JP5594350B2 - Electric motor - Google Patents

Description

  The present invention relates to an electric motor.

  In general, electric motors are used for industrial machines such as construction machines, agricultural machines, machine tools, and self-propelled vehicles such as automobiles. In such an industrial machine, since a large current is supplied to the electric motor, the electric motor has a cooling structure for suppressing heat generation at that time. For example, Patent Literature 1 discloses a technique related to a cooling structure that circulates cooling water along the circumferential direction around an outer peripheral portion of a case.

JP 2008-259326 A

  However, in the electric motor described in Patent Document 1, the cooling space for circulating the cooling water is formed over the entire circumferential direction in the outer peripheral portion of the case. However, the cooling water flowing in the cooling space is the event at that time. Therefore, the flow of cooling water is biased in the cooling space. Thus, the cooling effect is not always sufficient in the cooling structure in which the drift occurs.

  Therefore, the present invention has been made in view of such a point, and an object of the present invention is to provide an electric motor including a cooling structure capable of suppressing the drift of the fluid flowing in the cooling space. is there.

The electric motor of the present invention is an electric motor including a cylindrical case (13) that accommodates a rotor (17) and a stator (19), and the case (13) is formed in substantially the entire circumferential direction therein. And a cooling space (50) through which fluid can flow. The cooling space (50) has an inlet (60) through which the fluid flows and outlets (62, 63, 64) through which the fluid is discharged from the cooling space (50). The cooling space (50) includes a plurality of cooling portions (51, 52, 53, 54) arranged in the axial direction so as to divide the cooling space in the axial direction of the case. Each cooling unit can distribute the fluid over substantially the entire circumferential direction. The plurality of cooling units include a cooling unit provided with the inlet and a cooling unit provided with the outlet. The cooling part provided with the outlet and the cooling part adjacent to the cooling part on the first direction (D1) side in the axial direction are opposed to the outlet in the radial direction of the case (13). And communicate with each other at a joining portion located on the same side in the radial direction with the outlet. The said junction part is for joining the fluid in the said adjacent cooling part to the cooling part in which the said exit was provided. The communication part is for air venting having an opening area smaller than that of the merge part. The outlet and the communication part are located in positions adjacent to each other in the axial direction, and the outlet and the communication part are arranged in an upward position, and the air in the adjacent cooling part is moved by the communication part to the outlet. The fluid is guided to the side and discharged from the outlet together with the fluid flowing in the cooling section provided with the outlet.
In this configuration, the outlet and the communication portion are in positions adjacent to each other in the axial direction, and the electric motor is arranged with the outlet and the communication portion facing upward. In addition to being discharged from the outlet together with the fluid flowing in the cooling part, the air in the adjacent cooling part is also guided to the axial outlet side through the communicating part, and the fluid from the outlet adjacent in the axial direction to the communicating part. At the same time, it is discharged smoothly.

In the electric motor, the case (13) is arranged on the outer side of the cylindrical inner cylinder part (21) that houses the rotor (17) and the stator (19) and the inner cylinder part (21). A cylindrical outer cylinder part (23) fixed to the inner cylinder part (21) and forming the cooling space (50) between the inner cylinder part (21) and the inner cylinder part (21) And a partition (81 , 82, 83 ) provided along the circumferential direction between the outer cylinder portion and the outer cylinder portion (23) and dividing the cooling space (50) into the plurality of cooling portions. It is preferable.

In the motor, the partition (81, 82, 83) has an opening (71, 72, 73) that form structure of the merging portion preferably has a.

In the electric motor, the partition (81, 82, 83) preferably has an opening (25a) that constitutes the communication portion.

  As described above, according to the present invention, the cooling space is divided in the axial direction to provide a plurality of cooling units, and the cooling structure for forcibly flowing the fluid over substantially the entire circumferential direction of the cooling space is employed. This makes it possible to control both the axial and circumferential flows of the fluid flowing in the cooling space. Thereby, since the drift in the space for cooling can be suppressed effectively, the cooling effect can be enhanced and the heat generation of the electric motor can be suppressed.

It is sectional drawing which cut | disconnected the electric motor of 1st Embodiment of this invention to the axial direction of the shaft. It is sectional drawing which showed the inner cylinder part, outer cylinder part, and stator of 1st Embodiment, and cut | disconnected these in the axial direction. (A) is a perspective view which shows the structure of the inner cylinder part when the electric motor of 1st Embodiment is seen from the entrance side, (b) is a side from which this electric motor is opposed to a radial direction with respect to an entrance. It is a perspective view which shows the structure of the inner cylinder part when it sees. It is a perspective view which shows structures, such as a case and a stator, in the electric motor of 1st Embodiment. It is a perspective view which shows the shape of the space for cooling in the electric motor of 1st Embodiment. (A) is a perspective view which shows the structure of the inner cylinder part when the electric motor of 2nd Embodiment is seen from the entrance side, (b) is from the side which opposes this motor to a radial direction with respect to an entrance. It is a perspective view which shows the structure of the inner cylinder part when it sees. (A) is a perspective view which shows the structure of the inner cylinder part when the electric motor of 3rd Embodiment is seen from the entrance side, (b) is from the side which opposes this electric motor to a radial direction with respect to an entrance. It is a perspective view which shows the structure of the inner cylinder part when it sees.

  Embodiments of the present invention will be described below with reference to the drawings.

<First Embodiment>
As shown in FIG. 1, the electric motor 11 according to the first embodiment is attached to a case 13, a shaft 15 rotatably supported by the case 13 along the axial direction of the case 13, and the shaft 15. A cylindrical rotor 17 and a stator 19 facing the rotor 17 are provided.

  As shown in FIGS. 1 and 2, the case 13 includes a cylindrical inner cylinder portion 21, a cylindrical outer cylinder portion 23 that covers the outer surface of the inner cylinder portion 21, and both axial sides of the inner cylinder portion 21. The disk part 29 and the disk part 31 which block | close each opening part are included. The inner cylinder part 21, the outer cylinder part 23, the disk part 29, and the disk part 31 are manufactured separately and then integrated.

  The disc part 29 is fitted in the opening part of the inner cylinder part 21 on the first direction D1 side, and is fixed to the end part of the inner cylinder part 21 by a bolt (not shown). A concave portion in which one end portion of the shaft 15 is disposed is formed on the inner surface of the disk portion 29. A bearing 33 is interposed between the inner peripheral surface of the recess and the outer peripheral surface of the shaft 15.

  In addition to the form in which one end portion of the shaft 15 is disposed in the recess as shown in FIG. 1, for example, a not-shown through hole through which the shaft 15 can be inserted is provided in the disk portion 29, and the shaft 15 The form by which the one end part was penetrated may be sufficient. In the case of this form, it is possible to output rotational motion at both ends of the shaft 15. In the case of this embodiment, one end of the shaft 15 is set as the input side of the rotary motion, and the other end is set as the output side of the rotary motion, so that the input side assists the rotary motion on the output side. You can also.

  The disc part 31 is fitted in the opening part of the inner cylinder part 21 on the second direction D2 side, and is fixed to the end part of the inner cylinder part 21 by a bolt (not shown). A through hole through which the other end of the shaft 15 is inserted is formed at the center of the disk portion 31. A bearing 35 is interposed between the inner peripheral surface of the through hole and the outer peripheral surface of the shaft 15. In this way, the shaft 15 is rotatably supported by the disk portions 29 and 31. Note that the end portion of the shaft 15 on the second direction D2 side and the disk portion 31 are attached to the body of an industrial machine such as a hydraulic machine.

  A stator 19 is disposed on the inner surface of the inner cylinder portion 21 along the circumferential direction. The stator 19 is disposed opposite the outer peripheral surface of the rotor 17 with a predetermined gap. The stator 19 has a core 19a attached so as to be in thermal contact with the inner surface of the inner cylinder portion 21, and a winding 19b wound around the core 19a.

  As shown in FIGS. 3A and 3B, the inner cylinder part 21 includes a body part 40 that forms a cooling space 50 that serves as a fluid flow path together with the outer cylinder part 23, and a second part of the body part 40. And a flange portion 41 provided at the end on the direction D2 side. The flange portion 41 includes an insertion portion 43 having a through hole 43a and a wiring portion 45 having a through hole 45a (see FIG. 2) through which a conducting wire for supplying electric power to the electric motor 11 is inserted. As shown in FIG. 4, the inner cylinder portion 21 is configured such that the bolt 44 is inserted into the through hole in a state where the screw holes of the nut portion 46 provided on the outer surface of the outer cylinder portion 23 and the through holes 43 a of the insertion portion 43 are aligned. It is connected to the outer cylinder part 23 by being inserted into 43a and screwed into the screw hole of the nut part 46. A flat plate 47 that closes the opening of the wiring portion 45 is screwed to the side portion of the wiring portion 45.

  As shown in FIGS. 3A and 3B, the body portion 40 includes an outer edge portion 37 provided at an end portion on the first direction D1 side and an outer edge portion provided on an end portion on the second direction D2 side. 39 and a partition 81 provided between the outer edge portions 37 and 39. The outer edge portion 37, the outer edge portion 39, and the partition 81 have opposing surfaces 37a, 39a, 81a that face the inner surface of the outer cylinder portion 23 along the circumferential direction, respectively. In the present embodiment, the outer diameters of these facing surfaces 37a, 39a, 81a are adjusted to be approximately the same. However, the outer diameters of these facing surfaces 37a, 39a, 81a are not necessarily the same. That is, the space between the facing surface 37a and the inner surface of the outer cylinder portion 23 is sealed by an O-ring disposed in a lower groove 49 described later, and the space between the facing surface 39a and the inner surface of the outer tube portion 23 is on the upper side. What is necessary is just to be sealed to some extent by the partition 81 between the 1st cooling part 51 and the 2nd cooling part 52 which are sealed by the O-ring arrange | positioned in the groove | channel 49, and are mentioned later. If these conditions are satisfied, for example, the outer diameters of the opposing surfaces 37a, 39a, 81a may be different, and the inner surface of the outer cylinder portion 23 may be curved or inclined with respect to the axial direction.

  As shown in FIGS. 2 and 4, the outer cylinder part 23 is a cylindrical member that covers the outer surface of the body part 40 of the inner cylinder part 21. The outer cylinder portion 23 covers the outer surface of the body portion 40 and is disposed at a predetermined interval with respect to the outer surface, thereby forming a cooling space 50 through which fluid can flow with the body portion 40. ing. A fluid inlet 60 and an outlet 62 communicating with the cooling space 50 are provided on the outer surface of the outer cylinder portion 23.

  A first concave portion 91 having an outer diameter smaller than these is formed along the circumferential direction between the outer edge portion 37 and the partition 81, and the outer edge portion 39 and the partition 81 have an outer periphery smaller than these. A second recess 92 having a small diameter is formed along the circumferential direction. Thereby, when the outer cylinder part 23 is arranged so as to cover the outer surface of the inner cylinder part 21, the inner surface of the outer cylinder part 23 faces the outer edges 37, 39 and the opposing surfaces 37a, 39a, 81a of the partition 81. Thus, a space is formed between the first recess 91 and the second recess 92 between the inner surface of the outer cylinder portion 23. These spaces become the first cooling part 51 and the second cooling part 52 that constitute a part of the cooling space 50. Thus, the cooling space 50 is divided into the first cooling part 51 and the second cooling part 52 in the axial direction.

  Further, an O-ring groove 49 is formed along the circumferential direction between the outer edge portion 37 and the first recessed portion 91, and between the outer edge portion 39 and the second recessed portion 92 in the circumferential direction. Along with this, an O-ring groove 49 is formed. O-rings (not shown) are arranged in these grooves 49, respectively. Thereby, the watertightness between the outer cylinder part 23 and the outer edge parts 37 and 39 of the inner cylinder part 21 is improved.

  In the first recess 91 and the second recess 92, a plurality of grooves 27 (five grooves 27 in the first embodiment) that are recessed inward in the radial direction are respectively formed along the circumferential direction. The grooves 27 are substantially parallel to each other and are formed over substantially the entire circumferential direction.

  The first cooling part 51 communicates in the radially outer space while the radially inner space is partitioned into a plurality of spaces by the annular protrusions that form the wall surfaces of the grooves 27. . Similarly to the first cooling part 51, the second cooling part 52 has a radial inner space partitioned into a plurality of radial inner spaces by an annular protrusion constituting the wall surface of each groove 27. The space on the outer side of is communicated in the axial direction. By adopting such a configuration, in the first cooling part 51 and the second cooling part 52, the contact area between the fluid and the outer surface of the inner cylinder part 21 is increased on the radially inner side, while the radial direction is increased. It is possible to suppress an increase in fluid flow resistance on the outer side. Thereby, the cooling efficiency can be improved and the pressure loss when the fluid flows can be reduced.

  As shown in FIG. 3B, the partition 81 has an opening 71 located in a region in a predetermined range in the circumferential direction on the side facing the inlet 60 in the radial direction. The opening 71 is a recess recessed inward in the radial direction formed by cutting a part of the partition 81. The opening 71 constitutes the first junction 61 together with the inner surface of the outer cylinder 23 (see FIG. 5).

  The first merging portion 61 is a part of the cooling space 50, and is located in a region in a predetermined range in the circumferential direction on the side facing the inlet 60 in the radial direction, and the first cooling portion 51 and the second cooling portion. The part 52 is communicated.

  Here, in the present embodiment, the “region in a predetermined range in the circumferential direction on the side facing the inlet 60 in the radial direction” specifically means the following. First, the axial position of this region is between the first cooling part 51 and the second cooling part 52. Next, the position in the circumferential direction of this region can be exemplified in several forms as follows. As an example of the position in the circumferential direction, when the cooling space 50 is viewed in plan (when the cooling space 50 is viewed in the axial direction of the shaft 15), it is on the axis of the cylindrical first cooling unit 51. An area having a predetermined width in the circumferential direction from the opposite position is included. The first embodiment is this type.

  In addition, as another example of the circumferential position, the opposed position may not necessarily be included, and two regions separated from each other at substantially equal distances from the opposed position to one side and the other side in the circumferential direction. Is included. Further, as another example of the position in the circumferential direction, a region where the above two examples are combined can be cited.

  Further, from the viewpoint of enhancing the effect of suppressing the drift of the fluid in the first cooling section 51, the circumferential position of the first merging section 61 is substantially a line with respect to the straight line connecting the center of the inlet 60 and the facing position. It is preferable that the shape is symmetrical. In addition, it is more preferable that the range in which the first merging portion 61 extends on one side and the other side in the circumferential direction is included in a region of ± 45 ° from the facing position from the viewpoint of suppressing drift.

  In addition, the meaning content regarding the arrangement | positioning area | region of the above-mentioned 1st junction part 61 is the same also about the 2nd-4th junction part mentioned later. That is, the “region of a predetermined range in the circumferential direction on the side facing the inlet 60 in the radial direction” in the above description of the first merging portion 61 is referred to as “first merging portion 61 in the case of the second merging portion 62. In contrast, in the case of the third merging portion 63, “a predetermined range in the circumferential direction on the side facing the second merging portion 62 in the radial direction”. In the case of the fourth junction 64, it is read as "a region in a predetermined range in the circumferential direction on the side facing the third junction 63 in the radial direction".

  As shown in FIGS. 3A, 4, and 5, the cooling space 50 is a second merge located in a region in a predetermined range in the circumferential direction on the side facing the first merge portion 61 in the radial direction. A portion 62 is provided. This 2nd junction part 62 functions as the exit 62 for discharging | emitting a fluid outside in 1st Embodiment. The fluid flowing separately in the second cooling section 52 on one side and the other side in the circumferential direction merges at the outlet 62. The outlet 62 is located on the same side in the circumferential direction as the inlet 60 and is aligned with the inlet 60 in the axial direction.

  Further, as shown in FIG. 3A, the partition 81 has a circumferential position close to the inlet 60 and has an opening 25 a at a position between the inlet 60 and the outlet 62. The opening 25a is a recess that is formed by cutting a part of the partition 81 and is recessed inward in the radial direction. This opening 25a constitutes the communication part 25 for venting air with the inner surface of the outer cylinder part 23 (refer FIG. 5). The communication part 25 is a part of the cooling space 50 and communicates the first cooling part 51 and the second cooling part 52.

  The opening length in the circumferential direction of the opening 71 is not particularly limited as long as it is appropriately set according to the viscosity of the fluid to be used, the supply amount of the fluid, and the like, but is set to be at least larger than the opening 25a. Is done. That is, the opening area of the first merging portion 61 is applied to the fluid so that the fluid flowing through one side and the other side in the circumferential direction of the first cooling portion 51 merges and smoothly flows to the second cooling portion 52 side. It is set in consideration of resistance. On the other hand, the opening area of the communication part 25 can move the air staying in the first cooling part 51 to the second cooling part 52 side, and the fluid supplied from the inlet 60 passes through the communication part 25 to the first. It is preferable to set a value sufficiently smaller than that of the first merging portion 61 to such an extent that the flow to the second cooling portion 52 side can be suppressed as much as possible.

  Water can be used as the fluid, but the risk of electrical leakage can be reduced by using, for example, insulating oil. As the insulating oil, when the electric motor 11 is used in a hydraulic device, it is preferably a hydraulic oil for the hydraulic device.

  Next, the operation of the electric motor 11 of the first embodiment will be described. First, when electric power is supplied to the motor 11, a magnetic force is generated between the rotor 17 and the stator 19 and the shaft 15 rotates. As the electric motor 11 is driven, the rotor 17 and the stator 19 mainly generate heat. In order to suppress the temperature rise of the electric motor 11 due to this heat generation, for example, hydraulic oil as a cooling fluid is supplied to the cooling space 50 through the inlet 60.

  The fluid supplied from the inlet 60 branches into one side and the other side in the circumferential direction of the first cooling unit 51 and flows through the first cooling unit 51. In the present embodiment, since the first merging portion 61 is provided at the facing position, the ratio of the fluid that branches and flows to one side and the other side in the circumferential direction of the first cooling portion 51 becomes substantially equal.

  These branched fluids merge at the first merge unit 61 and flow into the second cooling unit 52. The fluid that has been branched in this way is once merged and then flowed into the second cooling unit 52, so that the uniformly mixed fluid is sent to the second cooling unit 52 when passing through the first merged unit 61. it can. Thereby, the dispersion | variation in the cooling effect in the 2nd cooling part 52 can be reduced.

  The fluid that has flowed into the second cooling unit 52 branches again to one side and the other side in the circumferential direction of the second cooling unit 52 and flows through the second cooling unit 52. These branched fluids join again at the second joining portion (exit) 62 and are discharged from the exit 62 to the outside. Since the outlet 62 is provided in a region in a predetermined range in the circumferential direction on the side facing the first merging portion 61 in the radial direction, the outlet 62 branches to one side and the other side in the circumferential direction of the second cooling unit 52. The ratio of flowing fluid is almost even. The discharged fluid may be cooled and reused after being circulated for cooling.

  As described above, according to the first embodiment, the cooling space 50 has the inlet 60 through which the fluid flows and the first cooling section 51 that can circulate the fluid over substantially the entire circumferential direction. It includes a second cooling section 52 that is located on one side in the axial direction of the case 13 relative to the first cooling section 51 and that can circulate fluid over substantially the entire circumferential direction. Further, the cooling space 50 has a first merging portion 61 located in a region in a predetermined range in the circumferential direction on the side opposite to the inlet 60 in the radial direction of the case 13, and the first merging portion 61. And a second merging portion 62 located in a region of a predetermined range in the circumferential direction on the side facing the radial direction. Thus, in the first embodiment, by adopting a cooling structure in which the fluid is forced to flow over substantially the entire circumferential direction of the cooling space 50 while dividing the cooling space 50 in the axial direction, Both the axial and circumferential flow in the fluid flowing through can be controlled. Thereby, since the drift in the space 50 for cooling can be suppressed effectively, the cooling effect can be improved and the heat_generation | fever of an electric motor can be suppressed.

  In the first embodiment, the second joining portion 62 is an outlet provided in the case 13 for discharging the fluid in the cooling space 50 to the outside. Located on the same side of the. Thereby, the inlet 60 and the outlet can be provided in close proximity. Thereby, it becomes easy to arrange | position the piping for fluids. Further, for example, when the electric motor is arranged so that the axial direction is substantially horizontal, both the inlet 60 and the outlet 62 can be arranged upward, so that air that may accumulate in the cooling space 50 is collected. It becomes easy to discharge.

  Further, in the first embodiment, the cooling space 50 is a region in a predetermined range in the circumferential direction on the side facing the first merging portion 61 in the radial direction, and the inlet 60 and the outlet 62. Since the opening area is smaller than the first merging portion 61 at a position between the first cooling portion 51 and the second cooling portion 52, the air vent communication portion 25 is provided. As described above, when the electric motor is disposed so that the axial direction is horizontal and the inlet 60 and the outlet 62 are both disposed upward, the air accumulated in the first cooling unit 51 is passed through the communication unit 25. It becomes easy to move to the 2nd cooling part 52 side and to make it discharge from an exit. Further, since the communication portion 25 has an opening area smaller than that of the first joining portion 61, the resistance that the fluid receives when passing through the communicating portion 25 is larger than the resistance that the fluid receives when passing through the first joining portion 61. Accordingly, the fluid is prevented from flowing from the first cooling part 51 to the second cooling part 52 through the communication part 25 and the most part of the fluid is transferred to one side and the other side in the circumferential direction of the first cooling part 51. Since it can flow along, it can suppress that a cooling effect falls.

  In the first embodiment, the case 13 is disposed outside the inner cylinder portion 21 and the inner cylinder portion 21 that accommodates the rotor 17 and the stator 19. A cylindrical outer cylinder portion 23 that is fixed to form the cooling space 50 between the inner cylinder portion 21 and the inner cylinder portion 21 and the outer cylinder portion 23 along the circumferential direction. Provided with a partition 81 that divides the cooling space 50 into the first cooling part 51 and the second cooling part 52, so that the outside forming the first cooling part 51 and the second cooling part 52 is provided. The cylinder part 23 can be comprised by one member instead of another member. Thereby, the structure of an outer cylinder part can be simplified.

  In the first embodiment, the partition 81 includes the first cooling part 51 and the second cooling part 52 in a predetermined range in the circumferential direction on the side facing the inlet 60 in the radial direction. It has the opening part 71 which communicates and comprises a part of said 1st junction part 61. As shown in FIG. When the partition 81 as described above is provided between the inner tube portion 21 and the outer tube portion 23 as described above, it is only necessary to adopt a simple structure in which the opening portion 71 is formed in the partition 81. Since a part or all of one merging portion can be configured, the manufacturing process can be simplified.

  In the first embodiment, since the outer cylinder portion 23 is configured separately from the inner cylinder portion 21, the outer cylinder portion 23 is processed when the partition described above is formed between the outer cylinder portion 23 and the inner cylinder portion 21. Becomes easier. Moreover, since the outer cylinder part 23 is comprised separately from the inner cylinder part 21, after forming an uneven | corrugated | grooved part etc. in the outer cylinder part 23 or the inner cylinder part 21 beforehand, the outer cylinder part 23 is made into the inner cylinder part 21. Since it can fix, the process of an uneven | corrugated | grooved part becomes easy. In particular, when the concavo-convex portion is provided on the outer surface of the inner cylinder portion 21, the processing is further facilitated as compared with the case where the concavo-convex portion is formed on the inner surface of the outer cylinder portion 23. Moreover, since the outer cylinder part 23 and the inner cylinder part 21 are separate bodies, the relative position of the outer cylinder part 23 with respect to the inner cylinder part 21 can be arbitrarily set, so that various needs can be met.

  In the first embodiment, the inner cylinder portion 21 has a plurality of grooves 27 provided on the outer surface thereof over substantially the entire circumferential direction, so that the contact area between the fluid and the inner cylinder portion 21 is increased. Thus, the cooling efficiency can be improved. In the first embodiment, since the plurality of grooves 27 are formed so as to extend in the circumferential direction, the groove 27 is formed in a direction along the fluid flow direction in the cooling unit. The fluid can be guided smoothly in the circumferential direction to smoothly flow the fluid.

  Moreover, in 1st Embodiment, when the said fluid is insulating oil, compared with the case where fluids, such as water, are used, a possibility of an electric leakage etc. can be reduced. Further, when the electric motor is used in a hydraulic device, when the insulating oil is the hydraulic oil for the hydraulic device, a part of the hydraulic oil can be used as a fluid flowing into the cooling space 50. Thereby, the piping structure, tank structure, etc. of hydraulic equipment can be simplified.

<Second Embodiment>
FIG. 6 is a perspective view showing the inner cylinder portion 21 of the electric motor 11 according to the second embodiment . In addition, the same code | symbol is attached | subjected to the same component as 1st Embodiment here, and the detailed description is abbreviate | omitted.

In the second embodiment , the cooling space 50 is different from the first embodiment in that it further includes a third cooling part 53, a third joining part 63, and a second partition 82. 6 (a) and 6 (b), the outer cylinder portion 23 is not shown, but the third recess 93 provided between the outer edge portion 39 and the second partition 82, and the outer cylinder portion. A space surrounded by the inner surface of 23 is the third cooling unit 53 (a region indicated by a dashed-dotted arrow 53 in FIGS. 6A and 6B).

  The third cooling part 53 is located on the second direction D2 side in the axial direction of the inner cylinder part 21 with respect to the second cooling part 52, and can circulate fluid over substantially the entire circumferential direction. The third junction 63 is a fluid outlet. The outlet 63 is configured by a cylindrical tube (not shown) provided on the outer surface of the outer cylinder portion 23. The outlet 63 is located in a region in a predetermined range in the circumferential direction on the side facing the second merging portion 62 in the radial direction. That is, the outlet 63 is located on the opposite side of the inlet 60 in the circumferential direction. The fluid in the 3rd cooling part 53 merges in the exit 63, and is discharged | emitted outside.

  Moreover, the 2nd junction part 62 does not function as an exit like 1st Embodiment, but connects the 2nd cooling part 52 and the 3rd cooling part 53, and makes the fluid of the 2nd cooling part 52 3rd. It plays a role of flowing into the cooling unit 53. The second merging portion 62 is configured by an opening 72 formed of a concave portion formed in the second partition 82 and recessed inward in the radial direction, and an outer surface of the outer cylinder portion 23.

  The second partition 82 has an opening 25a in a region in a predetermined range in the circumferential direction on the side facing the opening 25a of the first partition 81 in the radial direction. The opening 25 a becomes a communication part (not shown) for venting air together with the outer surface of the outer cylinder part 23.

In the second embodiment , the cooling space 50 further includes a third cooling part 53 and a third merging part 63, so that the distance between the partitions is shortened and the axial height of each cooling part. Becomes smaller. Thus, the cooling space 50 can be further subdivided in the axial direction. Thereby, since the drift in the axial direction can be suppressed in each cooling unit, the drift in the cooling space 50 can be more effectively suppressed.

<Third Embodiment>
FIG. 7 is a perspective view showing the inner cylinder portion 21 of the electric motor 11 according to the third embodiment . In addition, the same code | symbol is attached | subjected to the same component as 1st Embodiment and 2nd Embodiment here, and the detailed description is abbreviate | omitted.

In the third embodiment , the cooling space 50 is different from the first embodiment and the second embodiment in that it further includes a fourth cooling part 54, a fourth joining part 64, and a third partition 83. Is different. In FIGS. 7A and 7B, the outer cylinder portion 23 is not shown, but the fourth recess 94 provided between the outer edge portion 39 and the third partition 83, and the outer cylinder portion. A space surrounded by the inner surface of 23 is the fourth cooling unit 54 (a region indicated by a dashed-dotted arrow 54 in FIGS. 7A and 7B).

  The fourth cooling part 54 is located on the second direction D2 side in the axial direction of the inner cylinder part 21 with respect to the third cooling part 53, and can circulate fluid over substantially the entire circumferential direction. The fourth junction 64 is a fluid outlet. The outlet 64 is located in a region in a predetermined range in the circumferential direction on the side facing the third merging portion 63 in the radial direction. The fluid in the fourth cooling unit 54 merges at the outlet 64 and is discharged to the outside.

The third confluence unit 63, rather than functioning as an outlet as in the second embodiment, the third fluid cooling section 53 communicates with the third cooling unit 53 and a fourth cooling unit 54 fourth It plays a role of flowing into the cooling unit 54. The third merging portion 63 is configured by an opening 73 formed of a concave portion formed in the third partition 83 and recessed inward in the radial direction, and an outer surface of the outer cylinder portion 23.

  The third partition 83 has an opening 25a at substantially the same position in the axial direction as the opening 25a of the first partition 81. The opening 25 a becomes a communication part (not shown) for venting air together with the outer surface of the outer cylinder part 23.

In the third embodiment, the cooling space 50, since the fourth cooling section 54 has a fourth junction section 64 and further, the distance between the partition becomes shorter in the axial direction of the cooling section height Becomes smaller. Thus, the cooling space 50 can be further subdivided in the axial direction. Thereby, since the drift in the axial direction can be suppressed in each cooling unit, the drift in the cooling space 50 can be further effectively suppressed.

In the third embodiment, since the outlet 64 is located on the same side of the inlet 60 and the circumferential direction can be provided at a position close to the inlet 60 and outlet 64. Thereby, it becomes easy to arrange | position the piping for fluids. Further, for example, when the electric motor is arranged so that the axial direction is substantially horizontal, both the inlet 60 and the outlet 64 can be arranged upward, so that air that may accumulate in the cooling space 50 is collected. It becomes easy to discharge.

<Other embodiments>
Note that the present invention is not limited to the above-described embodiment, and various modifications and improvements can be made without departing from the spirit of the present invention. For example, in the first embodiment, the case where the first merging portion is configured by the concave portion as the opening provided in the partition and the inner surface of the outer cylinder portion is described as an example, but the present invention is not limited to this. . For example, the first merging portion can also be configured by providing a through-hole as an opening in the partition. The same applies to the other second to fourth junctions.

In the third embodiment, the first cooling portion cooling space 50, the second cooling unit, a case has been exemplified which is divided into third cooling unit and a fourth cooling unit may be further subdivided .

  Moreover, in the said embodiment, although the form in which the partition was formed along the circumferential direction on the outer surface of the inner cylinder part was illustrated, a partition is not the outer surface of an inner cylinder part but the inner surface of an outer cylinder part along the circumferential direction. It may be formed by a member different from the inner cylinder part and the outer cylinder part.

  Moreover, in the said embodiment, although the case where the inner cylinder part and outer cylinder part which form the space for cooling were separated was mentioned as an example, these inner cylinder parts and outer cylinder parts are not separate bodies. It may be an integral member.

  Moreover, in the said embodiment, although the case where several groove | channels substantially parallel to each other were provided in the outer surface of the inner cylinder part over the substantially whole circumferential direction, as such an uneven | corrugated | grooved part, for example, a helical groove | channel is mentioned. A plurality of protrusions, a plurality of dimples, and the like may be provided on the outer surface of the inner cylinder part or the inner surface of the outer cylinder part. Moreover, the above uneven | corrugated | grooved part does not necessarily need to be provided from a viewpoint of suppressing the drift of the fluid in the space for cooling.

  The above-described electric motor mainly includes an invention having the following configuration.

  The electric motor includes a cylindrical case (13) that houses a rotor (17) and a stator (19). The case (13) includes a cooling space (50) that is formed over substantially the entire circumference in the inside of the case (13) and allows fluid to flow therethrough. The cooling space (50) has an inlet (60) through which the fluid flows, and a first cooling part (51) capable of circulating the fluid over substantially the entire circumferential direction, and the first cooling part (51 ) On the one side in the axial direction of the case (13) and capable of circulating fluid over substantially the entire circumferential direction, and the case (13) with respect to the inlet (60). ) Is located in a region in a predetermined range in the circumferential direction on the side facing the radial direction, and the fluid in the first cooling part (51) merges and the first cooling part (51) and the second cooling part (52) is located in a region of a predetermined range in the circumferential direction on the side facing the first merging portion (61) in the radial direction with respect to the first merging portion (61). A second merging portion (62) where the fluid in the portion (52) merges. There.

  In this configuration, the fluid that has flowed into the first cooling section (51) from the inlet (60) branches to one side and the other side in the circumferential direction of the first cooling section (51), and the first cooling section (51). Through the first merging portion (61) provided in the region of the predetermined range in the circumferential direction on the side facing the inlet (60) in the radial direction, and flows into the second cooling portion (52). The second cooling section (52) is branched again to one side and the other side in the circumferential direction, flows through the second cooling section (52), and is on the side facing the first merging section (61) in the radial direction. The merging is performed again at the second merging portion (62) provided in the region of the predetermined range in the circumferential direction.

  Moreover, the first merging portion (61) is provided in a region in a predetermined range in the circumferential direction on the side facing the inlet (60) in the radial direction, and the second merging portion (62) is the first merging portion (61). Is provided in a region in a predetermined range in the circumferential direction on the side opposed to the radial direction. Therefore, the lengths of the passages on one side and the other side in the circumferential direction are approximately the same. Therefore, the resistance difference received by the fluid when flowing through one side and the other side in the circumferential direction of the first cooling unit (51) is reduced, and one side and the other side in the circumferential direction of the second cooling unit (52) are respectively set. The difference in resistance experienced by the fluid when flowing can be reduced. Thereby, in the 1st cooling part (51) and the 2nd cooling part (52), the ratio of the fluid branched to the one side and the other side of the peripheral direction can be controlled to substantially the same level.

  Thus, in this configuration, by adopting a cooling structure in which the fluid is forced to flow over substantially the entire circumferential direction of the cooling space (50) while dividing the cooling space (50) in the axial direction, (50) Both axial and circumferential flows in the fluid flowing in the fluid can be controlled. Thereby, since the drift in the cooling space (50) can be effectively suppressed, the cooling effect can be enhanced and the temperature rise of the motor due to the heat generated by the motor can be suppressed.

  The second junction (62) may be an outlet provided in the case (13) for discharging the fluid in the cooling space (50) to the outside.

  In this configuration, since the inlet (60) and the outlet can be provided close to each other, it is easy to arrange the fluid piping at the inlet (60) and the outlet. Further, for example, when the electric motor is arranged so that the axial direction is substantially horizontal, both the inlet (60) and the outlet can be arranged upward, so that they can be accumulated in the cooling space (50). It becomes easy to discharge some air.

  The cooling space (50) is a region in a predetermined range in the circumferential direction on the side facing the first merging portion (61) in the radial direction, and between the inlet (60) and the outlet. In the position, the opening area is smaller than that of the first merging portion (61), and there is a communication portion (25) for venting air that communicates the first cooling portion (51) and the second cooling portion (52). It is preferable.

  In this configuration, in addition to the second merging portion (62) being an outlet, and further having the communication portion (25), the electric motor is arranged so that the axial direction is horizontal as described above, When used with both the inlet (60) and the outlet positioned upward, the air accumulated in the first cooling part (51) is moved to the second cooling part (52) side through the communication part (25). It becomes easy to discharge from the outlet. Further, since the communication part (25) has an opening area smaller than that of the first joining part (61), the resistance received by the fluid when passing through the communicating part (25) is the resistance received when passing through the first joining part (61). Bigger than. As a result, it is possible to suppress the flow of fluid from the first cooling part (51) to the second cooling part (52) through the communication part (25) and to flow the most part of the fluid around the first cooling part (51). Since it can flow along one side and the other side of a direction, it can control that a cooling effect falls.

  The cooling space (50) is located on one side in the axial direction of the case (13) with respect to the second cooling part (52), and a third cooling part (through which the fluid can flow through substantially the entire circumferential direction ( 53) and a second region where the fluid in the third cooling portion (53) joins the second confluence portion (62) in a predetermined region in the circumferential direction on the side facing the radial direction. The second merging portion (62) may further communicate with the second cooling portion (52) and the third cooling portion (53).

  In this configuration, since the cooling space (50) further includes the third cooling portion (53) and the third merge portion (63) as described above, the cooling space (50) is axially disposed. It can be further subdivided. Thereby, the drift in the space for cooling (50) can be more effectively suppressed.

  The third junction (63) may be an outlet provided in the case (13) for discharging the fluid in the cooling space (50) to the outside.

  The cooling space (50) is located on one side in the axial direction of the case (13) with respect to the third cooling part (53), and a fourth cooling part (through which the fluid can flow through substantially the entire circumferential direction ( 54) and the third merging portion (63) in a region in a predetermined range in the circumferential direction on the side facing the radial direction, and the fluid in the fourth cooling portion (54) merges. 4 merging part (64), and the third merging part (63) may communicate the third cooling part (53) and the fourth cooling part (54).

  In this configuration, since the cooling space (50) further includes the fourth cooling portion (54) and the fourth merge portion (64), the cooling space (50) is further subdivided in the axial direction. can do. Thereby, the drift in the space for cooling (50) can be further effectively suppressed.

  The fourth joining portion (64) may be an outlet provided in the case (13) for discharging the fluid in the cooling space (50) to the outside.

  In this configuration, since the inlet (60) and the outlet can be provided close to each other, it is easy to arrange the fluid piping at the inlet (60) and the outlet. Further, for example, when the electric motor is arranged so that the axial direction is substantially horizontal, both the inlet (60) and the outlet can be arranged upward, so that they can be accumulated in the cooling space (50). It becomes easy to discharge some air.

  As means for providing the first cooling part (51) and the second cooling part (52), for example, the outer cylinder part (23) is constituted by two members, and the first cylinder together with the inner cylinder part (21) is formed using one member. The first cooling part (51) may be formed, and the second cooling part (52) may be formed together with the inner cylinder part (21) using the other member, but the following configuration is preferable. .

  That is, the case (13) is disposed outside the inner cylindrical portion (21) and the cylindrical inner cylindrical portion (21) that houses the rotor (17) and the stator (19), and the inner A cylindrical outer tube portion (23) fixed to the tube portion (21) to form the cooling space (50) between the inner tube portion (21), the inner tube portion (21), and the A partition (81) provided along the circumferential direction between the outer cylinder portion (23) and dividing the cooling space (50) into the first cooling portion (51) and the second cooling portion (52). ).

  By providing a partition (81) along the circumferential direction between the inner tube portion (21) and the outer tube portion (23) as in this configuration, the cooling space (50) is separated from the first cooling portion (51). If it divides | segments into a 2nd cooling part (52), an outer cylinder part (23) can be comprised by one member instead of another member. Thereby, the structure of an outer cylinder part (23) can be simplified.

  The partition (81) has the first cooling part (51) and the second cooling part (52) in a region in a predetermined range in the circumferential direction on the side facing the radial direction with respect to the inlet (60). It is preferable to have an opening part (71) which communicates and constitutes a part or all of the first merge part (61).

  In this configuration, the opening (71) provided in the partition (81) constitutes part or all of the first joining portion (61). Thus, when the partition (81) as described above is provided between the inner cylinder portion (21) and the outer cylinder portion (23), an opening (71) is formed in the partition (81). Since a part or the whole of the first joining portion can be configured simply by adopting such a simple structure, the manufacturing process can be simplified.

  The case (13) covers a cylindrical inner cylinder portion (21) that accommodates the rotor (17) and the stator (19), and an outer surface of the inner cylinder portion (21), and is predetermined with respect to the outer surface. A cylindrical outer cylinder part (23) that forms the cooling space (50) between the inner cylinder part (21) and the inner cylinder part (21). A first space that is provided along the circumferential direction between the outer cylinder portion (23) and divides the cooling space (50) into the first cooling portion (51) and the second cooling portion (52). A partition (81) is provided along the circumferential direction between the inner cylinder part (21) and the outer cylinder part (23), and the cooling space (50) is provided as the second cooling part (52). And a second partition (82) divided into the third cooling part (53), the inner cylinder part (21) and the outer cylinder part (23) A third partition (83) provided along the circumferential direction and dividing the cooling space (50) into the third cooling portion (53) and the fourth cooling portion (54). Yes.

  In this configuration, the cooling space (50) can be divided into a plurality of cooling parts by providing a plurality of partitions (81) along the circumferential direction between the inner cylinder part (21) and the outer cylinder part (23). If it does in this way, an outer cylinder part (23) can be comprised by one member instead of another member, and the structure of an outer cylinder part (23) can be simplified.

  The first partition (81) includes the first cooling part (51) and the second cooling part (52) in a region in a predetermined range in the circumferential direction on the side facing the radial direction with respect to the inlet (60). ) And a first opening (71) that constitutes part or all of the first merging portion (61). The second partition (82) includes the second cooling part (52) and the third cooling part in a region in a predetermined range in a circumferential direction on the side facing the first merging part (61) in the radial direction. A second opening (72) that communicates with the part (53) and forms part or all of the second merging part (62) is provided. The third partition (83) includes the third cooling part (53) and the fourth cooling part in a region in a predetermined range in the circumferential direction on the side facing the second merging part (62) in the radial direction. A third opening (73) that communicates with the part (54) and constitutes part or all of the third merge part (63) is provided.

  In this structure, each opening part (71, 72, 73) provided in each partition (81, 82, 83) comprises a part or all of the 1st-3rd joining part (61, 62, 63). Yes. Thus, when the above partitions (81, 82, 83) are provided between the inner cylinder portion (21) and the outer cylinder portion (23), the partitions (81, 82, 83) Since a part or all of the first to third joining portions (61, 62, 63) can be configured only by adopting a simple structure of forming the openings (71, 72, 73), the manufacturing process It can be simplified.

  When the outer cylinder part (23) is configured separately from the inner cylinder part (21), for example, when the partition described above is formed between the outer cylinder part (23) and the inner cylinder part (21), Processing is facilitated in the case where an uneven portion described later is formed on the outer surface of the inner cylinder portion (21).

  When the inner cylinder part (21) has a concavo-convex part (27) provided on the outer surface over substantially the entire circumferential direction, the contact area between the fluid and the inner cylinder part (21) is increased. Cooling efficiency can be improved.

  When the concavo-convex part (27) is a plurality of grooves (27) extending in the circumferential direction, the formation direction of the groove (27) is a direction along the fluid flow direction in the cooling part. Can easily flow the fluid in the circumferential direction to smoothly flow the fluid.

  When the fluid is insulating oil, it is possible to reduce the risk of electric leakage as compared with the case where a fluid such as water is used.

  When the electric motor is used for hydraulic equipment, it is preferable that the insulating oil is hydraulic oil for the hydraulic equipment.

  In this configuration, since the insulating oil is hydraulic oil for hydraulic equipment, a part of the hydraulic oil can be used as a fluid flowing into the cooling space (50). Thereby, the piping structure, tank structure, etc. of hydraulic equipment can be simplified.

DESCRIPTION OF SYMBOLS 11 Electric motor 13 Case 17 Rotor 19 Stator 21 Inner cylinder part 23 Outer cylinder part 25 Air venting communication part 27 Groove 50 Cooling space 51 1st cooling part 52 2nd cooling part 53 3rd cooling part 54 4th cooling part 60 Inlet 61 First junction 62 Exit (second junction)
63 Exit (3rd junction)
64 Exit (4th junction)
71 opening (first opening)
72 2nd opening 73 3rd opening 81 Partition (1st partition)
82 2nd partition 83 3rd partition

Claims (4)

An electric motor comprising a cylindrical case (13) for accommodating a rotor (17) and a stator (19),
The case (13) includes a cooling space (50) formed in the inside thereof in substantially the entire circumferential direction and capable of circulating a fluid.
The cooling space (50) has an inlet (60) through which the fluid flows, and outlets (62, 63, 64) through which the fluid is discharged from the cooling space (50).
The cooling space (50) includes a plurality of cooling portions (51, 52, 53, 54) arranged in the axial direction so as to divide the cooling space in the axial direction of the case. The fluid can flow through substantially the entire circumferential direction, and the plurality of cooling parts include a cooling part provided with the inlet and a cooling part provided with the outlet,
The cooling part provided with the outlet and the cooling part adjacent to the cooling part on the first direction (D1) side in the axial direction are opposed to the outlet in the radial direction of the case (13). Communicated at the joining portion located on the side to be communicated, and communicated at the communicating portion located on the same side in the radial direction as the outlet,
The merging part is for merging the fluid in the adjacent cooling part to the cooling part provided with the outlet, and the communication part is for venting the opening area smaller than the merging part,
The outlet and the communication part are located in positions adjacent to each other in the axial direction, and the outlet and the communication part are arranged in an upward position, and the air in the adjacent cooling part is moved by the communication part to the outlet. An electric motor that is guided to the side and discharged from the outlet together with a fluid flowing in a cooling section provided with the outlet. The case (13)
A cylindrical inner cylinder (21) for accommodating the rotor (17) and the stator (19);
A cylindrical outer portion that is disposed outside the inner cylinder portion (21) and is fixed to the inner cylinder portion (21) to form the cooling space (50) between the inner cylinder portion (21). A cylinder (23);
Partitions (81, 82,...) Provided along the circumferential direction between the inner cylinder part (21) and the outer cylinder part (23), and dividing the cooling space (50) into the plurality of cooling parts. 83). The electric motor according to claim 1, further comprising:   The electric motor according to claim 2, wherein the partition (81, 82, 83) has an opening (71, 72, 73) constituting the merging portion. The electric motor according to claim 2 or 3, wherein the partition (81, 82, 83) has an opening (25a) that constitutes the communication portion.

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