Scroll Compressor

Abstract

To provide a scroll compressor that improves cooling performance and strength.SOLUTION: A scroll compressor comprises: a shaft capable of rotating around an axis; a motor for rotating and driving the shaft; a compressor body to be driven by rotation of the shaft; a housing covering the motor and the compressor body, and comprising a bottom surface opposed to the motor from the direction of the axis; a suction port for guiding a refrigerant into the housing; and a heat dissipation fin formed on the bottom surface, extending in a flow direction of the refrigerant, and divided into a plurality of parts in the flow direction.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present disclosure relates to scroll compressors. [Background technology]

[0002] For example, a scroll compressor is known as a compressor used in a vehicle air conditioner (see Patent Document 1 below). The scroll compressor includes a motor, a compressor body driven by the motor, and a housing that accommodates the motor and the compressor body.

[0003] In recent years, in order to miniaturize the device, there are an increasing number of cases where an intelligent power module (IPM) is used as an inverter circuit to drive a scroll compressor. In this case, the heat generation density is higher than in conventional inverter circuits, so it is necessary to improve the cooling performance. In the device described in Patent Document 1, it is said that the cooling performance can be improved by providing multiple heat dissipation fins on the rear side (back side) of the inverter in the housing. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Patent No. 3976512 Summary of the Invention [Problem to be solved by the invention]

[0005] However, when providing the above-mentioned heat dissipation fins, depending on their shape and arrangement, the following problems may occur. For example, if the bottom surface of the housing is deformed by pressure, a large stress may be applied to the heat dissipation fins, which may cause them to break. In addition, when manufacturing the housing by casting, the increased thickness caused by forming the heat dissipation fins may cause cracks and voids.

[0006] The present disclosure has been made to solve the above-mentioned problems, and has an object to provide a scroll compressor with improved cooling performance and strength. [Means for solving the problem]

[0007] In order to solve the above problems, a scroll compressor according to the present disclosure includes a shaft rotatable about an axis, a motor that rotates and drives the shaft, a compressor body that is driven by the rotation of the shaft, a housing that covers the motor and the compressor body and has a bottom surface that faces the motor from the axial direction, a suction port that introduces a refrigerant into the housing, and heat dissipation fins that are formed on the bottom surface, extend in a flow direction of the refrigerant, and are divided into a plurality of parts in the flow direction, Since the suction port extends in a direction including a tangential component of a circle centered on the axis when viewed from the axial direction, the refrigerant flows from one side to the other in the circumferential direction centered on the axis on the bottom surface, and the heat dissipation fins extend from the end of the suction port over a region of approximately 180° in the direction of the refrigerant flow, centered on the axis. The scroll compressor according to the present disclosure comprises a shaft rotatable about an axis, a motor that drives and rotates the shaft, a compressor body driven by the rotation of the shaft, a housing that covers the motor and the compressor body and has a bottom surface that faces the motor from the axial direction, a suction port that guides a refrigerant into the housing, and heat dissipation fins formed on the bottom surface, extending in a flow direction of the refrigerant and divided into a plurality of pieces in the flow direction, wherein the suction port extends in a direction that includes a tangential component of a circle centered on the axis when viewed from the axial direction, so that the refrigerant flows on the bottom surface from one circumferential side to the other side in a circumferential direction centered on the axis, and the heat dissipation fins extend in an arc shape centered on the axis and are provided in a plurality of radial spaces, such that the divided heat dissipation fins located radially outward have larger dimensions in the flow direction, and the number of divisions increases as the divided heat dissipation fins are located radially inward. The scroll compressor according to the present disclosure includes a shaft rotatable about an axis, a motor that drives and rotates the shaft, a compressor body driven by the rotation of the shaft, a housing that covers the motor and the compressor body and has a bottom surface that faces the motor from the axial direction, a suction port that guides a refrigerant into the housing, and a heat dissipation fin formed on the bottom surface, extending in a flow direction of the refrigerant and having a plurality of fin pieces divided into a plurality of pieces in the flow direction, wherein the suction port extends in a direction that includes a tangential component of a circle centered on the axis when viewed from the axial direction, so that the refrigerant flows on the bottom surface from one side in a circumferential direction centered on the axis to the other side, and the heat dissipation fins extend radially inward as they move from one side in the circumferential direction to the other side centered on the axis, so as to approach the axis, and are provided in a plurality of circumferentially spaced relation, and the plurality of fin pieces in each of the heat dissipation fins have a smaller dimension in the flow direction as the fin pieces are located downstream in the flow direction. Effect of the Invention

[0008] According to the present disclosure, it is possible to provide a scroll compressor having improved cooling performance and strength. [Brief description of the drawings]

[0009] [Figure 1] 1 is a vertical sectional view of a scroll compressor according to a first embodiment of the present disclosure. FIG. [Diagram 2] 4A and 4B are diagrams showing the configuration of a bottom surface of a housing according to the first embodiment of the present disclosure. [Diagram 3] 13A and 13B are diagrams illustrating a modified example of the bottom surface of the housing according to the first embodiment of the present disclosure. [Figure 4] 13 is a diagram showing the configuration of a bottom surface of a housing according to a second embodiment of the present disclosure. FIG. [Diagram 5] 13A and 13B are diagrams showing the configuration of a bottom surface of a housing according to a third embodiment of the present disclosure. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0010] (Configuration of scroll compressor) A scroll compressor 100 according to an embodiment of the present disclosure will be described below with reference to Fig. 1 and Fig. 2. The scroll compressor 100 is used to compress a refrigerant for an air conditioner for a vehicle, for example. As shown in Fig. 1, the scroll compressor 100 includes a shaft 1, a motor 2, a compressor body 3, a housing 4, a cover 5, an upper bearing 6, a lower bearing 7, a drive bush 8, and a suction port 9.

[0011] (Shaft configuration) The shaft 1 extends along an axis O and is rotatable about the axis O. The shaft 1 has a shaft body 10, a small diameter portion 11, a large diameter portion 12, and an eccentric shaft portion 13. The shaft body 10 is cylindrical and has a center on the axis O. The shaft body 10 has a uniform diameter dimension over the entire area in the direction of the axis O. A rotor 21 (described later) of the motor 2 is attached to the outer circumferential surface of the shaft body 10.

[0012] A small diameter portion 11 is provided on one side (lower side) of the shaft body 10 in the direction of the axis O. The small diameter portion 11 is cylindrical and centered on the axis O, and has a smaller diameter dimension than the shaft body 10. The small diameter portion 11 is supported from one side (lower side) in the direction of the axis O by a lower bearing 7 attached to the housing 4.

[0013] A large diameter portion 12 is provided on the other side (upper side) of the shaft body 10 in the direction of the axis O. The large diameter portion 12 is cylindrical and centered on the axis O, and has a larger diameter dimension than the shaft body 10. The large diameter portion 12 is supported in the radial direction by an upper bearing 6 fixed to the housing 4.

[0014] An eccentric shaft portion 13 is provided further above the large diameter portion 12 (the other side in the direction of the axis O). The eccentric shaft portion 13 protrudes from the large diameter portion 12 toward the other side in the direction of the axis O. The eccentric shaft portion 13 is parallel to the axis O and has a cylindrical shape centered on an eccentric axis A that extends at a position radially displaced from the axis O. Therefore, when the shaft 1 rotates, the eccentric shaft portion 13 revolves (turns) around the axis O.

[0015] (Motor configuration) The motor 2 applies a rotational driving force to the shaft 1. The motor 2 has a rotor 21 and a stator 22. The rotor 21 is fixed to the shaft body 10. The rotor 21 is cylindrical with the axis O as its center. Although not shown in detail, the rotor 21 has a plurality of magnets. The stator 22 covers the rotor 21 from the outer periphery. The stator 22 is formed by stacking a plurality of steel plates in the direction of the axis O, and a plurality of coils are formed by winding copper wire around the stator 22.

[0016] When electricity is applied to the stator 22, an electromagnetic force is generated between the stator 22 and the rotor 21, and a rotational force about the axis O is applied to the rotor 21. As a result, the shaft 1 rotates about the axis O.

[0017] (Configuration of the compressor body) The compressor body 3 is driven by rotation of the shaft 1 by the motor 2. The compressor body 3 has a fixed scroll 31 and a movable scroll 32. The fixed scroll 31 has a disk-shaped first end plate 31A centered on the axis O, and a first spiral plate 31B provided on one side (lower side) of the first end plate 31A in the direction of the axis O. The first spiral plate 31B extends in a spiral shape centered on the axis O. The fixed scroll 31 is fixed to the housing 4.

[0018] The movable scroll 32 has a disk-shaped second end plate 32A, a second spiral plate 32B provided on the other side (upper side) of the second end plate 32A in the direction of the axis O, and a boss portion 32C. The second spiral plate 32B extends in a spiral shape centered on the axis O. The dimension of the second spiral plate 32B in the direction of the axis O is equal to the dimension of the first spiral plate 31B in the direction of the axis O. In this manner, the first spiral plate 31B and the second spiral plate 32B mesh with each other from the direction of the axis O, thereby forming a compression chamber between them.

[0019] The boss portion 32C is a cylindrical portion that protrudes from the second end plate 32A toward one side (downward) in the direction of the axis O. The boss portion 32C is attached to the eccentric shaft portion 13 of the shaft 1 via a drive bush 8. When the eccentric shaft portion 13 orbits about the axis O, an orbiting force is transmitted to the movable scroll 32 through the drive bush 8. As a result, the movable scroll 32 orbits about the axis O. Although not shown in detail, the rotation (autorotation) of the movable scroll 32 itself is regulated by an Oldham ring.

[0020] As the movable scroll 32 orbits, the volume of the compression chamber changes with time, and the refrigerant is compressed while being sent from the outside to the inside in the radial direction within the compression chamber, and the pressure of the refrigerant increases. The high-pressure refrigerant is guided into the housing 4 through an opening H formed in the first end plate 31A of the fixed scroll 31.

[0021] (Housing / Cover Configuration) The housing 4 is a cylindrical container with a bottom that accommodates the shaft 1, the motor 2, and the compressor body 3. Specifically, the housing 4 has a cylindrical housing body 41 centered on the axis O, a bottom portion 42 that closes an opening on one side in the direction of the axis O of the housing body 41, a lid portion 43 that closes an opening on the other side in the direction of the axis O, and the cover 5.

[0022] (Rib and heat sink configuration) Of the two surfaces in the thickness direction of the bottom portion 42, the surface facing the other side in the axial line O direction (i.e., the motor 2 side) is defined as a bottom surface 42A. As shown in FIG. 2, a plurality of ribs R and a plurality of heat dissipation fins F are formed on the bottom surface 42A.

[0023] The ribs R protrude from the bottom surface 42A toward the other side (upper side) in the direction of the axis O. The ribs R extend radially from the axis O. As an example, eight ribs R are provided. The ribs R are provided to suppress deformation of the housing 4 due to pressure on the suction side.

[0024] The heat dissipating fins F are arc-shaped about the axis O and are arranged at intervals in the radial and circumferential directions. That is, the heat dissipating fins F are divided into multiple parts in the circumferential direction. In other words, each heat dissipating fin F has multiple fin pieces f arranged in the circumferential direction. The fin pieces f protrude from the bottom surface 42A toward the other side (upper side) in the direction of the axis O, similar to the rib R. The protruding height of the fin pieces f (i.e., the dimension in the direction of the axis O) is greater than the protruding height of the rib R.

[0025] The radiating fin F located at the outermost position in the radial direction is the outer radiating fin F1. The radiating fin F located at the innermost position in the radial direction is the inner radiating fin F3. The radiating fin F located between the outer radiating fin F1 and the inner radiating fin F3 is the intermediate radiating fin F2.

[0026] In this embodiment, the number of divisions (the number of fin pieces f) of the heat dissipation fin F increases from the outer peripheral heat dissipation fin F1 to the inner peripheral heat dissipation fin F3. Furthermore, the circumferential dimension of the fin pieces f increases from the inner peripheral heat dissipation fin F3 to the outer peripheral heat dissipation fin F1.

[0027] The outer peripheral heat dissipating fin F1 extends from the end of the suction port 9 (described later) over a region of about 180° centered on the axis O when viewed from the direction of the axis O. On the other hand, the intermediate heat dissipating fin F2 and the inner peripheral heat dissipating fin F3 extend over a region of about 180° centered on the axis O from a circumferential position farther away from the suction port 9 than the outer peripheral heat dissipating fin F1. Some of these heat dissipating fins F overlap with the rib R in the circumferential direction. In other words, some of the fin pieces f are molded integrally with the rib R.

[0028] 1 again, the surface of the bottom portion 42 opposite to the bottom surface 42A (i.e., the surface facing outward) is the back surface 42B. The cover 5 is attached to the back surface 42B. Electrical equipment E including an IPM (intelligent power module) and the like is disposed on the back surface 42B and is covered from the outside by the cover 5.

[0029] (Intake port configuration) The housing body 41 is provided with a suction port 9 for introducing the refrigerant from the outside into the housing 4. The suction port 9 communicates the inside and outside of the housing body 41 and introduces the refrigerant toward the bottom surface 42A. As shown in FIG. 2, the suction port 9 extends in a direction including a tangential component of the circle formed by the bottom surface 42A when viewed from the axis O direction. Therefore, the refrigerant flows in a circumferential direction around the axis O on the bottom surface 42A. That is, the heat dissipation fins F are arranged in the direction in which the refrigerant flows (arrow Df in FIG. 2). The flow rate of the refrigerant is higher on the outer periphery side of the bottom surface 42A than on the inner periphery side. That is, since the dimension of the fin piece f in the flow direction is larger toward the outer periphery heat dissipation fin F1 as described above, it can be said that the dimension of the fin piece f is larger in the region where the refrigerant flow rate is higher.

[0030] (Action and effect)

[0031] Here, when providing the above-mentioned heat dissipating fins F, depending on their shape and arrangement, the following problems may occur. For example, if the bottom surface 42A of the housing 4 is deformed by the pressure on the suction side, a large stress may be generated in the heat dissipating fins F, which may cause breakage. In addition, when manufacturing the housing 4 by casting, there is a problem that defects including cracks and voids may occur due to the increased thickness caused by forming the heat dissipating fins F.

[0032] On the other hand, in this embodiment, the heat dissipation fins F are divided into multiple pieces in the flow direction of the refrigerant. This divides the boundary layer components of the flow along the surface of the heat dissipation fins F in the flow direction. As a result, multiple leading edge effects can be obtained for each heat dissipation fin F. This improves the cooling effect of the refrigerant on the bottom surface 42A (housing 4). (Note that the leading edge effect here refers to the phenomenon in which the thermal efficiency is highest at the location where the heat medium first collides.) Furthermore, if the heat dissipating fin F is not divided, deformation of the bottom surface 42A will cause a large stress between the bottom surface 42A and the center of the heat dissipating fin F, which may damage the heat dissipating fin F. However, according to the above configuration, the heat dissipating fin F is divided into multiple pieces, so that even if deformation occurs in the bottom surface 42A, the stress generated in each divided heat dissipating fin F can be kept small. This can improve the strength of the housing 4.

[0033] Furthermore, according to the above configuration, the size of the divided heat dissipation fins F (fin pieces f) in the flow direction is larger in the outer peripheral region where the flow velocity is higher. This allows the leading edge effect to be generated the appropriate number of times according to the flow velocity distribution. As a result, the cooling effect of the refrigerant on the bottom surface 42A (housing 4) can be further improved.

[0034] In addition, according to the above configuration, since multiple ribs R are provided, even if stress occurs on the bottom surface 42A (housing 4) due to the pressure on the suction side, the stress can be sufficiently resisted. Furthermore, the protruding height of the ribs R from the bottom surface 42A is smaller than the protruding height of the heat dissipating fins F. This reduces the possibility that the ribs R will obstruct the flow of the refrigerant at the tips of the heat dissipating fins F.

[0035] The first embodiment of the present disclosure has been described above. Note that various changes and modifications can be made to the above configuration without departing from the gist of the present disclosure.

[0036] For example, as shown in FIG. 3, it is also possible to change the flow direction of the refrigerant through the suction port 9 (i.e., the direction in which the radiating fins F' extend). Specifically, each radiating fin F' extends radially inward from one circumferential side (i.e., the side from which the refrigerant flows) toward the other side (the side from which the refrigerant flows away). A plurality (eight) of such radiating fins F' are arranged at intervals in the circumferential direction. Also, each radiating fin F' is divided into a plurality of parts in the refrigerant flow direction. In other words, each radiating fin F' has a plurality of fin pieces f' arranged in the flow direction. Of the plurality of fin pieces f', the fin pieces f' on the outer periphery where the refrigerant flow speed is higher have a larger dimension in the flow direction. With this configuration, it is possible to obtain the same effects as those of the first embodiment.

[0037] Second Embodiment Next, a second embodiment of the present disclosure will be described with reference to Fig. 4. Note that the same components as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted.

[0038] As shown in the figure, in this embodiment, the heat dissipating fin Fb extends in the circumferential direction centered on the axis O and is divided into a plurality of parts in the circumferential direction. That is, the heat dissipating fin Fb has a plurality (eight) of fin pieces fb arranged in the circumferential direction. Such heat dissipating fins Fb are provided in a plurality of rows (four rows) spaced apart in the radial direction. The divided heat dissipating fins located radially outward have larger dimensions in the flow direction. Furthermore, each fin piece fb is provided between a pair of ribs R adjacent in the circumferential direction. In other words, each fin piece fb and the rib R do not overlap in the circumferential direction. More specifically, a gap is formed in the circumferential direction between the fin piece fb and the rib R.

[0039] According to the above configuration, the heat dissipating fins F are provided between the ribs R. In other words, the heat dissipating fins F and the ribs R do not overlap in the circumferential direction. This causes turbulence in the flow of the refrigerant as it passes through the ribs R, and the refrigerant collides with the heat dissipating fins F in an accelerated state. As a result, the cooling effect of the heat dissipating fins F can be further improved. Furthermore, since the ribs R and the heat dissipating fins F are independent, no thick portions are formed. This can also reduce the possibility of defects occurring when the housing 4 is formed by casting.

[0040] The second embodiment of the present disclosure has been described above. Note that various changes and modifications can be made to the above configuration without departing from the gist of the present disclosure.

[0041] <Third embodiment> Next, a third embodiment of the present disclosure will be described with reference to Fig. 5. Note that the same components as those in the above-described embodiments are given the same reference numerals, and detailed description thereof will be omitted.

[0042] As shown in the figure, in this embodiment, the ribs R' are formed at different circumferential positions on the heat dissipation fins Fb similar to those in the second embodiment. Specifically, each rib R' is formed to overlap the heat dissipation fin Fb in the circumferential direction. In other words, four fin pieces fb and one rib R' are formed integrally.

[0043] According to the above configuration, the heat dissipating fins F and the ribs R overlap in the circumferential direction, so that the apparent volume of the heat dissipating fins F is increased. This can further improve the cooling effect of the heat dissipating fins F. In addition, when the bottom surface 42A is deformed, the stress generated in the heat dissipating fins F can be distributed to the ribs R as well, so that the possibility of the heat dissipating fins F being damaged can be further reduced.

[0044] The third embodiment of the present disclosure has been described above. Note that various changes and modifications can be made to the above configuration without departing from the gist of the present disclosure.

[0045] For example, the second and third embodiments described above can be combined and applied to each region of the bottom surface 42A.

[0046] <Additional Notes> The scroll compressor 100 described in each embodiment can be understood, for example, as follows.

[0047] (1) A scroll compressor 100 according to a first embodiment includes a shaft 1 rotatable about an axis O, a motor 2 that drives and rotates the shaft 1, a compressor body 3 that is driven by the rotation of the shaft 1, a housing 4 that covers the motor 2 and the compressor body 3 and has a bottom surface 42A that faces the motor 2 from the direction of the axis O, a suction port 9 that introduces a refrigerant into the housing 4, and heat dissipation fins F that are formed on the bottom surface 42A, extend in the flow direction of the refrigerant, and are divided into a plurality of parts in the flow direction.

[0048] According to the above configuration, the heat dissipating fins F are formed on the bottom surface 42A, and the heat dissipating fins F are divided into multiple parts in the flow direction of the refrigerant. This divides the boundary layer components of the flow along the surface of the heat dissipating fins F in the flow direction. As a result, multiple leading edge effects can be obtained for each heat dissipating fin F. This makes it possible to improve the cooling effect of the bottom surface 42A (housing 4) by the refrigerant. (Note that the leading edge effect here refers to the phenomenon in which the thermal efficiency is highest at the location where the heat medium first collides.) Furthermore, if the heat dissipating fin F is not divided, deformation of the bottom surface 42A will cause a large stress between the bottom surface 42A and the center of the heat dissipating fin F, which may damage the heat dissipating fin F. However, according to the above configuration, the heat dissipating fin F is divided into multiple pieces, so that even if deformation occurs in the bottom surface 42A, the stress generated in each divided heat dissipating fin F can be kept small. This can improve the strength of the housing 4.

[0049] (2) In the scroll compressor 100 according to the second embodiment, the divided heat dissipation fins F located in an area where the refrigerant flows at a higher velocity have larger dimensions in the flow direction.

[0050] According to the above configuration, the dimension of the divided heat dissipation fins F (fin pieces f) in the flow direction increases in the region where the flow velocity is high. This allows the leading edge effect to be generated an appropriate number of times according to the flow velocity distribution. As a result, the cooling effect of the refrigerant on the bottom surface 42A (housing 4) can be further improved.

[0051] (3) In the scroll compressor 100 of the third aspect, the heat dissipation fins F extend in an arc shape centered on the axis O and are arranged in a plurality of parts spaced apart in the radial direction, with the divided heat dissipation fins F located radially outward having larger dimensions in the flow direction.

[0052] According to the above configuration, when the flow direction of the coolant is the circumferential direction about the axis O, the leading edge effect can be more efficiently generated in accordance with the flow direction.

[0053] (4) In the scroll compressor 100 of the fourth aspect, the heat dissipation fins F extend radially inward from one side in the circumferential direction to the other side around the axis O, and are provided in multiple numbers spaced apart in the circumferential direction, with the divided heat dissipation fins F located radially outward having larger dimensions in the flow direction.

[0054] According to the above configuration, when the flow direction of the coolant is a direction toward the radially inward direction as it moves from one circumferential side to the other side, the leading edge effect can be generated more efficiently in accordance with the flow direction.

[0055] (5) The scroll compressor 100 according to the fifth aspect further includes a plurality of ribs R protruding from the bottom surface 42A and extending radially about the axis O, and the protruding height of the ribs R is smaller than the protruding height of the heat dissipation fins F.

[0056] According to the above configuration, since multiple ribs R are provided, even if stress occurs on the bottom surface 42A (housing 4) due to the pressure on the suction side, the stress can be sufficiently resisted. Furthermore, the protruding height of the ribs R from the bottom surface 42A is smaller than the protruding height of the heat dissipating fins F. This reduces the possibility that the ribs R will obstruct the flow of the refrigerant at the tips of the heat dissipating fins F.

[0057] (6) In the scroll compressor 100 according to the sixth aspect, the heat dissipating fin F is provided between a pair of the ribs R adjacent to each other in the circumferential direction.

[0058] According to the above configuration, the heat dissipating fins F are provided between the ribs R. In other words, the heat dissipating fins F and the ribs R do not overlap in the circumferential direction. This causes turbulence in the flow of the refrigerant as it passes through the ribs R, and the refrigerant collides with the heat dissipating fins F in an accelerated state. As a result, the cooling effect of the heat dissipating fins F can be further improved. Furthermore, since the ribs R and the heat dissipating fins F are independent, no thick portions are formed. This can also reduce the possibility of defects occurring when the housing 4 is formed by casting.

[0059] (7) In the scroll compressor 100 according to the seventh aspect, the heat dissipating fins F are provided so as to overlap with the ribs R in the circumferential direction.

[0060] According to the above configuration, the heat dissipating fins F and the ribs R overlap in the circumferential direction, so that the apparent volume of the heat dissipating fins F is increased. This can further improve the cooling effect of the heat dissipating fins F. In addition, when the bottom surface 42A is deformed, the stress generated in the heat dissipating fins F can be distributed to the ribs R as well, so that the possibility of the heat dissipating fins F being damaged can be further reduced. [Explanation of symbols]

[0061] 100 Scroll Compressor 1 Shaft 2 Motors 3 Compressor body 4. Housing 4S Inner surface 5 Cover 6 Upper bearing 7 Lower Bearing 8 Drive bush 9 Intake port 10 Shaft body 11 Small diameter section 12 Large diameter section 13 Eccentric shaft part 21 Rotor 22 Stator 31 Fixed Scroll 31A First end plate 31B First spiral plate 32 Movable scroll 32A Second end plate 32B Second spiral plate 32C boss part 41 Housing body 42 Bottom 42A Bottom 42B back side 43 Lid A Eccentric shaft f,f´,fb fin piece F, F´, Fb Heat dissipation fin F1 Peripheral heat dissipation fin F2 Intermediate heat dissipation fin F3 Inner heat dissipation fin H opening O axis P suction flow path R,R´ Rib

Claims

1. A shaft rotatable about an axis; A motor that rotates the shaft; a compressor body driven by rotation of the shaft; a housing that covers the motor and the compressor body and has a bottom surface that faces the motor in the axial direction; a suction port for introducing a refrigerant into the housing; a heat dissipation fin formed on the bottom surface, extending in a flow direction of the refrigerant, and divided into a plurality of fins in the flow direction; Equipped with The suction port extends in a direction including a tangential component of a circle centered on the axis when viewed from the axial direction, so that the refrigerant flows from one side to the other side in a circumferential direction centered on the axis on the bottom surface, The heat dissipation fins extend from the end of the suction port over a region of approximately 180° around the axis in the direction of refrigerant flow.

2. A shaft rotatable about an axis; A motor that rotates the shaft; a compressor body driven by rotation of the shaft; a housing that covers the motor and the compressor body and has a bottom surface that faces the motor in the axial direction; a suction port for introducing a refrigerant into the housing; a heat dissipation fin formed on the bottom surface, extending in a flow direction of the refrigerant, and divided into a plurality of fins in the flow direction; Equipped with The suction port extends in a direction including a tangential component of a circle centered on the axis when viewed from the axial direction, so that the refrigerant flows from one side to the other side in a circumferential direction centered on the axis on the bottom surface, The heat dissipation fins extend in an arc shape centered on the axis and are provided in multiple numbers spaced apart in the radial direction, the divided heat dissipation fins located radially outward have larger dimensions in the flow direction, and the divided fins located radially inward have a greater number of divisions.

3. A shaft rotatable about an axis; A motor that rotates the shaft; a compressor body driven by rotation of the shaft; a housing that covers the motor and the compressor body and has a bottom surface that faces the motor in the axial direction; a suction port for introducing a refrigerant into the housing; a heat dissipation fin formed on the bottom surface, extending in a flow direction of the coolant, and having a plurality of fin pieces divided into a plurality of pieces in the flow direction; Equipped with The suction port extends in a direction including a tangential component of a circle centered on the axis when viewed from the axial direction, so that the refrigerant flows from one side to the other side in a circumferential direction centered on the axis on the bottom surface, The heat dissipation fins extend radially inwardly from one side to the other side in the circumferential direction about the axis, and are provided at intervals in the circumferential direction. A scroll compressor in which the multiple fin pieces in each of the heat dissipation fins have smaller dimensions in the flow direction as the fin pieces are located more downstream in the flow direction.

4. The scroll compressor according to claim 1 , wherein the divided heat dissipation fins each have a larger dimension in the flow direction as they are positioned in an area where the refrigerant has a higher flow velocity.

5. 5. The heat sink according to claim 1, further comprising a plurality of ribs protruding from the bottom surface and extending radially from the axis line, the protruding height of the ribs being smaller than the protruding height of the heat sink fins. The scroll compressor according to any one of claims 1 to 5.

6. The scroll compressor according to claim 5 , wherein the heat dissipating fin is provided between a pair of the ribs adjacent in the circumferential direction.

7. 6. The heat dissipation fin according to claim 5, wherein the heat dissipation fin is provided so as to overlap the rib in the circumferential direction. Scroll compressor.

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