WO2019021432A1

WO2019021432A1 - Scroll compressor

Info

Publication number: WO2019021432A1
Application number: PCT/JP2017/027302
Authority: WO
Inventors: 光勇太田; 昌晃須川; 鉄郎平見
Original assignee: 三菱電機株式会社
Priority date: 2017-07-27
Filing date: 2017-07-27
Publication date: 2019-01-31
Also published as: JP6808044B2; CN211230820U; JPWO2019021432A1

Abstract

This scroll compressor comprises: a container; a stationary scroll provided within the container; an orbiting scroll provided within the container and combined with the stationary scroll; a main shaft provided within the container and causing the orbiting scroll to orbit; a rotor provided within the container and rotating the main shaft; a stator provided within the container and rotating the rotor; an orbiting bearing provided to the orbiting scroll and having inserted therein the eccentric shaft section of the main shaft; a slider fitted in the orbiting bearing and supporting the orbiting scroll; and a slider balancer provided to the eccentric shaft section and generating centrifugal force in the direction opposite the direction of eccentricity of the eccentric shaft section. The rotor has provided therein a weight adjustment section for offsetting centrifugal force occurring at the eccentric shaft section.

Description

Scroll compressor

The present invention relates to a scroll compressor used as one of the components of a refrigeration cycle.

Scroll compressors that conventionally exist generally include a fixed scroll, a rocking scroll, a stator, a rotor, a main shaft, a slider, an eccentric shaft, a compression unit, an electric mechanism, a shell, a suction pipe, a discharge pipe, and a frame. , Sub-frame, and positive displacement oil pump.

The fixed scroll constitutes the compression unit and is fixed to the frame.
The oscillating scroll constitutes a compression unit together with the fixed scroll, and has a rotating shaft eccentric to the center of the fixed scroll.
The stator constitutes an electric mechanism portion and is fixed to the shell.
The rotor constitutes an electric mechanism together with the stator, and is inserted at the center of the stator.
The main shaft is fixed to the rotor and rotationally driven by the electric mechanism.

The slider is installed to be fitted to a rocking bearing for revolving movement of the rocking scroll and supports the rocking scroll.
The eccentric shaft portion is a slider mounting shaft installed at an upper portion of the main shaft so that the slider is eccentric to the main shaft.
The compression unit includes a fixed scroll and an oscillating scroll, and compresses the refrigerant gas.
The electric mechanism portion functions as a motor, includes a stator and a rotor, and drives the oscillating scroll via a main shaft.
The shell accommodates the compression part and the electric mechanism part, and is a closed container.

The suction pipe is connected to the low pressure portion of the shell and introduces the refrigerant gas into the shell from the outside of the shell.
The discharge pipe is connected to the high pressure portion of the shell and discharges the refrigerant gas compressed in the compression unit to the outside of the shell.
The frame supports the oscillating scroll and the main shaft, and is fixed to the shell by bolts or the like with respect to the fixed scroll.
The sub-frame is fixed to the shell and rotatably supports the main shaft.
The positive displacement oil pump sucks up refrigeration oil accumulated in the bottom of the shell to the slider. The refrigeration oil sucked up by the positive displacement oil pump is guided to the slider through the oil supply passage in the main shaft.

Further, in the scroll compressor, the oscillating scroll is eccentric to the rotation axis of the main shaft in order to oscillate the oscillating scroll. Therefore, during operation of the scroll compressor, centrifugal force is generated on the main shaft by the oscillating scroll and peripheral members of the oscillating scroll, that is, the bush and the slider. Two balancers are provided to balance the generated centrifugal force in the rotational direction and the axial direction of the main shaft. The two balancers offset the centrifugal force generated by the eccentricity of the oscillating scroll.

As described in Patent Document 1, some scroll compressors include a balancer attached to the lower surface of the rotor integrally with the rotor.
Further, Patent Document 2 describes a compressor in which a balancer cover is provided on the outer periphery of a balancer attached to the lower surface of a rotor so as to prevent oil from rising.
Further, Patent Document 3 describes a scroll compressor in which a slider balancer is provided on the opposite side of the main shaft eccentric direction of the slider in addition to the two balancers. The scroll compressor described in Patent Document 3 makes it possible to offset the centrifugal force generated in the eccentric portion with an increase in the centrifugal force generated in the eccentric portion of the main shaft due to the acceleration of the compression portion.

Such a scroll compressor has a slider balancer, a first balancer, and a second balancer for operating against the centrifugal force Fc generated by the oscillating scroll, the eccentric portion of the main shaft, and the peripheral members of the oscillating scroll during operation. Is provided. The first balancer is attached to the top of the rotor. The second balancer is attached to the lower part of the rotor. The slider balancer is mounted on the side opposite to the main shaft eccentric direction of the slider.

Each of the slider balancer, the first balancer, and the second balancer is provided with an unbalanced portion. A centrifugal force Fb is generated in the slider balancer during operation. A centrifugal force F1 is generated in the first balancer during operation. A centrifugal force F2 is generated in the second balancer during operation. The slider balancer, the first balancer, and the second balancer make it possible to offset the centrifugal force Fc generated by the oscillating scroll or the like.

Since the slider balancer is provided at a position close to the eccentric portion of the main shaft, it is possible to offset most of the centrifugal force generated by the eccentric portion of the main shaft and the moment generated by the centrifugal force by increasing the weight. It is possible. However, since it is difficult to completely offset the centrifugal force Fc only with the slider balancer, the first balancer and the second balancer are required. Therefore, three balancers are to be installed, and the number of parts is increased, which causes a problem that the number of processing steps is increased.

Further, Patent Document 4 describes a compressor in which the force of the entire rotating portion is balanced by the arrangement of magnets without providing the first balancer and the second balancer.

Japanese Patent Application Laid-Open No. 04-112652 JP, 2015-166553, A Japanese Utility Model Publication No. 04-49602 International Publication No. 2016/974778

As described in Patent Document 1 and Patent Document 2, generally, the scroll compressor includes a first balancer and a second balancer, and cancels out the centrifugal force generated by the eccentricity of the oscillating scroll. Further, in the scroll compressor described in Patent Document 3, a slider balancer is further provided to offset the centrifugal force generated by the eccentricity of the oscillating scroll.
However, a compressor equipped with a balancer has problems such as an increase in work processes, an increase in cost due to an increase in the number of parts, and an inhibition of resource saving due to an increase in the number of parts.

Therefore, in the compressor described in Patent Document 4, the centrifugal force generated by the oscillating scroll or the like is offset without providing a balancer.
However, in the compressor described in Patent Document 4, although the centrifugal force generated by the oscillating scroll or the like is offset by the arrangement of the magnets, there is a portion where the magnet is not provided, and the size of the magnet It can not be said that the efficiency of the motor is good.

The present invention has been made to solve the above problems, and can reduce the balancer required to offset the centrifugal force generated by the eccentricity of the oscillating scroll without reducing the efficiency of the motor. The purpose is to provide a scroll compressor.

The scroll compressor according to the present invention comprises a container, a fixed scroll provided in the container, a rocking scroll provided in the container and combined with the fixed scroll, provided in the container, and A main shaft for oscillating movement of the moving scroll, a rotor provided in the container and rotating the main shaft, a stator provided in the container for rotating the rotor, and the rotating scroll provided on the oscillating scroll A swing bearing into which the eccentric shaft portion is inserted, a slider fitted with the swing bearing and supporting the swing scroll, and the eccentric shaft portion provided opposite to the eccentric direction of the eccentric shaft portion And a slider balancer for generating a centrifugal force, and a weight adjusting portion for canceling the centrifugal force generated in the eccentric shaft is provided inside the rotor.

According to the scroll compressor according to the present invention, by inserting the weight adjusting unit into the rotor, it is possible to generate centrifugal force due to mass imbalance, and cancel the centrifugal force generated by the eccentricity of the oscillating scroll. Can reduce the amount of balancers.

It is a schematic block diagram which roughly shows an example of an internal structure of the scroll compressor which concerns on Embodiment 1 of this invention. It is a block diagram which extracts and expands and shows a main axis, a rotor, and a sub frame of a scroll compressor concerning Embodiment 1 of the present invention. It is a top view of the electromagnetic steel plate which constitutes the rotor of the scroll compressor concerning Embodiment 1 of the present invention. It is a block diagram which extracts and expands and shows the principal axis and rotor of a scroll compressor concerning Embodiment 2 of the present invention. It is a top view of the electromagnetic steel plate which comprises the rotor of the scroll compressor concerning Embodiment 2 of the present invention. It is a top view of the electromagnetic steel plate which comprises the rotor of the scroll compressor concerning Embodiment 3 of the present invention.

Hereinafter, embodiments of the present invention will be described based on the drawings.
Embodiment 1
FIG. 1 is a schematic configuration view schematically showing an example of an internal configuration of a scroll compressor 100 according to Embodiment 1 of the present invention. The configuration and operation of the scroll compressor 100 will be described based on FIG. The scroll compressor 100 is used as one of the components of a refrigeration cycle. As an apparatus provided with a refrigerating cycle, various refrigerating cycle apparatuses, such as a refrigerator, a freezer, a vending machine, an air conditioning apparatus, a refrigerating apparatus, or a water heater, can be considered. In addition, in the following drawings including FIG. 1, the relationship of the magnitude | size of each structural member may differ from an actual thing.

<Overall Configuration of Scroll Compressor 100>
The scroll compressor 100 sucks, compresses and discharges the refrigerant circulating in the refrigeration cycle as a high-temperature and high-pressure state. The scroll compressor 100 has a compression unit 50 including the fixed scroll 9 and the oscillating scroll 10 and the like, and an electric mechanism unit 60 including the stator 2 and the rotor 3 and the like. The compression unit 50 and the electric mechanism unit 60 are housed in a container 1 which is a shell. As shown in FIG. 1, in the state where the scroll compressor 100 is installed, the compression unit 50 is disposed on the upper side of the container 1 and the electric mechanism unit 60 is disposed on the lower side of the container 1.

The container 1 is an airtight container provided with the upper container 1c in the upper part of the middle part container 1a, and the lower container 1b in the lower part of the middle part container 1a. The lower container 1 b is an oil reservoir 23 for storing refrigeration oil that is to be lubricating oil. A suction pipe 24 for suctioning the refrigerant gas is connected to the intermediate container 1a. A discharge pipe 25 for discharging the refrigerant gas is connected to the upper container 1c.

The compression unit 50 is configured to include the oscillating scroll 10, the fixed scroll 9, the frame 11, and the like. As shown in FIG. 1, the swing scroll 10 is installed below the container 1, and the fixed scroll 9 is installed above the container 1. Further, a thrust plate 14 for supporting the oscillating scroll 10 is provided between the oscillating scroll 10 and the frame 11. The rocking scroll 10 and the thrust plate 14 are in close contact with each other through a refrigerator oil to constitute a thrust bearing.

The fixed scroll 9 is formed with a wrap portion 9a which is a spiral protrusion standing on one surface. Further, the oscillating scroll 10 is also provided with a wrap portion 10a which is a spiral protrusion provided on one surface. The swing scroll 10 and the fixed scroll 9 are mounted in the container 1 by combining the wrap portion 10 a and the wrap portion 9 a with each other. When the rocking scroll 10 and the fixed scroll 9 are combined, the winding directions of the wrap portion 9a and the wrap portion 10a are opposite to each other.

And between the lap | wrap part 10a and the lap | wrap part 9a, the compression chamber 26 to which a volume changes relatively is formed. In the wrap portion 9a of the fixed scroll 9, a seal 28 is disposed on the lower end surface which is the tip end surface of the wrap portion 9a in order to reduce the refrigerant leakage from the tip end surface of the wrap portion 9a. In the wrap portion 10a of the orbiting scroll 10, a seal 27 is disposed on the upper end surface, which is the tip surface of the wrap portion 10a, in order to reduce the refrigerant leakage from the tip surface of the wrap portion 10a.

The fixed scroll 9 is fixed to the frame 11 by a bolt or the like (not shown). At a central portion of the fixed scroll 9, a discharge port 9b is formed which discharges the compressed refrigerant gas that has a high pressure. Then, the refrigerant gas that has been compressed to a high pressure is discharged to the discharge space 33 provided at the upper portion of the fixed scroll 9. The refrigerant gas discharged to the discharge space 33 is discharged to the refrigeration cycle through the discharge pipe 25. The discharge port 9 b is provided with a discharge valve 29 for preventing the backflow of the refrigerant from the discharge space 33 to the discharge port 9 b side.

The rocking scroll 10 is configured to perform a revolving movement (rocking movement) without rotating with respect to the fixed scroll 9 by the Oldham ring 15 for blocking the rotation. Further, a hollow cylindrical swing bearing 13 is formed at a substantially central portion of a thrust surface which is a surface opposite to the wrap 10 a forming surface of the swing scroll 10.

A slider 16 for rotating the oscillating scroll 10 is rotatably fitted to the oscillating bearing 13, and the oscillating scroll 10 is supported by the slider 16. An eccentric shaft 4 a provided at the upper end of the main shaft 4 is inserted into the slide surface of the slider 16. The eccentric shaft 4 a is a slider mounting shaft installed at the upper portion of the main shaft 4 so that the slider 16 is eccentric to the main shaft 4. Then, the inner peripheral portion of the rocking bearing 13 and the outer peripheral portion of the slider 16 are in close contact with each other through the refrigerator oil to constitute the rocking bearing portion. Further, a slider balancer 37 is attached to the eccentric shaft 4a.

The frame 11 is fixed to the inside of the container 1 by bolts or the like (not shown) and supports the swing scroll 10 and the main shaft 4. Further, at the central portion of the frame 11, a main bearing 12 into which the main shaft 4 is inserted and rotatably supported is formed.

The electric mechanism portion 60 includes the rotor 3 into which the main shaft 4 is inserted, the stator 2 and the main shaft 4 which is a rotating shaft. The rotor 3 is fixed to the main shaft 4 and is rotationally driven by starting energization of the stator 2 so as to rotate the main shaft 4. The rotor 3 is configured by laminating electromagnetic steel plates or the like, and the first weight adjusting unit 34 and the second weight adjusting unit 35 are inserted inside. As shown in FIG. 1, the first weight adjusting unit 34 is inserted to the compression unit 50 side. Further, the second weight adjusting unit 35 is inserted on the sub frame 20 side.

The main shaft 4 is rotated along with the rotation of the rotor 3 to swing the oscillating scroll 10. The upper portion of the main shaft 4 is supported by a main bearing 12 provided on the frame 11. A sleeve 17 is provided between the main bearing 12 and the main shaft 4 in order to make the main shaft 4 rotate smoothly.

On the other hand, the lower part of the main shaft 4 is rotatably supported by a ball bearing 21. The ball bearing 21 is press-fitted and fixed to a bearing accommodating portion 20 a formed at a central portion of a sub-frame 20 provided at the lower portion of the container 1. In addition, the sub-frame 20 is provided with a positive displacement oil pump 22. A pump shaft 4 b for transmitting a rotational force to the oil pump 22 is integrally formed with the main shaft 4. The refrigerating machine oil of the oil reservoir 23 sucked by the oil pump 22 is sent to each sliding portion such as the slider 16 via the oil hole 4 c and the like formed inside the main shaft 4.

<Overall Operation of Scroll Compressor 100>
When a voltage is applied to the motorized mechanism 60, a current flows in the stator 2 and a magnetic field is generated. This magnetic field acts to rotate the rotor 3. When the rotor 3 rotates, the main shaft 4 is rotationally driven accordingly. When the main shaft 4 is rotationally driven, the slider 16 is also rotated in the rocking bearing 13 via the eccentric shaft 4 a. Along with this, the rocking scroll 10 whose rotation is suppressed by the Oldham ring 15 performs rocking movement. When the oscillating scroll 10 performs the oscillating operation, the refrigerant is compressed by a known compression principle.

When the rocking scroll 10 starts rocking operation, the refrigerant sucked from the suction pipe 24 is introduced into the compression chamber 26. The compression chamber 26 moves to the center of the oscillating scroll 10 by the oscillating motion of the oscillating scroll 10, and the volume is reduced. Thus, the refrigerant is compressed. At this time, a load is applied to the fixed scroll 9 and the swing scroll 10 so as to be separated in the axial direction by the compressed refrigerant. This load is supported by the thrust plate 14. The compressed refrigerant passes through the discharge port 9 b of the fixed scroll 9, pushes the discharge valve 29 open, and flows into the discharge space 33. Then, it is discharged from the container 1 through the discharge pipe 25.

During operation of the scroll compressor 100, each sliding portion is supplied with refrigeration oil which is lubricating oil. As the sliding portion, the contact portion between the swing scroll 10 and the thrust plate 14, the contact portion between the swing bearing 13 and the slider 16, the contact portion between the eccentric shaft 4a and the slider 16, the contact portion between the main bearing 12 and the sleeve 17, And the contact part of the sleeve 17 and the main axis | shaft 4, etc. are mentioned. The refrigeration oil supplied to each sliding portion returns to the oil reservoir 23 again by gravity.
When energization of the stator 2 is stopped, the scroll compressor 100 stops its operation.

<Details of Main Shaft 4 and Rotor 3 of Scroll Compressor 100>
FIG. 2 is a configuration diagram extracting and enlarging the main shaft 4, the rotor 3 and the sub frame 20 of the scroll compressor 100. FIG. 3 is a plan view of the electromagnetic steel plate 38 which constitutes the rotor 3 of the scroll compressor 100. As shown in FIG. The main shaft 4 and the rotor 3 of the scroll compressor 100 will be described in detail based on FIGS. 2 and 3.

As described above, the main shaft 4 has the eccentric shaft 4a at the top. And, a slider balancer 37 is attached to the eccentric shaft 4a. The slider balancer 37 generates a centrifugal force in the direction opposite to the eccentric direction of the eccentric shaft 4 a. The slider 16 is rotatably fitted to the rocking bearing 13 of the rocking scroll 10. Therefore, a slide bearing structure is formed by the inner peripheral surface of the rocking bearing 13 and the outer peripheral surface of the slider 16. The supply of refrigeration oil to the slide bearing structure supports the transmission of force of the swing scroll 10 and the slider balancer 37 by the slide bearing structure.

The rotor 3 has a structure in which a plurality of electromagnetic steel plates 38 as shown in FIG. 3 are stacked. In the magnetic steel plate 38, a punching portion 39, a spindle insertion portion 42, a magnet insertion portion 47, and a slit 48 are formed to penetrate. The punched portion 39 may be formed so as to penetrate the first weight adjusting portion 34 and the second weight adjusting portion 35 at the position where the insertion is desired. Then, the first weight adjusting unit 34 and the second weight adjusting unit 35 are inserted into the inside of the rotor 3 through the punching unit 39.

The first weight adjusting unit 34 and the second weight adjusting unit 35 offset the centrifugal force Fc generated in the eccentric shaft 4 a. Therefore, the first weight adjusting unit 34 and the second weight adjusting unit 35 are set to a weight that produces a centrifugal force that can offset the centrifugal force Fc generated in the eccentric shaft 4a. The first weight adjusting unit 34 and the second weight adjusting unit 35 are formed using a material having a higher specific gravity than the electromagnetic steel plate 38. As materials for forming the first weight adjusting portion 34 and the second weight adjusting portion 35, an alloy such as zinc, lead, copper or brass can be considered. In addition, the first weight adjusting unit 34 and the second weight adjusting unit 35 may be magnetic members.
The first weight adjusting unit 34 and the second weight adjusting unit 35 may be formed so as to have a specific gravity different from that of the electromagnetic steel plate 38. The first weight adjusting unit 34 and the second weight adjusting unit 35 may be formed of a material having a specific gravity lower than that of the electromagnetic steel plate 38, or may be formed of an air gap.

Further, by laminating a plurality of electromagnetic steel plates 38 in which the punched portions 39 are formed, it is possible to form a space inside the rotor 3. The first weight adjusting portion 34 and the second weight adjusting portion 35 are inserted into the space formed by the punching portion 39. Then, the upper end surface and the lower end surface of the first weight adjusting unit 34 and the upper end surface and the lower end surface of the second weight adjusting unit 35 are fixed, and the movement of the first weight adjusting unit 34 and the second weight adjusting unit 35 is restricted. Do. The upper end surfaces of the first weight adjusting unit 34 and the second weight adjusting unit 35 are the end surfaces on the side of the compression unit 50, and the lower end surfaces of the first weight adjusting unit 34 and the second weight adjusting unit 35 are sub The end face on the frame 20 side.
The slider balancer 37 is fixed to the eccentric shaft 4 a by shrink fitting or press fitting.
The rotor 3 is fixed to the main shaft 4 by shrink fitting or press fitting.

Next, the centrifugal force during operation of the scroll compressor 100 will be described.
As shown in FIG. 2, during operation of the scroll compressor 100, centrifugal force Fc, centrifugal force Fb, centrifugal force F3, and centrifugal force F4 act on the main shaft 4. The centrifugal force Fc and the centrifugal force Fb are generated by the rocking motion of the rocking scroll 10. The centrifugal force F3 is generated due to the mass unbalance of the first weight adjusting unit 34 during the swinging motion of the swinging scroll 10. The centrifugal force F4 is generated due to the mass unbalance of the second weight adjusting unit 35 during the swinging motion of the swinging scroll 10.

Here, when the centrifugal force F is based on the central axis of the spindle 4,
It can be expressed by F = mrω ^2.
m is the weight [kg] of each part, r is the distance [m] from the center of the main shaft 4 to the position of the center of gravity of each part, and ω is the angular velocity [rad / s].

Since the slider balancer 37 and the rotor 3 are integrated with the main shaft 4, the angular velocities ω all have the same value. Therefore, in the scroll compressor 100, the centrifugal force Fc and the rotation of the main shaft 4 by the centrifugal force Fc are adjusted by adjusting the mass imbalance amount of the slider balancer 37, the first weight adjusting unit 34, and the second weight adjusting unit 35. The moments of the direction and the axial longitudinal direction of the main shaft 4 are offset.

The moment is the product of the strength of the centrifugal force and the distance from the ball bearing 21 supporting the main shaft 4. Therefore, as the strength of the centrifugal force increases or the distance from the ball bearing 21 increases, the influence on the moment increases.
The mass imbalance amount is determined by the weight of each part and the position of the center of gravity of each part.

The effects of the scroll compressor 100 will be described.
In the scroll compressor 100, the first weight adjusting unit 34 and the second weight adjusting unit 35 are inserted into the rotor 3, and the centrifugal force F3 is generated by mass imbalance by the first weight adjusting unit 34, and the second weight adjustment is performed. It is equipped with the structure which generates the centrifugal force F4 by the mass imbalance by the part 35. FIG. Therefore, according to the scroll compressor 100, even if the balancer is not provided, the same function and the same effect as those of the scroll compressor provided with the conventional balancer can be obtained.

Thereby, in the scroll compressor 100, the first balancer and the second conventionally required by using the centrifugal force of the first weight adjusting unit 34 and the second weight adjusting unit 35 to offset the centrifugal force Fc. It can be substituted for the centrifugal force of the balancer. Therefore, according to the scroll compressor 100, the first balancer and the second balancer can be eliminated, and the process of shrink fitting or press fitting, which is necessary when attaching the first balancer and the second balancer, can be omitted. it can.

Further, since the scroll compressor 100 is not provided with the first balancer and the second balancer, the stirring of the refrigerant and the refrigerator oil in the container 1 which is generated by the rotation of the first balancer and the second balancer during operation is also eliminated. Can. Therefore, according to the scroll compressor 100, the improvement of the oil increase can be expected, and the balancer cover attached to prevent the oil increase due to the stirring can be eliminated.

Further, the scroll compressor 100 can form the punched portion 39 simultaneously with the pressing of the electromagnetic steel plate 38, that is, the formation of the spindle insertion portion 42, the magnet insertion portion 47, and the slit 48. Therefore, according to the scroll compressor 100, the punching portion 39 can be formed with high accuracy without increasing the number of processing steps. That is, in the scroll compressor 100, the shape and the formation position of the punching portion 39 can be processed with high accuracy without increasing the processing cost.

The first weight adjusting portion 34 is inserted above the center of the rotor 3 in the height direction, and the second weight adjusting portion 35 is inserted below the center of the rotor 3 in the height direction. As a result, during operation, the centrifugal force Fc, the centrifugal force F3 generated in the opposite direction to the centrifugal force Fc, and the centrifugal force F4 in the same direction as the centrifugal force Fc act on the main shaft 4. Therefore, according to the scroll compressor 100, the generation position of the centrifugal force F3 generated by the first weight adjusting unit 34 and the centrifugal force F4 generated by the second weight adjusting unit 35 can be adjusted by the distance from the ball bearing 21. , It will be easier to balance the moment.

In addition, the first weight adjusting unit 34 is inserted in a direction opposite to the centrifugal force Fc, that is, in the direction opposite to the centrifugal force, and the second weight adjusting unit 35 is directed to the centrifugal force Fc. It is inserted below. Thereby, the centrifugal force F3 generated by the first weight adjusting unit 34 acts in the opposite direction to the centrifugal force Fc, and the centrifugal force F4 generated by the second weight adjusting unit 35 acts in the same direction as the centrifugal force Fc.

In addition, with respect to the distance from the ball bearing 21, the first weight adjusting unit 34 moves away and the second weight adjusting unit 35 approaches. Therefore, in consideration of the balance, the centrifugal force can be made smaller than the moment required to offset the moment due to the centrifugal force Fc. As a result, in the scroll compressor 100, the weight of the first weight adjusting unit 34 and the second weight adjusting unit 35 can be made smaller than the weight of the first balancer and the second balancer, and implementation at lower cost is possible. It becomes.

Second Embodiment
FIG. 4 is a structural view extracting and enlarging a main shaft 4, a rotor 3 and a sub frame 20 of a scroll compressor according to Embodiment 2 of the present invention. FIG. 5 is a plan view of an electromagnetic steel sheet 38 constituting the rotor 3 of the scroll compressor according to Embodiment 2 of the present invention. A main shaft 4 and a rotor 3 of a scroll compressor according to a second embodiment of the present invention will be described in detail based on FIGS. 4 and 5. In FIG. 5, a state in which the weight adjustment unit 36 is inserted into the punching unit 39 and the magnet 40 is inserted into the magnet insertion unit 47 is illustrated.
In the second embodiment, differences from the first embodiment will be mainly described, and the same parts as the first embodiment will be assigned the same reference numerals and descriptions thereof will be omitted.

The scroll compressor according to the second embodiment is different from the scroll compressor 100 according to the first embodiment in that the rotor attachment portion 41 of the main shaft 4 is eccentric in the anti-centrifugal direction of the centrifugal force Fc. . Further, in the scroll compressor according to the second embodiment, the scroll according to the first embodiment is that the main shaft insertion portion 42 of the magnetic steel plate 38 is eccentric from the central axis 43 of the main shaft 4 by the same amount as the rotor attachment portion 41. It differs from the compressor 100. Furthermore, the scroll compressor according to the second embodiment is different from the scroll compressor 100 according to the first embodiment in that the first weight adjusting unit 34 is not inserted into the rotor 3.

As described in the first embodiment, the main shaft 4 has the eccentric shaft 4a at the top. And, a slider balancer 37 is attached to the eccentric shaft 4a. The slider 16 is rotatably fitted to the rocking bearing 13 of the rocking scroll 10. Therefore, a slide bearing structure is formed by the inner peripheral surface of the rocking bearing 13 and the outer peripheral surface of the slider 16. The supply of refrigeration oil to the slide bearing structure supports the transmission of force of the swing scroll 10 and the slider balancer 37 by the slide bearing structure.

The main shaft 4 is formed using a material having a specific gravity higher than that of the electromagnetic steel plate 38 constituting the rotor 3. The rotor attachment portion 41 where the rotor 3 of the main shaft 4 is attached is decentered in the anti-centrifugal direction of the centrifugal force Fc generated on the eccentric shaft portion 4a.
Further, as shown in FIGS. 4 and 5, the main shaft insertion portion 42 of the magnetic steel plate 38 is also eccentric from the central axis 43 of the main shaft 4 by the same amount as the rotor attachment portion 41.
Furthermore, inside the rotor 3 is inserted a weight adjusting portion 36 made of a material having a higher specific gravity than the main shaft 4 in the direction of centrifugal force with respect to the centrifugal force Fc.
The weight adjusting unit 36 corresponds to the second weight adjusting unit 35 described in the first embodiment.

The rotor 3 has a structure in which a plurality of electromagnetic steel plates 38 as shown in FIG. 5 are stacked. In the magnetic steel plate 38, a punching portion 39, a spindle insertion portion 42, a magnet insertion portion 47, and a slit 48 are formed to penetrate. The punched portion 39 may be formed so as to penetrate the weight adjustment portion 36 at the position where it is desired to be inserted. Then, the weight adjusting unit 36 is inserted into the inside of the rotor 3 through the punching unit 39.

By laminating a plurality of electromagnetic steel plates 38 in which the punched portion 39 is formed, it is possible to form a space inside the rotor 3. That is, the weight adjusting portion 36 is inserted into the space formed by the punching portion 39. Then, the upper end surface and the lower end surface of the weight adjusting unit 36 are fixed, and the movement of the weight adjusting unit 36 is restricted. The upper end surface of the weight adjusting unit 36 is an end surface on the side of the compression unit 50, and the lower end surface of the weight adjusting unit 36 is an end surface on the sub frame 20 side.

Next, the centrifugal force during operation of the scroll compressor according to the second embodiment will be described.
As shown in FIGS. 4 and 5, in the scroll compressor according to the second embodiment, the rotor attachment portion 41 and the spindle insertion portion 42 are offset from the central axis 43 of the spindle 4. Thus, in the scroll compressor according to the second embodiment, when the rotor 3 rotates about the central axis 43 of the main shaft 4, the centrifugal force Fc generated in the eccentric shaft 4a due to the specific gravity difference with the electromagnetic steel plate 38. A centrifugal force F5 is generated due to mass imbalance in the direction of the anti-centrifugal force.

Therefore, during operation of the scroll compressor according to the second embodiment, centrifugal force Fc, centrifugal force Fb, centrifugal force F4, and centrifugal force F5 act on the main shaft 4.
The centrifugal force F5 is generated due to the mass unbalance of the rotor attachment portion 41 when the oscillating scroll 10 oscillates.

Thus, in the scroll compressor according to the second embodiment, the centrifugal force Fc, the centrifugal force Fb, the centrifugal force F4, and the centrifugal force F5 are offset each other to rotate the main shaft 4 by the centrifugal force Fc and the centrifugal force Fc. Balanced with the moment as well as the direction and axial longitudinal direction.

The effect of the scroll compressor according to the second embodiment will be described.
In the first embodiment, in order to offset the centrifugal force Fc, it is necessary to prepare the first weight adjusting unit 34 and the second weight adjusting unit 35 inside the rotor 3. On the other hand, in the scroll compressor according to the second embodiment, the centrifugal force F3 generated in the first weight adjusting unit 34 can be substituted by the centrifugal force F5 due to the mass imbalance of the rotor attachment unit 41. Therefore, according to the scroll compressor according to the second embodiment, the first weight adjusting unit 34 is not necessary, and one weight adjusting unit 36 may be inserted into the rotor 3.

Further, in the scroll compressor according to the second embodiment, the insertion position of the main shaft 4 is made eccentric from the central axis 43 in the anti-centrifugal force direction, thereby expanding the range in which the weight adjusting portion 36 can be inserted. It is easy to do. Therefore, according to the scroll compressor according to the second embodiment, the balance between the centrifugal force and the moment can be easily obtained.

Third Embodiment
FIG. 6 is a plan view of an electromagnetic steel sheet 38 constituting a rotor 3 of a scroll compressor according to Embodiment 3 of the present invention. A main shaft 4 and a rotor 3 of a scroll compressor according to a third embodiment of the present invention will be described in detail based on FIG. In FIG. 6, the second weight adjusting portion 35 is inserted into the punching portion 39, and the magnet 40 is inserted into the magnet insertion portion 47.
In the third embodiment, differences from the first embodiment and the second embodiment will be mainly described, and the same parts as the first embodiment and the second embodiment will be assigned the same reference numerals and descriptions thereof will be omitted. It shall be.

In the first embodiment and the second embodiment, although the specific properties of the first weight adjusting unit 34 and the second weight adjusting unit 35 are not mentioned, in the third embodiment, the first weight adjusting unit 34 and the second weight adjusting unit 35 are described. The second weight adjusting unit 35 is formed of a material that is a magnetic body. The first weight adjusting unit 34 and the second weight adjusting unit 35 may be magnetic members, and the material is not particularly limited.

The effects of the scroll compressor according to the third embodiment will be described.
Inside the rotor 3, a magnetic field is formed by the magnet 40, and from the magnet 40, magnetic lines of force are generated that return from the N pole and return to the S pole. If the amount of magnetic field lines returning to the S pole of the magnet 40 changes, it will affect the performance of the scroll compressor and so on.

Here, when the first weight adjusting portion 34 and the second weight adjusting portion 35 of nonmagnetic material are inserted into the rotor 3, magnetic lines of force can not pass through the first weight adjusting portion 34 and the second weight adjusting portion 35. Therefore, it is necessary to keep the formation position of the punching portion 39 away from the magnet 40 so that the magnetic lines of force do not change.
On the other hand, when inserting the 1st weight adjustment part 34 and the 2nd weight adjustment part 35 of a magnetic body into the inside of rotor 3, a line of magnetic force can pass the 1st weight adjustment part 34 and the 2nd weight adjustment part 35 become. Therefore, according to the scroll compressor according to the third embodiment, the formation position of the punching portion 39 can be determined without considering the position of the magnet 40.

Reference Signs List 1 container, 1a intermediate container, 1b lower container, 1c upper container, 2 stator, 3 rotor, 4 main shaft, 4a eccentric shaft, 4b pump shaft, 4c oil hole, 9 fixed scroll, 9a wrap, 9b discharge port, DESCRIPTION OF SYMBOLS 10 rocking scroll, 10a lap part, 11 frame, 12 main bearing, 13 rocking bearing, 14 thrust plate, 15 oldham ring, 16 slider, 17 sleeve, 20 sub frame, 20a bearing storage part, 21 ball bearing, 22 oil Pumps, 23 oil reservoirs, 24 suction pipes, 25 discharge pipes, 26 compression chambers, 27 seals, 28 seals, 29 discharge valves, 33 discharge spaces, 34 first weight adjusting section, 35 second weight adjusting section, 36 weight adjusting section , 37 slider balancer, 38 electrical steel plate, 39 Chipping part, 40 magnets, 41 rotor mounting parts, 42 spindle insertion parts, 43 central axes, 47 magnet insertion parts, 48 slits, 50 compression parts, 60 electric mechanism parts, 100 scroll compressor, F centrifugal force, F1 centrifugal force , F2 centrifugal force, F3 centrifugal force, F4 centrifugal force, F5 centrifugal force, Fb centrifugal force, Fc centrifugal force, ω angular velocity.

Claims

A container,
A fixed scroll provided in the container;
An oscillating scroll provided in the container and combined with the fixed scroll;
A main shaft provided in the container for oscillating movement of the oscillating scroll;
A rotor provided in the container for rotating the main shaft;
A stator provided in the container for rotating the rotor;
A rocking bearing provided on the rocking scroll and into which the eccentric shaft portion of the main shaft is inserted;
A slider fitted to the rocking bearing and supporting the rocking scroll;
And a slider balancer that is provided on the eccentric shaft and generates a centrifugal force in a direction opposite to the eccentric direction of the eccentric shaft.
A scroll compressor is provided with a weight adjustment unit that offsets the centrifugal force generated in the eccentric shaft inside the rotor.
The weight adjusting unit is
The scroll compressor according to claim 1, wherein the scroll compressor is made of a material having a specific gravity higher than that of a magnetic steel sheet constituting the rotor.
The weight adjusting unit is
A first weight adjusting unit provided on the upper side with respect to the center in the height direction of the rotor;
The scroll compressor according to claim 1, further comprising: a second weight adjusting unit provided on the lower side with respect to the center in the height direction of the rotor.
The first weight adjusting unit is
Provided at a position where a centrifugal force acts in a direction opposite to the centrifugal force of the eccentric shaft portion,
The second weight adjusting unit is
The scroll compressor according to claim 3, wherein centrifugal force acts in the same direction as the centrifugal force of the eccentric shaft portion.
The weight adjusting unit is
Provided at a position where a centrifugal force acts in the same direction as the centrifugal force of the eccentric shaft portion,
The scroll compressor according to claim 1 or 2, wherein the rotor attachment portion of the main shaft and the main shaft insertion portion of the rotor are eccentric with respect to the central axis of the main shaft to offset centrifugal force generated in the eccentric shaft portion. .
The scroll compressor according to claim 5, wherein the rotor mounting portion is eccentric in a direction opposite to a centrifugal force of the eccentric shaft portion.
The main spindle is
The scroll compressor according to claim 5 or 6, wherein the scroll compressor is formed of a material having a specific gravity higher than that of the electromagnetic steel plates constituting the rotor.
The weight adjusting unit is
The scroll compressor according to any one of claims 5 to 7, wherein the scroll compressor is formed of a material having a higher specific gravity than that of the main shaft.
The scroll compressor according to any one of claims 1 to 8, wherein the weight adjusting unit is made of a magnetic material.