JPWO2015087707A1 - Drive module - Google Patents

Abstract

It is an object of the present invention to obtain a drive module that can reliably discharge bubbles mixed in an annular flow path and can radiate heat efficiently with low pressure loss. The drive module according to the present invention includes a rotating electric machine, an inner cylinder in which the rotating electric machine is housed, a heat dissipating fin provided on the outer surface, an axial direction same as the inner cylinder, the inner cylinder covering the inner cylinder, and the inner cylinder An outer cylinder that forms an annular flow path for circulating the refrigerant between the first cylinder and the second flange that closes both ends of the inner cylinder and the outer cylinder, and the main shaft of the rotating electrical machine. A diversion header that divides the refrigerant into the annular flow path, a merging header that merges the refrigerant from the annular flow path, a partition plate that partitions the diversion header and the merging header, and a first flange or an outer cylinder. The partition plate is provided with an opening at a position closer to the second flange than the first flange in the direction of the main shaft of the rotating electrical machine.

Description

  The present invention relates to a drive module integrated with a liquid cooling jacket for cooling.

  In the conventional drive module, the refrigerant inlet and outlet are provided on the radially outer side of the annular flow path, and the partition plate is extended between the inlet and outlet. Further, the partition plate is provided with a gap between the outer cylinder or both flanges, and a structure in which a part of the refrigerant is discharged without passing through the annular flow path so that air is extracted through the gap. (For example, refer to Patent Document 1).

JP 2009-247085 A

  However, in the conventional drive module, since the refrigerant inlet and outlet are provided radially outside the annular channel, the cooling water is mainly discharged from the inlet through the annular channel. Since the partition plate is provided between the inlet and the outlet where the flow stagnate, not the flow section, the bubbles mixed in the annular channel cannot be pushed into the gap, and the bubbles stagnate. there were. Further, the inlet is provided at the upper position and the outlet is provided at an oblique position, so that the air bubbles stagnate on the outlet side of the partition plate that is likely to stagnate when there is no water flow. When the air bubbles stagnate, there is a problem that the pressure loss increases and the heat dissipation capability deteriorates.

  An object of the present invention was made to solve the above-described problems. A drive module that can reliably discharge bubbles mixed in an annular flow path and can dissipate heat efficiently with low pressure loss. To get.

  The drive module according to the present invention includes a rotating electric machine having a main shaft protruding on one side, an inner cylinder in which the rotating electric machine is housed and a heat dissipating fin on the outer surface, and an inner cylinder provided in the same axial direction as the inner cylinder. An outer cylinder that forms an annular flow path for circulating refrigerant between the inner cylinder, a first flange that closes one end of the inner cylinder and the outer cylinder, and the other of the inner cylinder and the outer cylinder A second flange that closes the end, a diversion header that extends in the direction of the main shaft of the rotating electrical machine and diverts the refrigerant into the annular channel, and an annular channel that extends in the direction of the main shaft of the rotating electrical machine. A merging header that merges the circulated refrigerant, a partition plate that extends in the direction of the main shaft of the rotating electrical machine and divides the divergence header and the merging header, and a first flange or a second flange of the outer cylinder. 1 through the inlet of the flange, and the first flange or outer cylinder The partition plate has an opening at a position closer to the second flange than the first flange in the direction of the main shaft of the rotating electrical machine. Is provided.

  According to the present invention, the air bubbles mixed in the annular channel can be efficiently discharged by the opening provided in the partition plate. As a result, a drive module that can dissipate heat with low pressure loss and high efficiency can be obtained.

It is a figure which shows the drive module which concerns on Embodiment 1 of this invention. It is sectional drawing of the injection port and discharge port of a drive module which concern on Embodiment 1 of this invention. It is the schematic diagram which expand | deployed the radiation fin which concerns on Embodiment 1 of this invention on the plane. It is the figure which expanded the opening vicinity which concerns on Embodiment 1 of this invention. It is a figure which shows the drive module which concerns on Embodiment 2 of this invention. It is a figure which shows the drive module which concerns on Embodiment 3 of this invention. It is a figure which shows the drive module which concerns on Embodiment 4 of this invention.

Embodiment 1 FIG.
FIG. 1 shows a drive module 100 according to the first embodiment. 1A is a cross-sectional view taken along the line BB in FIG. 1B, and FIG. 1B is a cross-sectional view taken along the line A-A in FIG. There is an outer cylinder 2 that covers the inner cylinder 1 in the same axial direction as the inner cylinder 1, and the flange 3 a and the flange 3 b serve to close both ends of the inner cylinder 1 and the outer cylinder 2. Inside the inner cylinder 1, a rotating electrical machine 4 and a power conversion device 6 having an electric circuit board 5 are accommodated in the direction of the rotating electrical machine 3 and the main shaft 4a. Here, the following will be described assuming that the rotating electrical machine 4 is a three-phase electric motor and the power conversion device 6 is an inverter that generates electric power for driving the electric motor. The main shaft 4a of the rotating electrical machine 4 protrudes on one side, and the power conversion device 6 is accommodated on the opposite side of the side on which the main shaft 4a of the rotating electrical machine 4 protrudes. The flange on the power conversion device 6 side is referred to as a flange 3a, and the flange on the rotating electrical machine 4 side is referred to as a flange 3b. The inner side of the inner cylinder 1 is partitioned by an intermediate partition plate 7, but the rotating electrical machine 4 and the power conversion device 6 are electrically connected by a cable (not shown) through the intermediate partition plate 7. The power conversion device 6 has an electric circuit board 5 as a power module that drives the rotating electrical machine 4. FIG. 1B shows a case where the number of electric circuit boards 5 is six, and the number is a multiple of three. Here, a multiple of 3 means 3, 6, 9,.

  An annular flow path 8 for circulating the refrigerant is formed between the inner cylinder 1 and the outer cylinder 2. That is, a liquid cooling jacket for cooling the rotating electrical machine 4 and the power conversion device 6 accommodated inside the inner cylinder 1 is constituted by the inner cylinder 1, the outer cylinder 2, and the flange 3 a and the flange 3 b closing both ends, An annular channel 8 through which the refrigerant circulates is formed inside the liquid cooling jacket. Note that heat radiating fins 14 are provided on the outer surface of the inner cylinder 1. As the refrigerant, for example, liquid such as water or antifreeze is used. Adjacent to one surface of the partition plate 9a extending in the direction of the main shaft 4a of the rotating electric machine 4, a diversion header 10a is provided extending in the direction of the main shaft 4a of the rotating electric machine 4. A junction header 11a is provided so as to extend in the direction of the main shaft 4a of the rotating electrical machine 4 adjacent to the surface of the partition plate 9a opposite to the side on which the diversion header 10a is provided. In other words, the diversion header 10a and the merge header 11a are provided adjacent to each other in the circumferential direction of the inner cylinder 1, and a partition plate 9a is provided between the diversion header 10a and the merge header 11a. The header 10a and the merge header 11a are partitioned.

  In the present embodiment, the diversion header 10 a and the merge header 11 a are formed as grooves deeper than the annular flow path 8 on the outer surface of the inner cylinder 1. Side surfaces of the grooves of the diversion header 10 a and the merge header 11 a are connected to the annular flow path 8. That is, the diversion header 10a and the merging header 11a are provided adjacent to each other in the plane perpendicular to the circumferential direction of the inner cylinder 1 extending to the annular flow path 8 and the main shaft 4a, respectively, and pressure loss can be reduced. The area of the cross section perpendicular to the direction of the main axis 4a of the diversion header 10a and the merging header 11a, particularly the cross-sectional area around the connection portion with the injection port 12 or the discharge port 13, is at least the disconnection of the injection port 12 or the discharge port 13. Over the area. As shown in FIG. 1B, the cross-sectional shapes of the diversion header 10a and the merge header 11a may be wider in the circumferential direction than the inlet 12 or the outlet 13 when viewed from the direction of the main shaft 4a. The cross-sectional area in the plane perpendicular to the main shaft 4a of the diversion header 10a and the merge header 11a is equal to or greater than the cross-sectional area in the plane perpendicular to the circumferential direction of the annular flow path 8 (flow path area flowing in the annular flow path 8). This is more desirable. Since the refrigerant that has entered the diversion header 10a having a large cross-sectional area from the inlet 12 enters the annular flow path 8 after the flow once becomes gentle, it is advantageous to make the distribution flowing through the annular flow path 8 uniform. It should be noted that the depth and width in the direction of the main shaft 4a of the diversion header 10a and the merge header 11a do not have to be uniform. For example, the cross-sectional area changes as it approaches the flange 3b side which is the end of the annular flow path 8. The distribution flowing through the annular flow path 8 may be adjusted by changing the depth and width. That is, as the flow height between the diversion header 10a and the merge header 11a is larger than the annular flow path 8, the pressure loss between the diversion header 10a and the merge header 11a can be reduced, and the drift can be further reduced. That is, the flow height of the diversion header 10a and the merge header 11a may be increased as it approaches the flange 3b side.

  The partition plate 9a may be formed integrally with the inner cylinder 1, or may be formed by joining those formed separately. Moreover, you may form in the outer cylinder 2 side. Although it is desirable to use a thin plate, it may be formed as a partition wall having a certain thickness in order to ensure strength.

  Refrigerant is injected from the inlet 12 that passes through the flange 3a on the power converter 6 side and is connected to the diversion header 10a. The refrigerant is discharged from an outlet 13 that passes through the flange 3a on the power conversion device 6 side and is connected to the merge header 11a. In FIG. 1A, the discharge port 13 is not shown because it is located in the back of the injection port 12. The refrigerant injected from the inlet 12 into the diversion header 10a is spread in the axial direction of the inner cylinder 1 by the diversion header 10a, and is diverted to the annular flow path 8 and spread in the circumferential direction, so that the refrigerant is Cycle 8. The annular flow path 8 has a portion in contact with the radiating fin 14 and a portion without the radiating fin 14, and the heat of the inner cylinder 1 is transmitted to the refrigerant particularly efficiently at the portion in contact with the radiating fin 14. Next, the refrigerant that has circulated through the annular flow path 8 flows from the annular flow path 8 into the merge header 11 a and is merged in the axial direction of the inner cylinder 1. The refrigerant merged at the merge header 11 a is discharged from the discharge port 13. As described above, the refrigerant for cooling the rotating electrical machine 4 and the power conversion device 6 housed inside the inner cylinder 1 is the inlet 12, the diversion header 10 a, the annular flow path 8, the merge header 11 a, and the outlet 13. It will flow in the order. The inlet 12 may be connected to the diversion header 10a and the outlet 13 to the merging header 11a on the flange 3a side, and may be connected to the outer cylinder 2 without the flange 3a.

  In FIG. 1 (a), BB in FIG. 1 (b) does not pass through the center of the cut surface in order to illustrate the internal structure of the inlet 12 and the radiation fin 14 in an easy-to-understand manner.

  In FIG. 1B, an extension line of the attachment position of the inlet 12 and the outlet 13 is indicated by a dotted line. As shown in FIG. 1 (b), the inlet 12 and the outlet 13 are provided closer to the annular channel 8 than the partition plate 9a in the circumferential direction of the annular channel 8, respectively. This makes it easier to connect the pipes to each other.

  FIG. 2 is a cross-sectional view taken along line CC of FIG. 1B of the inlet 12 and the outlet 13 of the drive module 100 according to Embodiment 1 of the present invention. As shown in FIG. 2, the connecting portion between the inlet 12 and the diversion header 10a has an enlarged flow path shape from the injection port 12 toward the diversion header 10a, so that the refrigerant can easily spread in the circumferential direction of the diversion header 10a. , Pressure loss can be reduced. Moreover, pressure loss can be reduced by making the connection part of the discharge port 13 and the confluence | merging header 11a into a reduced flow path shape toward the discharge port 13 from the confluence header 11a. Further, since the diversion header 10a and the merging header 11a are formed on the outer surface of the inner cylinder 1, the outer cylinder 2 can be formed with a simple cylindrical surface without a bulge, facilitating manufacturing and reducing the size.

  DC power is supplied to the power converter 6 from the outside via the flange 3 a on the power converter 6 side or the inner cylinder 1 and the outer cylinder 2. The electric power converted from direct current to alternating current by the power converter 6 is supplied to the rotating electrical machine 4 via the partition plate 7. The rotating electrical machine 4 converts the supplied electric power into mechanical energy, and the main shaft 4a passing through the flange 3b on the rotating electrical machine 4 side transmits the mechanical energy. At that time, heat generated in the rotating electrical machine 4 and the power conversion device 6 is radiated to the inner cylinder 1. Heat from the rotating electrical machine 4 and the power converter 6 received by the inner cylinder 1 is transmitted to the refrigerant. Here, the radiation fins 14 have a role of efficiently transferring the heat of the inner cylinder 1 to the refrigerant. The refrigerant that has received heat and has reached a high temperature flows from the annular flow path 8 into the merge header 11 a and is discharged from the discharge port 13. As described above, the refrigerant circulates through the liquid cooling jacket, whereby the rotating electrical machine 4 and the power converter 6 can be cooled.

  The heat radiating fins 14 are divided into six pieces which are the same number as the electric circuit board 5 and are arranged on the outer surface of the inner cylinder 1 at positions corresponding to the arrangement of the electric circuit boards 5. The effect equivalent to the increase in the area where the refrigerant contacts the inner cylinder 1 that has received the heat generated by the rotating electrical machine 4 and the power converter 6 is obtained by the radiating fins 14. Also, the cross-sectional area that flows is reduced. That is, the diameter per pressure of the refrigerant is reduced. As a result, the heat dissipation characteristics are improved.

  In the present embodiment, as shown in FIG. 1B, the radiating fins 14 are divided and arranged, and the annular flow path 8 is formed from a portion where the radiating fins 14 are attached and a portion where the radiating fins 14 are not attached. Become. By providing a portion where the radiation fins 14 are not mounted between the divided radiation fins 14, the pressure loss can be reduced. Further, by dividing the radiating fins 14, a portion where the refrigerant contacts the radiating fins 14 is generated by the number of divisions. Heat transfer is promoted to the portion where the refrigerant of the radiating fin 14 increased by the number of divisions by dividing the radiating fin 14 flows due to the leading edge effect. Furthermore, by dividing the radiation fins 14, the flow path length of each radiation fin 14 is shortened, so the development of the temperature boundary layer formed on the surface of the radiation fins 14 can be suppressed, and the radiation characteristics can be improved. Can be improved. Further, since the portion where the radiating fins 14 are not attached communicates in the axial direction, the flow equalization is promoted toward the flange 3b side of the annular flow path 8, and the flange 3b side of the annular flow path 8 where the heat radiating capacity is likely to be insufficient. It can dissipate heat appropriately.

  Note that, due to this leading edge effect, the side of the diversion header 10a of the radiating fin 14 can radiate heat more efficiently. Here, the shunt header 10a side of the radiating fin 14 is the upstream side when viewed from the refrigerant flow. Therefore, as for the positional relationship between the electric circuit board 5 and the heat radiation fins 14, the heat radiation fins 14 can be radiated more efficiently if they are arranged slightly shifted from the electric circuit board 5 toward the joining header 11a.

  Further, the rotating electrical machine 4 and the power conversion device 6 often require different heat dissipation capabilities, and in that case, the structure, shape, and dimensions of the heat dissipation fins 14 may be different from each other. Furthermore, by changing the configuration of the heat dissipating fins 14 in several stages in the axial direction, it is possible to further suppress the drift that has occurred in the axial direction (the flow in which the flow rate deviation has occurred).

  FIG. 3 is an example of a schematic diagram illustrating the entire heat dissipating fins 14 including the fins 14a on the rotating electrical machine 4 side and the fins 14b on the power converter 6 side in a plane. The arrows in FIG. 3 indicate the flow of the refrigerant flowing into the annular flow path 8 from the diversion header 10a. In FIG. 3, the length in the left-right direction is referred to as the axial width, the length in the vertical direction is referred to as the circumferential width, and the length from the back to the front, that is, the length in the radial direction of the inner cylinder 1 is referred to as height. These definitions are used both when expressing the shape of the annular flow path 8 and when expressing the shape of the radiating fins 14. Here, the axial width and the circumferential width of the flow path flowing between the fins 14a in the circumferential direction are the same as the axial width and the circumferential width of the flow path flowing between the fins 14b in the circumferential direction, respectively. It is. Furthermore, the height of the fin 14a and the fin 14b is the same. When the heat dissipating fins 14 including the fins 14a and the fins 14b in which the axial widths of the fins 14a on the rotating electrical machine 4 side and the fins 14b on the power converting apparatus 6 side are different are used, the rotating electrical machine 4 and the power converting apparatus 6 The heat dissipation capability can be controlled. At the same time, since the flow paths are the same, deterioration due to deposits such as scales occurs similarly. Therefore, the change in flow characteristics is the same, and the influence of drift due to secular change can be suppressed, which is more preferable.

  In other words, on the rotating electrical machine 4 side and the power converter 6 side, the axial width Wa of the fin 14a and the axial width Wb of the fin 14b are different, but the interval Wga between the fins 14a and the interval between the fins 14b. Wgb is the same.

  The fin 14a and the fin 14b may be divided into a plurality of portions in the circumferential direction as shown in FIG. 3, and the shape of the fin 14a and the fin 14b is corrugated so that the flow path between the fin 14a and the fin 14b undulates. May be.

  As shown in FIG. 3, by setting the axial width Wa of the fins 14a to be larger than the axial width Wb of the fins 14b, more refrigerant flows on the power converter 6 side than refrigerant flows on the rotating electrical machine 4 side. Therefore, the cooling performance on the side of the power converter 6 that generates a large amount of heat can be increased. Moreover, since the shape of a flow path is the same, the influence of the drift by a secular change can be suppressed. If heat generation is greater on the rotating electrical machine 4 side, the axial width Wa of the fin 14a may be set smaller than the axial width Wb of the fin 14b.

  According to the configuration of the present embodiment, the rotating electric machine 4 is configured by converting the supplied electric power into mechanical energy and outputting the mechanical energy to the outside while discharging the heat generated by this operation with the refrigerant. And the apparatus which comprises the power converter device 6 can be kept below each allowable temperature, and can convert electric power into mechanical energy stably.

  4 is a view seen from the position D in FIG. 1B in the direction of the arrow D. The flange on the rotating electrical machine 4 side is easy to understand the flow of the refrigerant in the diversion header 10a and the merge header 11a. It is the figure which expanded the 3b side edge part. FIG. 4A shows the flow of the refrigerant when the end portions of the diversion header 10a and the merge header 11a and the end portions of the annular flow path 8 substantially coincide with each other. The arrows in FIG. 4 indicate the flow of the refrigerant. As shown in FIG. 4, in the present embodiment, an opening 15 is provided at a position far from the inlet 12 and outlet 13 in the direction of the main shaft 4a of the rotating electrical machine 4 of the partition plate 9a and close to the flange 3b. Yes. FIG. 4A is an enlarged view of the present embodiment, and FIG. 4B is an enlarged view of a modified example of the present embodiment.

  First, the present embodiment will be described with reference to FIG. The opening 15 provided in the partition plate 9a is mixed with the refrigerant in the diversion header 10a when the main shaft 4a is installed and used so that the main shaft 4a is substantially horizontal and the partition plate 9a is positioned almost directly above the main shaft 4a. It has the role which pushes out the bubble which is done to the merge header 11a from the diversion header 10a. When bubbles flow into the opening 15, a protruding gas-liquid interface is formed on the side of the branching header 10 a and the side of the merging header 11 a, and a capillary force acts to make it easier for the bubbles to stagnate near the opening 15. Therefore, in order to discharge the bubbles, the differential pressure generated between the diversion header 10a and the merge header 11a is designed to be larger than the capillary force, or conversely, the opening is made so that the capillary force is smaller than the differential pressure. The diameter of 15 needs to be increased.

  For example, when the coolant is water, the opening 15 may be a hole having an inner diameter of 2 to 4 mm. Since the surface tension varies depending on the type of refrigerant, the diameter of the opening 15 may be adjusted according to the type of refrigerant. The larger the opening 15, the easier it is for air bubbles to escape. However, if the opening 15 is increased, the amount of refrigerant that bypasses the direct flow header 10 a directly to the confluence header 11 a increases, so it is desirable to keep the size moderate.

  In the present embodiment, when the refrigerant is not flowing through the annular flow path 8, that is, when the refrigerant is stationary in the annular flow path 8, the divergence header 10a provided at the upper portion and the merge are formed by the buoyancy of bubbles. Air bubbles collect in the header 11a. On the other hand, when the refrigerant is flowing through the annular flow path 8, the bubbles stagnating in the diversion header 10 a are pushed to the opening 15 due to the flow from the inlet 12 to the diversion header 10 a, and the merging header 11 a through the opening 15. Further, the bubbles stagnating in the merge header 11a are pushed to the discharge port 13 by the bypass flow that flows out from the opening 15 to the merge header 11a and the main flow of the refrigerant that flows from the annular flow path 8 to the merge header 11a. According to the present embodiment, the bubbles in the annular flow path 8 can be reliably discharged as described above. As described above, in the present embodiment, the diversion header 10a and the merging header 11a on the flange 3b side also have a refrigerant flow from the opening 15, and since there is no stagnation part over almost the entire area, air bubbles are reliably discharged. be able to.

  Further, since the opening 15 is provided between the diversion header 10a and the merging header 11a whose flow path height is higher than that of the annular flow path 8, it is possible to make a relatively large size hole, and the surface tension is large. It is easy to deal with refrigerants. In addition, since the diversion header 10a and the merge header 11a are arranged in a substantially horizontal position with respect to the direction of gravity, the buoyancy acting on the bubbles is not affected, and the bubbles can be discharged through the opening 15. From the viewpoint of easy extrusion of bubbles, it is desirable that the partition plate 9a be as thin as possible if the strength is sufficient.

  In the present embodiment, the shape of the opening 15 is the radial direction of the inner cylinder 1 and the outer cylinder 2 on the surface of the opening 15 in the main shaft 4a direction of the rotating electrical machine 4 (hereinafter referred to as the side in the main shaft 4a direction). Although the ellipses, i.e., circles, having the same value of the sides (hereinafter referred to as the sides in the radial direction) are used, it goes without saying that there is no problem even if they are squares. However, in order to obtain a further effect, when the opening 15 is a square, the inner cylinder 1 and the width of the surface of the opening 15 in the direction of the main shaft 4a of the rotating electrical machine 4 (hereinafter referred to as the width in the direction of the main shaft 4a) It is desirable that the aspect ratio, which is a ratio to the radial width of the outer cylinder 2 (hereinafter referred to as the radial width), is close to 1. In other words, it is desirable that the width in the direction of the main shaft 4a / the width in the radial direction are equal. When the opening 15 is an ellipse, the width in the direction of the main axis 4a corresponds to the width in the direction of the main axis 4a, and the width in the radial direction of the inner cylinder 1 and the outer cylinder 2 corresponds to the inner cylinder 1 and the outer cylinder. This is the side of the cylinder 2 in the radial direction.

  The opening 15 is provided at a position far from the inlet 12 and the outlet 13, that is, closer to the flange 3b. As a result, a bypass flow is generated between the diversion header 10a and the merge header 11a via the partition plate 9a. The bubbles mixed in the diversion header 10a are swept away by the inertial force of the refrigerant, collected on the end side near the flange 3b on the rotating electric machine 4 side, move to the merge header 11a through the opening 15, and flow out from the opening 15. Due to the bypass flow, the merge header 11a is forced to flow to the discharge port 13.

  In the drive module 100 according to the present embodiment, since a flow in which the refrigerant circulates in the annular flow path 8 occurs, centrifugal force acts on the bubbles mixed in the annular flow path 8, and the bubbles are pressed against the outer cylinder 2. The bubbles are also pressed against the outer cylinder 2 by buoyancy acting on the mixed bubbles. Therefore, it is easier to discharge the mixed bubbles if the opening 15 is provided close to the outer cylinder 2 side of the partition plate 9a.

  According to the present embodiment, since the air that has flowed into the annular flow path 8 can be efficiently discharged, the annular flow path 8 can be filled with the refrigerant, and pressure loss can be reduced. As a result, the desired refrigerant flow rate and heat dissipation capability can be obtained, and the effects that the lifespan of the devices constituting the rotating electrical machine 4 and the power conversion device 6 are increased can be obtained.

  Moreover, according to this Embodiment, the refrigerant | coolant which flows into the merge header 11a from the opening 15 can increase the refrigerant | coolant movement amount of the edge part near the flange 3b of the merge header 11a with a small refrigerant | coolant movement amount. As a result, after the air is collected at the end of the diversion header 10a near the flange 3b, the air bubbles that have flowed into the confluence header 11a through the opening 15 and have stagnated can be easily washed away by the refrigerant, and the air bubbles can be efficiently discharged. it can.

  Under conditions where bubbles are easily discharged, the bypass flow rate of the refrigerant at the opening 15 increases. When the bypass flow rate increases, the flow rate of the refrigerant that should flow through the annular flow path 8 becomes insufficient, and the desired heat dissipation capability cannot be obtained. Therefore, when the flow rate of the refrigerant supplied from the inlet 12 is increased, the pressure loss at the inlet 12 and the outlet 13 increases, and the refrigerant circulation loop (pipe, reservoir tank) connected to the inlet 12 and the outlet 13 is increased. Pressure loss in pumps and refrigerant-air heat exchangers (radiators, etc.) increases, pumps that generate refrigerant circulation driving force increase in size, and pipe diameters increase to reduce pressure loss, etc. The problem is that both the volume and weight of the system increase. A modification of the present embodiment for solving this problem is shown in FIG. 4B and will be described below.

  FIG. 4B illustrates a case where the end portions of the diversion header 10a and the merge header 11a are closer to the flange 3b than the end portion of the annular flow path 8 as a modified example of FIG. It is shown. In other words, the normal direction of the surface of the opening 15 is the wall 16, and the opening 15 is configured not to face the end of the annular flow path 8. As in FIG. 4A, the arrows indicate the flow of the refrigerant. According to this modification, the opening 15 and the end of the annular flow path 8 are arranged so as not to face each other, so that the refrigerant flow flowing from the annular flow path 8 and the bypass flow flowing out from the opening 15 collide. , Can prevent interference. As a result, a desired stable refrigerant flow rate and heat dissipation capability can be obtained. Furthermore, the space | interval of the opening 15 and the wall 16 is narrow compared with the width | variety of the circumferential direction of the diversion header 10a and the merge header 11a. For this reason, the refrigerant | coolant which flowed out from the opening 15 collides with the wall 16 as a collision jet, and a bypass flow volume can be suppressed by the pressure loss accompanying this collision jet. With a configuration that generates a small bypass flow rate, it is possible to smoothly discharge the bubbles from the opening 15 to the merge header 11a from the diversion header 10a, and to achieve a desired heat dissipation capability efficiently.

  The drive module 100 according to the present embodiment includes the rotating electrical machine 4 and the power conversion device 6 and is a three-phase drive system. Therefore, each of the drive modules 100 has a configuration of elemental devices based on multiples of 3. For example, the rotating electrical machine 4 is mainly composed of a stator in contact with the inner cylinder 1 and a mover built in the stator (not shown), and the stator is a multiple element of 3 (for example, a tooth or a coil group). It consists of the combination of. In addition, the power conversion device 6 includes an electric circuit board 5 for U phase, V phase, and W phase, a control board, a capacitor, and the like. In particular, the electric circuit board 5 that requires high-efficiency cooling is used for three phases. It consists of a number such as individual or six.

  Note that the rotating electrical machine 4 may change the number of electrical circuit boards 5 of the power converter 6 (for example, four or five teeth) to smooth the operation of the rotating electrical machine 4. Therefore, although the rotary electric machine 4 and the power converter device 6 are comprised from the element apparatus of the multiple of 3, it cannot be overemphasized that it is not restricted to the same number and a different division | segmentation number may be sufficient.

  In addition, although the case where the power converter device 6 was an inverter was demonstrated above, the power converter device 6 converts alternating current power into direct current power, and also converts this direct current power into alternating current power required for the drive of the rotary electric machine 4. It goes without saying that the same effect can be obtained even if the converter and the inverter are combined.

  As described above, in the drive module 100 according to the first embodiment, the rotary electric machine 4 whose main shaft protrudes on one side and the rotary electric machine 4 provided side by side on the opposite side to the one side and driving the rotary electric machine 4 are converted. The inner cylinder 1 in which the rotating electrical machine 4 and the power conversion device 6 are accommodated on the inside, the heat dissipating fins 14 are provided on the outer surface, the inner cylinder 1 is covered in the same axial direction as the inner cylinder 1, The outer cylinder 2 that forms the annular flow path 8 for circulating the refrigerant between the first cylinder 3, the first flange 3 a that closes the ends of the inner cylinder 1 and the outer cylinder 2 on the power conversion device 6 side, and the inner cylinder and the outer cylinder A second flange 3b that closes the end of the rotating electrical machine side, a branch header 10a that extends in the direction of the main shaft 4a of the rotating electrical machine 4 and diverts the refrigerant into the annular flow path 8, and a main shaft 4a of the rotating electrical machine 4 A merging header 11a extending in the direction and merging the refrigerant circulating in the annular flow path 8; A partition plate 9a that extends in the direction of the main shaft 4a of the rotating electrical machine 4 and divides between the diversion header 10a and the merging header 11a, and a first flange 3a or a position opposite to one side of the diversion header 10a. The inlet 12 provided through one of the outer cylinders 2 and the first flange 3a or the outer cylinder 2 provided at a position opposite to one side of the merge header 11a. The partition plate 9a is provided with an opening 15 at a position far from the inlet 12 and the outlet 13 in the direction of the main shaft 4a of the rotating electrical machine 4 and close to the second flange 3b. ing. For this reason, the drive module 100 according to Embodiment 1 can reliably discharge the air bubbles mixed in the annular flow path 8, and can dissipate heat efficiently with low pressure loss.

Embodiment 2. FIG.
FIG. 5 shows a drive module 200 according to the second embodiment. FIG. 5 is a cross-sectional view at the same position as FIG. The present embodiment is the same as the first embodiment except for the arrangement of the diversion header 10b, the merge header 11b, and the partition plate 9b from the first embodiment. In the present embodiment, the diversion header 10b, the merging header 11b, and the partition plate 9b are shaped to protrude outward from the outer cylinder 2 as compared with the first embodiment.

  According to this embodiment, since the thickness of the inner cylinder 1 can be reduced without reducing the flow cross-sectional area of the diversion header 10b and the merge header 11b, the cooling capacity of the liquid cooling jacket is maintained. Light weight or downsizing can be realized. On the other hand, when it is desired to increase the cooling capacity of the liquid cooling jacket, according to the present embodiment, the flow cross-sectional area of the diversion header 10b and the merge header 11b can be increased, and the pressure loss can be further increased. Since it can reduce and the drift of the annular flow path 8 can be suppressed more, the flow volume of a refrigerant | coolant can be increased.

Embodiment 3 FIG.
FIG. 6 is a diagram showing a drive module 300 according to the third embodiment. 6A is a cross-sectional view taken along line FF in FIG. 6B, and FIG. 6B is a cross-sectional view taken along line EE in FIG. 6A. The present embodiment is the same as the second embodiment except that the drain channel 17, the drain hole 18, and the plug 19 are provided in addition to the configuration of the second embodiment.

  In FIG. 6 (a), EE in FIG. 1 (b) does not pass through the center of the cut surface in order to illustrate the internal structure of the drain channel 17, the drain hole 18, and the plug 19 in an easy-to-understand manner.

  The drain channel 17 is a recess extending in the direction of the main shaft 4a in the lowermost part of the annular channel 8, that is, the inner surface of the outer cylinder 2 on the opposite side of the partition plate 9b by 180 degrees. The drain channel 17 is provided so that the flow cross-sectional area is larger than that of the annular channel 8. By providing the drain channel 17, dust contained in the refrigerant and dust generated by corrosion in the annular channel 8 can be trapped in the drain channel 17.

  Further, a drain hole 18 for discharging dust trapped in the drain channel 17 is provided through the outer cylinder 2. A plug 19 that closes the drain hole 18 is also provided. By providing the drain hole 18, it becomes easy to discharge the refrigerant in the annular flow path 8, and dust in the annular flow path 8 can be discharged.

  In the present embodiment, the drain hole 18 and the plug 19 are provided in the drain channel 17, but the outer cylinder is also provided in the configuration without the drain channel 17 as in the first and second embodiments. 2 can be provided with a drain hole 18 and a plug 19.

Embodiment 4 FIG.
FIG. 7 is a diagram showing a drive module 400 according to the fourth embodiment. 7A is a cross-sectional view taken along line H-H in FIG. 7B, and FIG. 7B is a cross-sectional view taken along line GG in FIG. 7A. In the drive module 100 shown in the first embodiment, the rotating electrical machine 4 and the power conversion device 6 are accommodated inside the inner cylinder 1. In the drive module 400 shown in the fourth embodiment, the rotating electrical machine 4 is accommodated inside the inner cylinder 1, but the power converter 6 is not accommodated inside the inner cylinder 1. Other configurations and functions of the drive module 400 shown in the fourth embodiment are the same as those of the drive module 100 shown in the first embodiment. In addition, illustration of the rotary electric machine 4 is abbreviate | omitted in sectional drawing of FIG.7 (b).

  As shown in FIG. 7B, the heat radiating fins 14 are divided into a plurality in the circumferential direction of the inner cylinder 1 or the rotating electrical machine 4 along the annular flow path 8 and arranged on the outer surface of the inner cylinder 1. . The radiation fin 14 provides the same effect as increasing the area in which the refrigerant contacts the inner cylinder 1 that has received the heat generated by the rotating electrical machine 4. Also, the cross-sectional area that flows is reduced. That is, the diameter per pressure of the refrigerant is reduced. As a result, the heat dissipation characteristics are improved.

  In the fourth embodiment, as shown in FIG. 7B, the radiating fins 14 are divided and arranged, and the annular flow path 8 includes a portion where the radiating fins 14 are attached and a portion where the radiating fins 14 are not attached. Consists of. By providing a portion where the radiation fins 14 are not mounted between the divided radiation fins 14, the pressure loss can be reduced. Further, by dividing the radiating fins 14, a portion where the refrigerant contacts the radiating fins 14 is generated by the number of divisions. Heat transfer is promoted to the portion where the refrigerant of the radiating fin 14 increased by the number of divisions by dividing the radiating fin 14 flows due to the leading edge effect. Furthermore, by dividing the radiation fins 14, the flow path length of each radiation fin 14 is shortened, so the development of the temperature boundary layer formed on the surface of the radiation fins 14 can be suppressed, and the radiation characteristics can be improved. Can be improved. Further, since the portion where the radiating fins 14 are not attached communicates in the axial direction, the flow equalization is promoted toward the flange 3b side of the annular flow path 8, and the flange 3b side of the annular flow path 8 where the heat radiating capacity is likely to be insufficient. It can dissipate heat appropriately.

  As described above, in the drive module 400 according to the fourth embodiment, the rotating electrical machine 4 in which the main shaft 4a protrudes on one side, the inner cylinder 2 in which the rotating electrical machine 4 is housed and the radiating fins 14 are provided on the outer surface, and An outer cylinder 1 that is provided in the same axial direction as the inner cylinder 2, covers the inner cylinder 2, and forms an annular flow path 8 that circulates refrigerant between the inner cylinder 2 and one of the inner cylinder 2 and the outer cylinder 1. The first flange 3a that closes the end portion of the inner cylinder 2, the second flange 3b that closes the other end portion of the inner cylinder 2 and the outer cylinder 1, and the main shaft 4a of the rotating electrical machine 4 extend in the direction of the ring to circulate the refrigerant. In the direction of the main shaft 4a of the rotating electric machine 4 and the diversion header 10a extending in the direction of the main shaft 4a of the rotating electric machine 4 and the merging header 11a that merges the refrigerant circulating through the annular flow path 8 A partition plate 9a extending to partition between the diversion header 10a and the merge header 10b; The inlet 12 provided through the first flange 3a or the second flange 3b of the outer cylinder to the first flange 3a side, and the first flange 3a or the second flange 3b of the outer cylinder 1 1 and the discharge port 13 provided penetrating to the flange 3a side, and the partition plate 9a is closer to the second flange 3b than the first flange 3a in the direction of the main shaft 4a of the rotating electrical machine 4. An opening 15 is provided. For this reason, the drive module 400 according to Embodiment 4 can reliably discharge the air bubbles mixed in the annular flow path 8, and can dissipate heat with low pressure loss and high efficiency.

  It should be noted that the present invention can be freely combined with each other within the scope of the invention, and each embodiment can be appropriately modified or omitted.

1 inner cylinder, 2 outer cylinder, 3a flange, 3b flange, 4 rotating electrical machine, 4a spindle,
5 electric circuit board, 6 power converter, 8 annular flow path, 9a partition plate, 9b partition plate,
10a shunt header, 10b shunt header, 11a join header, 11b join header, 12 inlet, 13 outlet, 14 heat radiation fin, 15 opening, 17 drain flow path,
100, 200, 300, 400 Drive module

Claims (11)

A rotating electric machine whose main shaft protrudes on one side;
An inner cylinder in which the rotating electrical machine is accommodated on the inner side and a heat radiating fin is provided on the outer surface;
An outer cylinder that is provided in the same axial direction as the inner cylinder, covers the inner cylinder, and forms an annular flow path for circulating a refrigerant between the inner cylinder;
A first flange for closing one end of the inner cylinder and the outer cylinder;
A second flange for closing the other end of the inner cylinder and the outer cylinder;
A diversion header extending in the direction of the main shaft of the rotating electrical machine and diverting the refrigerant into the annular flow path;
A merge header that extends in the direction of the main shaft of the rotating electrical machine and merges the refrigerant that has circulated through the annular flow path;
A partition plate extending in the direction of the main shaft of the rotating electrical machine and partitioning between the diversion header and the merge header;
An inlet provided penetrating from the first flange or the second flange of the outer cylinder to the first flange;
A discharge port provided penetrating to the first flange side from the first flange or the second flange of the outer cylinder;
With
The drive module according to claim 1, wherein an opening is provided in the partition plate at a position closer to the second flange than the first flange in the direction of the main shaft of the rotating electrical machine. Provided inside the inner cylinder side by side with the rotating electrical machine in the direction of the main shaft of the rotating electrical machine, comprising a power conversion device that drives the rotating electrical machine,
The first flange closes the power converter side end of the inner cylinder and the outer cylinder,
The drive module according to claim 1, wherein the second flange closes ends of the inner cylinder and the outer cylinder on the rotating electrical machine side. The drive module according to claim 1, wherein a wall is provided in a direction normal to the surface of the opening. The power conversion device has a plurality of electric circuit boards arranged in the circumferential direction on the inner surface of the inner cylinder,
The heat dissipating fins are divided in the circumferential direction of the inner cylinder by the same number as the number of the electric circuit boards included in the power converter, and each of the divided heat dissipating fins is the plurality of the electric circuits. The drive module according to claim 2, wherein the drive module is provided on an outer surface of the inner cylinder corresponding to each arrangement of the substrates. The drive module according to claim 4, wherein the number of the electric circuit boards is a multiple of three. Of the heat dissipating fins, the structure of the portion in the annular flow path that is adjacent to the rotating electrical machine via the inner cylinder, and the portion of the ring flow path that is adjacent to the power conversion device via the inner cylinder The drive module according to claim 2, wherein the structure is different. The position where the injection port and the discharge port pass through the first flange are closer to the annular channel than the partition plate in the circumferential direction of the annular channel, respectively. The drive module described in 1. The drive module according to claim 1, wherein a connection portion between the inlet and the diversion header has an enlarged flow path shape from the inlet toward the diversion header. The drive module according to claim 1, wherein a connection portion between the discharge port and the merge header has a reduced flow path shape from the merge header toward the discharge port. 3. The drive module according to claim 1, wherein the branch header, the partition plate, and the merge header have a shape protruding from the outer cylinder toward a radially outer side of the outer cylinder. The drive module according to claim 1, wherein a depression is provided at a lowermost part in the annular flow path.

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