vibration due to the resonance of the oil drain pipe itself generated by propagating the vibration of the motor 30 to the oil drain pipe 12 can be set to 1000 Hz or higher, and 1000 Hz. It is possible to sufficiently reduce the generation of low frequency noise less than. That is, even if low-frequency vibration is applied to the oil drain pipe 12, it does not resonate at that low frequency, so that low-frequency vibration is immediately attenuated, so that the generation of low-frequency vibration noise is significantly suppressed. Can be done. Further, since the vibration amplitude of the oil drain pipe can be suppressed to be small, the loudness of noise can be reduced.

Therefore, in the present embodiment, by covering the outside of the scroll compressor 1 with a soundproof cover, noise of 1000 Hz or higher can be easily soundproofed, and the generation of low frequency noise can be significantly suppressed. Therefore, in the entire audible range. , Noise due to resonance of the oil drain pipe 12 can be reduced.

In order to confirm that the oil drain pipe in the present embodiment having the above-described configuration has a natural frequency of 1000 Hz or higher, there are a method of obtaining the natural frequency by numerical calculation and a method of obtaining it by a striking test. By using the striking test method, the natural frequency can be obtained accurately and reliably.

As the material constituting the reinforcing member 12d described above, it is preferable to use the same iron-based material as the material of the oil conducting portion 12b of the oil drain pipe 12, but if it is possible to increase the rigidity of the oil drain pipe 12. Other metal materials and materials other than metal materials may be used. The means for fixing the reinforcing member 12d to the oil guiding portion 12b of the oil drain pipe 12 may be a method other than press fitting or shrink fitting, and may be configured to be fixed by means such as welding.

Further, in order to increase the rigidity of the oil drain pipe 12, an oil drain pipe having a large diameter over the entire length of the oil drain pipe 12 may be used, but the penetration portion 12a of the oil drain pipe 12 is inserted into the frame 20. There is a limit to expanding the portion of the hole 20a to the periphery, and if the oil drain pipe is made thicker, the cost increases. From these facts, the reinforcing member 12d is placed at a position where the rigidity of the oil drain pipe 12 is low, that is, near the center (center part) of the oil guide portion 12b, preferably from the vicinity of the upper part of the stator 31 of the motor 30 to the vicinity of the lower part of the stator. It is good to provide it in a limited way.

Further, the oil drain pipe 12 is arranged so as to pass through a gap formed between the closed container 4 and the stator 31 of the motor 30, but is arranged on the outer peripheral surface of the stator 31 in the axial direction. A notch is provided, and the oil drain pipe 12 is arranged in the notch. If the notch is made larger, the slot area of the stator becomes smaller and the amount of stator windings needs to be reduced (the number of turns is reduced), which lowers the performance of the motor. Therefore, there is a limit to the size of the notch so as not to affect the motor performance.

On the other hand, the natural frequency of the oil drain pipe 12 can be increased by increasing the outer diameter of the reinforcing member 12d, but the size of the notch on the outer periphery of the stator is limited, so that the reinforcing member 12d The outer diameter of the above must be large enough to allow the oil drainage pipe to be placed in the notch on the outer circumference of the stator.

When the notch portion has a size that does not affect the performance of the motor, the outer diameter of the reinforcing member 12d that can be arranged here is generally about 15 mmφ or less. In the first embodiment, when the outer diameter of the reinforcing member 12d is 15 mmφ, the natural frequency of the oil drain pipe is about 1300 Hz. From these facts, it is preferable that the natural frequency of the oil drain pipe 12 is 1000 Hz to 1300 Hz.

As described above, according to the present embodiment, it is possible to obtain a compressor capable of sufficiently reducing the noise of less than 1000 Hz due to the resonance of the oil drain pipe itself generated by the propagation of the vibration of the motor.

Example 2 of the compressor of the present invention will be described with reference to FIG. 1 and the like with reference to FIG. FIG. 5 is a perspective view for explaining the structure of the oil drain pipe in the second embodiment. In the second embodiment, the parts different from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be described. The description of the above will be omitted.

In order to set the natural frequency of the oil drain pipe 12 to 1000 Hz or higher, an example in which the reinforcing member 12d is provided in the oil guiding portion 12b has been described in the first embodiment, but in the second embodiment, instead of providing the reinforcing member 12d. The diameter of the oil guiding portion 12b of the oil draining pipe 12 is increased by means such as pipe expansion.

As the material of the oil drain pipe in this embodiment, the length of the oil guide portion 12b is 250 mm and the outer diameter of the pipe is 7 mmφ (thickness 0.7 mm), as in the conventional example shown in FIG. ing. As a result of expanding the oil conducting portion 12b of this pipe to have an outer diameter of 12.5 mmφ, the wall thickness is 0.36 mm.

Even if the oil drain pipe 12 is configured in this way and the scroll compressor is operated, the deformation of the oil guide portion 12b in the oil drain pipe 12 can be suppressed and the vibration can be suppressed, and the natural frequency thereof is increased to 1042 kHz. I was able to. As described above, also in the second embodiment, the rigidity of the oil drain pipe 12 can be improved to easily increase the natural frequency to 1000 kHz or more, and the generation of low vibration noise having a frequency of less than 1000 kHz is significantly suppressed. can do. Further, since the vibration amplitude of the oil drain pipe 12 can be significantly suppressed, the generation of noise can also be suppressed.

Further, according to the present embodiment, since it is not necessary to provide the reinforcing member 12d of the first embodiment, the number of parts can be reduced, the cost can be reduced, and the assembly man-hours can be reduced. Further, according to the present embodiment, there is an effect that the weight of the oil drain pipe can be prevented from increasing.

Example 3 of the compressor of the present invention will be described with reference to FIG. 1 and the like with reference to FIG. FIG. 6 is a perspective view for explaining the structure of the oil drain pipe in the second embodiment. In the explanation of the third embodiment, the parts different from the first and second embodiments described above will be mainly described, and the first and second embodiments will be described. The description of the same part as in 2 will be omitted.

In order to set the natural frequency of the oil drain pipe 12 to 1000 Hz or higher, in the first embodiment, the reinforcing member 12d is provided in the oil guide portion 12b, and in the second embodiment, the diameter of the oil guide portion 12b of the oil drain pipe 12 is set. An example of enlarging by means such as pipe expansion was explained.

As the material of the oil drain pipe in the third embodiment, the same as the conventional example shown in FIG. 2, the oil guide portion 12b has a length of 250 mm and the outer diameter of the pipe is 7 mmφ (thickness 0.7 mm). doing.

In the third embodiment as well, similarly to the second embodiment, the oil conducting portion 12b of the oil drain pipe 12 is expanded to have an outer diameter of 12.5 mmφ and a wall thickness of 0.36 mm. However, in the third embodiment, unlike the second embodiment, the diameter of the lower end side 12ba of the oil conducting portion 12b in the oil draining pipe 12 is configured to be smaller than the pipe expanding portion 12bb near the center of the oil conducting portion 12b. Is what it is. That is, in the third embodiment, the lower end side 12ba of the oil drain pipe 12 is not expanded and is near the center (center portion) of the oil guiding portion 12d, preferably the same as the installation range of the reinforcing member 12d of the first embodiment. , Only the portion from the vicinity of the upper portion of the stator 31 of the motor 30 to the vicinity of the lower portion of the stator is expanded to form a thick tube expansion portion 12bb.

Even if the oil drain pipe 12 is configured in this way and the scroll compressor is operated, the deformation of the oil guide portion 12b in the oil drain pipe 12 can be suppressed and the vibration can be suppressed, and the natural frequency thereof is increased to 1036 kHz. I was able to. As described above, also in the third embodiment, the rigidity of the oil drain pipe 12 can be improved to easily increase the natural frequency to 1000 kHz or more, and the generation of low vibration noise having a frequency of less than 1000 kHz is significantly suppressed. can do. Further, since the vibration amplitude of the oil drain pipe 12 can be significantly suppressed, the generation of noise can also be suppressed.

Further, the same effect as that of the second embodiment can be obtained. That is, it is not necessary to provide the reinforcing member 12d as in the first embodiment, the cost can be reduced, the number of assembly steps can be reduced, and the weight of the oil drain pipe can be prevented from increasing. The third embodiment is particularly effective when the space around the bottom of the closed container 4 is limited.

As a means for molding the oil drain pipe 12 as in this embodiment, for example, it can be processed by bulge molding. Hydroforming is a hollow molding of a metal pipe that fills a pipe set in a mold with an ultra-high pressure liquid, compresses both ends of the pipe in the axial direction, and processes it into the shape engraved in the mold at once. Also called hydroforming, it is plastic working using metal pipe as a material.

The present invention is not limited to the above-described examples, and includes various modifications. For example, in the above embodiment, the scroll compressor has been described as an example of the compression chamber, but the present invention is not limited to the scroll compressor, and if it includes an oil drain pipe, a rotary compressor or the like may be used. The same applies to compressors of the type.

In addition, the above-described embodiment has been described in detail in order to explain the present invention in an easy-to-understand manner, and is not necessarily limited to the one including all the described configurations.

1 ... Scroll compressor (compressor), 2 ... Compression mechanism, 3 ... Drive, 4 ... Sealed container,
5 ... lower frame, 6 ... auxiliary bearing, 7 ... suction pipe, 8 ... discharge space, 9 ... discharge pipe,
10 ... refueling pump, 11 ... oil sump,
12 ... Oil drain pipe, 12a ... Connection part (insertion part),
12b ... Oil guide section, 12ba ... Lower end side of oil guide section, 12bb ... Tube expansion section,
12c ... Bent part, 12d: Reinforcing member,
13 ... Oil drain pipe support member,
20 ... frame, 20a ... through hole,
21 ... Fixed scroll, 21a ... Discharge port,
22 ... Swivel scroll, 22a ... Swivel boss,
23 ... Compression chamber,
24 ... main bearing, 25 ... swivel bearing, 26 ... old dam ring, 27 ... intermediate pressure chamber,
30 motors, 31 ... stators, 32 ... rotors,
33 ... Rotating shaft (crankshaft), 33a ... Crank portion, 33b ... Refueling passage.

Claims (12)

The airtight container has a compression mechanism unit, a drive unit that drives the compression mechanism unit via a rotating shaft, and an oil reservoir, and oil supplied to the sliding portion of the compression mechanism unit is used as the oil reservoir. In a compressor with a return oil drain pipe
The oil drain pipe includes a connection portion connected to the compression mechanism portion and a linear oil guide portion that guides oil to the oil sump.
The outer diameter of at least the central portion of the oil conducting portion is configured to be larger than the outer diameter of the other portion of the oil drain pipe .
A compressor characterized in that the natural frequency of the oil drain pipe is 1000 Hz or higher . A frame fixed in a closed container, a fixed scroll fixed to the upper part of the frame, and a swirl scroll provided between the frame and the fixed scroll and meshed with the fixed scroll to form a compression chamber. It has a compression mechanism unit including, a drive unit arranged below the compression mechanism unit to drive the compression mechanism unit via a rotation shaft, and an oil sump formed at the bottom of the closed container. In a compressor provided with an oil drain pipe that returns the oil supplied to the sliding portion of the compression mechanism portion to the oil sump.
The oil drain pipe includes a connection portion connected to the compression mechanism portion and a linear oil guide portion that guides oil to the oil sump.
The outer diameter of at least the central portion of the oil conducting portion is configured to be larger than the outer diameter of the other portion of the oil drain pipe .
A compressor characterized in that the natural frequency of the oil drain pipe is 1000 Hz or higher . The airtight container has a compression mechanism unit, a drive unit that drives the compression mechanism unit via a rotating shaft, and an oil reservoir, and oil supplied to the sliding portion of the compression mechanism unit is used as the oil reservoir. In a compressor with a return oil drain pipe
The oil drain pipe includes a connection portion connected to the compression mechanism portion and a linear oil guide portion that guides oil to the oil sump.
The outer diameter of at least the central portion of the oil conducting portion is configured to be larger than the outer diameter of the other portion of the oil drain pipe .
The drive unit includes a stator fixed to the closed container and a rotor arranged on the inner peripheral side of the stator, and the oil drain pipe is formed between the closed container and the stator. A compressor characterized in that it is configured to reach the oil sump side of the inner bottom of the closed container through a gap . A frame fixed in a closed container, a fixed scroll fixed to the upper part of the frame, and a swirl scroll provided between the frame and the fixed scroll and meshed with the fixed scroll to form a compression chamber. It has a compression mechanism unit including, a drive unit arranged below the compression mechanism unit to drive the compression mechanism unit via a rotation shaft, and an oil sump formed at the bottom of the closed container. In a compressor provided with an oil drain pipe that returns the oil supplied to the sliding portion of the compression mechanism portion to the oil sump.
The oil drain pipe includes a connection portion connected to the compression mechanism portion and a linear oil guide portion that guides oil to the oil sump.
The outer diameter of at least the central portion of the oil conducting portion is configured to be larger than the outer diameter of the other portion of the oil drain pipe .
The drive unit includes a stator fixed to the closed container and a rotor arranged on the inner peripheral side of the stator, and the oil drain pipe is formed between the closed container and the stator. A compressor characterized in that it is configured to reach the oil sump side of the inner bottom of the closed container through a gap . In the compressor according to claim 3 or 4 ,
A compressor characterized in that the natural frequency of the oil drain pipe is 1000 Hz or higher. In the compressor according to any one of claims 1, 2 and 5 .
A compressor characterized in that the natural frequency of the oil drain pipe is 1000 Hz to 1300 kHz. In the compressor according to claim 1 or 2.
The drive unit includes a stator fixed to the closed container and a rotor arranged on the inner peripheral side of the stator, and the oil drain pipe is formed between the closed container and the stator. A compressor characterized in that it is configured to reach the oil sump side of the inner bottom of the closed container through a gap. In the compressor according to claim 4 ,
The frame is provided with a main bearing that supports the rotating shaft, and the oil in the oil sump is supplied to the main bearing through an oil supply passage formed in the rotating shaft and supplied to the main bearing. A compressor characterized in that oil is guided to the oil drain pipe from a through hole formed in the frame and returned to the oil sump. In the compressor according to claim 8 ,
A compressor characterized in that the outer diameter of at least a portion of the oil guide portion of the oil drain pipe from the upper portion to the lower portion of the stator is larger than the outer diameter of the other portion of the oil drain pipe. In the compressor according to claim 9 ,
A compressor characterized in that the outer diameter of the oil-conducting portion of the oil-draining pipe is made large by inserting a cylindrical reinforcing member into the oil-conducting portion of the oil-draining pipe and fixing it integrally. In the compressor according to claim 9 ,
A compressor characterized in that the outer diameter of the oil guide portion is increased by expanding the oil guide portion of the oil drain pipe. In the compressor according to claim 8 ,
The oil drain pipe is formed in an L shape, and has an upper connecting portion that is inserted into a through hole of the frame, a linear oil guiding portion that extends downward along the inner wall surface of the closed container, and the connecting portion. It is characterized in that it has a bent portion that connects the oil conducting portion and the oil conducting portion, and at least the central portion of the linear oil conducting portion is formed to have a larger diameter than the connecting portion and the bent portion of the oil drain pipe. Compressor.

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