JP2011099377A - Refrigerant compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerant compressor which controls the interference at the operation of a balancer provided for a rotor bottom and a refrigerating machine oil, and suppresses performance deterioration by stirring loss of the refrigerating machine oil by the balancer. <P>SOLUTION: The balancer 5a has a shape that is obtained by roughly halving a thick-wall cylinder in a cylinder direction, wherein the top face and the bottom face are almost parallel to each other, and it satisfies θ1<θ2. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a refrigerant compressor used as one component of a refrigeration cycle employed in, for example, an air conditioner or a refrigeration apparatus.

  A general refrigerant compressor that has existed conventionally has an electric motor (electric element) composed of at least a rotor (rotor) and a stator (stator). This rotor is usually shrink-fitted to the main shaft and fixedly supported, and a balancer (balance weight) is attached to the bottom. This balancer is usually made of a brass material, has a predetermined height, and has a shape (hereinafter referred to as a semi-thick cylindrical shape) obtained by dividing a thick cylinder into approximately half in the cylindrical direction. . As such, “in a scroll compressor having a rotating shaft that is inserted into the rotor of the electric element and is driven to rotate integrally with the rotor, a vibration balance is established between the upper and lower sides of the rotor and the rotating shaft. A scroll type compressor provided with a balance weight is disclosed (for example, see Patent Document 1).

JP-A-64-8387 (FIG. 3 etc.)

  The balancer provided at the bottom of the rotor in the refrigerant compressor described in Patent Document 1 uses a brass material in terms of high density, workability, and cost, and the balancer shape is semi-thick. It has a cylindrical shape. During operation of such a refrigerant compressor, the refrigerating machine oil stored in the bottom of the compressor becomes a mortar-like oil surface shape by the rotation of the main shaft. If it does so, the balancer provided in the bottom part of the rotor will interfere with refrigerating machine oil, the stirring loss of refrigerating machine oil by a balancer will arise, and the performance fall of a refrigerant compressor will be caused.

  The present invention has been made to solve the above-described problems, and suppresses interference during operation between the balancer provided at the bottom of the rotor and the refrigerating machine oil, and suppresses performance degradation due to the refrigerating machine agitation loss caused by the balancer. It is an object of the present invention to provide a refrigerant compressor.

  A refrigerant compressor according to the present invention includes a hermetic container, a stator fixedly supported in the hermetic container, a rotor rotatably disposed on an inner peripheral surface side of the stator, and a central portion of the rotor A main shaft that rotates together with the rotor, a balancer that is attached to the bottom of the rotor and rotates together with the rotor, and a fixing member that fixes the balancer to the rotor, and the balancer is a thick cylinder Is divided into approximately half along the cylinder direction, and the upper surface and the lower surface are formed substantially parallel to each other, and the inner peripheral wall and the outer peripheral wall are inclined.

  A refrigerant compressor according to the present invention includes a hermetic container, a stator fixedly supported in the hermetic container, a rotor rotatably disposed on an inner peripheral surface side of the stator, and a central portion of the rotor A main shaft that rotates together with the rotor, a balancer that is attached to the bottom of the rotor and rotates together with the rotor, and a fixing member that fixes the balancer to the rotor. A thick cylinder formed by laminating thin plates has a shape divided into approximately half along the cylinder direction, and the upper surface and the lower surface are formed substantially parallel to each other, and the lower surface is longer than the radial length of the upper surface. The length in the radial direction is shortened, and the step width on the inner peripheral wall surface side is smaller than the step width on the outer peripheral wall surface side.

  According to the refrigerant compressor of the present invention, it is possible to suppress the interference between the balancer provided at the bottom of the rotor and the refrigerating machine oil, and to reduce the performance degradation due to the refrigerating machine agitation loss by the balancer. become.

It is a longitudinal cross-sectional view which shows the cross-sectional structural example of the refrigerant compressor which concerns on Embodiment 1 of this invention. It is the schematic for demonstrating the oil surface state of the refrigerating machine oil inside the airtight container at the time of the driving | operation of the refrigerant compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating the balancer mounted in the refrigerant compressor which concerns on Embodiment 1 of this invention. It is the schematic which shows an example of the shape of the balancer mounted in the refrigerant compressor which concerns on Embodiment 1 of this invention. It is the schematic which shows another example of the shape of the balancer mounted in the refrigerant compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating the balancer mounted in the refrigerant compressor which concerns on Embodiment 2 of this invention. It is explanatory drawing for demonstrating the balancer mounted in the refrigerant compressor which concerns on Embodiment 3 of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Embodiment 1.
FIG. 1 is a longitudinal sectional view showing a sectional configuration example of a refrigerant compressor 100 according to Embodiment 1 of the present invention. Based on FIG. 1, the structure and operation | movement of the refrigerant compressor 100 are demonstrated. The refrigerant compressor 100 is one of components of a refrigeration cycle used in various industrial machines such as a refrigerator, a freezer, a vending machine, an air conditioner, a refrigeration apparatus, and a water heater. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one.

  FIG. 1 shows an example of a scroll compressor in which the refrigerant compressor 100 forms a compression chamber 22 by combining spiral bodies (the spiral body 2b and the spiral body 3b) as the compression mechanism portion 35. The refrigerant compressor 100 has a function of sucking in refrigerant, compressing it, and discharging it in a high temperature and high pressure state. The refrigerant compressor 100 is configured such that the compression mechanism portion 35, the drive mechanism portion 36, and other components are housed in the sealed container 1 constituting the outer shell. As shown in FIG. 1, the compression mechanism 35 is disposed on the upper side and the drive mechanism 36 is disposed on the lower side in the sealed container 1. The bottom of the hermetic container 1 is an oil reservoir 11 that stores the refrigerating machine oil 6.

  The compression mechanism 35 has a function of compressing the refrigerant sucked from the suction pipe 33 and discharging it to the high-pressure chamber 21 formed above the sealed container 1. The refrigerant discharged into the high-pressure chamber 21 is discharged from the discharge pipe 34 to the outside of the refrigerant compressor 100. The drive mechanism unit 36 serves to drive the orbiting scroll 3 constituting the compression mechanism unit 35 so that the compression mechanism unit 35 compresses the refrigerant. That is, the driving mechanism 36 drives the orbiting scroll 3 via the main shaft 8, so that the refrigerant is compressed by the compression mechanism 35.

  The compression mechanism unit 35 includes at least a fixed scroll 2 and an orbiting scroll 3. As shown in FIG. 1, the orbiting scroll 3 is arranged on the lower side, and the fixed scroll 2 is arranged on the upper side. The fixed scroll 2 includes a base plate 2a and a spiral body 2b that is a spiral projection provided upright on one surface of the base plate 2a. The orbiting scroll 3 is composed of a base plate 3a and a spiral body 3b which is a spiral projection standing on one surface of the base plate 3a. The fixed scroll 2 and the orbiting scroll 3 are mounted in the hermetic container 1 with the spiral body 2b and the spiral body 3b meshing with each other. And between the spiral body 3b and the spiral body 2b, the compression chamber 22 whose volume changes relatively is formed.

  The fixed scroll 2 is fixed in the sealed container 1 through the frame 9. A discharge port 53 for discharging the compressed and high-pressure refrigerant is formed in the center of the fixed scroll 2. Then, the compressed and high pressure refrigerant is discharged into a high pressure chamber 21 provided in the upper part of the fixed scroll 2. The orbiting scroll 3 performs a revolving motion without rotating with respect to the fixed scroll 2. A hollow cylindrical concave bearing 3d for receiving a driving force is formed at a substantially central portion of a surface (hereinafter referred to as a thrust surface) opposite to the surface on which the spiral body 3b is formed of the orbiting scroll 3. An eccentric pin portion 56 provided at the upper end of the main shaft 8 to be described later is fitted (engaged) with the concave bearing 3d.

  The drive mechanism 36 is fixedly held inside the sealed container 1, is rotatably disposed on the inner peripheral surface side of the stator 4, is a rotor 5 fixed to the main shaft 8, and is perpendicular to the sealed container 1. The main shaft 8 that is housed in the direction and is a rotating shaft and the balancer 14 that balances the mass with respect to the rotation are at least configured. The stator 4 has a function of rotating the rotor 5 when energized. The stator 4 is fixedly supported on the hermetic container 1 by outer shrinkage or the like.

  The rotor 5 has a function of rotating and rotating the main shaft 8 when the stator 4 is energized. In addition, a balancer 5a is caulked to the bottom of the rotor 5 with a rivet 10 as a fixing member and fixed. This rotor 5 uses high-frequency heating, is partially heated to expand its inner diameter, is shrink-fitted on the outer periphery of the main shaft 8, has a permanent magnet inside, and is held with a slight gap from the stator 4. ing. The balancer 5a has a function of rotating together with the rotor 5 and balancing the mass with respect to this rotation. The balancer 5a will be described in detail with reference to FIGS.

  The main shaft 8 rotates with the rotation of the rotor 5 to drive the orbiting scroll 3 to rotate. The main shaft 8 is rotatably supported by a bearing portion 9b positioned at the center of the frame 9 on the upper side and a sub-bearing 58 positioned at the center of the subframe 57 fixedly disposed below the sealed container 1 on the lower side. It is supported. At the upper end portion of the main shaft 8, an eccentric pin portion 56 that is rotatably fitted to the concave bearing 3d of the orbiting scroll 3 is formed. An oil passage 8 a that communicates with the upper end surface is formed inside the main shaft 8. The oil passage 8 a communicates with the discharge port of the oil pump 7 and serves as a flow path for the refrigerating machine oil 6 stored at the bottom of the sealed container 1.

  On the lower end side of the main shaft 8, an oil pump 7 that pumps up the refrigerating machine oil 6 as the main shaft 8 rotates is provided so that the suction port opens to the refrigerating machine oil 6 of the oil storage 11. The refrigeration oil 6 is pumped up by the oil pump 7, flows through the oil passage 8 a, and is supplied to the compression mechanism unit 35.

  Further, a suction pipe 33 for sucking the refrigerant is connected to the sealed container 1. The suction pipe 33 opens to the low pressure chamber 20. A discharge pipe 34 for discharging the refrigerant is connected to the sealed container 1. The discharge pipe 34 opens to the high pressure chamber 21.

  Further, a frame 9 is fixed inside the sealed container 1. The frame 9 is fixed to the inner peripheral surface of the sealed container 1, and a through hole is formed in the center for supporting the main shaft 8. The frame 9 indicates the swing scroll 3 with the thrust receiving portion 9a and supports the main shaft 8 rotatably with the bearing portion 9b. Further, the frame 9 is formed with an oil return passage 61 penetrating from the thrust surface side of the orbiting scroll 3 to the axially lower side so that the refrigerating machine oil 6 lubricating the thrust receiving portion 9 a is returned to the oil reservoir 11. It has become. Although FIG. 1 shows an example in which only one oil return passage 61 is formed, the present invention is not limited to this. For example, two or more oil return passages 61 may be formed. Note that the outer peripheral surface of the frame 9 may be fixed to the inner peripheral surface of the sealed container 1 by shrink fitting, welding, or the like.

  A subframe 57 is fixed inside the sealed container 1. The sub frame 57 is fixed to the inner peripheral surface of the sealed container 1, and a through hole is formed at the center for supporting the main shaft 8. The sub-frame 57 supports the main shaft 8 rotatably with a sub-bearing 58. As shown in FIG. 1, the frame 9 is fixed to the inside upper side of the sealed container 1 and the subframe 57 is fixed to the inside lower side of the sealed container 1.

  In the sealed container 1, an Oldham ring (not shown) for preventing the rotating motion of the orbiting scroll 3 during the eccentric orbiting motion is disposed. This Oldham ring is disposed, for example, between the orbiting scroll 3 and the frame 9 and serves to prevent the orbiting scroll 3 from rotating and to enable a revolving motion. That is, the Oldham ring functions as a rotation prevention mechanism for the orbiting scroll 3.

Here, the operation of the refrigerant compressor 100 will be briefly described.
The rotor 5 rotates by receiving a rotational force (torque) from a rotating magnetic field generated by the stator 4 to which power is supplied. As the rotor 5 rotates, the main shaft 8 fixed to the rotor 5 and supported by the bearing portion 9b and the auxiliary bearing 58 rotates. The orbiting scroll 3 is engaged with the eccentric pin portion 56 of the main shaft 8, and the rotation motion of the orbiting scroll 3 is converted into the revolution motion by the rotation prevention mechanism of the Oldham ring. When the rotor 5 rotates, the balancer 5a attached to the lower surface of the rotor 5 and the balancer 14 fixed to the main shaft 8 keep a balance with respect to the eccentric revolving motion of the orbiting scroll 3. As a result, the orbiting scroll 3 that is eccentrically supported on the upper part of the main shaft 8 is swung to start revolving and compress the refrigerant by a known compression principle.

  First, the rotation of the main shaft 8 causes the refrigerant present in the sealed container 1 to flow into the compression chamber 22 formed by the spiral body 2b of the fixed scroll 2 and the spiral body 3b of the swing scroll 3, and the suction process. Starts. This suction process starts when low-pressure refrigerant gas is sucked into the compression chamber 22 from the outside through the suction pipe 33 and through the low-pressure chamber 20. When the refrigerant gas is sucked into the compression chamber 22, the compression process of reducing the volume of the compression chamber 22 by the compression action of the fixed scroll 2 and the orbiting scroll 3 by the revolving orbiting motion of the eccentric orbiting scroll 3. Migrate to

  That is, in the compression mechanism portion 35, when the orbiting scroll 3 rotates orbits, the refrigerant gas is taken in from the outermost peripheral openings of the orbiting scroll 3b of the orbiting scroll 3 and the spiral body 2b of the fixed scroll 2 serving as suction ports. As the rocking scroll 3 rotates, it gradually goes to the center while being compressed. Then, the refrigerant gas compressed in the compression chamber 22 moves to the discharge process. That is, the compressed high-pressure refrigerant gas passes through the discharge port 53 of the fixed scroll 2, passes through the high-pressure chamber 21, and then is discharged to the outside of the refrigerant compressor 100 through the discharge pipe 34.

  Note that the low-pressure refrigerant gas in the low-pressure chamber 20 and the high-pressure refrigerant gas in the high-pressure chamber 21 are partitioned so as to be kept airtight by the fixed scroll 2 and the frame 9, and therefore may be mixed in the sealed container 1. Absent. When the main shaft 8 is rotated, the refrigeration oil 6 is sucked by the oil pump 7 and supplied to the bearing portion 9b, the auxiliary bearing 58 and the like through the oil passage 8a provided in the main shaft 8, and then returned to the oil by gravity. It returns to the oil reservoir 11 again through the passage 61. When the energization of the stator 4 is stopped, the refrigerant compressor 100 stops its operation.

  FIG. 2 is a schematic diagram for explaining the oil level state of the refrigerating machine oil 6 inside the sealed container 1 during operation of the refrigerant compressor 100. FIG. 3 is an explanatory diagram for explaining the balancer 5a. FIG. 4 is a schematic view showing an example of the shape of the balancer 5a. FIG. 5 is a schematic view showing another example of the shape of the balancer 5a. Based on FIGS. 2-5, the balancer 5a which is the characteristic matter of the refrigerant compressor 100 is demonstrated in detail. 3A is an enlarged longitudinal sectional view showing an outline of the drive mechanism portion 36, and FIG. 3B is a bottom view showing a state in which the rotor 5 is viewed from the bottom side. .

  As shown in FIG. 3A, the balancer 5 a is caulked and fixed to the bottom of the rotor 5 with a rivet 10. The balancer 5a has a semi-thick cylindrical shape (see FIG. 3B). The longitudinal cross-sectional shape of the balancer 5a in the radial direction includes a surface in contact with the rotor 5 (a surface on the upper surface of the paper, hereinafter referred to as an upper surface) and a rivet surface (a surface fixed by caulking with the rivet 10, that is, a surface on the lower surface of the paper) (Hereinafter referred to as the lower surface) is a substantially parallel trapezoid.

  As shown in FIG. 2, when the refrigerant compressor 100 is in operation, the refrigerating machine oil 6 stored in the oil reservoir 11 of the hermetic container 1 becomes a “mortar-like” oil surface shape by the rotational movement of the rotor 5. (Shaded area). At this time, if the balancer 5a collides with the refrigerating machine oil 6, the balancer 5a causes a stirring loss of the refrigerating machine oil 6. Therefore, in the refrigerant compressor 100, the balancer 5a is prevented from colliding with the refrigerating machine oil 6 even during operation. Specifically, as shown in FIGS. 3A and 4, the longitudinal cross-sectional shape of the balancer 5a in the radial direction is substantially trapezoidal.

  The shape of the balancer 5a will be described in more detail with reference to FIG. As shown in FIG. 4, the balancer 5a has a taper shape such that the upper surface and the lower surface are substantially parallel and θ1 <θ2. θ1 represents the taper angle of the inner peripheral wall of the balancer 5a (side located on the inner diameter side in the longitudinal sectional shape of the balancer 5a), that is, the inclination angle of the inner peripheral wall. Further, θ2 represents the taper angle of the outer peripheral wall of the balancer 5a (side located on the outer diameter side in the longitudinal sectional shape of the balancer 5a), that is, the inclination angle of the outer peripheral wall. That is, the inner peripheral wall and the outer peripheral wall of the balancer 5a are inclined so that the area of the lower surface is smaller than the area of the upper surface, and the inclination angle of the inner peripheral wall is made smaller.

  The balancer 5a is generally manufactured from brass, cast iron, sintering, or the like, and has a draft from the mold. Therefore, as shown in FIG. 4, the balancer 5a has a tapered shape such that θ1 <θ2 to prevent the refrigerating machine oil 6 and the balancer 5a from contacting each other during operation of the refrigerant compressor 100. can do. Therefore, the interference between the balancer 5a and the refrigerating machine oil 6 can be suppressed, the stirring loss of the refrigerating machine oil 6 by the balancer 5a can be suppressed, and the performance deterioration of the refrigerant compressor 100 due to the stirring loss of the refrigerating machine oil 6 can be reduced.

As shown in FIG. 5, the balancer 5a may be configured by laminating a plurality of thin plates. In this case, the inner peripheral wall of the balancer 5a (side located on the inner diameter side in the cross-sectional shape of the balancer 5a) and the outer peripheral wall of the balancer 5a (side located on the outer diameter side in the cross-sectional shape of the balancer 5a) are not linear. , W1> W2 and W3 <W4 can be substantially tapered, and the same effect as the tapered shape can be obtained. W1 is the width of the upper surface, that is, the length of the upper surface in the radial direction, W2 is the width of the lower surface, that is, the length of the lower surface in the radial direction,
W3 represents the step width on the inner peripheral wall surface side, and W4 represents the step width on the outer peripheral wall surface side.

Embodiment 2. FIG.
FIG. 6 is an explanatory diagram for explaining the balancer 5b mounted on the refrigerant compressor 200 according to Embodiment 2 of the present invention. Based on FIG. 6, the characteristic part of Embodiment 2 is demonstrated. In the second embodiment, differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted. FIG. 6A is an enlarged longitudinal sectional view showing an outline of the drive mechanism portion 36, and FIG. 6B is a bottom view showing a state in which the rotor 5 is viewed from the bottom side. .

  In the first embodiment, the balancer 5a has a tapered shape such that θ1 <θ2 or a substantially tapered shape such that W1> W2 and W3 <W4. However, in the second embodiment, In addition to the features of the first embodiment, an example is shown in which a groove 12 is provided on the contact surface between the balancer 5b and the rotor 5 (the upper surface of the balancer 5b) to reduce the contact area between the balancer 5b and the rotor 5. ing.

  When the rotor 5 is shrink-fitted on the main shaft 8, in order to increase productivity, it is a common practice to employ high-frequency heating to heat the rotor 5 and partially warm the rotor 5 to expand the inner diameter. . Since the balancer 5b is generally made of brass or the like like the balancer 5a, heat absorption by the brass increases when the contact area between the balancer 5b and the rotor 5 is large. If it becomes so, the temperature fall of the rotor 5 will arise and the internal diameter expansion of the shrink-fit part of the main axis | shaft 8 of the rotor 5 will reduce. Thereby, shrink fitting of the rotor 5 to the main shaft 8 becomes difficult, resulting in a decrease in assemblability.

  Therefore, in the refrigerant compressor 200 according to Embodiment 2, the contact area between the balancer 5b and the rotor 5 is reduced. That is, in the refrigerant compressor 200, the groove 12 is provided on the upper surface of the balancer 5b so that the contact area between the balancer 5b and the rotor 5 is reduced. As described above, the balancer 5b has a shape in which the groove 12 is provided on the upper surface thereof, and by reducing the contact area between the balancer 5b and the rotor 5, heat absorption by the balancer 5b when the rotor 5 is shrink-fitted is reduced. As a result, the inner diameter of the rotor, which is a shrink-fitted portion, can be easily enlarged, and the assemblability can be improved.

  Therefore, in the refrigerant compressor 200 according to the second embodiment, the interference between the balancer 5b and the refrigerating machine oil 6 can be suppressed, the stirring loss of the refrigerating machine oil 6 by the balancer 5b is suppressed, and the refrigerant compressor 200 due to the stirring loss of the refrigerating machine oil 6 is suppressed. The performance degradation can be reduced. In addition, in the refrigerant compressor 200 according to the second embodiment, by reducing the contact area between the balancer 5b and the rotor 5, heat absorption by the balancer 5b during shrink fitting of the rotor 5 can be reduced, and the main shaft 8 can be baked. The inner diameter of the rotor, which is the fitting portion, can be easily enlarged, and the assemblability can be improved. The shape, size, groove depth, and the like of the groove 12 are not particularly limited, and may be determined according to the shape, size, etc. of the balancer 5b.

Embodiment 3 FIG.
FIG. 7 is an explanatory diagram for explaining the balancer 5c mounted on the refrigerant compressor 300 according to Embodiment 3 of the present invention. Based on FIG. 7, the characteristic part of Embodiment 3 is demonstrated. In the third embodiment, differences from the first and second embodiments will be mainly described, and the same parts as those in the first and second embodiments will be denoted by the same reference numerals and the description thereof will be omitted. It shall be. FIG. 7A is an enlarged longitudinal sectional view showing an outline of the drive mechanism portion 36, and FIG. 7B is a bottom view showing a state in which the rotor 5 is viewed from the bottom side. .

  In Embodiment 2, the groove 12 is provided on the contact surface (the upper surface of the balancer 5b) between the balancer 5b and the rotor 5, and the contact area between the balancer 5b and the rotor 5 is reduced as an example. In the third embodiment, in addition to the features of the first embodiment, a protrusion 13 is provided in the vicinity of the rivet through hole on the contact surface between the balancer 5c and the rotor 5 (the upper surface of the balancer 5c), and the contact between the balancer 5c and the rotor 5 is achieved. The case where the area is reduced is shown as an example.

  As described in the second embodiment, in order to improve the assemblability, it is required to reduce the contact area between the balancer 5c and the rotor 5. Therefore, in the second embodiment, the groove 12 is provided on the upper surface of the balancer 5b to reduce the contact area between the balancer 5b and the rotor 5. However, in the third embodiment, the protrusion 13 is provided on the upper surface of the balancer 5c. Thus, the contact area between the balancer 5c and the rotor 5 is reduced.

  Therefore, in the refrigerant compressor 300 according to Embodiment 3, the interference between the balancer 5c and the refrigerating machine oil 6 can be suppressed, the stirring loss of the refrigerating machine oil 6 by the balancer 5c is suppressed, and the refrigerant compressor 300 due to the stirring loss of the refrigerating machine oil 6 is suppressed. The performance degradation can be reduced. In addition, in the refrigerant compressor 300 according to the third embodiment, by reducing the contact area between the balancer 5c and the rotor 5, heat absorption by the balancer 5c during shrink fitting of the rotor 5 can be reduced, and the main shaft 8 can be baked. The inner diameter of the rotor, which is the fitting portion, can be easily enlarged, and the assemblability can be improved. Note that the shape, size, groove depth, and the like of the protrusion 13 are not particularly limited, and may be determined according to the shape, size, etc. of the balancer 5c.

  DESCRIPTION OF SYMBOLS 1 Airtight container, 2 fixed scroll, 2a base plate, 2b spiral body, 3 rocking scroll, 3a base plate, 3b spiral body, 3d concave bearing, 4 stator, 5 rotor, 5a balancer, 5b balancer, 5c balancer, 6 freezing Machine oil, 7 Oil pump, 8 Main shaft, 8a Oil passage, 9 Frame, 9a Thrust receiving part, 9b Bearing part, 10 Rivet, 11 Oil reservoir, 12 Groove, 13 Protrusion, 14 Balancer, 20 Low pressure chamber, 21 High pressure chamber, 22 Compression chamber, 33 Suction pipe, 34 Discharge pipe, 35 Compression mechanism section, 36 Drive mechanism section, 53 Discharge port, 56 Eccentric pin section, 57 Subframe, 58 Sub bearing, 61 Oil return passage, 100 Refrigerant compressor, 200 Refrigerant Compressor, 300 Refrigerant compressor.

Claims (6)

A sealed container;
A stator fixedly supported in the sealed container;
A rotor rotatably disposed on the inner peripheral surface side of the stator;
A main shaft inserted into the center of the rotor and driven to rotate together with the rotor;
A balancer attached to the bottom of the rotor and rotating with the rotor;
A fixing member for fixing the balancer to the rotor,
The balancer is
Refrigerant compression characterized in that the thick cylinder has a shape divided into approximately half along the cylinder direction, its upper and lower surfaces are formed substantially parallel, and the inner and outer peripheral walls are inclined. Machine. The inner peripheral wall and the outer peripheral wall are:
The inclination of the lower surface is made smaller than the area of the upper surface, and the inclination angle of the inner peripheral wall is made smaller than the inclination angle of the outer peripheral wall. Refrigerant compressor. A sealed container;
A stator fixedly supported in the sealed container;
A rotor rotatably disposed on the inner peripheral surface side of the stator;
A main shaft inserted into the center of the rotor and driven to rotate together with the rotor;
A balancer attached to the bottom of the rotor and rotating with the rotor;
A fixing member for fixing the balancer to the rotor,
The balancer is
A thick cylinder formed by laminating a plurality of thin plates has a shape divided into approximately half along the cylinder direction, and the upper surface and the lower surface are formed substantially parallel to each other, and are longer than the radial length of the upper surface. A refrigerant compressor, wherein the length of the lower surface in the radial direction is shortened, and the step width on the inner peripheral wall surface side is smaller than the step width on the outer peripheral wall surface side. The groove | channel which reduces the contact area of the said balancer and the said rotor was provided in the said upper surface of the said balancer. The refrigerant compressor as described in any one of Claims 1-3 characterized by the above-mentioned. The refrigerant compressor according to any one of claims 1 to 3, wherein a protrusion that reduces a contact area between the balancer and the rotor is provided on the upper surface of the balancer. The refrigerant compressor according to claim 5, wherein the protrusion is provided in the vicinity of the through hole of the fixing member.

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