阅读说明：本技术 电动机的冷却装置 (Cooling device for electric motor ) 是由 山中健太郎 于 2019-06-12 设计创作，主要内容包括：本发明提供一种电动机的冷却装置,在壳体的圆筒部与电动机的定子之间插入有圆筒状的冷却套筒,从而在该冷却套筒与圆筒部之间形成冷却流体通路,冷却流体通路包括：翅片区域,其具有多个冷却通道；以及分流集管区域和合流集管区域,它们与冷却通道的周向两端部连通,在圆筒部设置有向分流集管区域导入冷却流体的冷却流体导入口和从合流集管区域导出冷却流体的冷却流体导出口,电动机的冷却装置至少实现了分流集管区域中冷却效率的提高。在分流集管区域(AB)和合流集管区域(AJ)中的至少分流集管区域(AB)中,在冷却套筒(14)的外表面形成有以沿着冷却流体的规定的流动方向的方式延伸的多个引导凹部(31A、31B、31C、31D、31E、31F)。(The present invention provides a cooling device for an electric motor, wherein a cylindrical cooling sleeve is inserted between a cylindrical part of a housing and a stator of the electric motor, so that a cooling fluid passage is formed between the cooling sleeve and the cylindrical part, the cooling fluid passage comprises: a fin region having a plurality of cooling channels; and a branch header region and a merge header region which communicate with both circumferential end portions of the cooling passage, and in which a cooling fluid inlet port for introducing the cooling fluid into the branch header region and a cooling fluid outlet port for discharging the cooling fluid from the merge header region are provided in the cylindrical portion, the cooling device of the motor achieves at least an improvement in cooling efficiency in the branch header region. At least in the flow dividing header region (AB) of the flow dividing header region (AB) and the flow merging header region (AJ), a plurality of guide concave portions (31A, 31B, 31C, 31D, 31E, 31F) extending along a predetermined flow direction of the cooling fluid are formed on the outer surface of the cooling sleeve (14).)

1. A cooling device of an electric motor, the electric motor (5) having a rotor (6) and a stator (7) surrounding the rotor (6), the electric motor (5) being housed in a case (8) having a cylindrical portion (8a) coaxial with a rotation axis of the electric motor (5), a cylindrical cooling sleeve (14) being inserted between the cylindrical portion (8a) of the case (8) and the stator (7), the cooling sleeve (14) having a partition wall (23) and a plurality of cooling fins (22) on an outer peripheral surface thereof, the plurality of cooling fins (22) extending in a circumferential direction and being arranged at intervals in an axial direction, the partition wall (23) being arranged between both ends of the cooling fins (22), the cooling fins (22) and the partition wall (23) being in contact with or close to an inner surface of the cylindrical portion (8a), a cooling fluid passage (25) being formed between the cooling sleeve (14) and the cylindrical portion (8a) The method comprises the following steps: a fin region (AF) having a plurality of cooling channels (26A, 26B, 26C, 26D, 26E, 26F) through which a cooling fluid flows along the plurality of cooling fins (22); and a branch header region (AB) and a merge header region (AJ) which are disposed on both sides of the partition wall (23) and communicate with both circumferential ends of the cooling passages (26A-26F), wherein the cylindrical portion (8a) is provided with a cooling fluid inlet port (27) for introducing a cooling fluid into the branch header region (AB) and a cooling fluid outlet port (28) for discharging the cooling fluid from the merge header region (AJ),

the cooling device of the electric motor is characterized in that,

at least in the flow dividing header region (AB) of the flow dividing header region (AB) and the flow merging header region (AJ), a plurality of guide concave portions (31A, 31B, 31C, 31D, 31E, 31F) extending along a predetermined flow direction of the cooling fluid are formed on the outer surface of the cooling sleeve (14).

2. The cooling apparatus of an electric motor according to claim 1,

a cooling fluid introduction port (27) is provided in the cylindrical portion (8a) at a portion corresponding to a corner of the flow-dividing header region (AB), a cooling fluid discharge port (28) is provided in the cylindrical portion (8a) at a portion corresponding to a corner of the flow-merging header region (AJ), and a plurality of the cooling fins (22) are formed such that: the distance between both ends of the cooling fin (22) and the partition wall (23) in the circumferential direction of the cooling sleeve (14) is reduced as the distance from the cooling fluid inlet (27) and the cooling fluid outlet (28) increases.

3. The cooling apparatus of an electric motor according to claim 2,

the peripheral edge shape of the guide recessed portions (31A-31F) is formed into an oblong shape that is long in the predetermined flow direction of the cooling fluid.

4. The cooling apparatus of an electric motor according to claim 2,

the guide recesses (31A-31F) are formed in a non-circular shape in which a plurality of arc portions are combined and which is long in the predetermined flow direction.

5. The cooling apparatus of an electric motor according to claim 3 or 4,

the guide concave portions (31A-31F) are formed in the flow dividing header region (AB) in the cooling sleeve (14) so as to be enlarged as the guide concave portions become farther from the cooling fluid inlet (27).

6. The cooling apparatus of an electric motor according to claim 5,

the guide recessed portions (31A-31F) are formed to extend into the cooling passages (26A-26F).

7. The cooling apparatus of an electric motor according to claim 5,

in the flow dividing header region (AB), a groove (32) extending along the partition wall (23) is formed in the outer surface of the cooling sleeve (14), and the groove (32) communicates with the partition wall (23) -side end portions of the plurality of guide concave portions (31A-31F) in common.

8. The cooling apparatus of an electric motor according to claim 6,

in the flow dividing header region (AB), a groove (32) extending along the partition wall (23) is formed in the outer surface of the cooling sleeve (14), and the groove (32) communicates with the partition wall (23) -side end portions of the plurality of guide concave portions (31A-31F) in common.

Technical Field

The present invention relates to a cooling device for an electric motor having a rotor and a stator surrounding the rotor, the electric motor being housed in a casing having a cylindrical portion coaxial with a rotation axis of the electric motor, a cylindrical cooling sleeve being inserted between the cylindrical portion of the casing and the stator, the cooling sleeve having a partition wall and a plurality of cooling fins on an outer circumferential surface, the plurality of cooling fins being arranged at intervals in an axial direction and extending in a circumferential direction, the partition wall being arranged between both ends of the plurality of cooling fins, the cooling fins and the partition wall being in contact with or closely opposed to an inner surface of the cylindrical portion, a cooling fluid passage being formed between the cooling sleeve and the cylindrical portion, the cooling fluid passage including: a fin region having a plurality of cooling channels for circulating a cooling fluid along a plurality of the cooling fins; and a flow dividing header region and a flow merging header region which are disposed on both sides of the partition wall and communicate with both circumferential end portions of the cooling passage, and the cylindrical portion is provided with a cooling fluid inlet port for introducing a cooling fluid into the flow dividing header region and a cooling fluid outlet port for discharging the cooling fluid from the flow merging header region.

Background

A cooling device for such a motor is known from patent document 1.

Disclosure of Invention

The present invention has been made in view of the above circumstances, and an object thereof is to provide a cooling device for an electric motor, which improves cooling efficiency at least in a manifold region.

Means for solving the problems

In order to achieve the above object, the present invention is a cooling device for an electric motor having a rotor and a stator surrounding the rotor, the electric motor being housed in a casing having a cylindrical portion coaxial with a rotation axis of the electric motor, a cylindrical cooling sleeve being inserted between the cylindrical portion of the casing and the stator, the cooling sleeve having a partition wall and a plurality of cooling fins on an outer circumferential surface, the plurality of cooling fins being arranged at intervals in an axial direction and extending in a circumferential direction, the partition wall being arranged between both ends of the cooling fins, the cooling fins and the partition wall being in contact with or closely opposed to an inner surface of the cylindrical portion, a cooling fluid passage being formed between the cooling sleeve and the cylindrical portion, the cooling fluid passage including: a fin region having a plurality of cooling channels for circulating a cooling fluid along a plurality of the cooling fins; and a flow dividing header region and a flow merging header region which are disposed on both sides of the partition wall and communicate with both circumferential end portions of the cooling passage, and in which a cooling fluid inlet port for introducing a cooling fluid into the flow dividing header region and a cooling fluid outlet port for leading out the cooling fluid from the flow merging header region are provided in the cylindrical portion, wherein a plurality of guide concave portions extending along a predetermined flow direction of the cooling fluid are formed in an outer surface of the cooling sleeve in at least the flow dividing header region and the flow merging header region.

A 2 nd aspect of the present invention is summarized as the configuration of the 1 st aspect, wherein the cooling fluid introduction port is provided in the cylindrical portion at a portion corresponding to a corner of the divergent header region, the cooling fluid discharge port is provided in the cylindrical portion at a portion corresponding to a corner of the convergent header region, and the plurality of cooling fins are formed such that: the distance between the partition wall and both ends of the cooling fin along the circumferential direction of the cooling sleeve is reduced as the distance from the cooling fluid inlet and the cooling fluid outlet increases.

A 3 rd aspect of the present invention is the cooling device according to the 2 nd aspect, wherein a peripheral edge shape of the guide recess is formed in an oval shape that is long in the predetermined flow direction of the cooling fluid.

A 4 th aspect of the present invention is the fluid container according to the 2 nd aspect, wherein the guide recess has a peripheral edge shape formed in a non-circular shape that is long in the predetermined flow direction and that combines a plurality of arc portions.

A 5 th aspect of the present invention is the cooling fluid supply device according to the 3 rd or 4 th aspect, wherein the guide concave portion is formed in the flow dividing header region so as to be enlarged with increasing distance from the cooling fluid introduction port.

The 6 th feature of the present invention is that, in addition to the structure of the 5 th feature, the guide recess is formed to extend into the cooling passage.

Further, according to a 7 th aspect of the present invention, in addition to the structure according to the 5 th or 6 th aspect, a groove extending along the partition wall is formed in an outer surface of the cooling sleeve in the flow distribution header region, and the groove communicates with end portions of the plurality of guide concave portions on the partition wall side in common.

Effects of the invention

According to the first aspect of the present invention, since the plurality of guide concave portions are formed on the outer surface of the cooling sleeve at least in the flow dividing header region, the contact area between the cooling fluid and the cooling sleeve in the flow dividing header region can be increased, and the cooling efficiency at least in the flow dividing header region can be improved, and further, since the guide concave portions extend along the predetermined flow direction of the cooling fluid, the cooling fluid can be smoothly flowed without being blocked.

Further, according to the 2 nd feature of the present invention, the cooling fluid introduction port and the cooling fluid discharge port are provided in the cylindrical portion of the casing at portions corresponding to corners of the diverging header region and the converging header region, and the intervals between the plurality of cooling fins and the partition wall decrease as they become farther from the cooling fluid introduction port and the cooling fluid discharge port, so that the flow cross-sectional area of the cooling fluid in the diverging header region decreases as the cooling fluid introduced from the cooling fluid introduction port is branched to the cooling passage, and the flow cross-sectional area of the cooling fluid flowing from the cooling passage into the converging header region increases as it approaches the cooling fluid discharge port. Therefore, the cooling fluid can be made to flow without stagnation so that the cooling fluid flow rate of each cooling passage is made uniform, and the heat distribution over the entire circumference of the motor can be equalized.

According to the feature 3 of the present invention, since the peripheral edge of the guide recessed portion is formed in the oval shape, the cooling fluid flows in a swirling manner around the peripheral edge of the guide recessed portion, and the cooling efficiency can be further improved.

According to the feature 4 of the present invention, since the peripheral edge of the guide recess is non-circular, the cooling fluid flows in a swirling manner around the peripheral edge of the guide recess, and the cooling efficiency can be further improved.

According to the 5 th aspect of the present invention, since the guide concave portion is increased in size as it is spaced apart from the cooling fluid inlet port, the flow rate of the cooling fluid in the distribution header region is decreased, and the distribution of the cooling fluid to the respective cooling passages can be equalized because the guide concave portion is increased in size.

According to the feature 6 of the present invention, since the guide recess extends into the cooling passage, the cooling fluid can be smoothly introduced into the cooling passage from the manifold region.

Further, according to the 7 th aspect of the present invention, since the groove communicating with the plurality of guide concave portions is formed on the outer surface of the cooling jacket so as to extend along the partition wall, the cooling fluid from the cooling fluid inlet can be smoothly flowed to the guide concave portions.

Drawings

Fig. 1 is a longitudinal sectional view of a motor and a cooling device.

FIG. 2 is a side view of a cooling sleeve.

Fig. 3 is a perspective view of a cooling sleeve.

Fig. 4 is a cross-sectional view taken along line 4-4 of fig. 2.

Description of the reference symbols

5: an electric motor;

6: a rotor;

7: a stator;

8: a housing;

8 a: a cylindrical portion;

14: cooling the sleeve;

22: cooling the fins;

23: a partition wall;

25: a cooling fluid passage;

26A, 26B, 26C, 26D, 26E, 26F: a cooling channel;

27: a cooling fluid introduction port;

28: a cooling fluid outlet;

31A, 31B, 31C, 31D, 31E, 31F: a guide recess;

32: a groove;

AB: a manifold area;

AF: a fin region;

AJ: a converging header region.

Detailed Description

Referring to fig. 1 to 4, an embodiment of the present invention will be described, first, in fig. 1, the motor 5 includes a rotor 6 and a cylindrical stator 7 surrounding the rotor 6, and the motor 5 is accommodated in a housing 8.

The housing 8 is formed of a light metal such as aluminum, and integrally includes: a cylindrical portion 8a coaxial with the rotation axis of the motor 5; a 1 st inward flange 8b that extends radially inward from one end (left end in fig. 1) of the cylindrical portion 8 a; a 1 st bearing housing portion 8c of a short cylindrical shape continuous with an inner periphery of the 1 st inward flange portion 8 b; a 1 st outward flange 8d that extends radially outward from the other end (right end in fig. 1) of the cylindrical portion 8 a; reinforcing ribs 8e provided so as to protrude from a plurality of portions (for example, 8 portions) of the outer periphery of the cylindrical portion 8a at equal intervals in the circumferential direction; and support projections 8f projecting radially outward from the 1 st outward flange 8d at a plurality of locations (for example, 4 locations) equally spaced in the circumferential direction of the cylindrical portion 8 a.

The reinforcing ribs 8e are provided in succession to the 1 st outward flange portion 8d so that the amount of projection from the cylinder portion 8a to the outside in the radial direction increases as going from one end portion to the other end portion of the cylinder portion 8a, and the support projection portion 8f projects from the 1 st outward flange portion 8d to the outside in the radial direction between the reinforcing ribs 8e adjacent to each other and paired in the circumferential direction of the 1 st outward flange portion 8 d.

One end of a rotating shaft 10 provided coaxially with the rotor 6 penetrates the center of the 1 st inward flange 8b, and a 1 st ball bearing 11 is interposed between the 1 st bearing housing 8c and the rotating shaft 10. Further, a resolver 12 surrounding a projecting portion of the rotating shaft 10 projecting from the 1 st inward flange portion 8b is supported at a central portion of the 1 st inward flange portion 8b, and a cover 13 covering one end portion of the rotating shaft 10 from the outside together with the resolver 12 is attached to an outer surface of the central portion of the 1 st inward flange portion 8 b.

Referring to fig. 2 and 3 together, a cylindrical cooling sleeve 14 is inserted between the cylindrical portion 8a of the housing 8 and the stator 7. An end portion of the cooling sleeve 14 on the opposite side to the 1 st inward flange portion 8b is integrally provided with: a 2 nd inward flange portion 14a that protrudes radially inward from the end portion (the end portion on the opposite side of the 1 st inward flange portion 8 b) of the cooling jacket 14; and a 2 nd outward flange portion 14b that protrudes outward in the radial direction so as to overlap the 1 st outward flange portion 8d of the housing 8 from the outside, a 2 nd bearing housing portion 14c having a short cylindrical shape is integrally formed on the inner periphery of the 2 nd inward flange portion 14a, a 2 nd ball bearing 24 interposed between the 2 nd ball bearing and the rotary shaft 10 is attached to the 2 nd bearing housing portion 14c, and attachment protrusions 14d that protrude outward in the radial direction so as to overlap the support protrusions 8f of the housing 8 from the outside are integrally provided at a plurality of locations (for example, 4 locations) of the 2 nd outward flange portion 14b that are spaced apart at equal intervals in the circumferential direction, and the attachment protrusions 14d protrude outward in the radial direction. The mounting projections 14d are fastened to the support projections 8f by a plurality of bolts 15, respectively.

The outer surface of the cooling sleeve 14 is provided with: an annular 1 st seal projection 18 having a 1 st seal groove 17 formed over the entire circumference, and an annular 1 st seal member 16 elastically contacting the inner surface of one end portion of the cylindrical portion 8a in the housing 8 being fitted into the 1 st seal groove 17; an annular 2 nd sealing protrusion 21 connected to the 2 nd outward flange 14b and having a 2 nd sealing groove 20 formed over the entire circumference, and an annular 2 nd sealing member 19 elastically contacting the inner surface of the other end of the cylindrical portion 8a being fitted into the 2 nd sealing groove 20; a plurality of (e.g., 5) cooling fins 22 extending in the circumferential direction and arranged between the 1 st and 2 nd sealing projections 18 and 21 at equal intervals; and a partition wall 23 disposed between both ends of the cooling fins 22 and connecting the 1 st sealing protrusion 18 and the 2 nd sealing protrusion 21.

The cooling fins 22 and the partition wall 23 protrude from the outer surface of the cooling sleeve 14 so as to abut against or closely face the inner surface of the cylindrical portion 8a in the housing 8, and the partition wall 23 is formed, for example, so as to be inclined so as to be positioned on one side in the circumferential direction as it approaches the 2 nd sealing protrusion 21 side from the 1 st sealing protrusion 18.

By inserting such a cooling sleeve 14 between the cylindrical portion 8a of the housing 8 and the stator 7, a cooling fluid passage 25 is formed between the cooling sleeve 14 and the cylindrical portion 8a, and the cooling fluid passage 25 includes: a fin region AF having a plurality of, for example, 6 cooling passages 26A, 26B, 26C, 26D, 26E, 26F through which a cooling fluid flows along the plurality of cooling fins 22; and a diverging header region AB and a converging header region AJ that are disposed on both sides of the partition wall 23 and communicate with both circumferential ends of the cooling passage 26.

A cooling passage 26A is formed between the 1 st sealing protrusion 18 and the cooling fin 22 closest to the 1 st sealing protrusion 18, cooling passages 26B to 26E are formed between the plurality of cooling fins 22, and a cooling passage 26F is formed between the 2 nd sealing protrusion 21 and the cooling fin 22 closest to the 2 nd sealing protrusion 21.

The cylindrical portion 8a of the housing 8 is provided with: a cooling fluid introduction port 27 disposed at a portion corresponding to a corner portion of the flow dividing header region AB; and a cooling fluid outlet 28 disposed at a portion corresponding to a corner of the merged pipe region, and a cooling fluid inlet pipe 29 connected to the cooling fluid inlet 27 and a cooling fluid outlet pipe 30 connected to the cooling fluid outlet 28 are connected to the cylindrical portion 8a so as to protrude laterally from the cylindrical portion 8 a.

Further, the plurality of cooling fins 22 are formed such that: the interval between the partition wall 23 and both ends of the cooling fin 22 in the circumferential direction of the cooling jacket 14 is reduced as the distance from the cooling fluid inlet 27 and the cooling fluid outlet 28 increases.

Referring also to fig. 4, in at least the flow dividing header region AB of the flow dividing header region AB and the flow merging header region AJ, in the present embodiment, a plurality of, for example, 6 guide concave portions 31A, 31B, 31C, 31D, 31E, and 31F extending along a predetermined flow direction of the cooling fluid (a direction indicated by an arrow in fig. 2 and 4) are formed in the outer surface of the cooling liner 14 in the flow dividing header region AB.

The peripheral edge shape of the guide concave portions 31A to 31F is formed in an oval shape that is long in the predetermined flow direction of the cooling fluid in the present embodiment, but may be formed in a non-circular shape that is long in the predetermined flow direction and combines a plurality of circular arc portions, such as a banana (fruit), for example.

The plurality of guide concave portions 31A to 31F are formed in the flow dividing header region AB in the cooling jacket 14 so as to be enlarged with distance from the cooling fluid introduction port 27 and extend into the cooling passages 26A to 26F. That is, of the guide concave portions 31A to 31F, the guide concave portion 31A closest to the cooling fluid introduction port 27 is formed to be the smallest, and the guide concave portion 31F farthest from the cooling fluid introduction port 27 is formed to be the largest.

In the flow dividing header region AB, a groove 32 extending along the partition wall 23 is formed in the outer surface of the cooling jacket 14, and the groove 32 communicates with the partition wall 23-side end portions of the plurality of guide concave portions 31A to 31F in common.

Next, the operation of this embodiment will be described, and since a plurality of guide concave portions 31A to 31F extending in a predetermined flow direction of the cooling fluid are formed in the outer surface of the cooling sleeve 14 in the flow dividing header region AB and the flow merging header region AJ in the flow dividing header region AB, the contact area between the cooling fluid and the cooling sleeve 14 in the flow dividing header region AB can be increased, the cooling efficiency in the flow dividing header region AB can be improved, and the guide concave portions 31A to 31F extend in the predetermined flow direction of the cooling fluid, so that the cooling fluid can flow smoothly without being blocked.

Further, the cooling fluid introduction port 27 is provided in the cylindrical portion 8a of the casing 8 at a portion corresponding to a corner of the flow dividing header region AB, the cooling fluid discharge port 28 is provided in the cylindrical portion 8a at a portion corresponding to a corner of the flow converging header region AJ, and the plurality of cooling fins 22 are formed such that: since the interval between the partition walls 23 and the both end portions of the cooling fins 22 along the circumferential direction of the cooling sleeve 14 decreases as they are spaced apart from the cooling fluid introduction port 27 and the cooling fluid discharge port 28, the flow cross-sectional area of the cooling fluid in the branch header region AB decreases as the cooling fluid introduced from the cooling fluid introduction port 27 is branched into the cooling passages 26A to 26F, and the flow cross-sectional area of the cooling fluid flowing from the cooling passages 26A to 26F into the merging header region AJ in the merging header region AJ increases as it approaches the cooling fluid discharge port 28. Therefore, the cooling fluid can be made to flow without stagnation so as to equalize the cooling fluid flow rates of the respective cooling passages 26A to 26F, and the heat distribution of the entire circumference of the motor 5 can be equalized.

Further, since the peripheral edge shape of the guide concave portions 31A to 31F is formed in an oval shape that is long in the predetermined flow direction of the cooling fluid, the cooling fluid flows in a swirling manner in the peripheral edges of the guide concave portions 31A to 31F, and the cooling efficiency can be further improved. Further, the peripheral edge shape of the guide recess may be a non-circular shape which is long in the predetermined flow direction and combines a plurality of circular arc portions, and thus the cooling efficiency can be further improved in the same manner.

Further, since the guide concave portions 31A to 31F are formed in the flow dividing header region AB so as to be increased in size as being distant from the cooling fluid introduction port 27, the guide concave portions 31A to 31F are increased in size as the flow rate of the cooling fluid in the flow dividing header region AB is decreased, and the cooling fluid can be equally divided into the cooling passages 26A to 26F.

Further, since the guide recessed portions 31A to 31F are formed to extend into the cooling passages 26A to 26F, the cooling fluid can be smoothly flowed into the cooling passages 26A to 26F from the branch header region AB.

In the flow dividing header region AB, the grooves 32 extending along the partition wall 23 are formed on the outer surface of the cooling jacket 14 so as to commonly communicate with the partition wall 23-side end portions of the plurality of guide concave portions 31A to 31F, and therefore the cooling fluid from the cooling fluid introduction port 27 can smoothly flow toward the guide concave portions 31A to 31F.

While the embodiments of the present invention have been described above, the present invention is not limited to the above embodiments, and various design changes may be made without departing from the present invention described in the claims.

For example, in the above embodiment, the guide concave portions are disposed only in the flow dividing header region AB of the flow dividing header region AB and the flow merging header region AJ, but the guide concave portions may be formed on the outer surface of the cooling jacket 14 in both the flow dividing header region AB and the flow merging header region AJ.