JP6257765B2 - Scroll compressor and manufacturing method thereof - Google Patents

Description

  The present invention relates to a scroll compressor and a method for manufacturing the same, and more particularly to a balancer structure.

2. Description of the Related Art Conventionally, two or more balancers are attached to a main shaft of a scroll compressor in order to cancel out centrifugal force of an oscillating vortex that is eccentrically oscillated. In order to decenter the center of gravity, the balancer has a semicircular shape or a sector shape in plan view. Therefore, when the balancer rotates, the surrounding fluid is agitated, causing the following problems.
If the balancer is located at the bottom of the main bearing, the oil dripping from the main bearing will scatter in the form of mist due to the rotation of the balancer, and will be taken out together with the refrigerant to the compressor side. End up. Further, when the balancer is disposed in the frame above the main bearing, the balancer rotates in a space filled with oil, and thus power loss due to oil agitation occurs.

In order to solve the above problem, a scroll compressor that prevents the fluid from being stirred by a balancer has been proposed (for example, see Patent Document 1).
In Patent Document 1, the outer shape of the balancer is a circular cylinder in plan view, and by providing a cavity inside, the centrifugal force necessary to balance the centrifugal force of the oscillating swirl is secured, and the surrounding fluid To prevent stirring.

JP 2002-31070 A (see, for example, [0016] and FIG. 2)

  However, in Patent Document 1, since a cavity for decentering the center of gravity is provided inside the balancer, when the balancer is arranged in a space filled with oil, the oil enters the cavity. For this reason, the centrifugal force generated in the balancer has a deviation from the design value, which causes an increase in vibration.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a scroll compressor that can prevent an increase in vibration while preventing stirring of a fluid and a method for manufacturing the same. Yes.

The scroll compressor according to the present invention includes a fixed scroll having a spiral portion, a swing scroll having a spiral portion, which is combined with the spiral portion of the fixed scroll to form a compression chamber for compressing a refrigerant, and the swing swing A main shaft that transmits a driving force to the scroll, an electric motor unit that rotates the main shaft, and a first balancer that cancels an unbalance with respect to the rotation center of the main shaft of the orbiting scroll, and the first balancer The outer shape is cylindrical, and is composed of a high-density portion made of a high-density material and a low-density portion made of a low-density material having a density lower than that of the high-density material. The low density part is formed of a resin material .

  According to the scroll compressor according to the present invention, the outer shape of the balancer is cylindrical, so that stirring of the surrounding fluid can be prevented even if the balancer rotates. In addition, since there is no cavity for decentering the center of gravity inside the balancer, there is no deviation from the design value in the centrifugal force generated in the balancer, and an increase in vibration can be prevented.

It is a longitudinal cross-sectional view of the scroll compressor which concerns on Embodiment 1 of this invention. It is a figure which shows the low density part of the 1st balancer of the scroll compressor which concerns on Embodiment 1 of this invention. It is a figure which shows the assembly method of the 1st balancer of the scroll compressor which concerns on Embodiment 1 of this invention. It is an enlarged view near slider ASSY with a balancer of the scroll compressor concerning Embodiment 2 of the present invention. It is a figure which shows the slider ASSY with a balancer of the scroll compressor which concerns on Embodiment 2 of this invention. It is a figure explaining the rollover prevention of the slider ASSY with a balancer of the scroll compressor which concerns on Embodiment 2 of this invention. It is a longitudinal cross-sectional view of the scroll compressor which concerns on Embodiment 3 of this invention. It is a figure which shows the method of attaching the 2nd balancer of the scroll compressor which concerns on Embodiment 3 of this invention to a rotor. It is an enlarged view of the vicinity of the second balancer of the scroll compressor according to Embodiment 3 of the present invention. It is a longitudinal cross-sectional view of the scroll compressor which concerns on Embodiment 4 of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited to the embodiments described below. Moreover, in the following drawings, the relationship of the size of each component may be different from the actual one.

Embodiment 1 FIG.
First, the structure of the scroll compressor 100 according to the first embodiment will be described.
FIG. 1 is a longitudinal sectional view of a scroll compressor 100 according to Embodiment 1 of the present invention.
The scroll compressor 100 sucks the refrigerant circulating in the refrigeration cycle, compresses it, and discharges it as a high-temperature and high-pressure state. As shown in FIG. 1, the scroll compressor 100 includes a compression mechanism portion and an electric motor portion in a shell, and the compression mechanism portion is disposed above and the electric motor portion is disposed below.

The shell includes a cylindrical middle shell 25, a lower shell 26 that is sealed to the lower surface opening of the middle shell 25 by welding or the like, and an upper shell 24 that is sealed to the upper surface opening of the middle shell 25 by welding or the like. A pressure vessel constructed.
The middle shell 25 forms a part of the refrigerant circuit and is connected to a suction pipe 7 for taking the refrigerant into the shell. The frame 6 is fixed to the inner periphery of the upper end portion, and the stator 11 is fixed to the inner periphery of the intermediate portion. ing. The bottom of the lower shell 26 constitutes an oil reservoir 18 that stores oil that lubricates each bearing. An oil drain pipe 8 is connected to the bottom surface of the frame 6 to return the oil staying in the frame 6 to the oil reservoir 18. Connected to the upper shell 24 is a discharge pipe 1 for discharging compressed refrigerant from the shell to the refrigerant circuit.

The compression mechanism section includes a fixed scroll 4 having a spiral portion 4 a on one surface, a swing scroll 5 having a spiral portion 5 a having a reverse winding direction to the fixed scroll 4 on one surface, and a reverse of the swing scroll 5. A rocking bearing 21 provided on the compression chamber side and swingably supported by the eccentric slider shaft portion 14a, a frame 6 having a fixed scroll 4 fixedly disposed and having a main bearing 19 in the center, and fixed to the outer periphery. The rotor 12 includes at least a main shaft 14 that transmits a driving force to the orbiting scroll 5, and is connected to the electric motor unit to compress the refrigerant.
Here, the eccentric slider shaft portion 14 a is a slider mounting shaft installed on the upper portion of the main shaft 14 so that the slider 22 is eccentric with respect to the main shaft 14.

  Between the fixed scroll 4 and the orbiting scroll 5, the spiral portions 4a and 5a are combined with each other to form a plurality of compression chambers (not shown). Further, in order to reduce refrigerant leakage from the front end surfaces of the spiral portion 4 a of the fixed scroll 4 and the spiral portion 5 a of the swing scroll 5, the front end surface of the spiral portion 4 a of the fixed scroll 4 and the spiral portion 5 a of the swing scroll 5. Seals (not shown) are respectively disposed on the front end surfaces of.

  A discharge port 28 for discharging the compressed and high-pressure refrigerant gas is formed at the center of the fixed scroll 4. The compressed refrigerant gas having a high pressure is discharged to a high pressure portion (not shown) in the upper shell 24. The refrigerant gas discharged to the high pressure part is discharged to the refrigeration cycle via the discharge pipe 1. In addition, the discharge port 28 is provided with a discharge valve 29 that prevents the refrigerant from flowing backward from the high-pressure portion to the discharge port 28 side.

  The electric motor part is composed of a rotor 12 fixed to the main shaft 14 and a stator 11 fixed to the middle shell 25, and is driven by energization of the stator 11 to rotate the main shaft 14, and further rotate the main shaft 14 Accordingly, the swing scroll 5 is swung.

  In addition, the scroll compressor 100 swings on the frame 6 in order to prevent the rotation of the swing scroll 5 and to provide a swing motion, and a thrust plate 30 serving as a thrust bearing for supporting the swing scroll 5 in the axial direction. An Oldham joint 23 that is freely supported, a slider 22 that supports the orbiting scroll 5 to revolve the orbiting scroll 5, and the main bearing 19 and main shaft 14 of the frame 6 in the vicinity of the eccentric slider shaft portion 14a. The first balancer 27 and the second balancer 13 for canceling out the unbalance with respect to the rotation center of the main shaft 14 of the orbiting scroll 5 that performs the orbiting movement by the eccentric slider shaft portion 14a. And. The first balancer 27 is provided above the electric motor part, and the second balancer 13 is provided below the electric motor part.

  The main shaft 14 rotates with the rotation of the rotor 12 to revolve the orbiting scroll 5. The upper portion of the main shaft 14 is supported by a main bearing 19 formed on the frame 6. On the other hand, the lower portion of the main shaft 14 is rotatably supported by a sub bearing 16 formed at the center of a sub frame 15 provided at the lower portion of the shell. The sub-bearing 16 is press-fitted and fixed in a bearing housing portion whose outer ring is formed at the center of the sub-frame 15.

The subframe 15 is provided with a positive displacement oil pump 17 for pumping oil from an oil reservoir 18 at the bottom of the shell and supplying the oil to each sliding portion, and a pump shaft that transmits rotational force to the oil pump 17. The portion 14b is integrally formed with the main shaft 14.
In the main shaft 14, an oil supply vertical hole that penetrates in the vertical direction (axial direction) from the lower end of the pump shaft portion 14 b to the upper end of the eccentric slider shaft portion 14 a and supplies it to the sliding portion of the bearing or the compression mechanism portion. 14c is formed.

  The first balancer 27 includes a high density portion 10 and a low density portion 9 having a lower density than the high density portion 10, and is configured by attaching the high density portion 10 to the low density portion 9. The first balancer 27 has a cylindrical outer shape and does not agitate the surrounding fluid when rotating. A high density material such as a metal is used for the high density portion 10, and a low density material such as a resin material is used for the low density portion 9. By doing so, since the first balancer 27 has an eccentric center of gravity toward the high-density portion 10 side, it is possible to generate a centrifugal force necessary as a balancer. Further, the first balancer 27 is substantially solid and has a very small cavity so that the centrifugal force does not shift due to oil entering the inside.

Next, the operation of the scroll compressor 100 will be described.
In the scroll compressor 100 configured as described above, when power is supplied to the stator 11, the rotor 12 is rotated by the rotational force from the rotating magnetic field generated by the stator 11, and the main shaft 14 is rotated by the rotation of the rotor 12. Is rotated.

  When the main shaft 14 rotates, the eccentric slider shaft portion 14 a rotates in the rocking bearing 21 via the slider 22 and transmits a driving force to the rocking scroll 5. At this time, an Oldham groove (not shown) of the orbiting scroll 5 that accommodates a key portion (not shown) formed on one surface of the Oldham joint 23 and a key formed on the other surface of the Oldham joint 23. The oscillating scroll 5 performs oscillating motion while its rotation is suppressed by the Oldham groove (not shown) of the frame 6 that accommodates the portion (not shown) and the Oldham coupling 23 that reciprocates inside the frame. Although the frame 6 and the sub frame 15 are fixed in the shell, the main shaft 19 and the sub bearing 16 are misaligned due to variations in accuracy during fixing and variations in accuracy of individual components. Further, the deflection of the main shaft 14 is also added, and the main bearing 19 and the main shaft 14 and the auxiliary bearing 16 and the main shaft 14 are not necessarily parallel.

  Here, the sleeve 20 is accommodated between the main shaft 14 and the main bearing 19 in order to make the sliding surfaces in the main bearing 19 parallel. When the axial misalignment between the main bearing 19 and the sub bearing 16 occurs, the main shaft 14 is inclined with respect to the main bearing 19, but the piped portion (not shown) of the main shaft 14 contacts the inner peripheral surface of the sleeve 20. The piped portion absorbs the inclination of the main shaft 14. As a result, the outer periphery of the sleeve 20 can always slide with the main bearing 19 in parallel.

  When the swing scroll 5 swings, centrifugal force is generated in the swing scroll 5, and the eccentric slider shaft portion 14a of the main shaft 14 slides within a slidable range within a slide surface (not shown) in the slider 22. To do. The spiral portion 5a of the orbiting scroll 5 and the spiral portion 4a of the fixed scroll 4 come into contact with each other to form a compression chamber. The centrifugal force of the orbiting scroll 5 and the radial load generated to compress the refrigerant act on the eccentric slider shaft portion 14a of the main shaft 14, and the eccentric slider shaft portion 14a bends, whereby the eccentric slider shaft portion 14a is The inner surface of the rocking bearing 21 provided at the center of the lower surface of the rocking scroll 5 is not necessarily parallel to the inner surface.

  Here, a slider 22 is accommodated between the eccentric slider shaft portion 14 a of the main shaft 14 and the swing bearing 21 in order to make the sliding surface in the swing bearing 21 parallel. Therefore, when the eccentric slider shaft portion 14a is bent, the eccentric slider shaft portion 14a of the main shaft 14 is inclined with respect to the swing bearing 21, but the piped portion (not shown) of the eccentric slider shaft portion 14a is the slider of the slider 22. The piped part absorbs the inclination of the main shaft 14 in contact with the surface. Thereby, the outer periphery of the slider 22 can always slide in parallel with the rocking bearing 21.

  The refrigerant in the refrigerant circuit is sucked into the shell from the suction pipe 7, and is formed by a spiral portion 5 a of the swing scroll 5 and a spiral portion 4 a of the fixed scroll 4 from a suction port (not shown) of the frame 6. to go into. The compression chamber is moved to the center of the orbiting scroll 5 by the orbiting motion of the orbiting scroll 5, and the refrigerant is compressed by further reducing the volume. At this time, a load is applied to the fixed scroll 4 and the orbiting scroll 5 by the compressed refrigerant so that the fixed scroll 4 and the orbiting scroll 5 are separated from each other. The orbiting scroll 5 is loaded by a bearing constituted by the orbiting bearing 21 and the thrust plate 30. Is supported. The compressed refrigerant passes through the discharge port 28 of the fixed scroll 4, pushes open the discharge valve 29, passes through the high pressure portion in the upper shell 24, and is discharged from the shell to the refrigerant circuit through the discharge pipe 1.

  In the series of operations as described above, the oil pump 17 is driven by the pump shaft portion 14b of the rotating main shaft 14, and the oil is pumped up from the oil reservoir 18 at the bottom of the shell through the oil supply vertical hole 14c. The pumped-up oil is supplied to the main bearing 19, the sub bearing 16, and the rocking bearing 21, respectively. Then, the oil that has lubricated the main bearing 19 and the sub-bearing 16 hangs down and returns to the oil reservoir 18 at the bottom of the shell. The oil that has lubricated the rocking bearing 21 is stored in the frame inner space 6a. The oil in the space 6a in the frame is used for oil supply to the thrust bearing, oil supply to the Oldham joint 23, oil supply to the spiral portions 4a and 5a, oil supply to the main bearing 19, and the cooling bearing 21 and cooling of the main bearing 19. Fulfill. An oil drain pipe 8 is provided in the frame inner space 6 a, and excess oil is returned from the frame inner space 6 a to the oil reservoir 18 at the bottom of the shell through the oil drain pipe 8.

Next, the first balancer 27 according to the first embodiment will be described.
FIG. 2 is a diagram showing the low density portion 9 of the first balancer 27 of the scroll compressor 100 according to Embodiment 1 of the present invention. 2A is a plan view of the low density portion 9 of the first balancer 27, and FIG. 2B is a cross-sectional view taken along the line AA in FIG. 2A.
The low-density portion 9 of the first balancer 27 is composed of a low-density main portion 9c and a cover portion 9d. Further, the shaft balance hole 9a for passing the main shaft 14 and the high-density portion 10 are stored. A high density portion storage hole 9b and a low density fastening hole 9e for fastening with the high density portion 10 are formed. The outer shape of the low density portion 9 is cylindrical, and has a shape obtained by hollowing out a through hole 9a, a high density portion storage hole 9b, and a low density fastening hole 9e from a column.

FIG. 3 is a diagram showing an assembling method of the first balancer 27 of the scroll compressor 100 according to Embodiment 1 of the present invention. 3A shows the first balancer 27 before assembly, and FIG. 3B shows the first balancer 27 after assembly.
The high-density portion 10 of the first balancer 27 is formed with a high-density fastening hole 10a for fastening with the low-density portion 9, and the position of the high-density fastening hole 10a is low-density fastening of the low-density portion 9. The high-density part 10 is fitted into the high-density part storage hole 9b of the low-density part 9 so as to match the hole 9e. At this time, if the clearance between the high density portion 10 and the high density portion storage hole 9b of the low density portion 9 is 1 mm or less so that the positional relationship between the high density portion 10 and the low density portion 9 is uniquely determined without large variation. Good. After the fitting, the low density portion 9 and the high density portion 10 are fastened to the low density fastening hole 9e and the high density fastening hole 10a using the first fastening member 2 such as a bolt or a rivet.

  Further, since the low density portion 9 supports the high density portion 10 by the frictional force of the fastening surface between the cover portion 9d of the low density portion 9 and the high density portion 10, the centrifugal force generated when the first balancer 27 rotates. Prevents the two from shifting. Therefore, it is possible to prevent oil from entering the first balancer 27 and to prevent the centrifugal force from shifting.

  As described above, according to the first balancer 27 according to the first embodiment, since the outer shape is cylindrical, stirring of the surrounding fluid can be prevented even if it rotates. Moreover, by comprising the low density part 9 and the high density part 10, it can have an eccentric gravity center in the high density part 10 side, and can generate the centrifugal force required as a balancer. Further, the first balancer 27 is substantially solid and has a small cavity, so that the centrifugal force is not shifted due to oil entering the inside. Therefore, the design value does not deviate from the centrifugal force generated in the balancer, and an increase in vibration can be prevented.

Embodiment 2. FIG.
Hereinafter, although Embodiment 2 will be described, the same elements as those in Embodiment 1 are omitted, and the same or corresponding parts as those in Embodiment 1 are denoted by the same reference numerals.
4 is an enlarged view of the vicinity of the slider ASSY 40 with a balancer of the scroll compressor 100 according to Embodiment 2 of the present invention, and FIG. 5 shows the slider ASSY 40 with a balancer of the scroll compressor 100 according to Embodiment 2 of the present invention. FIG. 5A is a side view of the slider ASSY 40 with a balancer, and FIG. 5B is a cross-sectional view taken along line BB in FIG. 5A.

  In the second embodiment, a slider ASSY 40 with a balancer is provided in the compression mechanism. The balancer-equipped slider ASSY 40 includes a balancer-equipped slider 40a having a high-density balancer 40f attached to the slider 40d, and a low-density portion 40b attached to the balancer-equipped slider 40a. Since the space in which the slider 40a with balancer rotates is filled with oil, the oil agitation loss can be reduced by attaching the low density portion 40b to the slider 40a with balancer.

  As shown in FIG. 5, the slider ASSY 40 with a balancer is provided with a low density portion 40b so as to cover the high density balancer 40f. The slider 40a with a balancer is provided with a gap 40c for oil draining of about 0.5 mm to 3 mm in order to drain the oil that has flowed out from below the rocking bearing 21. By providing the oil drain gap 40c near the lower end of the rocking bearing 21, oil can be efficiently drained in the shortest flow path. Further, an eccentric slider fitting hole 40e for fitting the eccentric slider shaft portion 14a is provided at the center of the balancer-equipped slider ASSY40.

FIG. 6 is a diagram illustrating prevention of rollover of the slider ASSY 40 with balancer of the scroll compressor 100 according to Embodiment 2 of the present invention.
When a parallel slide bearing is used as the rocking bearing 21, the central point of action of the rocking bearing reaction force exists at the center height of the rocking bearing 21. When the height of the centrifugal force acting center point of the slider ASSY 40 with balancer is made to coincide with the center height of the rocking bearing, the centrifugal force (arrow α41) and the rocking bearing reaction force (arrow β42) act at the same height. Therefore, it is possible to prevent a moment from overturning from occurring in the slider ASSY 40 with balancer. As a result, it is possible to prevent the rocking bearing 21 from coming into contact with each other, and the reliability of the rocking bearing 21 is ensured. Further, when the slider 40a with a balancer is covered with a hollow cover, there is a problem that a moment to try to roll over the slider 40a with a balancer is generated by the centrifugal force acting on the oil that has entered the cover. So this problem does not occur.

Embodiment 3 FIG.
Hereinafter, although Embodiment 3 will be described, the same elements as those in Embodiment 1 are omitted, and the same or corresponding parts as those in Embodiment 1 are denoted by the same reference numerals.
FIG. 7 is a longitudinal sectional view of scroll compressor 100 according to Embodiment 3 of the present invention.
In the third embodiment, the second balancer 13 includes a high density portion 52 and a low density portion 51 having a density lower than that of the high density portion 52 as shown in FIG.
Even when the refrigerant stagnates and the second balancer 13 is operated in a state where it is immersed in a mixed liquid of liquid refrigerant and oil, since the oil and liquid refrigerant do not enter the second balancer 13, the centrifugal force of the second balancer 13 Deviation from the design value does not occur, and an increase in vibration can be prevented.

FIG. 8 is a diagram illustrating a method of attaching the second balancer 13 of the scroll compressor 100 according to Embodiment 3 of the present invention to the rotor 12. FIG. 8A is a plan view of the second balancer 13, and FIG. 8B is a side view of the second balancer 13.
A high-density fastening hole 52a is formed in the high-density portion 52 of the second balancer 13, and a low-density fastening hole 51a is formed in the low-density portion 51. The high-density portion 52, the low-density portion 51, Thus, a shaft through hole 50 is formed. Then, the second fastening member 3 such as a bolt or a rivet is passed through the high density fastening hole 52a and the low density fastening hole 51a, and the high density portion 52 and the low density portion 51 are caulked together with the rotor 12 to form the second balancer. 13 is attached to the rotor 12. By doing so, high productivity can be obtained.

FIG. 9 is an enlarged view of the vicinity of the second balancer 13 of the scroll compressor 100 according to Embodiment 3 of the present invention.
The second balancer 13 composed of the high density part 52 and the low density part 51 may be separated from the rotor 12 and provided at a position closer to the auxiliary bearing 16 than the rotor 12 as shown in FIG. In this case, even if the first balancer 27 and the second balancer 13 are further downsized, the centrifugal force of the orbiting scroll 5 can be offset. Further, when the position of the second balancer 13 is moved downward, the second balancer 13 is easily immersed in the oil. However, since the second balancer 13 is solid and has an outer shape cylindrical, the second balancer having a semi-cylindrical shape is used. Unlike the case where the oil is applied alone, the oil is not agitated and vibration does not increase.

Embodiment 4 FIG.
Hereinafter, although Embodiment 4 will be described, the same elements as those in Embodiment 1 are omitted, and the same or corresponding parts as those in Embodiment 1 are denoted by the same reference numerals.
FIG. 10 is a longitudinal sectional view of scroll compressor 100 according to Embodiment 4 of the present invention.
In the fourth embodiment, the first balancer 27 is provided below the main bearing 19 as shown in FIG. 10, and the first balancer 27 is provided above the main bearing 19 as shown in FIG. The position of the first balancer 27 is different from that of the first embodiment. However, the same effect as in the first embodiment can be obtained even in the position of the fourth embodiment.

  DESCRIPTION OF SYMBOLS 1 Discharge pipe, 2 First fastening member, 3 Second fastening member, 4 Fixed scroll, 4a Swirl part of (fixed scroll), 5 Swing scroll, 5a Swirl part of (scrolling scroll), 6 Frame, 6a Space in frame, 7 Suction pipe, 8 Oil drain pipe, 9 Low density part (of first balancer), 9a Shaft through hole 9b High density part storage hole, 9c Low density main part, 9d Cover part, 9e For low density fastening Hole, 10 High-density part, 10a High-density part fastening hole, 11 Stator, 12 Rotor, 13 Second balancer, 14 Main shaft, 14a Eccentric slider shaft part, 14b Pump shaft part, 14c Oil supply vertical hole, 15 Subframe, 16 Sub Bearing, 17 Oil pump, 18 Oil reservoir, 19 Main bearing, 20 Sleeve, 21 Swing bearing, 22 Slider, 23 Oldham coupling, 24 Upper shell, 2 Middle shell, 26 Lower shell, 27 First balancer, 28 Discharge port, 29 Discharge valve, 30 Thrust plate, 40 Slider assembly with balancer, 40a Slider with balancer, 40b Low density part, 40c Clearance for oil drainage, 40d Slider, 40e Eccentricity Slider fitting hole, 40f balancer, 50 shaft through hole, 41 arrow α, 42 arrow β, 51 low density portion (second balancer), 51a low density fastening hole, 52 high density portion (second balancer), 52a High density fastening hole, 100 scroll compressor.

Claims (10)

A fixed scroll having a spiral portion;
An orbiting scroll having a spiral portion and forming a compression chamber in combination with the spiral portion of the fixed scroll to compress the refrigerant;
A main shaft for transmitting driving force to the orbiting scroll;
An electric motor section for rotating the main shaft;
A first balancer for canceling an unbalance with respect to the rotation center of the main shaft of the orbiting scroll,
The first balancer has a cylindrical outer shape, and includes a high-density portion made of a high-density material and a low-density portion made of a low-density material having a lower density than the high-density material,
The low density part covers the outer peripheral surface of the high density part ,
The low-density portion is a scroll compressor formed of a resin material . A fixed scroll having a spiral portion;
An orbiting scroll having a spiral portion and forming a compression chamber in combination with the spiral portion of the fixed scroll to compress the refrigerant;
A main shaft for transmitting driving force to the orbiting scroll;
An electric motor section for rotating the main shaft;
A first balancer for canceling an unbalance with respect to the rotation center of the main shaft of the orbiting scroll,
The first balancer has a cylindrical outer shape, and includes a high-density portion made of a high-density material and a low-density portion made of a low-density material having a lower density than the high-density material,
The low density part covers the outer peripheral surface of the high density part,
A slider for supporting the orbiting scroll;
The first balancer is attached to the slider
Scroll compressor. The scroll compressor according to claim 2 , wherein the slider is provided with a gap for oil removal from which oil is released. A fixed scroll having a spiral portion;
An orbiting scroll having a spiral portion and forming a compression chamber in combination with the spiral portion of the fixed scroll to compress the refrigerant;
A main shaft for transmitting driving force to the orbiting scroll;
An electric motor section for rotating the main shaft;
A first balancer for canceling an unbalance with respect to the rotation center of the main shaft of the orbiting scroll,
The first balancer has a cylindrical outer shape, and includes a high-density portion made of a high-density material and a low-density portion made of a low-density material having a lower density than the high-density material,
The low density part covers the outer peripheral surface of the high density part,
The low-density portion of the first balancer includes a shaft through hole for passing the main shaft, a high-density portion storage hole for storing the high-density portion, and a low density for fastening with the high-density portion. A fastening hole is formed,
The high-density portion of the first balancer has a high-density fastening hole for fastening with the low-density portion,
The first balancer is
The positions of the high-density fastening holes and the low-density fastening holes are aligned, and the high-density portion is fitted into the high-density portion storage hole, and the high-density portion and the low-density are formed by a first fastening member. The part is concluded
Scroll compressor. Wherein the first balancer scroll compressor according to any one of claims 1 to 4 provided above the motor unit. A second balancer for canceling an unbalance with respect to the rotation center of the main shaft of the orbiting scroll is provided below the electric motor unit,
The second balancer outer shape is cylindrical, of claim 1 to 5, which is composed of a low-density portion comprising a high density portion and a low-density material which has lower density than the high density material made of high density material The scroll compressor as described in any one. A secondary bearing for supporting a lower portion of the main shaft;
The scroll compressor according to claim 6 , wherein the second balancer is provided at a position closer to the auxiliary bearing than the electric motor unit. The electric motor part is composed of a rotor and a stator,
A low density fastening hole for fastening with the rotor is formed in the low density portion of the second balancer,
A high-density fastening hole for fastening with the rotor is formed in the high-density portion of the first balancer,
The second balancer is
The scroll compressor according to claim 6 or 7 , wherein the high-density portion and the low-density portion are fastened to the rotor by a second fastening member. The first balancer is
The high-density portion is fitted into the high-density portion storage hole so that the positions of the high-density fastening hole and the low-density fastening hole are aligned. The method for manufacturing a scroll compressor according to claim 4 , wherein the scroll compressor is assembled by fastening the parts. The second balancer is
The method for manufacturing a scroll compressor according to claim 8 , wherein the high-density portion and the low-density portion are attached to the rotor by a second fastening member.

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