Scroll compressor

Abstract

The scroll compressor of the present invention comprises: a shaft capable of rotating around an axis; a motor for driving the shaft to rotate; a compressor body driven by the rotation of the shaft; a shell covering the motor and the compressor body and having a bottom surface opposite to the motor in the axial direction; an intake port for guiding refrigerant into the shell; and a heat sink formed on the bottom surface, extending along the flow direction of the refrigerant, and divided into a plurality of fins in the flow direction.

Description

Technical Field

[0001] The present invention relates to a scroll compressor. This application claims priority based on Japanese Patent Application No. 2020-174866 filed on October 16, 2020, the contents of which are incorporated herein by reference. Background Art

[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, the use of intelligent power modules (IPM) as inverter circuits for driving scroll compressors has increased. At this time, compared with the existing inverter circuits, the heat density is increased, so it is necessary to improve the cooling performance. In the device described in Patent Document 1, the cooling performance is improved by providing a plurality of heat sinks on the back side (inner side) of the inverter in the housing.

[0004] Previous technical literature

[0005] Patent Literature

[0006] Patent Document 1: Japanese Patent No. 3976512 Summary of the invention

[0007] Technical issues to be solved by the invention

[0008] However, when the heat sink is provided as described above, the following problems may occur depending on its shape and arrangement. For example, when the bottom surface of the housing is deformed due to pressure, a large stress may be generated on the heat sink, thereby damaging the heat sink. In addition, when the housing is manufactured by casting, cracks or casting holes may occur due to the thickening of the wall caused by the formation of the heat sink.

[0009] The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide a scroll compressor having improved cooling performance and strength.

[0010] Means for solving technical problems

[0011] In order to solve the above-mentioned problems, the scroll compressor involved in the present invention comprises: a shaft capable of rotating around an axis; a motor for rotating and driving the shaft; a compressor body driven by the rotation of the shaft; a shell covering the motor and the compressor body and having a bottom surface opposite to the motor from the axis direction; an intake port for guiding refrigerant into the shell; and a heat sink formed on the bottom surface, extending along the flow direction of the refrigerant, and divided into multiple pieces in the flow direction.

[0012] Effects of the Invention

[0013] According to the present invention, it is possible to provide a scroll compressor having improved cooling performance and strength. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] Figure 1 It is a longitudinal sectional view of the scroll compressor concerning the first embodiment of the present invention.

[0015] Figure 2 It is a diagram showing the structure of the bottom surface of the casing according to the first embodiment of the present invention.

[0016] Figure 3 It is a diagram showing a modified example of the bottom surface of the casing according to the first embodiment of the present invention.

[0017] Figure 4 It is a diagram showing the structure of the bottom surface of a casing according to the second embodiment of the present invention.

[0018] Figure 5 It is a diagram showing the structure of the bottom surface of a casing according to the third embodiment of the present invention. DETAILED DESCRIPTION

[0019] (Structure of scroll compressor)

[0020] Below, reference Figure 1 and Figure 2 , a scroll compressor 100 according to an embodiment of the present invention will be described. The scroll compressor 100 is used, for example, to compress a refrigerant in a vehicle air conditioner. Figure 1 As shown, the scroll compressor 100 includes a shaft 1 , a motor 2 , a compressor body 3 , a casing 4 , a cover 5 , an upper bearing 6 , a lower bearing 7 , a driver bushing 8 , and a suction port 9 .

[0021] (Shaft structure)

[0022] The shaft 1 extends along the 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 centered on the axis O. The shaft body 10 has the same diameter size over the entire area in the direction of the axis O. A rotor 21 (described later) of the motor 2 is mounted on the outer peripheral surface of the shaft body 10.

[0023] 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 centered on the axis O and has a smaller diameter than the shaft body 10. The small diameter portion 11 is supported by a lower bearing 7 mounted on the housing 4 from one side (lower side) in the direction of the axis O.

[0024] 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 centered on the axis O and has a larger diameter than the shaft body 10. The large diameter portion 12 is supported radially by an upper bearing 6 fixed to the housing 4.

[0025] An eccentric shaft portion 13 is provided on the upper side (the other side in the direction of the axis O) of the large diameter portion 12. 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 cylindrical with an eccentric axis A as the center, and the eccentric axis A is parallel to the axis O and extends at a position radially deviated from the axis O. Therefore, when the shaft 1 rotates, the eccentric shaft portion 13 revolves (revolves) around the axis O.

[0026] (Motor structure)

[0027] The motor 2 imparts 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 the center. Although not shown in detail, the rotor 21 has a plurality of magnets. The stator 22 covers the rotor 21 from the outer peripheral side. 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 wires around it.

[0028] When the stator 22 is energized, 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.

[0029] (Structure of the compressor body)

[0030] The compressor body 3 is driven by the rotation of the shaft 1 caused by the motor 2. The compressor body 3 has a fixed scroll 31 and a movable scroll 32. The fixed scroll 31 has: a first end plate 31A in the shape of a disk centered on the axis O; and a first scroll plate 31B, which is arranged on one side (lower side) of the first end plate 31A in the direction of the axis O. The first scroll plate 31B extends in a spiral shape centered on the axis O. The fixed scroll 31 is fixed to the housing 4.

[0031] The movable scroll plate 32 has: a disc-shaped second end plate 32A; a second scroll plate 32B, which is arranged 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 scroll plate 32B extends in a spiral shape with the axis O as the center. The dimension of the second scroll plate 32B in the direction of the axis O is equivalent to the dimension of the first scroll plate 31B in the direction of the axis O described above. In this way, the first scroll plate 31B and the second scroll plate 32B are meshed from the direction of the axis O, so that a compression chamber is formed between the two.

[0032] The boss portion 32C is a cylindrical portion protruding from the second end plate 32A toward one side (lower side) in the direction of the axis O. The boss portion 32C is mounted on the eccentric shaft portion 13 of the shaft 1 via the driver bushing 8. The eccentric shaft portion 13 rotates around the axis O, so that the rotation force is transmitted to the movable scroll 32 through the driver bushing 8. As a result, the movable scroll 32 rotates around the axis O. In addition, although not shown in detail, the rotation (autorotation) of the movable scroll 32 itself is restricted by an Oldham ring.

[0033] The movable scroll 32 rotates, and the volume of the compression chamber changes with time. The refrigerant is compressed while being transported from the radial outside to the inside of the compression chamber, and its pressure rises. The high-pressure refrigerant is guided into the housing 4 through the opening H formed in the first end plate 31A of the fixed scroll 31.

[0034] (Structure of the housing / cover)

[0035] The housing 4 is a bottomed cylindrical container that accommodates the shaft 1, the motor 2, and the compressor body 3. Specifically, the housing 4 comprises: a cylindrical housing body 41 centered on the axis O; a bottom 42 that closes an opening on one side of the housing body 41 in the direction of the axis O; a cover 43 that closes an opening on the other side in the direction of the axis O; and a cover 5.

[0036] (Structure of ribs / heat sink)

[0037] Of the two surfaces in the thickness direction of the bottom 42, the surface facing the other side in the direction of the axis O (that is, the motor 2 side) is defined as the bottom surface 42A. Figure 2 As shown, a plurality of ribs R and a plurality of radiating fins F are formed on the bottom surface 42A.

[0038] 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 around 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.

[0039] The heat sink F is in an arc shape with the axis O as the center, and is arranged at intervals in the radial direction and the circumferential direction. That is, the heat sink F is divided into a plurality of pieces in the circumferential direction. In other words, each heat sink F has a plurality of heat sink pieces f arranged in the circumferential direction. The heat sink pieces f protrude from the bottom surface 42A toward the other side (upper side) in the direction of the axis O, similarly to the ribs R. The protruding height of the heat sink pieces f (that is, the dimension in the direction of the axis O) is greater than the protruding height of the ribs R.

[0040] The fins F located most radially outward are outer fins F1. The fins F located most radially inward are inner fins F3. The fins F disposed between the outer fins F1 and the inner fins F3 are intermediate fins F2.

[0041] In this embodiment, the number of fins F divided (the number of fin bodies f) increases from the outer fins F1 toward the inner fins F3. The circumferential dimension of the fin bodies f increases from the inner fins F3 toward the outer fins F1.

[0042] When the outer fin F1 is viewed from the axis O direction, it extends from the end of the suction port 9 described later to a region of about 180° with the axis O as the center. On the other hand, the intermediate fin F2 and the inner fin F3 extend from a circumferential position farther from the suction port 9 than the outer fin F1 to a region of about 180° with the axis O as the center. Some of these fins F overlap with the ribs R in the circumferential direction. That is, a part of the fin body f is integrally formed with the ribs R.

[0043] Again Figure 1 As shown, the surface of the bottom 42 opposite to the bottom surface 42A (i.e., the surface facing outward) is set as the back surface 42B. The cover 5 is installed on the back surface 42B. The electrical equipment E including the IPM (intelligent power module) is arranged on the back surface 42B and is covered by the cover 5 from the outside.

[0044] (Structure of the suction port)

[0045] The shell body 41 is provided with a suction port 9 for guiding the refrigerant from the outside into the shell 4. The suction port 9 communicates the inside and outside of the shell body 41 and guides the refrigerant toward the bottom surface 42A. Figure 2 As shown in FIG. 1 , when viewed from the axis O direction, the suction port 9 extends in a direction including a tangential component of the circle formed by the bottom surface 42A. Therefore, on the bottom surface 42A, the refrigerant flows in a circumferential direction centered on the axis O. That is, the heat sink F described above extends in the direction of the refrigerant flow ( Figure 2 The cooling fins F1 and the cooling fins F2 are arranged as shown in the arrow Df in the figure. Moreover, the flow velocity of the refrigerant is higher on the outer peripheral side of the bottom surface 42A than on the inner peripheral side. That is, as described above, the closer the outer peripheral cooling fins F1 are, the larger the size of the cooling fin body f in the flow direction Df is. Therefore, the larger the size of the cooling fin body f is in the area with higher flow velocity of the refrigerant.

[0046] (Effect)

[0047] Here, when the heat sink F is provided as described above, the following problems may occur depending on its shape and arrangement. For example, when the bottom surface 42A of the housing 4 is deformed due to the pressure on the suction side, a large stress may be generated on the heat sink F, thereby damaging the heat sink. In addition, when the housing 4 is manufactured by casting, defects such as cracks or casting holes may occur due to the wall thickness caused by forming the heat sink F.

[0048] On the other hand, in this embodiment, the heat sink F is divided into a plurality of parts in the flow direction Df of the refrigerant. As a result, the boundary layer component of the flow along the surface of the heat sink F is divided in the flow direction Df. As a result, each heat sink F can obtain multiple leading edge effects. Therefore, the cooling effect of the bottom surface 42A (shell 4) generated by the refrigerant can be improved. (In addition, the leading edge effect mentioned here refers to the phenomenon that the thermal efficiency is the highest at the part where the heat medium first collides.)

[0049] Furthermore, when the heat sink F is not divided, a large stress is generated between the center portion of the heat sink F and the bottom surface 42A as the bottom surface 42A deforms, which may damage the heat sink F. However, according to the above structure, since the heat sink F is divided into a plurality of pieces, even if the bottom surface 42A deforms, the stress generated in each of the divided heat sinks F can be suppressed to a small level. As a result, the strength of the housing 4 can be improved.

[0050] Moreover, according to the above structure, the larger the size of the divided heat sink F (heat sink body f) in the flow direction Df is in the peripheral area where the flow velocity is higher. Thus, the leading edge effect can be generated at an appropriate number of times according to the flow velocity distribution. As a result, the cooling effect of the bottom surface 42A (shell 4) generated by the refrigerant can be further improved.

[0051] Furthermore, according to the above structure, since a plurality of ribs R are provided, even when stress caused by the pressure on the suction side is generated on the bottom surface 42A (shell 4), the stress can be sufficiently resisted. Moreover, the protruding height of the ribs R from the bottom surface 42A is smaller than the protruding height of the heat sink F. Thus, the possibility that the flow of the refrigerant on the front end of the heat sink F is blocked by the ribs R can be reduced.

[0052] The first embodiment of the present invention has been described above. In addition, various changes or modifications can be made to the above-mentioned structure without departing from the gist of the present invention.

[0053] For example Figure 3As shown, the flow direction Df of the refrigerant based on the suction port 9 (i.e., the direction in which the heat sink F' extends) can also be changed. Specifically, each heat sink F' extends radially inward from one circumferential side (i.e., the side where the refrigerant flows in) toward the other side (the side where the refrigerant flows out). There are a plurality of (8) such heat sinks F' arranged at intervals in the circumferential direction. Moreover, each heat sink F' is divided into a plurality of heat sinks F' in the flow direction Df of the refrigerant. In other words, each heat sink F' has a plurality of heat sink bodies f' arranged along the flow direction Df. Among the plurality of heat sink bodies f', the heat sink body f' on the outer peripheral side where the flow velocity of the refrigerant is higher has a larger size in the flow direction Df. According to this structure, the same effect as the first embodiment described above can be obtained.

[0054] <Second Embodiment>

[0055] Next, refer to Figure 4 , a second embodiment of the present invention will be described. In addition, the same reference numerals are given to the same structures as those in the first embodiment, and detailed descriptions thereof will be omitted.

[0056] like Figure 4 As shown, in the present embodiment, the heat sink Fb extends in the circumferential direction with the axis O as the center, and is divided into a plurality of pieces in the circumferential direction. That is, the heat sink Fb has a plurality of (8) heat sink fin bodies fb arranged in the circumferential direction. Such heat sink Fb is arranged in multiple rows (4 rows) at intervals in the radial direction. The more the divided heat sink Fb is located radially outward, the larger the size in the flow direction Df. Moreover, each heat sink fin body fb is arranged between a pair of ribs R adjacent to each other in the circumferential direction. In other words, each heat sink fin body fb does not overlap with the rib R in the circumferential direction. In more detail, a gap is formed in the circumferential direction between the heat sink fin body fb and the rib R.

[0057] According to the above structure, the heat sink Fb is arranged between the ribs R. In other words, the heat sink Fb and the ribs R do not overlap in the circumferential direction. As a result, the flow of the refrigerant is disturbed when passing through the ribs R, and the refrigerant collides with the heat sink Fb in an accelerated state. As a result, the cooling effect generated by the heat sink Fb can be further improved. In addition, since the ribs R and the heat sink Fb are independent, no thick wall portion is generated. As a result, the possibility of a defect occurring when the housing 4 is formed by casting can also be reduced.

[0058] The second embodiment of the present invention has been described above. In addition, various changes or modifications can be made to the above-mentioned structure without departing from the gist of the present invention.

[0059] <Third Embodiment>

[0060] Next, refer to Figure 5, a third embodiment of the present invention will be described. In addition, the same reference numerals are given to the same structures as those in the above-mentioned embodiments, and detailed descriptions thereof will be omitted.

[0061] like Figure 5 As shown, in this embodiment, the ribs R' are formed at different circumferential positions relative to the heat sink Fb that is the same as the second embodiment. Specifically, each rib R' is formed in a manner overlapping with the heat sink Fb in the circumferential direction. That is, four heat sink pieces fb are formed integrally with one rib R'.

[0062] According to the above structure, since the heat sink Fb and the rib R' overlap in the circumferential direction, the apparent volume of the heat sink Fb becomes larger. As a result, the cooling effect generated by the heat sink Fb can be further improved. In addition, the stress generated in the heat sink Fb when the bottom surface 42A is deformed can also be dispersed to the rib R', so the possibility of damage to the heat sink Fb can be further reduced.

[0063] The third embodiment of the present invention has been described above. In addition, various changes or modifications can be made to the above-mentioned configuration without departing from the gist of the present invention.

[0064] For example, the second embodiment and the third embodiment described above can be applied in combination to each region of the bottom surface 42A.

[0065] <Notes>

[0066] The scroll compressor 100 described in each embodiment can be understood, for example, as follows.

[0067] (1) The scroll compressor 100 involved in the first embodiment comprises: a shaft 1 capable of rotating around an axis line O; a motor 2 for rotationally driving the shaft 1; a compressor body 3 driven by the rotation of the shaft 1; a shell 4 covering the motor 2 and the compressor body 3 and having a bottom surface 42A opposite to the motor 2 in the direction of the axis line O; an intake port 9 for guiding refrigerant into the shell 4; and heat sinks F, F′, Fb formed on the bottom surface 42A, extending along the flow direction Df of the refrigerant, and divided into a plurality of fins in the flow direction Df.

[0068] According to the above structure, a heat sink F is formed on the bottom surface 42A, and the heat sink F, F', Fb is divided into a plurality of parts in the flow direction Df of the refrigerant. As a result, the boundary layer component of the flow along the surface of the heat sink F is divided in the flow direction Df. As a result, each heat sink F, F1, Fb can obtain multiple leading edge effects. Therefore, the cooling effect of the bottom surface 42A (shell 4) generated by the refrigerant can be improved. (In addition, the leading edge effect mentioned here refers to the phenomenon that the thermal efficiency is the highest at the part where the heat medium first collides.)

[0069] Furthermore, when the heat sink F, F5, Fb is not divided, a large stress is generated between the center of the heat sink F, F1, Fb and the bottom surface 42A as the bottom surface 42A deforms, and the heat sink F, F', Fb may be damaged. However, according to the above structure, since the heat sink F, F', Fb is divided into a plurality of pieces, even if the bottom surface 42A deforms, the stress generated in each of the divided heat sinks F, F', Fb can be suppressed to a small level. As a result, the strength of the housing 4 can be improved.

[0070] (2) In the scroll compressor 100 according to the second aspect, the divided fins F, F', and Fb are larger in size in the flow direction Df as they are located in a region where the flow velocity of the refrigerant is higher.

[0071] According to the above structure, the higher the flow velocity is, the larger the size of the divided heat sink F, F', Fb (heat sink body f, f', fb) in the flow direction Df is. Thus, the leading edge effect can be generated in an appropriate number of times according to the flow velocity distribution. As a result, the cooling effect of the bottom surface 42A (shell 4) generated by the refrigerant can be further improved.

[0072] (3) In the scroll compressor 100 involved in the third embodiment, the heat sink F, Fb extends in an arc shape centered on the axis O, and a plurality of heat sink fins F, Fb are provided at intervals in the radial direction, and the more the divided heat sink fins F, Fb are located radially outward, the larger the size in the flow direction Df.

[0073] According to the above configuration, when the flow direction Df of the refrigerant is the circumferential direction with respect to the axis O, the leading edge effect can be more effectively generated according to the flow direction Df.

[0074] (4) In the scroll compressor 100 involved in the fourth embodiment, the heat sink F′ extends radially inward from one circumferential side to the other side with the axis O as the center, and a plurality of heat sinks F′ are arranged at intervals in the circumferential direction, and the more the divided heat sinks F′ are located radially outward, the larger the size of the divided heat sinks F′ in the flow direction Df.

[0075] According to the above configuration, when the flow direction Df of the refrigerant is directed radially inward as it moves from one circumferential side to the other side, the leading edge effect can be more effectively generated according to the flow direction Df.

[0076] (5) The scroll compressor 100 according to the fifth aspect further includes a plurality of ribs R, R' protruding from the bottom surface 42A and extending radially around the axis O, wherein the protruding height of the ribs R, R' is smaller than the protruding height of the fins F, F', Fb.

[0077] According to the above structure, since a plurality of ribs R and R' are provided, even when stress caused by the pressure on the suction side is generated on the bottom surface 42A (shell 4), the stress can be sufficiently resisted. Moreover, the protruding height of the ribs R and R' from the bottom surface 42A is smaller than the protruding height of the heat sinks F, F' and Fb. Thus, the possibility that the flow of the refrigerant on the front end of the heat sinks F, F' and Fb is blocked by the ribs R and R' can be reduced.

[0078] (6) In the scroll compressor 100 according to the sixth aspect, the heat dissipation fins Fb are provided between a pair of the ribs R adjacent to each other in the circumferential direction.

[0079] According to the above structure, the heat sink Fb is arranged between the ribs R. In other words, the heat sink Fb and the ribs R do not overlap in the circumferential direction. As a result, the flow of the refrigerant is disturbed when passing through the ribs R, and the refrigerant collides with the heat sink Fb in an accelerated state. As a result, the cooling effect generated by the heat sink Fb can be further improved. In addition, since the ribs R and the heat sink Fb are independent, no thick wall portion is generated. As a result, the possibility of a defect occurring when the housing 4 is formed by casting can also be reduced.

[0080] (7) In the scroll compressor 100 according to the seventh aspect, the heat dissipation fins Fb are provided so as to overlap with the ribs R' in the circumferential direction.

[0081] According to the above structure, since the heat sink Fb and the rib R' overlap in the circumferential direction, the apparent volume of the heat sink Fb becomes larger. As a result, the cooling effect generated by the heat sink Fb can be further improved. In addition, the stress generated in the heat sink Fb when the bottom surface 42A is deformed can also be dispersed to the rib R', so the possibility of damage to the heat sink Fb can be further reduced.

[0082] Industrial Applicability

[0083] The present invention relates to a scroll compressor. According to the present invention, a scroll compressor having improved cooling performance and strength can be provided.

[0084] Explanation of symbols

[0085] 100-Scroll compressor, 1-shaft, 2-motor, 3-compressor body, 4-housing, 4S-inner circumferential surface, 5-cover, 6-upper bearing, 7-lower bearing, 8-driver bushing, 9-intake port, 10-shaft body, 11-small diameter portion, 12-large diameter portion, 13-eccentric shaft portion, 21-rotor, 22-stator, 31-fixed scroll plate, 31A-first end plate, 31B-first scroll plate, 32-movable scroll plate, 3 2A-second end plate, 32B-second scroll plate, 32C-boss portion, 41-shell body, 42-bottom, 42A-bottom surface, 42B-back surface, 43-cover portion, A-eccentric shaft, Df-flow direction, f, f′, fb-heat sink body, F, F′, Fb-heat sink, F1-peripheral heat sink, F2-middle heat sink, F3-inner heat sink, H-opening portion, O-axis line, P-intake flow path, R, R′-ribs.

Claims

1. A scroll compressor comprising: A shaft, capable of rotation about an axis; A motor for driving the shaft to rotate; a compressor body driven by the rotation of the shaft; a housing covering the motor and the compressor body and having a bottom surface facing the motor in the axial direction; a heat sink formed on the bottom surface, extending along the flow direction of the refrigerant, and divided into a plurality of fins in the flow direction; and a suction port for guiding the refrigerant into the shell from an end of the suction port along a tangent direction tangent to the heat sink, The heat sink extends in an arc shape with the axis as the center, and a plurality of heat sinks are provided at intervals in the radial direction. The radially outermost peripheral heat sink extends over an area of ​​about 180° with the axis as the center from the end of the intake port when viewed from the axial direction. On the other hand, the heat sink located radially inner than the peripheral heat sink extends over an area of ​​about 180° with the axis as the center from a circumferential position farther from the intake port than the peripheral heat sink.

2. The scroll compressor according to claim 1, wherein: The divided fins located radially outward have larger dimensions in the flow direction.

3. The scroll compressor according to claim 1 or 2, wherein: The scroll compressor further includes a plurality of ribs protruding from the bottom surface and extending radially around the axis, wherein a protruding height of the ribs is smaller than a protruding height of the heat sink.

4. The scroll compressor according to claim 3, wherein: The heat sink is provided so as to overlap with the rib in the circumferential direction.

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