compressor

Abstract

The compressor of the present application provides a compressor (10) capable of increasing the amount of refrigerant passing through the rotor (14b) and improving the compressor performance, by setting the range of the setting angle X of the refrigerant inflow side weight (17a) on the refrigerant inflow side rotor end face, setting the range of the setting angle X as the weight setting area A, setting the range outside the setting angle X as the weight non-setting area B, setting the total weight setting area opening area of the refrigerant passages (44A1), (44A2) located in the weight setting area A as As, setting the total weight non-setting area opening area of the refrigerant passages (44Bb1), (44Bb2), (44Bb1), (44Bf1) located in the weight non-setting area B as Bs, and making the weight non-setting area unit opening area per unit angle (Bs / (360°-X)) of the total weight non-setting area opening area Bs larger than the weight setting area unit opening area per unit angle (As / X) of the total weight setting area opening area As.

Description

Technical Field

[0001] This invention relates in particular to compressors for use in refrigeration devices such as air conditioners, water heaters, and cold storage facilities. Background Technology

[0002] The compressor has a compression mechanism and an electric mechanism inside the sealed container. After the refrigerant is compressed by the compression mechanism, it passes through the electric mechanism and is discharged from the discharge pipe. The compressor performance can be improved by reducing the pressure loss of the refrigerant when passing through the electric mechanism.

[0003] Patent Document 1 discloses a refrigerant passage in which the passage area on the outflow side of the rotor is larger than the passage area on the inflow side. By making the passage area on the outflow side larger than the passage area on the inflow side, Patent Document 1 reduces the flow rate of the refrigerant on the outflow side, thereby causing lubricating oil separation.

[0004] Existing technical documents

[0005] Patent documents

[0006] Patent Document 1: Japanese Patent Application Publication No. 2016-109065 Summary of the Invention

[0007] The problem that the invention aims to solve

[0008] However, in Patent Document 1, it is not possible to increase the amount of refrigerant passing through the refrigerant passage.

[0009] To reduce structural imbalances, compressors include counterweights on the end faces of the rotor.

[0010] Due to this counterweight, the amount of refrigerant flowing in varies among the multiple refrigerant passages formed in the rotor.

[0011] Figure 6 It is a diagram showing the different amounts of refrigerant flowing into multiple refrigerant pathways.

[0012] Figure 6 (a) shows the refrigerant inflow side end face of the rotor.

[0013] like Figure 6 As shown in (a), the rotor 14b has a plurality of refrigerant passages 44, and a counterweight 17 is included circumferentially on a portion of the end face of the rotor 14b. Each refrigerant passage 44 has the same opening area and is arranged at equal intervals on the circumference.

[0014] Figure 6 (a) The arrow R shown indicates the direction of rotation of rotor 14b.

[0015] Figure 6 (b) shows the flow through Figure 6(a) shows the refrigerant flow rates of each refrigerant passage 44.

[0016] like Figure 6 As shown in (b), the refrigerant flow rate is different in each refrigerant passage 44. In refrigerant passages 44-5 and 44-6, which are located within the range where the counterweight is installed, the refrigerant flow rate is low. In refrigerant passages 44-1, 44-2, 44-3 and 44-4, which are located outside the range where the counterweight is installed, the refrigerant flow rate is high.

[0017] Therefore, the object of the present invention is to provide a compressor that can improve compressor performance by increasing the amount of refrigerant passing through the rotor.

[0018] Methods for solving problems

[0019] The compressor of the present invention, according to a first aspect, has a suction pipe 11 for drawing in refrigerant and a discharge pipe 12 for discharging the refrigerant connected to a sealed container 1. Inside the sealed container 1, a compression mechanism 13 for compressing the refrigerant drawn in from the suction pipe 11 and an electric mechanism 14 for driving the compression mechanism 13 are disposed. The electric mechanism 14 consists of a stator 14a fixed to the sealed container 1 and a rotor 14b disposed on the inner circumference of the stator 14a. The rotor 14b has a cylindrical rotor core 41 formed by stacking disc-shaped rotor chips. The rotor core 41 has a plurality of refrigerant passages 44 along the axial direction. A refrigerant inflow side counterweight 17a is provided on the refrigerant inflow side rotor end face of the rotor 14b, which serves as the inflow side of the refrigerant passages 44. The refrigerant compressed by the compression mechanism 13 passes through the refrigerant passages 44 and is then discharged from the discharge pipe 12. The compressor is characterized in that, when the setting range of the refrigerant inflow side counterweight 17a on the rotor end face of the refrigerant inflow side is set as setting angle X, the range within the setting angle X is set as counterweight setting area A, the range outside the setting angle X is set as counterweight non-setting area B, and the total opening area of ​​the refrigerant passages 44A1 and 44A2 located in the counterweight setting area A is set as As, and the total opening area of ​​the refrigerant passages 44Bb1, 44Bb2, 44Bb3, 44Bf1, and 44Bf2 located in the counterweight non-setting area B is set as Bs, the unit opening area of ​​the counterweight non-setting area per unit angle of the total opening area Bs (Bs / (360°-X)) is larger than the unit opening area of ​​the counterweight setting area per unit angle of the total opening area As (As / X).

[0020] The second aspect of the invention is characterized in that, in the compressor of the first aspect, when the counterweight non-setting region B located in front of the rotor 14b in the rotation direction is designated as the front counterweight non-setting region Bf, the counterweight non-setting region B located behind the rotor 14b in the rotation direction is designated as the rear counterweight non-setting region Bb, and the total front opening area of ​​the refrigerant passages 44Bf1 and 44Bf2 located in the front counterweight non-setting region Bf is designated as Bfs, and the total rear opening area of ​​the refrigerant passages 44Bb1, 44Bb2 and 44Bb3 located in the rear counterweight non-setting region Bb is designated as Bbs, the unit rear opening area of ​​the total rear opening area of ​​the total rear opening area of ​​the counterweight non-setting region Bbs per unit angle is larger than the unit front opening area of ​​the total front opening area of ​​the counterweight non-setting region Bfs per unit angle.

[0021] The third aspect of the invention is characterized in that, in the compressor of the first or second aspect, the refrigerant passages 44 are regularly arranged on a circumference such that the opening areas 44Bbs1, 44Bbs2, 44Bbs3 of the non-weight setting region of the refrigerant passages 44Bb1, 44Bb2, 44Bb3 located in the non-weight setting region B are larger than the opening areas 44As1, 44As2 of the weight setting region of the refrigerant passages 44A1, 44A2 located in the weight setting region A.

[0022] The fourth aspect of the invention is characterized in that, in the compressor of the second aspect, the refrigerant passages 44 are regularly arranged on a circumference such that the rear opening area of ​​the non-weighted areas of the refrigerant passages 44Bb1, 44Bb2, 44Bb3 located in the rear non-weighted area Bb is larger than the front opening area of ​​the non-weighted areas of the refrigerant passages 44Bf1, 44Bf2 located in the front non-weighted area Bf.

[0023] The fifth aspect of the invention is characterized in that, in the compressor described in the third or fourth aspect, the refrigerant passages 44 are arranged at equal intervals.

[0024] The invention is characterized in that, in the compressor of any one of the first to fifth aspects, an end plate 18a is provided between the refrigerant inflow side rotor end face and the refrigerant inflow side counterweight 17a, and the end plate 18a is used to close at least a portion of the refrigerant passage 44 located in the counterweight setting region A.

[0025] The invention is characterized in that, in the compressor of the second aspect, an end plate 18a is provided between the refrigerant inflow side rotor end face and the refrigerant inflow side counterweight 17a, and the end plate 18a is used to close at least a portion of the refrigerant passage 44 located in the counterweight setting region A.

[0026] Invention Effects

[0027] According to the present invention, the amount of refrigerant flowing through the refrigerant passage can be increased. Furthermore, according to the present invention, it is not necessary to use rotor chips with different shapes for each chip, nor is it necessary to stagger the stacking of each rotor chip, thus simplifying rotor manufacturing. Attached Figure Description

[0028] Figure 1 This is a structural diagram of a refrigeration device using a compressor according to an embodiment of the present invention.

[0029] Figure 2 This is a structural diagram of the rotor according to the first embodiment of the present invention.

[0030] Figure 3 This is a structural diagram of the rotor according to the second embodiment of the present invention.

[0031] Figure 4 This is a structural diagram of the rotor according to the third embodiment of the present invention.

[0032] Figure 5 This is a graph showing the refrigerant dosage and refrigerant flow rate in the refrigerant passages of the rotors in various embodiments of the present invention.

[0033] Figure 6 It is a diagram showing the different amounts of refrigerant flowing into multiple refrigerant pathways. Detailed Implementation

[0034] In the compressor of the first embodiment of the present invention, the range of the refrigerant inflow side counterweight on the rotor end face on the refrigerant inflow side is set as a setting angle X, the range within the setting angle X is set as a counterweight setting region A, the range outside the setting angle X is set as a counterweight non-setting region B, and the total opening area of ​​the refrigerant passage located in the counterweight setting region A is set as As, and the total opening area of ​​the refrigerant passage located in the counterweight non-setting region B is set as Bs, such that the unit opening area of ​​the counterweight non-setting region per unit angle of the total opening area of ​​the counterweight non-setting region (Bs / (360°-X)) is larger than the unit opening area of ​​the counterweight setting region per unit angle of the total opening area of ​​the counterweight setting region (As / X). According to this embodiment, the amount of refrigerant flowing into the refrigerant passage can be increased by utilizing the pressure difference generated by the refrigerant inflow side counterweight rotating together with the rotor.

[0035] The second embodiment of the present invention is as follows: In the compressor of the first embodiment, when the counterweight non-setting region B located in front of the rotor's rotation direction is designated as the front counterweight non-setting region Bf, and the counterweight non-setting region B located behind the rotor's rotation direction is designated as the rear counterweight non-setting region Bb, and the total front opening area of ​​the refrigerant passage in the front counterweight non-setting region Bf is designated as Bfs, and the total rear opening area of ​​the refrigerant passage in the rear counterweight non-setting region Bb is designated as Bbs, the unit rear opening area of ​​the total rear opening area Bbs is larger per unit angle than the unit front opening area Bfs. According to this embodiment, the amount of refrigerant flowing into the refrigerant passage can be further increased.

[0036] The third embodiment of the present invention involves a compressor in the first or second embodiment in which refrigerant passages are regularly arranged on a circumference, and the opening area of ​​the non-weighted region of the refrigerant passage located in the non-weighted region B is larger than the opening area of ​​the weighted region of the refrigerant passage located in the weighted region A. According to this embodiment, since the refrigerant passages are typically regularly arranged, the refrigerant flow rate can be increased simply by changing the opening area.

[0037] The fourth embodiment of the present invention is as follows: In the compressor of the second embodiment, the refrigerant passages are regularly arranged on a circumference, and the opening area behind the non-weighted region Bb of the refrigerant passage is larger than the opening area in front of the non-weighted region Bf of the refrigerant passage. According to this embodiment, since the refrigerant passages are generally regularly arranged, the refrigerant flow rate can be increased simply by changing the opening area.

[0038] A fifth embodiment of the present invention involves arranging refrigerant passages at equal intervals in the compressor of the third or fourth embodiment. According to this embodiment, since the refrigerant passages are typically arranged at equal intervals, the refrigerant flow rate can be increased simply by changing the opening area.

[0039] The sixth embodiment of the present invention is as follows: In the compressor described in any one of claims 1 to 5, an end plate is provided between the refrigerant inflow side rotor end face and the refrigerant inflow side counterweight, and the end plate closes at least a portion of the refrigerant passage located in the counterweight setting region A. The asymmetrical configuration of the refrigerant passage amplifies the effects of imbalance, but according to this embodiment, the opening area can be changed using the end plate, thus reducing the effects of imbalance.

[0040] The seventh embodiment of the present invention is as follows: In the compressor described in the second embodiment, an end plate is provided between the refrigerant inflow side rotor end face and the refrigerant inflow side counterweight, and the end plate closes at least a portion of the refrigerant passage located in the counterweight setting region A. The asymmetrical configuration of the refrigerant passage amplifies the effects of imbalance, but according to this embodiment, the opening area can be changed using the end plate, thus reducing the effects of imbalance.

[0041]

Example

[0042] The following describes embodiments of the present invention relating to compressors. However, the present invention is not limited to the following embodiments.

[0043] Figure 1 This is a structural diagram of a refrigeration device using the compressor of this embodiment.

[0044] The sealed container 1 is connected to a suction pipe 11 for drawing in refrigerant and a discharge pipe 12 for discharging refrigerant. Inside the sealed container 1 is a compression mechanism 13 for compressing the refrigerant drawn in from the suction pipe 11 and an electric mechanism 14 for driving the compression mechanism 13.

[0045] The compression mechanism 13 consists of a cylinder 13a, a piston 13b, blades (not shown), a main bearing 13c, and a secondary bearing 13d. The cylinder 13a is fixed to the sealed container 1. The piston 13b is rotatably fitted into the eccentric portion 15a of the shaft 15 that passes through the cylinder 13a. The blades follow the piston 13b, which rotates along the inner wall of the cylinder 13a, and reciprocate in the blade slots. The main bearing 13c and the secondary bearing 13d seal the upper and lower end faces of the cylinder 13a and support the shaft 15.

[0046] The electric mechanism 14 consists of a stator 14a fixed to the sealed container 1 and a rotor 14b disposed on the inner periphery of the stator 14a.

[0047] A counterweight 17 is provided on the end face of the rotor 14b.

[0048] The refrigerant inflow side counterweight 17a is located on the lower end face of the rotor 14b, and the refrigerant outflow side counterweight 17b is located on the upper end face of the rotor 14b.

[0049] The refrigerant is drawn into the compression unit 13 from the suction pipe 11 and compressed by the compression unit 13. Then, the refrigerant passes through the electric mechanism unit 14 and is discharged from the discharge pipe 12.

[0050] In this embodiment, the compressor 10, condenser 21, pressure reducing device 22, and evaporator 23 of the refrigeration apparatus are connected in a ring by piping. The condenser 21 condenses the refrigerant discharged from the discharge pipe 12, the pressure reducing device 22 reduces the pressure of the refrigerant condensed by the condenser 21, and the evaporator 23 evaporates the refrigerant that has been reduced in pressure by the pressure reducing device 22.

[0051] The refrigerant evaporated by evaporator 23 returns to compressor 10 via accumulator 16.

[0052] Figure 2 This is a structural diagram of the rotor according to the first embodiment of the present invention. Figure 2 (a) is a top view of the rotor end face that forms the refrigerant outlet side. Figure 2 (b) is an axial side view. Figure 2 (c) is a bottom view of the rotor end face that forms the refrigerant inflow side. Figure 2 (d) is a three-dimensional view of the rotor. Figure 2 (e) is Figure 2 (c) Section II-II view.

[0053] The rotor 14b has a cylindrical rotor core 41 formed by stacking disc-shaped rotor chips and a permanent magnet 42 disposed on the outer periphery of the rotor core 41.

[0054] The rotor core 41 has a through hole 43 at its center for arranging the shaft 15, and a plurality of refrigerant passages 44 are arranged axially around the through hole 43.

[0055] The refrigerant passage 44 allows the refrigerant compressed by the compression mechanism 13 to pass through.

[0056] In this embodiment, the refrigerant passages 44 are arranged regularly and at equal intervals on the circumference.

[0057] like Figure 2 As shown in (a), a refrigerant outflow side counterweight 17b is present on the refrigerant outflow side rotor end face of the rotor 14b, which forms the outflow side of the refrigerant passage. An end plate 18b is provided on the refrigerant outflow side rotor end face of the rotor 14b. The end plate 18b is disposed between the refrigerant outflow side rotor end face and the refrigerant outflow side counterweight 17b. In this embodiment, an opening is formed on the end plate 18b at the same position as the opening of the refrigerant passage 44. The opening is the same size as the opening of the refrigerant passage 44.

[0058] In addition, such as Figure 2 As shown in (c), the refrigerant inflow side counterweight 17a is present on the refrigerant inflow side rotor end face of the rotor 14b, which forms the refrigerant passage. An end plate 18a is provided on the refrigerant inflow side rotor end face of the rotor 14b. The end plate 18a is disposed between the refrigerant inflow side rotor end face and the refrigerant inflow side counterweight 17a. In this embodiment, an opening is formed on the end plate 18a at the same position as the opening of the refrigerant passage 44. The opening is the same size as the opening of the refrigerant passage 44.

[0059] The refrigerant inflow side counterweight 17a and the refrigerant outflow side counterweight 17b are fixed to the rotor 14b by fixed rivets 19.

[0060] The fixed rivet 19 passes through the refrigerant inflow side counterweight 17a, end plate 18a, rotor 14b, end plate 18b and refrigerant outflow side counterweight 17b.

[0061] The refrigerant inflow side counterweight 17a and the refrigerant outflow side counterweight 17b are configured in a manner that gives them a specified height in the axial direction of the rotor 14b, in a portion of the circumference of the rotor 14b.

[0062] like Figure 2 As shown in (c), the angle between the rotation center of the rotor 14b and the two ends of the refrigerant inflow side counterweight 17a is taken as the setting angle X of the refrigerant inflow side counterweight 17a on the end face of the refrigerant inflow side rotor. That is, the range of this setting angle X is the setting range of the refrigerant inflow side counterweight 17a, and this setting range is set as the counterweight setting area A.

[0063] In addition, the area outside the range of the setting angle X (360°-X) is designated as the non-setting area B for the counterweight.

[0064] exist Figure 2 In (c), refrigerant passages 44A1 and 44A2 are located in counterweight setting area A, while refrigerant passages 44Bf1, 44Bb1, 44Bb2, and 44Bb3 are located in counterweight non-setting area B.

[0065] The refrigerant passages 44Bb1, 44Bb2, and 44Bb3 have larger passage areas than the refrigerant passages 44A1, 44A2, and 44Bf1, that is, the opening area at the refrigerant inflow side rotor end face of rotor 14b is larger.

[0066] The sum of the opening area 44As1 of the counterweight setting area of ​​refrigerant passage 44A1 and the opening area 44As2 of the counterweight setting area of ​​refrigerant passage 44A2 is the total opening area As of the counterweight setting area.

[0067] In addition, the total open area of ​​the non-weighted area of ​​refrigerant passage 44Bf1 (44Bfs1), the open area of ​​the non-weighted area of ​​refrigerant passage 44Bb1 (44Bbs1), the open area of ​​the non-weighted area of ​​refrigerant passage 44Bb2 (44Bbs2), and the open area of ​​the non-weighted area of ​​refrigerant passage 44Bb3 (44Bbs3) is the total open area of ​​the non-weighted area Bs.

[0068] Furthermore, the unit opening area of ​​the non-set area of ​​the total counterweight Bs per unit angle (Bs / (360°-X)) is larger than the unit opening area of ​​the set area As per unit angle (As / X).

[0069] In this way, the unit opening area (Bs / (360°-X)) of the non-weighted area is made larger than the unit opening area (As / X) of the weighted area. In this way, the amount of refrigerant flowing into the refrigerant passage 44 can be increased by utilizing the pressure difference generated by the refrigerant inflow side counterweight 17a rotating together with the rotor 14b.

[0070] In addition, such as Figure 2 As shown in (c), the counterweight non-setting area B located in front of the rotor 14b in the rotation direction is designated as the front counterweight non-setting area Bf, and the counterweight non-setting area B located behind the rotor 14b in the rotation direction is designated as the rear counterweight non-setting area Bb.

[0071] In this embodiment, refrigerant passage 44Bf1 is located in the front counterweight non-setting area Bf, and refrigerant passages 44Bb1, 44Bb2 and 44Bb3 are located in the rear counterweight non-setting area Bb.

[0072] The opening area 44Bfs1 of the non-weighted area of ​​refrigerant passage 44Bf1 becomes the total opening area Bfs in front of the non-weighted area. The total opening area 44Bbs1 of the non-weighted area of ​​refrigerant passage 44Bb1, the opening area 44Bbs2 of the non-weighted area of ​​refrigerant passage 44Bb2, and the opening area 44Bbs3 of the non-weighted area of ​​refrigerant passage 44Bb3 becomes the total opening area Bbs behind the non-weighted area.

[0073] Furthermore, the unit opening area behind the non-set area of ​​the total counterweight is made larger per unit angle than the unit opening area in front of the non-set area of ​​the total non-set area of ​​the counterweight is ... counterweight is larger per unit angle than the unit opening area in front of the non-set area of ​​the total non-set area of ​​the counterweight is larger per unit

[0074] This is achieved by making the unit opening area behind the non-counterweight area larger than the unit opening area in front of the non-counterweight area. In this way, the amount of refrigerant flowing into the refrigerant passage 44 can be increased by utilizing the pressure difference generated by the refrigerant inflow side counterweight 17a rotating together with the rotor 14b.

[0075] Furthermore, in this embodiment, by making the refrigerant passages 44Bb1, 44Bb2, and 44Bb3 larger than the refrigerant passages 44A1, 44A2, and 44Bf1, the opening area on the refrigerant inflow side rotor end face of rotor 14b is increased. However, it is also possible to make the passage areas of refrigerant passages 44Bb1, 44Bb2, 44Bb3, 44A1, 44A2, and 44Bf1 all the same, and reduce the opening area of ​​refrigerant passages 44A1, 44A2, and 44Bf1 by changing the size of the opening formed in end plate 18a. By closing at least a portion of the refrigerant passages 44 located in the counterweight setting area A and the front counterweight non-setting area Bf with end plate 18a in this way, the effect of imbalance can be reduced compared to the case where no refrigerant passages 44 are provided.

[0076] Furthermore, the division of the non-set area Bf of the front counterweight and the non-set area Bb of the rear counterweight can be set at any position without considering the opening area of ​​the refrigerant passage 44.

[0077] For example, refrigerant passages 44Bf1 and 44Bb1 can be located in the front non-weight-setting region Bf, and refrigerant passages 44Bb2 and 44Bb3 can be located in the rear non-weight-setting region Bb. In this case, the opening areas 44Bfs1 and 44Bbs1 of the non-weight-setting region of refrigerant passages 44Bf1 and 44Bbs1 of refrigerant passages 44Bb1 become the total front opening area Bfs of the non-weight-setting region. Furthermore, the sum of the opening areas 44Bbs2 and 44Bbs3 of the non-weight-setting region of refrigerant passages 44Bb2 and 44Bbs3 of refrigerant passages 44Bb3 becomes the total rear opening area Bbs of the non-weight-setting region. Further, the unit opening area per unit angle of the rear opening area Bbs of the total rear opening area Bbs is larger than the unit opening area per unit angle of the front opening area Bfs of the total front opening area Bfs.

[0078] Figure 3 This is a structural diagram of the rotor according to the second embodiment of the present invention. Figure 3 (a) is a top view of the rotor end face that forms the refrigerant outlet side. Figure 3 (b) is an axial side view. Figure 3 (c) is a bottom view of the rotor end face that forms the refrigerant inflow side. Figure 3 (d) is a three-dimensional view of the rotor. Figure 3 (e) is Figure 3(c) Section III-III. Additionally, components that function identically to those in the first embodiment are labeled with the same symbols and their descriptions are omitted.

[0079] In this embodiment, the refrigerant passages 44A1, 44A2, and 44Bf1 of the first embodiment are not present.

[0080] That is, there is no refrigerant passage 44 in the counterweight setting area A and the front counterweight non-setting area Bf, and only in the rear counterweight non-setting area Bb are refrigerant passages 44Bb1, 44Bb2 and 44Bb3 provided.

[0081] Therefore, since the total opening area As of the counterweight setting area is zero, the unit opening area (Bs / (360°-X)) of the non-counterweight setting area is larger than the unit opening area (As / X) of the counterweight setting area. In this way, the amount of refrigerant flowing into the refrigerant passage 44 can be increased by utilizing the pressure difference generated by the refrigerant inflow side counterweight 17a rotating together with the rotor 14b.

[0082] Furthermore, since the opening area in front of the non-counterweight area is zero, the unit opening area behind the non-counterweight area is larger than the unit opening area in front of the non-counterweight area. In this way, the amount of refrigerant flowing into the refrigerant passage 44 can be increased by utilizing the pressure difference generated by the refrigerant inflow side counterweight 17a rotating together with the rotor 14b.

[0083] In addition, in this embodiment, the case where the refrigerant passages 44A1, 44A2 and 44Bf1 shown in the first embodiment are not provided is described, but the refrigerant passages 44A1, 44A2 and 44Bf1 can also be closed by end plate 18a.

[0084] Without refrigerant passages 44A1, 44A2, and 44Bf1, refrigerant passage 44 is asymmetrically configured, increasing the impact of imbalance. However, by sealing the opening with end plate 18a, the impact of imbalance can be reduced.

[0085] Figure 4 This is a structural diagram of the rotor according to the third embodiment of the present invention. Figure 4 (a) is a top view of the rotor end face that forms the refrigerant outlet side. Figure 4 (b) is an axial side view. Figure 4 (c) is a bottom view of the rotor end face that forms the refrigerant inflow side. Figure 4 (d) is a three-dimensional view of the rotor. Figure 4 (e) is Figure 4(c) is a cross-sectional view along line IV-IV. Additionally, components that function identically to those in the first embodiment are labeled with the same symbols and their descriptions are omitted.

[0086] In this embodiment, the refrigerant passage 44Bb1 in the first embodiment is replaced with a refrigerant passage 44Bf2, which has a smaller opening area than the refrigerant passage 44Bb1. Furthermore, the refrigerant passage 44Bf2 is set to have the same opening area as the refrigerant passage 44Bf1.

[0087] In this embodiment, refrigerant passages 44Bf1 and 44Bf2 are located in the front counterweight non-setting area Bf, and refrigerant passages 44Bb2 and 44Bb3 are located in the rear counterweight non-setting area Bb.

[0088] The opening area 44Bfs1 of the non-weighted area of ​​refrigerant passage 44Bf1 and the opening area 44Bfs2 of the non-weighted area of ​​refrigerant passage 44Bf2 become the total opening area Bfs in front of the non-weighted area. The total opening area 44Bbs2 of the non-weighted area of ​​refrigerant passage 44Bb2 and the opening area 44Bbs3 of the non-weighted area of ​​refrigerant passage 44Bb3 become the total opening area Bbs behind the non-weighted area.

[0089] Furthermore, the unit opening area behind the non-set area of ​​the total counterweight is made larger per unit angle than the unit opening area in front of the non-set area of ​​the total non-set area of ​​the counterweight is ... counterweight is larger per unit angle than the unit opening area in front of the non-set area of ​​the total non-set area of ​​the counterweight is larger per unit

[0090] This is achieved by making the unit opening area behind the non-counterweight area larger than the unit opening area in front of the non-counterweight area. In this way, the amount of refrigerant flowing into the refrigerant passage 44 can be increased by utilizing the pressure difference generated by the refrigerant inflow side counterweight 17a rotating together with the rotor 14b.

[0091] Furthermore, in this embodiment, by making the refrigerant passages 44Bb2 and 44Bb3 larger than the refrigerant passages 44A1, 44A2, 44Bf1, and 44Bf2, the opening area in the refrigerant inflow side rotor end face of rotor 14b is increased. However, it is also possible to make the passage areas of refrigerant passages 44Bb1, 44Bb2, 44Bb3, 44A1, 44A2, and 44Bf1 all the same, and reduce the opening area of ​​refrigerant passages 44A1, 44A2, 44Bf1, and 44Bf2 by changing the size of the opening formed in end plate 18a. By closing at least a portion of the refrigerant passages 44 located in the counterweight setting area A and the front counterweight non-setting area Bf with end plate 18a in this way, the effect of imbalance can be reduced compared to the case where no refrigerant passages 44 are provided.

[0092] Furthermore, in this embodiment, the division of the front counterweight non-setting area Bf and the rear counterweight non-setting area Bb can also be set at any position without considering the opening area of ​​the refrigerant passage 44.

[0093] Figure 5 This is a graph showing the refrigerant dosage and refrigerant flow rate in the refrigerant passages of the rotors in various embodiments of the present invention.

[0094] Figure 5 (a) is a bottom view of the rotor end face of Comparative Example 1. Figure 5 (b) is a bottom view of the rotor end face of Comparative Example 2. The total opening area of ​​the refrigerant passage 44 in Comparative Example 2 is 1.94 times that of the total opening area of ​​the refrigerant passage 44 in Comparative Example 1.

[0095] Figure 5 (c) is a graph showing a comparison of the amount of refrigerant flowing through refrigerant passage 44 in Comparative Example 1, Comparative Example 2, Example 1, Example 2 and Example 3.

[0096] The first embodiment is Figure 2 The rotor 14b shown is the second embodiment. Figure 3 The rotor 14b shown is the third embodiment. Figure 4 The rotor 14b is shown.

[0097] In Comparative Example 2, the total opening area of ​​the refrigerant passage 44 is approximately twice that of Comparative Example 1. When the total opening area of ​​the refrigerant passage 44 is made approximately twice, the refrigerant flow rate is also approximately twice. However, when the refrigerant passage 44 is enlarged, the magnetic circuit of the rotor 14b is reduced, which adversely affects the performance of the motor.

[0098] like Figure 5 As shown in (c), the rotor 14b of the first embodiment has a total open area 1.46 times that of the refrigerant passage 44 in Comparative Example 1, but the refrigerant flow rate is 1.82 times. Furthermore, the rotor 14b of the second embodiment has a total open area 0.97 times that of the refrigerant passage 44 in Comparative Example 1, but the refrigerant flow rate is 1.66 times. Furthermore, the rotor 14b of the third embodiment has a total open area 1.29 times that of the refrigerant passage 44 in Comparative Example 1, but the refrigerant flow rate is 1.48 times. That is, in each embodiment, the refrigerant flow rate increases by a proportion exceeding the amplification ratio of the total open area of ​​the refrigerant passage 44. Therefore, the deterioration of motor performance is suppressed, the refrigerant flow rate increases, and the performance of the compressor 10 is improved.

[0099] As described above, according to this embodiment, the unit opening area (Bs / (360°-X)) of the non-weighted area is larger than the unit opening area (As / X) of the weighted area. In this way, the amount of refrigerant flowing into the refrigerant passage 44 can be increased by utilizing the pressure difference generated by the refrigerant inflow side counterweight 17a rotating together with the rotor 14b.

[0100] Furthermore, according to this embodiment, the unit opening area behind the non-weight setting area is larger than the unit opening area in front of the non-weight setting area. In this way, the amount of refrigerant flowing into the refrigerant passage 44 can be increased by utilizing the pressure difference generated by the refrigerant inflow side counterweight 17a rotating together with the rotor 14b.

[0101] Furthermore, according to this embodiment, the opening areas 44Bbs1, 44Bbs2, 44Bbs3, 44Bf1, 44Bf2 of the refrigerant passages 44Bb1, 44Bb2, 44Bb3, 44Bf1, 44Bf2 located in the non-weight setting region B are larger than the opening areas 44As1, 44As2 of the refrigerant passages 44A1, 44A2 located in the weight setting region A. This increases the refrigerant flow rate into the rotor 14b.

[0102] Furthermore, according to this embodiment, the opening area behind the non-weighted area of ​​the refrigerant passage 44 located in the rear non-weighted area Bb is larger than the opening area in front of the non-weighted area of ​​the refrigerant passage 44 located in the front non-weighted area Bf. This increases the refrigerant flow rate into the rotor 14b.

[0103] In addition, in this embodiment, a rotary compression mechanism consisting of one piston 13b is described as the compression mechanism part 13, but it may also be a rotary compression mechanism with two pistons 13b, or it may be a vortex compression mechanism or other compression mechanisms.

[0104] Industrial availability

[0105] The compressor of the present invention is useful in refrigeration cycle devices such as hot water heating devices, air conditioning devices, water heaters or refrigerators.

[0106] Explanation of reference numerals in the attached figures

[0107] 1. Sealed container

[0108] 10 Compressors

[0109] 11. Inhalation tube

[0110] 12 Discharge pipe

[0111] 13 Compression Mechanism Department

[0112] 13a Cylinder Block

[0113] 13b Piston

[0114] 13C main bearing

[0115] 13d secondary bearing

[0116] 14 Electric Mechanism Department

[0117] 14a stator

[0118] 14b Rotor

[0119] 15-axis

[0120] 15a Eccentric part

[0121] 16 reservoir

[0122] 17. Counterweight

[0123] 17a Refrigerant inflow side counterweight

[0124] 17b Refrigerant outlet side counterweight

[0125] 18a end plate

[0126] 18b end plate

[0127] 19. Fastening rivets

[0128] 21 Condenser

[0129] 22 Pressure reducing device

[0130] 23 Evaporator

[0131] 41 Rotor core

[0132] 42 Permanent Magnets

[0133] 43 Through hole

[0134] 44 Refrigerant Pathway

[0135] 44A1, 44A2 refrigerant passages

[0136] Opening area of ​​the counterweight setting area for 44As1 and 44As2

[0137] 44Bb1, 44Bb2, 44Bb3, 44Bf1, 44Bf2 refrigerant passages

[0138] 44Bbs1, 44Bbs2, 44Bbs3, 44Bfs1, 44Bfs2: Opening area of ​​the non-setting area of ​​the counterweight.

[0139] A. Weight setting area

[0140] As the total open area of ​​the counterweight setting area

[0141] B. Counterweight non-setting area

[0142] Bs Total counterweight non-setting area opening area

[0143] Bb Rear counterweight non-setting area

[0144] Bf Front counterweight not in the designated area

[0145] Bfs Total counterweight non-setting area front opening area

[0146] Bbs total area of ​​the opening behind the non-setting area of ​​the counterweight

[0147] X sets the angle.

Claims

1. A compressor, characterized in that: A sealed container is connected to a suction pipe for drawing in refrigerant and a discharge pipe for discharging the refrigerant. Inside the sealed container is a compression mechanism for compressing the refrigerant drawn in from the suction pipe and an electric mechanism for driving the compression mechanism. The electric mechanism includes a stator fixed to the sealed container and a rotor disposed on the inner circumference of the stator. The rotor has a cylindrical rotor core formed by stacking disc-shaped rotor chips. The rotor core has multiple refrigerant passages in the axial direction. A refrigerant inflow side counterweight is provided on the rotor end face of the rotor that serves as the inflow side of the refrigerant passage. The refrigerant, compressed by the compression mechanism, passes through the refrigerant passage and is then discharged from the discharge pipe. The setting range of the refrigerant inflow side counterweight at the rotor end face on the refrigerant inflow side is set as the setting angle X. Define the range of the set angle X as the counterweight setting area A. The area outside the set angle X is designated as the non-set area B of the counterweight. Furthermore, the total opening area of ​​the refrigerant passage located in the counterweight setting area A is set as As. When the total opening area of ​​the refrigerant passage located in the non-weight setting area B is set as Bs, The unit opening area per unit angle of the total non-set area of ​​the counterweight, Bs / (360°-X), is larger than the unit opening area per unit angle of the total set area of ​​the counterweight, As / X. The area B in front of the rotor's rotation direction where the counterweight is not set is designated as the front counterweight non-set area Bf. The non-displaced counterweight region B located behind the rotor in the direction of rotation is designated as the rear non-displaced counterweight region Bb. Furthermore, the total opening area in front of the non-weighted area of ​​the refrigerant passage located in the non-weighted area Bf is set as Bfs. When the total area of ​​the refrigerant passage behind the non-weighted area Bb is set as Bbs, The unit opening area per unit angle of the non-set area behind the total counterweight area Bbs is larger than the unit opening area per unit angle of the non-set area in front of the total counterweight area Bfs.

2. The compressor as described in claim 1, characterized in that: The refrigerant passages are regularly arranged on a circumference. The opening area of ​​the refrigerant passage in the non-weight setting area B is larger than the opening area of ​​the refrigerant passage in the weight setting area A.

3. The compressor as described in claim 1, characterized in that: The refrigerant passages are regularly arranged on a circumference. The area of ​​the opening behind the non-weighted area Bb of the refrigerant passage is larger than the area of ​​the opening in front of the non-weighted area Bf of the refrigerant passage.

4. The compressor as described in claim 2 or claim 3, characterized in that: The refrigerant passages are arranged at equal intervals.

5. The compressor according to any one of claims 1 to 3, characterized in that: An end plate is provided between the rotor end face on the refrigerant inflow side and the counterweight on the refrigerant inflow side. The end plate is used to seal off at least a portion of the refrigerant passage located in the counterweight setting area A.

6. The compressor as described in claim 1, characterized in that: An end plate is provided between the rotor end face on the refrigerant inflow side and the counterweight on the refrigerant inflow side. The end plate is used to seal off at least a portion of the refrigerant passage located in the counterweight setting area A.

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