WO2015087707A1 - Module d'entraînement - Google Patents

Module d'entraînement Download PDF

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Publication number
WO2015087707A1
WO2015087707A1 PCT/JP2014/081366 JP2014081366W WO2015087707A1 WO 2015087707 A1 WO2015087707 A1 WO 2015087707A1 JP 2014081366 W JP2014081366 W JP 2014081366W WO 2015087707 A1 WO2015087707 A1 WO 2015087707A1
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WIPO (PCT)
Prior art keywords
flange
inner cylinder
header
flow path
drive module
Prior art date
Application number
PCT/JP2014/081366
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English (en)
Japanese (ja)
Inventor
一法師　茂俊
浩之 東野
義浩 深山
淳一 相澤
康滋 椋木
井上　正哉
佳明 橘田
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2015552385A priority Critical patent/JP6042000B2/ja
Publication of WO2015087707A1 publication Critical patent/WO2015087707A1/fr

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    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K11/00—Structural association of dynamo-electric machines with electric components or with devices for shielding, monitoring or protection
    • H02K11/30—Structural association with control circuits or drive circuits
    • H02K11/33—Drive circuits, e.g. power electronics
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/20—Casings or enclosures characterised by the shape, form or construction thereof with channels or ducts for flow of cooling medium
    • H02K5/203—Casings or enclosures characterised by the shape, form or construction thereof with channels or ducts for flow of cooling medium specially adapted for liquids, e.g. cooling jackets

Definitions

  • the present invention relates to a drive module integrated with a liquid cooling jacket for cooling.
  • the refrigerant inlet and outlet are provided on the radially outer side of the annular channel, 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.
  • 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.
  • 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.
  • An inlet provided through the flange side of the first flange, and the first flange or outer cylinder And a discharge port provided penetrating from the second flange to the first flange side, and the partition plate is opened at a position closer to the second flange than the first flange in the direction of the main shaft of the rotating electrical machine.
  • the air bubbles mixed in the annular flow path can be efficiently discharged by the opening provided in the partition plate.
  • a drive module that can dissipate heat with low pressure loss and high efficiency can be obtained.
  • 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
  • FIG. 1B is a cross-sectional view taken along the line AA in FIG.
  • 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.
  • 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
  • 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.
  • a diversion header 10a 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.
  • 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.
  • 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.
  • 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.
  • 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 separately formed members. 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • an extension line of the attachment position of the inlet 12 and the outlet 13 is indicated by a dotted line.
  • 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 the 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.
  • 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.
  • pressure loss can be reduced by making the connection part of the discharge port 13 and the confluence
  • 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 3a 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.
  • 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.
  • the refrigerant circulates through the liquid cooling jacket, whereby the rotating electrical machine 4 and the power converter 6 can be cooled.
  • the heat dissipating fins 14 are divided into six, which is 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.
  • 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.
  • 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.
  • 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.
  • the heat distribution fin 14 can radiate heat more efficiently on the shunt header 10a side.
  • 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.
  • 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 showing the entire heat dissipating fin 14 composed of 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.
  • 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
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the axial width Wa of the fins 14a may be set smaller than the axial width Wb of the fin 14b.
  • 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.
  • 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.
  • FIG. 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.
  • FIG. 4A is an enlarged view of the present embodiment
  • FIG. 4B is an enlarged view of a modified example of the present embodiment.
  • 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.
  • 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.
  • 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.
  • the opening 15 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.
  • 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.
  • 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.
  • 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.
  • the bubbles in the annular flow path 8 can be reliably discharged as described above.
  • 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.
  • 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.
  • 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.
  • 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).
  • the ellipses, i.e., circles, having the same value of the sides hereinafter referred to as the sides in the radial direction
  • 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.
  • the width in the direction of the main axis 4a corresponds to the width in the direction of the main axis 4a
  • 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.
  • 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.
  • the air flowing into the annular flow path 8 can be efficiently discharged, the inside of the annular flow path 8 can be filled with the refrigerant, and the pressure loss can be reduced.
  • 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.
  • the refrigerant flowing into the merge header 11a from the opening 15 can increase the amount of refrigerant moved at the end of the merge header 11a near the flange 3b with a small amount of refrigerant move.
  • 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.
  • 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.
  • 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.
  • the arrows indicate the flow of the refrigerant.
  • 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.
  • interval of the opening 15 and the wall 16 is narrow compared with the width
  • 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.
  • 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 includes the rotating electrical machine 4 and the power converter 6 and is a three-phase drive system, and thus has a configuration of elemental devices based on multiples of 3 respectively.
  • 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.
  • 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.
  • 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.
  • the rotating electrical machine 4 may change the number of electric circuit boards 5 of the power conversion device 6 (for example, four or five teeth) to make the operation of the rotating electrical machine 4 smooth. 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
  • 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.
  • 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 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
  • the inlet 12 provided through one of the outer cylinders 2 and the first flange 3a or the outer cylinder 2 are provided at a position opposite to one side of the joining 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. It has been. 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • FIG. 6 is a diagram showing a drive module 300 according to the third embodiment.
  • 6A is a sectional view taken along line FF in FIG. 6B
  • FIG. 6B is a 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.
  • 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, drain hole 18 and 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 side opposite to 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.
  • 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.
  • 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.
  • FIG. 7 is a diagram showing a drive module 400 according to the fourth embodiment. 7A is a cross-sectional view taken along line HH in FIG. 7B, and FIG. 7B is a cross-sectional view taken along line GG in FIG. 7A.
  • the rotating electrical machine 4 and the power conversion device 6 are accommodated inside the inner cylinder 1.
  • 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.
  • illustration of the rotary electric machine 4 is abbreviate
  • 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.
  • 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.
  • 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.
  • 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
  • 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.
  • a partition plate 9a extending to partition between the diversion header 10a and the merge header 10b From 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 from the first flange 3a or the second flange 3b of the outer cylinder 1 And a discharge port 13 provided penetrating to the first flange 3a side.
  • 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 in the front.

Landscapes

  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Microelectronics & Electronic Packaging (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Motor Or Generator Frames (AREA)

Abstract

Le but de la présente invention est d'obtenir un module d'entraînement grâce auquel des bulles d'air piégées dans un chemin de flux annulaire peuvent être évacuées de manière fiable, et une chaleur peut être dissipée très efficacement avec une faible perte de pression. Un module d'entraînement selon la présente invention comporte : une machine électrique rotative ; un cylindre interne qui possède la machine électrique rotative reçue dans celui-ci, et qui possède des ailettes de dissipation thermique disposées sur une surface externe de celui-ci ; un cylindre externe qui est disposé de manière coaxiale par rapport au cylindre interne, qui recouvre le cylindre interne, et qui, en association avec le cylindre interne, forme un chemin de flux annulaire dans lequel un réfrigérant est réalisé pour circuler ; une première bride et une seconde bride qui ferment les deux extrémités du cylindre interne et du cylindre externe ; un collecteur de branchement qui s'étend le long d'une direction d'un arbre principal de la machine électrique rotative, et qui branche le réfrigérant dans le chemin de flux annulaire ; un collecteur de fusion qui s'étend le long de la direction de l'arbre principal de la machine électrique rotative, et qui fusionne le réfrigérant en provenance du chemin de flux annulaire ; une plaque de séparation qui forme une séparation entre le collecteur de branchement et le collecteur de fusion ; et une entrée et une sortie qui sont disposées afin de passer à travers la première bride et le cylindre externe. Dans la plaque de séparation, une ouverture est disposée dans un emplacement plus proche de la seconde bride que de la première bride dans la direction de l'arbre principal de la machine électrique rotative.
PCT/JP2014/081366 2013-12-11 2014-11-27 Module d'entraînement WO2015087707A1 (fr)

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JP2013-255770 2013-12-11
JP2013255770 2013-12-11

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WO2015087707A1 true WO2015087707A1 (fr) 2015-06-18

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Cited By (8)

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JP2017212821A (ja) * 2016-05-26 2017-11-30 本田技研工業株式会社 ステータ
FR3051995A1 (fr) * 2016-05-27 2017-12-01 Valeo Systemes De Controle Moteur Compresseur electrique avec circuit de refroidissement en trois parties
JP2019083633A (ja) * 2017-10-31 2019-05-30 三菱電機株式会社 回転電機
JP2020516218A (ja) * 2017-03-28 2020-05-28 エルジー エレクトロニクス インコーポレイティド モーター
WO2021079557A1 (fr) * 2019-10-23 2021-04-29 株式会社明電舎 Structure de passage de réfrigérant pour moteur
US11011955B2 (en) 2017-03-28 2021-05-18 Lg Electronics Inc. Motor
JP2023504625A (ja) * 2019-12-06 2023-02-06 珠海英搏爾電気股▲フン▼有限公司 積層バスバーユニット、モータ制御装置、駆動アセンブリ、及び交通機関
DE112015002495B4 (de) 2014-05-28 2023-10-05 Mitsubishi Electric Corporation Elektrische Energie umwandelnde Vorrichtung

Families Citing this family (1)

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DE102021201804A1 (de) * 2021-02-25 2022-08-25 Volkswagen Aktiengesellschaft Gehäuse für eine elektrische Maschine mit einem sich selbst entlüftenden Kühlmantel

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JP2007143247A (ja) * 2005-11-16 2007-06-07 Ishikawajima Harima Heavy Ind Co Ltd 水冷モータおよびそのモータフレームの水路加工方法
JP2009247085A (ja) * 2008-03-31 2009-10-22 Hitachi Ltd 回転電機
US20120025638A1 (en) * 2010-07-30 2012-02-02 General Electric Company Apparatus for cooling an electric machine

Patent Citations (3)

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JP2007143247A (ja) * 2005-11-16 2007-06-07 Ishikawajima Harima Heavy Ind Co Ltd 水冷モータおよびそのモータフレームの水路加工方法
JP2009247085A (ja) * 2008-03-31 2009-10-22 Hitachi Ltd 回転電機
US20120025638A1 (en) * 2010-07-30 2012-02-02 General Electric Company Apparatus for cooling an electric machine

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112015002495B4 (de) 2014-05-28 2023-10-05 Mitsubishi Electric Corporation Elektrische Energie umwandelnde Vorrichtung
JP2017212821A (ja) * 2016-05-26 2017-11-30 本田技研工業株式会社 ステータ
FR3051995A1 (fr) * 2016-05-27 2017-12-01 Valeo Systemes De Controle Moteur Compresseur electrique avec circuit de refroidissement en trois parties
US11011955B2 (en) 2017-03-28 2021-05-18 Lg Electronics Inc. Motor
JP2020516218A (ja) * 2017-03-28 2020-05-28 エルジー エレクトロニクス インコーポレイティド モーター
JP2019083633A (ja) * 2017-10-31 2019-05-30 三菱電機株式会社 回転電機
CN114586262A (zh) * 2019-10-23 2022-06-03 株式会社明电舍 电机的冷却液通路结构
JP7053554B2 (ja) 2019-10-23 2022-04-12 株式会社明電舎 モータの冷却液通路構造
JP2021069179A (ja) * 2019-10-23 2021-04-30 株式会社明電舎 モータの冷却液通路構造
CN114586262B (zh) * 2019-10-23 2022-09-23 株式会社明电舍 电机的冷却液通路结构
WO2021079557A1 (fr) * 2019-10-23 2021-04-29 株式会社明電舎 Structure de passage de réfrigérant pour moteur
JP2023504625A (ja) * 2019-12-06 2023-02-06 珠海英搏爾電気股▲フン▼有限公司 積層バスバーユニット、モータ制御装置、駆動アセンブリ、及び交通機関
JP7427818B2 (ja) 2019-12-06 2024-02-05 珠海英搏爾電気股▲フン▼有限公司 モータ制御装置、駆動アセンブリ、及び交通機関
JP7427816B2 (ja) 2019-12-06 2024-02-05 珠海英搏爾電気股▲フン▼有限公司 積層バスバーユニット、モータ制御装置、駆動アセンブリ、及び交通機関
JP7427817B2 (ja) 2019-12-06 2024-02-05 珠海英搏爾電気股▲フン▼有限公司 モータ制御装置、駆動アセンブリ、及び交通機関
JP7443522B2 (ja) 2019-12-06 2024-03-05 珠海英搏爾電気股▲フン▼有限公司 駆動アセンブリ、及び交通機関
JP7506778B2 (ja) 2019-12-06 2024-06-26 珠海英搏爾電気股▲フン▼有限公司 駆動アセンブリ、及び交通機関

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