Motor unit

Abstract

To provide a motor unit which allows improvement in cooling performance.SOLUTION: A motor unit comprises: a motor; a housing which houses the motor; and a coolant path, provided inside the wall surface of the housing, through which a coolant circulates. The coolant path has: an inflow path which receives the coolant from the outside; a branch path, connected to the inflow path, into which the coolant flows from the inflow path; a first flow path, connected to the branch path, into which the coolant flows from the branch path; and a second flow path, connected to the branch path, into which the coolant flows from the branch path, and whose path length is shorter than that of the first flow path. The first flow path and the second flow path each have a structure in which a plurality of straight parts is serially connected by a plurality of bent parts. The cross section of each of the straight parts in the first flow path is larger than the cross section of each of the straight parts in the second flow path.SELECTED DRAWING: Figure 4

Description

[Technical Field]

[0001] The technology disclosed in the present specification relates to a motor unit. [Background Art]

[0002] Patent Document 1 discloses a motor unit including two systems of refrigerant paths, a first flow path and a second flow path. [Prior Art Documents] [Patent Documents]

[0003] [Patent Document 1] International Publication No. WO2023 / 074571 [Summary of the Invention] [Problem to be Solved by the Invention]

[0004] When there is a difference in path length between the first flow path and the second flow path, a difference in the amount of pressure loss occurs between the two flow paths. As a result, the flow rate balance between the two flow paths is disrupted, and an undesired difference in cooling capacity between the two flow paths may occur in some cases. [Means for Solving the Problem]

[0005] In a first aspect of the present technology, the motor unit includes a motor, a housing that accommodates the motor, and a refrigerant flow path provided within a wall surface of the housing and configured to allow a refrigerant to flow therethrough. The refrigerant flow path includes an inflow path that receives the refrigerant from the outside, a branch path connected to the inflow path and into which the refrigerant flows from the inflow path, a first flow path connected to the branch path and into which the refrigerant flows from the branch path, and a second flow path connected to the branch path, into which the refrigerant flows from the branch path, and having a shorter path length than the first flow path. The first flow path and the second flow path each have a structure in which a plurality of straight portions are connected in series by a plurality of bent portions. A cross-sectional area of the straight portion of the first flow path is larger than a cross-sectional area of the straight portion of the second flow path.

[0006] In the above configuration, the path length of the first flow path is longer than that of the second flow path. Furthermore, the cross-sectional area of ​​the straight section of the first flow path is larger than that of the straight section of the second flow path. This reduces the pressure loss in the first flow path compared to the case where the cross-sectional area of ​​the straight section of the first flow path is equal to that of the straight section of the second flow path. As the pressure loss in the first flow path is reduced, the flow rate of the refrigerant can be adjusted so that the flow rate of the refrigerant flowing into the first flow path increases. This makes it possible to appropriately set the balance of cooling capacity between the first and second flow paths. [Brief explanation of the drawing]

[0007] [Figure 1] This is a schematic cross-sectional view of motor unit 1. [Figure 2] This is a plan view of the fuselage section 33. [Figure 3] This is a plan view of the first cover 31. [Figure 4] This is an exploded view of the refrigerant flow path 40. [Figure 5] This is a magnified view of the enlarged region EA1 in Figure 2. [Figure 6] This is an enlarged view of the area near the branch road 42 in Example 2. [Figure 7] This is an enlarged view of the area near the branch road 42 in the modified example. [Modes for carrying out the invention]

[0008] In a second embodiment, in the first embodiment, the straight-line portion of the first flow path and the straight-line portion of the second flow path may extend in a direction parallel to the rotation axis of the motor.

[0009] In a third embodiment, in the first embodiment, the refrigerant flow path may further include an outlet for discharging refrigerant from the first and second flow paths. When viewed from the direction of the motor's rotation axis, the positions of the inlet and outlet may be different in the circumferential direction of the housing. The first flow path may be provided in a first region in the circumferential direction of the housing, extending from the inlet to the outlet on one side in the circumferential direction. The second flow path may be provided in a second region in the circumferential direction of the housing, extending from the inlet to the outlet on the other side in the circumferential direction.

[0010] According to the above configuration, the circumferential direction of the housing can be divided into a first region and a second region. The first region can then be cooled by a first flow path, and the second region can be cooled by a second flow path.

[0011] In a fourth embodiment, in the first embodiment, the housing may include a cylindrical body portion having a shape around the rotation axis of the motor, a first cover that closes a first end face of the body portion on one side of the rotation axis, and a second cover that closes a second end face of the body portion on the other side of the rotation axis. The straight portion of the first flow path and the straight portion of the second flow path may be formed in the body portion. The bent portion of the first flow path and the bent portion of the second flow path may be formed in the first cover and the second cover.

[0012] According to the above configuration, by covering both ends of the fuselage with the first and second covers, a structure can be realized in which multiple straight sections are connected in a series by multiple bent sections.

[0013] In the fifth embodiment, the torso portion may be a cast product, as in the fourth embodiment described above.

[0014] In the sixth embodiment, in the first embodiment described above, the cross-sectional area of ​​the bent portion of the first channel and the cross-sectional area of ​​the bent portion of the second channel may be equal.

[0015] According to the above configuration, the shape of the inner surface of the bent portion can be made common between the first flow path and the second flow path. It is possible to simplify the processing of the bent portion and improve the assemblability of the first cover and the second cover.

Example

[0016] (Configuration of Motor Unit 1) FIG. 1 shows a schematic cross-sectional view of the motor unit 1 according to the present embodiment. In FIG. 1, the z-axis direction is the vertical direction, and the x-axis direction and the y-axis direction are horizontal directions. The x-axis direction is the direction in which the rotating shaft 11 extends. The coordinate relationship is the same in the subsequent figures.

[0017] The motor unit 1 is mounted on an electric vehicle. Electric vehicles include hybrid vehicles and electric vehicles. In an electric vehicle, the motor 2 may be used as a traveling motor that generates power for propelling the vehicle, or may be used as a generator that generates electric power by regenerative braking force or surplus power of the engine. In an electric vehicle, the motor unit 1 is mounted such that the negative direction of the z-axis coincides with the direction of gravity.

[0018] The motor unit 1 mainly includes a motor 2, a housing 30, and a coolant flow path 40. The coolant in the present embodiment is, for example, water. The motor 2 mainly includes a rotor 10 and a stator 20. The rotor 10 has a rotating shaft 11. The rotor 10 is fixed to the rotating shaft 11. The stator 20 includes a stator core 21 and coils 22. The stator core 21 is a substantially annular member made of laminated steel sheets or the like. The stator core 21 is provided with a central axis CA. The central axis CA of the stator core 21 coincides with the central axis of the rotating shaft 11. The stator core 21 has a cylindrical shape centered on the central axis CA.

[0019] The housing 30 is a member that accommodates the rotor 10 and the stator 20. The housing 30 includes a first cover 31, a second cover 32, and a body portion 33. The body portion 33 has a cylindrical shape around the rotating shaft 11 of the motor 2. The central axis CA of the housing 30 is common with the central axis of the rotating shaft 11. The manufacturing method and material of the body portion 33 can be appropriately selected. In the present embodiment, the body portion 33 is a cast product. The first cover 31 closes the first end surface 33E1 of the body portion 33 on one side of the rotating shaft 11 (the +x direction side). The second cover 32 closes the second end surface 33E2 of the body portion 33 on the other side of the rotating shaft 11 (the -x direction side). The rotating shaft 11 is supported by the housing 30 via a bearing 34 and is rotatable.

[0020] (Configuration of Refrigerant Flow Path 40) The refrigerant flow path 40 will be described with reference to FIGS. 2 to 5. The refrigerant flow path 40 is provided in the wall surface of the housing 30, and is a flow path configured to allow refrigerant to circulate therethrough. FIG. 2 is a plan view of the first end surface 33E1 of the body portion 33 as viewed from the +x direction side. In FIG. 2, for ease of understanding, the positions of the inflow path 41, the branch paths 42, the confluence path 45, and the discharge port 46 are indicated by alternate long and short dash lines. FIG. 3 is a plan view of the joint surface of the first cover 31 as viewed from the -x direction side. FIG. 4 is a developed view of the refrigerant flow path 40. Note that FIG. 4 is a schematic view, and there are portions that differ from actual dimensions.

[0021] The refrigerant flow path 40 comprises an inlet passage 41, a branch passage 42, a first flow path 43, a second flow path 44, a confluence passage 45, and an outlet 46. The inlet passage 41, branch passage 42, confluence passage 45, and outlet 46 are formed in the first cover 31. The inlet passage 41 is a flow path that receives refrigerant from the outside. The inlet passage 41 is connected to the branch passage 42. Refrigerant flows into the branch passage 42 from the inlet passage 41. The first flow path 43 and the second flow path 44 are connected to the branch passage 42 (see Figure 4, dotted arrow). Refrigerant flows into the first flow path 43 and the second flow path 44 from the branch passage 42 (see Figure 4, arrow Y1). The outlets of the first flow path 43 and the second flow path 44 are connected to the confluence passage 45, as well as the outlet 46. Refrigerant flows into the confluence passage 45 from the first flow path 43 and the second flow path 44 (see Figure 4, arrow Y2). The refrigerant that flows into the confluence channel 45 is discharged to the outside through the outlet 46.

[0022] The first flow path 43 comprises straight sections 43s1-43s6 and bent sections 43b1-43b5. The straight sections 43s1-43s6 are formed in the body section 33 and extend parallel to each other in a direction parallel to the rotation axis 11 (x-axis direction). The ±x ends of the straight sections 43s1-43s6 are connected by bent sections 43b1-43b5. The bent sections 43b2 and 43b4 connecting the +x end have groove shapes formed in the first cover 31. The bent sections 43b1, 43b3 and 43b5 connecting the -x end have groove shapes formed in the second cover 32. By fixing the first cover 31 and the second cover 32 to the body section 33 with fastening members (not shown), the first flow path 43, which is a series of continuous paths, is formed (see Figure 4, dotted arrow).

[0023] Similarly, the second flow path 44 comprises straight sections 44s1-43s4 and bent sections 44b1-44b3. The straight sections 44s1-43s4 are formed in the body section 33 and extend parallel to each other in a direction parallel to the rotation axis 11 (x-axis direction). The ±x ends of the straight sections 44s1-43s4 are connected by bent sections 44b1-44b3. The bent section 44b2 connecting the +x end has a groove shape formed in the first cover 31. The bent sections 44b1 and 44b3 connecting the -x end have groove shapes formed in the second cover 32. By fixing the first cover 31 and the second cover 32 to the body section 33 with fastening members (not shown), the second flow path 44, which is a series of continuous paths, is formed (see Figure 4, dotted arrow).

[0024] The cross-sectional area of ​​the straight section 43s1-43s6 of the first channel 43 is larger than the cross-sectional area of ​​the straight section 44s1-43s4 of the second channel 44. Furthermore, the grooves forming the bent sections 43b1-43b5 of the first channel 43 and the grooves forming the bent sections 44b1-44b3 of the second channel 44 all have the same shape. Therefore, the cross-sectional areas of the bent sections 43b1-43b5 and the cross-sectional areas of the bent sections 44b1-44b3 are all equal.

[0025] As shown in Figure 2, when viewed from the direction of the rotation axis (x direction), the positions of the inlet passage 41 and the outlet 46 are different in the circumferential direction of the housing 30. Here, we define a first region R1 and a second region R2. The first region R1 is the region in the circumferential direction of the housing 30 from the inlet passage 41 toward one side in the circumferential direction (counterclockwise side in Figure 2) toward the outlet 46. The second region R2 is the region in the circumferential direction of the housing 30 from the inlet passage 41 toward the other side in the circumferential direction (clockwise side in Figure 2) toward the outlet 46. The first flow path 43 is located in the first region R1. The second flow path 44 is located in the second region R2. The second region R2 is smaller than the first region R1. Also, the path length of the second flow path 44 is shorter than that of the first flow path 43.

[0026] (Structure of branch road 42) Figure 5 shows an enlarged view of the enlarged region EA1 in Figure 2. The enlarged region EA1 is the area near the branching channel 42. The upper part of Figure 5 is a plan view from the x-direction. In the upper plan view of Figure 5, the positions of the branching channel 42 and the inlet 42i are indicated by dashed lines. The lower part of Figure 5 is a cross-sectional view along line BB of the upper plan view of Figure 5.

[0027] An inlet 42i, a first outlet 42d1, and a second outlet 42d2 are defined on the inner surface of the branch passage 42. The inlet 42i is an opening through which refrigerant flows in from the inlet passage 41. The first outlet 42d1 is an opening through which refrigerant flows out to the straight section 43s1, which is the inlet of the first flow path 43. The second outlet 42d2 is an opening through which refrigerant flows out to the straight section 44s1, which is the inlet of the second flow path 44. The area of ​​the first outlet 42d1 is larger than the area of ​​the second outlet 42d2. The first outlet 42d1 and the second outlet 42d2 are located adjacent to each other on the first end face 33E1 of the body section 33. The inlet 42i of the branch passage 42 is located on the first cover 31, facing the first outlet 42d1 and the second outlet 42d2.

[0028] The first outlet 42d1 is the overlapping region of the opening area of ​​the straight section 43s1 and the opening area of ​​the branching passage 42 when viewed from the x-axis direction. The second outlet 42d2 is the overlapping region of the opening area of ​​the straight section 44s1 and the opening area of ​​the branching passage 42 when viewed from the x-axis direction. In the example of the plan view at the top of Figure 5, the entire opening area of ​​the straight section 43s1 and the entire opening area of ​​the straight section 44s1 are included in the opening area of ​​the branching passage 42. Therefore, the opening area of ​​the straight section 43s1 corresponds to the first outlet 42d1, and the opening area of ​​the straight section 44s1 corresponds to the second outlet 42d2.

[0029] Here, as shown in the plan view at the top of Figure 5, we consider the center CP0 of the inlet 42i, the center CP1 of the first outlet 42d1, and the center CP2 of the second outlet 42d2 when viewed from the direction of the rotation axis 11 (x direction). As shown in the cross-sectional view at the bottom of Figure 5, the distance CD1 between centers CP0 and CP1 is smaller than the distance CD2 between centers CP0 and CP2.

[0030] Furthermore, as shown in the cross-sectional view at the bottom of Figure 5, we consider the shortest distance SD1 from the inlet 42i to the first outlet 42d1, and the shortest distance SD2 from the inlet 42i to the second outlet 42d2. The shortest distance SD1 is smaller than the shortest distance SD2. Note that the shortest distance is the shortest distance in the path through which the refrigerant flows. For example, if a virtual straight line is drawn connecting the inlet 42i to the first outlet 42d1, the minimum length of the virtual straight line corresponds to the shortest distance SD1.

[0031] (effect) Let me explain the problem. When there is a difference in path length between the first flow path 43 and the second flow path 44, a difference in pressure loss occurs between the two flow paths. As a result, an undesirable difference in cooling capacity occurs between the two flow paths, and the motor 2 may not be cooled uniformly. In addition, since the refrigerant pumping capacity needs to be increased to match the flow path with the larger pressure loss, the pumping pump (not shown) may become unnecessarily large. Therefore, in the technology described herein, the cross-sectional area of ​​the straight section 43s1-43s6 of the first flow path 43 is made larger than the cross-sectional area of ​​the straight section 44s1-43s4 of the second flow path 44. This makes it possible to reduce the pressure loss in the first flow path 43 compared to the case where the cross-sectional area of ​​the straight section 43s1-43s6 is equal to the cross-sectional area of ​​the straight section 44s1-43s4. Consequently, the flow rate of refrigerant flowing into the first flow path 43 can be made larger than the flow rate of refrigerant flowing into the second flow path 44. As a result, the refrigerant flow rate distribution can be adjusted so that the refrigerant flow rate in the first flow path 43 becomes larger. This makes it possible to appropriately set the balance of cooling capacity between the first flow path 43 and the second flow path 44, thereby enabling uniform cooling of the motor 2. In addition, since the difference in pressure loss between the first flow path 43 and the second flow path 44 can be reduced, it becomes possible to suppress the unnecessary increase in the size of the pressure pump.

[0032] For example, consider a case where the pressure loss in the first channel 43, which has a longer flow path length, is reduced by increasing the cross-sectional area of ​​the bent section. In this case, as shown in Figure 4, one possible method is to remove multiple regions CR located on the end face of the partition wall separating the straight sections by machining. However, this increases the number of steps and leads to a deterioration in the yield of the base material. On the other hand, the technology described herein makes it possible to reduce the pressure loss in the first channel 43 by appropriately setting the relative sizes of the cross-sectional areas of the straight sections 43s1-43s6 and the straight sections 44s1-43s4. Since additional processes such as machining of the partition wall are unnecessary, it is possible to reduce manufacturing costs and improve yield.

[0033] In the technology described herein, the cross-sectional area of ​​the straight section 43s1-43s6 of the first channel 43 is made larger than the cross-sectional area of ​​the straight section 44s1-43s4 of the second channel 44. This makes it possible to reduce the arrangement density of the first channel 43 compared to the arrangement density of the second channel 44 while maintaining the same area ratio of the channels to the outer circumference of the housing 30 between the first channel 43 and the second channel 44. As a result, the number of straight sections of the first channel 43 can be reduced, making it possible to reduce the number of bends (i.e., the number of bends). This reduces the bending resistance in the first channel 43, making it possible to reduce the pressure loss in the first channel 43.

[0034] (Example 1, Modified Version) The positional and area relationships between the inlet 42i, the first outlet 42d1, and the second outlet 42d2 can be changed in various ways. For example, in Figure 5, the area of ​​the first outlet 42d1 and the area of ​​the second outlet 42d2 may be equal. In this configuration as well, the flow rate distribution of the refrigerant can be adjusted so that the refrigerant flow rate in the first flow path 43 becomes larger by having a relationship where distance CD1 is smaller than distance CD2, or where the shortest distance SD1 is smaller than the shortest distance SD2.

[0035] (Second variation of Example 1) The cross-sectional areas of the straight sections 43s1-43s6 of the first flow path 43 are not all constant and can be varied in various ways. For example, the straight section 43s6 closer to the outlet 46 may have a larger cross-sectional area than the straight section 43s1 closer to the inlet 41. Alternatively, the cross-sectional area may be gradually increased as the flow progresses from the straight section 43s1 to 43s6. The effects are explained below. As the refrigerant approaches the outlet 46, the heat absorption time increases and the temperature rises, thus reducing its cooling capacity. Therefore, by increasing the cross-sectional area of ​​the straight section closer to the outlet 46, the refrigerant flow velocity in the straight section closer to the outlet 46 can be reduced compared to the refrigerant flow velocity in the straight section closer to the inlet 41. This increases the residence time of the refrigerant in the straight section closer to the outlet 46, thereby increasing the cooling capacity in the straight section closer to the outlet 46. This makes it possible to suppress the difference in cooling capacity between the straight section closer to the outlet 46 and the straight section closer to the inlet 41. [Examples]

[0036] In Example 2, the positional and area relationships between the inlet 42i, the first outlet 42d1, and the second outlet 42d2 differ from those in Example 1. Components common to both Example 1 and Example 2 are denoted by the same reference numerals, and their explanations are omitted. Figure 6 shows an enlarged view of the vicinity of the branching channel 42 in Example 2. The area shown in Figure 6 is the same as the area shown in Figure 5 of Example 1.

[0037] In Example 2, the cross-sectional area of ​​the straight section 43s1 of the first channel 43 and the cross-sectional area of ​​the straight section 44s1 of the second channel 44 are the same. When the straight section 43s1 is viewed from the x-axis direction, the entire opening region of the straight section 43s1 is included in the opening region of the branching channel 42. Therefore, the area AR1 of the first outlet 42d1 is equivalent to the cross-sectional area of ​​the straight section 43s1. On the other hand, when the straight section 44s1 is viewed from the x-axis direction, only about half of the opening region of the straight section 44s1 is included in the opening region of the branching channel 42 (see region IR). Therefore, the area AR2 of the second outlet 42d2 is smaller than the cross-sectional area of ​​the straight section 44s1 and also smaller than the area AR1 of the first outlet 42d1.

[0038] Here, as shown in the plan view at the top of Figure 6, we consider the center CP0 of the inlet 42i, the center CP1 of the first outlet 42d1, and the center CP2 of the second outlet 42d2 when viewed from the direction of the rotation axis 11 (x direction). As shown in the cross-sectional view at the bottom of Figure 6, the distance CD1a between centers CP0 and CP1 is equivalent to the distance CD2a between centers CP0 and CP2.

[0039] Furthermore, as shown in the cross-sectional view at the bottom of Figure 6, we consider the shortest distance SD1a from the inlet 42i to the first outlet 42d1, and the shortest distance SD2a from the inlet 42i to the second outlet 42d2. The shortest distances SD1a and SD2a are equivalent.

[0040] As explained above, in Embodiment 2, in the relationship between the inlet 42i, the first outlet 42d1, and the second outlet 42d2, the area AR2 of the second outlet 42d2 is made smaller than the area AR1 of the first outlet 42d1. This makes it possible to reduce the pressure loss in the first flow path 43 even when the distances CD1a and CD2a are equal, or when the shortest distance SD1a and shortest distance SD2a are equal. In other words, by appropriately setting the area relationship between the first outlet 42d1 and the second outlet 42d2, it is possible to adjust the flow rate distribution of the refrigerant so that the refrigerant flow rate in the first flow path 43 becomes larger.

[0041] The specific examples of the technology disclosed in this specification have been described in detail above, but these are merely illustrative and do not limit the scope of the claims. The technology described in the claims includes various modifications and changes to the specific examples described above.

[0042] (Other variations) The positional relationship between the inlet 42i, the first outlet 42d1, and the second outlet 42d2 is not limited to the configuration described herein and can take various forms. That is, Figures 5 and 6 illustrate the case where the direction of the refrigerant flowing in from the inlet 42i and the direction of the refrigerant flowing out to the first outlet 42d1 and the second outlet 42d2 are all in the x direction. However, it is not limited to this configuration. As shown in the example in Figure 7, the inlet passage 41 may extend in the z direction, and the direction of the refrigerant flowing in from the inlet 42i may be in the z direction. In this case as well, the distance CD1b between the center CP0 of the inlet 42i and the center CP1 of the first outlet 42d1 may be smaller than the distance CD2b between the center CP0 and the center CP2 of the second outlet 42d2. Alternatively, the shortest distance SD1b from the inlet 42i to the first outlet 42d1 may be smaller than the shortest distance SD2b from the inlet 42i to the second outlet 42d2. This allows the flow rate distribution of the refrigerant to be adjusted so that the refrigerant flow rate in the first flow path 43 becomes larger.

[0043] The direction in which the straight sections 43s1-43s6 and 44s1-43s4 extend is not limited to the direction parallel to the rotation axis 11 (the x-axis direction). For example, they may extend diagonally at an angle with respect to the rotation axis. Alternatively, they may extend in a circumferential direction around the rotation axis 11.

[0044] Furthermore, the technical elements described herein or in the drawings demonstrate technical usefulness individually or in various combinations, and are not limited to the combinations described in the claims at the time of filing. In addition, the technologies illustrated herein or in the drawings can achieve multiple objectives simultaneously, and achieving even one of these objectives constitutes technical usefulness in itself. [Explanation of Symbols]

[0045] 1: Motor unit 2: Motor 30: Housing 40: Refrigerant flow path 41: Inlet path 42: Branch path 42i: Inlet 42d1: First outlet 42d2: Second outlet 43: First flow path 44: Second flow path 43s1-43s6, 44s1-43s4: Straight section 43b1-43b5, 44b1-44b3: Bending section CD1, CD2: Distance SD1, SD2: Shortest distance

Claims

1. Motor and, A housing for the motor, A refrigerant flow path is provided within the wall surface of the housing and configured for the flow of refrigerant, Equipped with, The refrigerant flow path is An inlet passage for receiving the refrigerant from the outside, A branch passage connected to the aforementioned inflow passage into which the refrigerant flows from the aforementioned inflow passage, A first flow path is connected to the aforementioned branch path, and the refrigerant flows into it from the aforementioned branch path, A second flow path is connected to the aforementioned branch path, into which the refrigerant flows from the aforementioned branch path, and which has a shorter path length than the first flow path, It is equipped with, The first and second channels have a structure in which a plurality of straight sections are connected in a series by a plurality of bent sections. The cross-sectional area of ​​the straight portion of the first channel is larger than the cross-sectional area of ​​the straight portion of the second channel. The cross-sectional area of ​​the bent portion of the first channel is equal to the cross-sectional area of ​​the bent portion of the second channel. Motor unit.

2. The motor unit according to claim 1, wherein the straight-line portion of the first flow path and the straight-line portion of the second flow path extend in a direction parallel to the rotation axis of the motor.

3. The refrigerant flow path further includes an outlet for discharging the refrigerant from the first flow path and the second flow path. When viewed from the direction of the rotation axis of the motor, the position of the inlet passage and the position of the outlet are different in the circumferential direction of the housing. The first flow path is provided in a first region in the circumferential direction of the housing, extending from the inlet to one side in the circumferential direction to the outlet. The motor unit according to claim 1, wherein the second flow path is provided in a second region in the circumferential direction of the housing, and extends from the inlet passage toward the other side in the circumferential direction to the outlet.

4. The aforementioned housing is A cylindrical body portion around the rotation axis of the motor, A first cover that covers the first end face of the body portion on one side of the rotating shaft, A second cover that closes the second end face of the body portion on the other side of the rotating shaft, It is equipped with, The straight-line portion of the first channel and the straight-line portion of the second channel are formed in the body portion, The motor unit according to claim 1, wherein the bent portion of the first channel and the bent portion of the second channel are formed in the first cover and the second cover.

5. The motor unit according to claim 4, wherein the fuselage portion is a cast product.

Images