JP6996356B2 - Rotating machine cooling device - Google Patents

Description

The present disclosure relates to a cooling device for a rotary electric machine.

Conventionally, in an electric motor, a cooling device in which an oil passage is provided in the core of a rotor, cooling oil is supplied to the oil passage, and the cooling oil is further injected into the inside of a housing from an opening of the oil passage is known (for example, Patent Document). 1).
Further, in the above-mentioned conventional technique, the discharge side of the pump is connected to the oil passage, the suction side of the pump is connected to the bottom of the motor housing, and the cooling oil is circulated in the oil passage.

Japanese Unexamined Patent Publication No. 2012-105487

In the above prior art, bubbles are generated when the cooling oil is agitated in the housing. Then, the cooling oil containing the bubbles is sucked by a pump, supplied to the oil passage, and injected into the housing again, and the circulation is repeated.
Therefore, there is a possibility that the bubbles expand in volume due to heat and cause oil leakage, or the heat transfer coefficient of the cooling oil is lowered by the bubbles and the cooling performance is deteriorated.

The present invention has been made by paying attention to the above problems, and an object of the present invention is to provide a cooling device for a rotary electric machine capable of reducing air bubbles generated in cooling oil and suppressing oil leakage and deterioration of cooling performance.

In order to achieve the above-mentioned object, the cooling device of the rotary electric machine of the present disclosure is used.
A tubular portion formed in a tubular shape, a spiral oil passage formed spirally along the outer circumference of the tubular portion, and a hollow formed inside the tubular portion in the housing oil passage through which the cooling oil flows. A gas-liquid separation section including a gas-liquid separation communication passage that communicates the section and the spiral oil passage is provided.

In the cooling device of the rotary electric machine of the present disclosure, it is possible to remove air bubbles from the cooling oil flowing through the housing oil passage and suppress oil leakage and deterioration of cooling performance caused by the air bubbles contained in the cooling oil.

It is an overall schematic diagram which shows the whole outline of the cooling device of the rotary electric machine of Embodiment 1. FIG. It is sectional drawing of the cooling device of the rotary electric machine of Embodiment 1, and shows the sectional view of the position of the S2-S2 line of FIG. It is a perspective view which shows the spiral oil passage forming member of the cooling device of the rotary electric machine of Embodiment 1. FIG. FIG. 5 is an enlarged cross-sectional view of a main part of the cooling device of the rotary electric machine according to the first embodiment. It is a top view which shows the 1st plate material used for the cooling device of the rotary electric machine of Embodiment 1. FIG. It is a top view which shows the 2nd plate material used for the cooling device of the rotary electric machine of Embodiment 1. FIG. It is explanatory drawing of the molding method of each plate material of the cooling device of the rotary electric machine of Embodiment 1. FIG. It is explanatory drawing of the manufacturing procedure of the spiral oil passage forming member in the cooling device of the rotary electric machine of Embodiment 1. FIG. It is explanatory drawing of the manufacturing procedure of the spiral oil passage forming member in the cooling device of the rotary electric machine of Embodiment 1. FIG. It is a front view which shows the connection port of the 1st side oil passage in the cooling device of the rotary electric machine of Embodiment 1. FIG. It is sectional drawing which shows the non-gas-liquid separation part in the cooling apparatus of the rotary electric machine of Embodiment 1, and shows the sectional view at the position of the line S8B-S8B of FIG. It is sectional drawing which shows the gas-liquid separation part in the cooling apparatus of the rotary electric machine of Embodiment 1, and shows the sectional view at the position of the S8C-S8C line of FIG. It is sectional drawing which shows the main part of the housing oil passage in the cooling device of the rotary electric machine of Embodiment 1, and shows the sectional drawing at the position of the S8D-S8D line of FIG. It is sectional drawing which shows the main part of the housing oil passage in the cooling device of the rotary electric machine of Embodiment 1, and shows the sectional view at the position of the S8E-S8E line of FIG. It is sectional drawing which shows the main part of the housing oil passage in the cooling device of the rotary electric machine of Embodiment 1, and shows the sectional drawing at the position of the S8F-S8F line of FIG. It is an operation explanatory drawing in the spiral oil passage of the cooling device of the rotary electric machine of Embodiment 1. FIG. It is a perspective view of the main part of the cooling device of the rotary electric machine of Embodiment 1, and shows the part surrounded by the P9B line of FIG. It is an operation explanatory view which shows the gas-liquid separation state in the cooling device of the rotary electric machine of Embodiment 1. FIG. It is a top view which shows the other example of a plate material. It is a top view which shows the other example of a plate material. It is a top view which shows the other example of a plate material.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
(Embodiment 1)
First, the cooling device of the rotary electric machine of the first embodiment (hereinafter, simply referred to as a cooling device) will be described with reference to FIG.

This cooling device uses cooling oil to cool the rotor 1 (see FIG. 2) and the stator 2 (see FIG. 2) as cooling target portions inside the motor M, and circulates the oil pump 10 and the cooling oil. A circulation oil passage 20 is provided.

The circulation oil passage 20 includes a lower oil passage 21, a first side oil passage 22, a housing oil passage 23, a second side oil passage 24, and a motor internal oil passage 25.
The lower oil passage 21 connects the oil pan 31 provided at the bottom of the motor housing 30 forming the outer shell of the motor M and the suction port of the oil pump 10.

The first side oil passage 22 passes through the first cover 51 that closes one end (the left end in FIG. 1) of the motor housing 30 in the axial direction (arrow direction), and is from the discharge side of the oil pump 10 to the motor housing 30. It is an oil channel extending to the upper part.

The housing oil passage 23 is an oil passage formed in the upper part of the motor housing 30 along an axial direction (direction of arrow C in FIG. 1) which is a direction along the rotation center axis of the motor M.
Further, in the motor housing 30, as shown in the side view of the motor housing 30 viewed from the arrow SS direction in FIG. 1, a cooling water channel 32 having a substantially C-shaped cross section so as to surround the stator 2 is provided in the motor housing 30. It is provided along the axial direction. Although detailed description is omitted, the motor M is cooled by the cooling water circulating in the cooling water channel 32.
The housing oil passages 23 are arranged side by side in the vicinity of the cooling water passages 32.

The second side oil passage 24 is formed in a second cover 52 that closes the other end in the axial direction of the motor housing 30 (the right end in FIG. 1), and communicates the housing oil passage 23 and the motor internal oil passage 25. It is an oil channel extending in the vertical direction.

The oil passage 25 inside the motor is an oil passage that supplies cooling oil to the heat generating portion of the motor M. As such a motor internal oil passage 25, for example, similar to that described in Patent Document 1, oil passes through the inside of the rotary shaft 1a and the rotor core 1b of the rotor 1 of the motor M and toward the stator 2 on the outer periphery thereof. It is possible to use an opening so as to scatter. As shown in FIG. 1, the oil scattered from the oil passage 25 inside the motor to the motor chamber 30a accommodating the rotor 1 of the motor M and the like falls into the oil pan 31 described above and is temporarily stored.

(Explanation of spiral oil passage)
The housing oil passage 23 is provided with a pair of spiral oil passages 61, 61.
These spiral oil passages 61 and 61 are formed by a circular tubular hole 33 having a circular cross-sectional shape and a spiral oil passage forming member 70 shown in FIG. 3 inserted into the circular tubular hole 33.

FIG. 3 is a perspective view showing a spiral oil passage forming member 70.
As shown in the figure, the spiral oil passage forming member 70 has a circular inner cylinder portion 71 and a spiral that is raised from the outer periphery of the inner cylinder portion 71 and is centered on the axis of the inner cylinder portion 71. It has a pair of spiral vertical walls 72, 72 in shape.

The spiral oil passage forming member 70 is inserted into the circular tubular hole 33, and the tips of the spiral vertical walls 72 and 72 are in contact with or close to the inner circumference of the circular tubular hole 33. A pair of spiral oil passages 61, 61 are formed between the tubular portion 71 and the circular tubular hole 33.

The circular tubular hole 33 may be formed directly in the motor housing 30, but in the first embodiment, the spiral oil passage is provided in the outer pipe 75 (see FIG. 4) having the inner peripheral surface as the circular tubular hole 33. The one in which the forming member 70 is inserted is integrally inserted into the hole 33a formed in the motor housing 30.

Further, the inner cylinder portion 71 is formed in a hollow cylindrical shape, and an air passage (hollow passage) 73 having a circular cross section is provided inside the inner cylinder portion 71.

FIG. 4 is an enlarged cross-sectional view showing a portion of the housing oil passage 23 of the motor housing 30 and the second side oil passage 24 of the second cover 52. As shown in FIG. 4, the portion of the housing oil passage 23 having the spiral oil passages 61 and 61 is axially divided into a non-air-liquid separation portion 61a and a gas-liquid separation portion 61b.

As will be described later, the gas-liquid separation unit 61b is a region for separating the cooling oil into the cooling oil (air) containing bubbles and the cooling oil (liquid) not containing bubbles, and the spiral oil passages 61 and 61, respectively. It is provided with a gas-liquid separation communication passage 74 (see FIGS. 8C and 9B) that communicates the air passage 73 with the air passage 73.
On the other hand, the non-air-liquid separation portion 61a does not have the gas-liquid separation communication passage 74, and the spiral oil passages 61 and 61 and the air passage 73 are blocked by the inner cylinder portion 71.

Next, the details of the spiral oil passage forming member 70 including the description of the non-air-liquid separation portion 61a and the gas-liquid separation portion 61b will be described.
The spiral oil passage forming member 70 is formed by laminating a first plate material 81 and a second plate material 82 having a planar shape shown in FIGS. 5A and 5B in a direction along the axial direction.

The plate members 81, 82 extend in the outer radial direction from the outer circumferences of the annular portions 81a, 82a and the annular portions 81a, 82a, and are symmetrically provided at positions different from each other by 180 degrees in the circumferential direction in the annular portions 81a, 82a. The pair of ribs 81b and 82b are provided. The second plate material 82 has a notch 82c formed in the annular portion 82a at the center position between the ribs 81b and 81b by cutting the annular portion 82a and communicating the inside and outside thereof.

At the tips of the ribs 81b and 82b, protrusions 81d and 82d protruding in the axial direction are provided on one of the front and back surfaces (upper surface in the drawing). The protrusion margins of these protrusions 81d and 82d in the axial direction have dimensions equal to the plate thickness of each of the plate members 81 and 82. Further, the protrusions 81d and 82d are formed by molding the plate materials 81 and 82, respectively.

Further, in the first embodiment, the first plate material 81 and the second plate material 82 are formed from the electromagnetic steel sheet 100 shown in FIG. 6, which is used to form the rotor core 1b. That is, it is known that the rotor core 1b is formed by laminating an annular plate member 101. When such an electromagnetic steel sheet 100 is punched out to form an annular plate material 101, a scrap material 102 is generated on the inner circumference thereof. In the first embodiment, the scrap 102 is punched out to form the second plate 82 and the first plate 81 (not shown in FIG. 6). Therefore, the offcuts 102 can be effectively used.

Next, a procedure for manufacturing the spiral oil passage forming member 70 by laminating the first plate material 81 and the second plate material 82 in the axial direction and the spiral oil passage forming member 70 will be described.
In the spiral oil passage forming member 70, the non-air-liquid separation portion 61a is formed by laminating the first plate member 81. Further, the gas-liquid separation portion 61b is formed by laminating the second plate material 82.

When laminating the two plate materials 81 and 82, the laminating jig 200 shown in FIG. 7A is used.
The laminating jig 200 is formed by erecting a cylindrical portion 202 at a right angle on a disk-shaped base portion 201. Further, the cylindrical portion 202 can be fitted to the annular portions 81a and 82a of the plate members 81 and 82 so as to be relatively rotatable, and its outer diameter is slightly smaller than the inner diameter of the annular portions 81a and 82a. It is formed.

Then, the respective plate materials 81 and 82 are laminated on the base portion 201 as shown in FIG. 7A by inserting the cylindrical portion 202 of the laminating jig 200 into the annular portions 81a and 82a.
At the time of this laminating, first, the first plate material 81 is laminated in order to form the non-air-liquid separation portion 61a. Further, after this laminating, the inner circumference of the annular portion 81a of the first plate material 81 is used as a rotation hole, and the first plate material 81 is rotated with respect to the cylindrical portion 202 of the laminating jig 200.

That is, as shown in FIG. 7B, when the upper first plate material 81 is rotated in the clockwise direction with respect to the lower first plate material 81, the rotation is caused by the upper first plate material 81. The clockwise edge of the rib 81b abuts against the protrusion 81d of the lower rib 81b and is regulated.

By stacking the first plate materials 81 in order from the lower side while repeating such stacking and clockwise rotation, the first plate materials 81 that are vertically adjacent to each other are positioned in the circumferential direction by the width dimension of the protrusion 81d. The ribs 81b are continuously arranged in a spiral shape. Due to the ribs 81b arranged continuously in this way, a pair of spiral vertical walls 72 (see FIG. 2) are arranged side by side apart from each other in the axial direction, and between the spiral vertical walls 72 and 72. Each spiral oil passage 61, 61 is formed. Further, the inner circumference of the annular portion 81a is continuous in the axial direction to form the inner cylinder portion 71 and the air passage 73.

Next, the formation of the gas-liquid separation portion 61b will be described.
As described above, after a predetermined number of first plate materials 81 are laminated to form the non-air-liquid separation portion 61a, the second plate material 82 is laminated and rotated clockwise in the same manner as the first plate material 81. By repeating the motion, the gas-liquid separation portion 61b can be formed. That is, the notch 82c is arranged spirally continuously or discontinuously to form a gas-liquid separation communication passage 74 (see FIG. 9B), and both spiral oil passages 61 and 61 and the air passage 73 are communicated with each other. ..

As shown in FIG. 5B, when one second plate material 82 has a structure having only one notch 82c, the air passages 73 communicate with each of the pair of spiral oil passages 61 and 61. It is necessary to form the liquid separation communication passage 74.

Therefore, a plurality of second plate materials 82 are laminated to form a gas-liquid separation communication passage 74 that communicates one of the pair of spiral oil passages 61, 61 with the air passage 73, and then the other spiral oil passage 74 is formed. A gas-liquid separation communication passage 74 that communicates the passage 61 and the air passage 73 is formed.

Specifically, one of the gas-liquid separation communication passages 74 (first gas-liquid separation communication passage 74) is, for example, a second plate material 82 in which the notch 82c is arranged at the position shown in FIG. 5B in the clockwise direction. It is formed by stacking multiple sheets while shifting the phase. In that case, the gas-liquid separation communication passage 74 (second gas-liquid separation communication passage 74) communicating the other spiral oil passage 61 and the air passage 73 is a second plate material in which the second plate material 82 is shown in FIG. 5B. It is formed by laminating the 82 in a state where the phase is shifted 180 degrees in the clockwise direction and the left and right sides are relatively reversed.

In the above, it is described that a plurality of the second plate materials 82 are laminated, but for example, the second plate materials 82 whose phases are shifted in the clockwise direction by 180 degrees may be alternately arranged. In this case, the first gas-liquid separation communication passage 74 and the second gas-liquid separation communication passage 74 are discontinuous in the direction of the spiral, and are arranged every other second plate material 82.

In any case (whether the gas-liquid separation communication passage 74 is continuous or discontinuous to some extent), the gas-liquid separation communication passage 74 is located at the intermediate position between the spiral vertical walls 72 in the axial direction. It is formed so as to penetrate the inner cylinder portion 71 in the radial direction (see FIG. 9B).

The laminated two plate materials 81 and 82 are integrally bonded to each other by adhesion, welding, engagement, or the like. Alternatively, the cylindrical portion 202 may be removable from the base portion 201, and both plate members 81, 82 laminated while attached to the cylindrical portion 202 may be sandwiched and fixed by fastening members or the like from both sides in the axial direction. ..

Next, based on FIGS. 4, 8A, 8B, 8C, 8D, 8E, and 8F, the two spiral oil passages 61, 61 and the air passage 73, and the first side oil passage 22, the first side oil passage 22, No. The connection between the two side oil passages 24 and the motor chamber 30a will be described.
8A, 8B, 8C, 8D, 8E, and 8F are S8A-S8A line, S8B-S8B line, S8C-S8C line, S8D-S8D line, and S8E-S8E, respectively, in FIG. The cross section of the position of the line, S8F-S8F line is shown. Further, in FIG. 4, the spiral oil passages 61 and 61 are shown in a shape continuous in the axial direction by omitting the illustration of the spiral vertical wall 72.

As shown in FIG. 4, the cooling oil inlet 61c at the upstream end (left end in the figure) of each spiral oil passage 61, 61 is connected to the first side oil passage 22. Since each of the spiral oil passages 61 and 61 is partitioned by a spiral vertical wall 72, the first side oil passage 22 is connected to each of the spiral oil passages 61 and 61 by two connections shown in FIG. 8A. It has mouths 22a and 22a. Therefore, the cooling oil inlets 61c of the spiral oil passages 61 and 61 are connected to the connection port 22a of the first side oil passage 22, respectively.

Then, at the position of the non-air-liquid separation portion 61a (see FIG. 4), as shown in FIG. 8B, each spiral oil passage 61, 61 has an air passage 73 due to an inner cylinder portion 71 formed by the annular portion 81a. Is blocked.

On the other hand, at the position of the gas-liquid separation portion 61b (see FIG. 4), as shown in FIG. 8C, the inner circumference of both spiral oil passages 61 and 61 and the air passage 73 are formed by the notch 82c. The separated communication passage 74 penetrates the inner cylinder portion 71 and communicates with the inner cylinder portion 71.

The communication shown in FIG. 8D is connected to a portion (position of the S8D-S8D line in FIG. 4) adjacent to the downstream end portion (rightward end portion in FIG. 4) of the spiral oil passage forming member 70 in the motor housing 30. An oil passage 34 and a bubble discharge passage 35 are formed.

The communication oil passage 34 is formed in an annular shape at positions continuously in the axial direction at the outlets (spiral oil passage outlets) 61d and 61d of both spiral oil passages 61 and 61. Further, the bubble discharge passage 35 is continuously arranged in the axial direction at the hollow portion outlet 73a at the right end in FIG. 4 of the air passage 73, and has a circular cross section as shown in FIG. 8D. It is formed. The bubble discharge passage 35 is shielded from the communication oil passage 34 by a cylindrical portion 36 having substantially the same diameter as the inner cylinder portion 71 of the spiral oil passage forming member 70.

Further, the motor housing 30 is formed integrally with the cylindrical portion 36 at a position near the second cover 52 (position of the S8E-S8E line in FIG. 4) as shown in FIG. 8E, and is formed at the lower part of the communication oil passage 34. A barrier wall portion 37 is provided to block the oil in the axial direction.

Further, in the motor housing 30, at the position of the S8F-S8F line in FIG. 4 which is closer to the second cover 52, as shown in FIG. 8F, the motor chamber 30a passes from the bubble discharge path 35 through the blocking wall portion 37. The bubble discharge droop 38 communicated with the above is formed. See FIG. 4 for the point that the bubble discharge droop 38 is communicated with the motor chamber 30a.

Further, as shown in FIG. 4, the communication oil passage 34 is connected to the second side oil passage 24 formed in the second cover 52 without interfering with the barrier wall portion 37 and the bubble discharge hanging passage 38. There is.

Next, the details and operations of both spiral oil passages 61 and 61 will be described.
When the cooling oil is supplied from the first side oil passage 22 to the spiral oil passages 61, 61, the cooling oil flows spirally along the spiral vertical wall 72 as it flows along the axial direction. , As shown by the arrow FL in FIG. 9A, the centrifugal force acts in the outer radial direction.

At this time, the centrifugal force (centrifugal acceleration a (m / s ² )) is such that the spiral oil passages 61 and 61 have an oil passage radius of r (m: see FIG. 9A), an input flow rate of V (L / min), and oil. When the road cross-sectional area is S (m ² : see FIG. 9B), it can be expressed by the following equation (1).
a∝ [V ² / ⁽ S2 ・ r)] ・ ・ ・ (1)

Therefore, the centrifugal force (centrifugal acceleration a) is proportional to the input flow rate V and inversely proportional to the oil passage cross-sectional area S and the oil passage radius r. The oil passage cross-sectional area S is determined by the distance d between the spiral vertical walls 72 and 72 determined by the thickness of each plate material 81 and 82 and the number of laminated plates, and the radial length hr of the ribs 81b and 82b. It is possible to set based on.
Then, in the first embodiment, these values are set so that the centrifugal force (centrifugal acceleration a) acting on the cooling oil becomes larger than the buoyancy of the bubbles.

As a result, when the cooling oil flows through the spiral oil passages 61 and 61, the inner cylinder portion 71 in which the cooling oil having a low volume fraction containing bubbles and bubbles flows in the inner diameter direction of the spiral oil passages 61 and 61. Gather around the perimeter of. On the other hand, the cooling oil having a high volume fraction that does not contain bubbles or has a low content of bubbles collects in the inner circumference of the circular tubular hole 33 in the outer diameter direction of each of the spiral oil passages 61 and 61.

FIG. 10 is a diagram showing the distribution of cooling oils having different volume fractions when the cooling oil containing bubbles is actually flowed into the spiral oil passages 61 and 61.
As shown in this figure, in the initial inflow (corresponding to the non-gas-liquid separation portion 61a) flowing into the cooling oil inlet 61c of each of the spiral oil passages 61 and 61 on the left side in the figure, the volume fraction of the cooling oil as a whole. Is low and the bubbles are totally dispersed.

On the other hand, in the late inflow period (corresponding to the gas-liquid separation portion 61b) after the middle in the left-right direction in the figure, the cooling oil having a high volume fraction, that is, the cooling oil containing no bubbles, moves along the outer circumference of the spiral. .. On the other hand, it can be seen that the cooling oil having a low volume fraction, that is, the cooling oil containing a large amount of air bubbles, moves in the air passage 73 at the axial center portion.

As described above, the cooling oil containing a large amount of air bubbles is collected in the inner circumference of the spiral oil passage 61 when passing through the gas-liquid separation portion 61b of the spiral oil passages 61 and 61, and is collected from the gas-liquid separation communication passage 74. Collected in the air passage 73.

Therefore, when the cooling oil passes through the spiral oil passages 61 and 61 of the housing oil passage 23, most of the bubbles are collected in the air passage 73 in the gas-liquid separation portion 61b, and the arrow Bu in FIG. 1 indicates. As shown, it is returned to the motor chamber 30a through the bubble discharge droop 38.

On the other hand, the cooling oil from which the air bubbles have been removed by the gas-liquid separation portion 61b is supplied to the motor internal oil passage 25 from the communication oil passage 34 of the motor housing 30 through the second side oil passage 24 of the second cover 52. , The rotor 1 of the motor M, the stator 2, and other heat-generating parts are cooled.

Therefore, as compared with the case where the cooling oil containing bubbles is directly supplied to the heat generating portion of the motor M, the thermal conductivity of the cooling oil can be maintained high and the cooling performance can be improved. Further, it is possible to suppress the occurrence of cooling oil leakage due to the volume expansion due to the heat of the bubbles, the deterioration of the lubricity due to the inclusion of the bubbles, and the promotion of cavitation, noise generation and deterioration due to the suppression.

(Effect of Embodiment 1)
(1) The cooling device for the rotary electric machine according to the first embodiment is
A cooling device for a rotary electric machine that circulates cooling oil inside the motor M to cool the heat generating portion inside the motor M.
A housing oil passage 23 forming a part of the circulation oil passage 20 for circulating the cooling oil is provided in the motor housing 30.
In the housing oil passage 23, an inner cylinder portion 71 as a tubular portion formed in a tubular shape and a spiral oil passage which is a flow path for cooling oil and is spirally formed along the outer periphery of the inner cylinder portion 71. A gas-liquid separation portion 61b including 61, 61, a gas-liquid separation communication passage 74 for communicating an air passage 73 as a hollow portion formed inside the inner cylinder portion 71, and a spiral oil passage 61 is provided. ing.
Therefore, when the cooling oil circulating in the circulating oil passage 20 flows through the housing oil passage 23, air bubbles can be removed from the air passage 73.
This makes it possible to suppress oil leakage and deterioration of cooling performance caused by air bubbles contained in the cooling oil.

(2) The cooling device for the rotary electric machine according to the first embodiment is
A cooling oil inlet 61c provided at the upstream end of the spiral oil passage 61 in the direction of the cooling oil flow is provided as a cooling oil introduction port to the gas-liquid separation portion 61b.
As the outlet of the cooling oil from the gas-liquid separation portion 61b, the spiral oil passage outlet 61d provided at the downstream end in the direction of the cooling oil flow in the spiral oil passage 61 and the direction of the cooling oil flow in the air passage 73. The hollow portion outlet 73a provided downstream of the gas-liquid separation communication passage 74 is provided.
Therefore, the cooling oil flowing through the gas-liquid separation portion 61b may discharge the cooling oil containing a large amount of air bubbles from the hollow portion outlet 73a, while the cooling oil containing no air bubbles may be discharged from the spiral oil passage outlet 61d. can.

(3) The cooling device for the rotary electric machine according to the first embodiment is
The spiral oil passage outlet 61d is connected upstream from the heat generating portion of the circulating oil passage 20.
The hollow portion outlet 73a is opened in the motor chamber 30a inside the motor housing 30.
Therefore, while the cooling oil from which bubbles have been removed is supplied to the heat generating portion in the circulating oil passage 20, the cooling oil containing bubbles can be discharged from the hollow portion outlet 73a to the motor chamber 30a so as not to pass through the heat generating portion. ..
Therefore, it is possible to more reliably suppress oil leakage and deterioration of cooling performance caused by air bubbles contained in the cooling oil.

(4) The cooling device for the rotary electric machine according to the first embodiment is
The housing oil passage 23
A non-gas-liquid separation section 61a in which the spiral oil passage 61 and the air passage 73 are blocked is provided upstream of the gas-liquid separation section 61b.
Therefore, in the non-gas-liquid separation unit 61a, the cooling oil in a state where the air bubbles are surely moved to the inner diameter side and the air-liquid separation is sufficiently separated is supplied to the gas-liquid separation unit 61b, and the cooling oil containing the air bubbles is efficiently supplied. It can be moved to the air passage 73.
As a result, gas-liquid separation can be performed efficiently.

(5) The cooling device for the rotary electric machine according to the first embodiment is
In the gas-liquid separation unit 61b, the input flow rate (V) of the cooling oil, the cross-sectional area of the oil passage (S), and the radius of the oil passage (r) act on the cooling oil flowing through the spiral oil passage 61 (centrifugal acceleration a). ) Is set to exceed the buoyancy of the bubbles contained in the cooling oil.
Therefore, when the cooling oil flows through the spiral oil passage 61, the cooling oil containing no bubbles is collected on the outer diameter side by centrifugal force, and the bubbles are pressed against the inner cylinder portion 71 on the inner diameter side and moved to the air passage 73. be able to.

(6) The cooling device for the rotary electric machine according to the first embodiment is
The gas-liquid separation portion 61b is formed by laminating the second plate material 82 in the axial direction.
The second plate material 82 is formed by inserting the cylindrical portion 202 of the laminating jig 200 into the inner circumference of the annular portion 82a as a rotating hole that can rotate around the cylindrical portion 202, and the inner cylinder portion 71 in a laminated state. An annular portion 82a as an annular portion forming an annular portion, a rib 82b extending in the outer radial direction from the annular portion 82a and forming a spiral vertical wall 72 of the spiral oil passage 61 in a laminated state, and an annular portion. A notch 82c that communicates the inside and outside of the portion 82a in the radial direction is provided.
Therefore, the second plate member 82 can be laminated to form the spiral oil passage forming member 70 having the spiral vertical wall 72 having a complicated shape for forming the spiral oil passage 61. Therefore, it can be manufactured easily and inexpensively as compared with the case where the spiral oil passage forming member 70 is formed by molding or the like.

(7) The cooling device for the rotary electric machine according to the first embodiment is
In the first plate material 81 and the second plate material 82, when the plate materials 81 and 82 are rotated around the annular portions 81a and 82a as rotation holes, the plate materials 81 and 82 adjacent to each other in the stacking direction are adjacent to each other. The ribs 81b and 82b are provided with protrusions 81d and 82d as engaging portions that engage with the ribs 81b and 82b at positions where they are displaced and overlap each other in the rotational direction.
Therefore, it becomes easy to stack the first plate material 81 and the second plate material 82 while shifting the positions of the adjacent plate materials 81 and 82 in the rotation direction, and the workability can be improved.

(8) The cooling device for the rotary electric machine according to the first embodiment is
The first plate material 81 and the second plate material 82 are formed of scraps 102 on the inner circumference of the electromagnetic steel sheet 100 forming the rotor 1 of the motor M.
Therefore, the scrap material 102 can be effectively used, and the cost of the first plate material 81 and the second plate material 82 can be reduced.

(9) The cooling device for the rotary electric machine according to the first embodiment is
The motor housing 30 is provided with a cooling water channel 32, and the motor housing 30 is provided with a cooling water channel 32.
The housing oil passage 23 is juxtaposed with the cooling water passage 32.
Therefore, the cooling oil moving in the housing oil passage 23 can be cooled, and the cooling oil can be efficiently cooled.

(10) The cooling device for the rotary electric machine according to the first embodiment is
A housing oil passage 23 is provided in the upper part of the motor housing 30.
Therefore, it is easy to return the bubbles discharged from the air passage 73 to the motor chamber 30a.

(Other embodiments)
The cooling device of the rotary electric machine of another embodiment will be described below. In addition, in describing the cooling device of the rotary electric machine of another embodiment, common reference numerals are given to common ones and the description thereof will be omitted.

(Embodiment 2)
In the cooling device of the rotary electric machine of the second embodiment, the shapes of the first plate material (not shown) and the second plate material 282 (see FIG. 11A) are different from those of the first embodiment.

The second plate material 282 is an example in which only one rib 282b extends in the outer diameter direction from the annular portion 282a. Further, the annular portion 282a is formed with a notch 282c that communicates inside and outside the annular portion 282a in the radial direction as in the first embodiment, and the rib 282b is formed with a protruding portion 282d. ..

Further, the first plate material (not shown) is different from the second plate material 282 only in that it does not have the notch 282c, as in the first embodiment. The inner circumference of the annular portion 282a is used as a rotating hole through which the cylindrical portion 202 of the laminating jig 200 is inserted and rotated, as in the first embodiment.

When such a first plate material (not shown) and a second plate material 282 are laminated using the protrusion 282d while being displaced in the circumferential direction in the same manner as in the first embodiment, the second plate material 282 is not shown in the second embodiment. A spiral oil passage is formed around the inner cylinder portion of the.
Therefore, the second embodiment differs from the first embodiment in that the spiral oil passage forming member (not shown in the second embodiment) has one spiral oil passage (not shown in the second embodiment). ..

Therefore, also in the second embodiment, the cooling oil flowing through the spiral oil passage flows spirally, centrifugal force acts on the cooling oil, bubbles are collected in the air passage inside the inner cylinder portion, and cooling with few bubbles is performed. Separated from oil.

(Embodiment 3)
Also in the cooling device of the rotary electric machine of the third embodiment, the shapes of the first plate material (not shown) and the second plate material 382 (see FIG. 11B) are different from those of the first embodiment.

As shown in FIG. 11B, the rib 382b of the second plate member 382 is integrally formed with an arcuate flange 382f centered on the axial center of the annular portion 382a at the tip end portion in the outer diameter direction thereof. The ring portion 382a has a notch portion 382c, and the rib 382b has a protrusion portion 382d.
Further, the first plate material (not shown) is different from the second plate material 382 only in that it does not have the cutout portion 382c, as in the first and second embodiments.

Therefore, even in the third embodiment, the first plate material (not shown) and the second plate material 382 are laminated to form a spiral oil passage forming member. Then, in the third embodiment, the vertical wall (72) of the spiral oil passage forming member (70) integrally has a wall in the circumferential direction formed by the flange 382f.
Therefore, the cooling oil that moves in the outer diameter direction due to the centrifugal force can be reliably stored in the vicinity of the tip portion of the vertical wall (72) as compared with the one having no wall in the circumferential direction.

(Embodiment 4)
The shape of the first plate material (not shown) and the second plate material 482 (see FIG. 11C) of the rotary electric machine cooling device of the fourth embodiment is also different from that of the first embodiment.

As shown in FIG. 11C, the second plate member 482 includes a connecting portion 482e that connects the ribs 482b and 482b to each other inside the annular portion 482a. Further, in the connecting portion 382e, the annular portion 482a has a circular rotation hole 482f at the position of the axial center of the annular portion 482a. Further, in the fourth embodiment, the annular portion 482a has two notches 482c at an intermediate position between the ribs 482b and 482b in the circumferential direction. The rib 482b has a protrusion 482d as in the first to third embodiments.
Further, the first plate material (81) (not shown) is only a point that does not have a notch portion 482c, as in the first to third embodiments.

In the fourth embodiment, when the first plate material (not shown) and the second plate material 482 are laminated to form a spiral oil passage forming member, a cylinder (not shown) or a cylinder (cylinder) is formed in the rotating hole 482f. ) Is inserted, and both plate members 482 are rotated.

The spiral oil passage forming member (70) formed in the fourth embodiment has a gas-liquid separation communication passage (not shown) formed by the cutout portion 482c, and the spiral oil passage (not shown) is continuous with each spiral oil passage (not shown). Can be formed as a spiral.

The cooling device for the rotary electric machine of the present disclosure has been described above based on the embodiment, but the specific configuration is not limited to this embodiment, and the gist of the invention according to each claim is described. Design changes and additions are acceptable as long as they do not deviate.

For example, in the embodiment, an example in which the non-gas-liquid separation section 61a is provided upstream of the gas-liquid separation section 61b is shown, but the present invention is not limited to this, and the spiral oil is not provided without the non-gas-liquid separation section 61a. The gas-liquid separation communication passage 74 may be provided over the entire length of the path 61 to serve as the gas-liquid separation portion 61b.
Further, in the embodiment, the spiral oil passage forming member 70 is shown by showing an example in which the metal plates 81 and 82 are laminated, but the present invention is not limited to this. For example, the spiral oil passage forming member 70 may be formed by casting, cutting, or the like. Further, when a resin or the like is used as the material for forming the spiral oil passage forming member 70, another manufacturing method such as mold molding can be used.
Further, in the embodiment, an example in which the cooling device is applied to a motor as a rotary electric machine is shown, but it can also be applied to a generator.
Further, when the plate materials are laminated and rotated around the rotation hole, a protrusion is shown as an engaging portion that engages with the adjacent plate materials, but the present invention is not limited to this, and for example, a part of the plate material. It may be cut and raised, or it may have a structure in which the cut and raised portion and the cutout portion are engaged with each other. Further, the position where the engaging portion is provided is provided on the rib if it engages with the rib, but may be provided on the annular portion when the cut-up portion and the notch portion are engaged as described above.

1 Rotor 20 Circulating oil passage 23 Housing oil passage 30 Motor housing 30a Motor chamber 32 Cooling water passage 61 Spiral oil passage 61a Non-gas-liquid separation part 61b Gas-liquid separation part 61c Cooling oil inlet 61d Spiral oil passage outlet 70 Spiral oil passage Forming member 71 Inner cylinder 72 Spiral vertical wall 73 Air passage (hollow)
73a Hollow part outlet 74 Gas-liquid separation communication passage 75 Outer pipe 81 First plate material 81a Circular part 81b Rib 81d Projection part (engagement part)
82 Second plate 82a Annulus (rotating hole)
82b Rib 82c Notch 82d Protrusion (engagement)
100 Electrical steel sheet 102 Scrap material 200 Laminating jig 202 Cylindrical part M motor (rotary electric machine)

Claims (9)

A cooling device for a rotary electric machine that circulates cooling oil inside the rotary electric machine to cool a heat generating portion inside the rotary electric machine.
A housing oil passage forming a part of the circulation passage for circulating the cooling oil is provided in the housing of the rotary electric machine.
A tubular portion formed in a tubular shape in the housing oil passage, a spiral oil passage spirally formed along the outer periphery of the tubular portion, which is a flow path for the cooling oil, and the tubular portion. A cooling device for a rotary electric machine provided with a gas-liquid separation section including a gas-liquid separation communication passage for communicating a hollow portion formed inside the section and the spiral oil passage. In the cooling device of the rotary electric machine according to claim 1,
The cooling oil inlet provided at the upstream end of the spiral oil passage in the direction of the cooling oil flow is provided as the cooling oil inlet to the gas-liquid separation portion.
As outlets for the cooling oil from the gas-liquid separation portion, a spiral oil passage outlet provided at a downstream end in the direction of the flow of the cooling oil in the spiral oil passage, and a flow of the cooling oil in the hollow portion. A cooling device for a rotary electric machine provided with a hollow portion outlet provided downstream of the gas-liquid separation communication passage in the above direction. In the cooling device of the rotary electric machine according to claim 2.
The spiral oil passage outlet is connected upstream of the heat generating portion of the circulation passage.
The hollow portion outlet is a cooling device for a rotary electric machine that is opened inside the housing. The cooling device for a rotary electric machine according to any one of claims 1 to 3.
The housing oil passage is
A cooling device for a rotary electric machine provided with a non-gas-liquid separation section in which the spiral oil passage and the hollow portion are blocked upstream of the gas-liquid separation section. The cooling device for a rotary electric machine according to any one of claims 1 to 4.
In the gas-liquid separation section, the input flow rate of the cooling oil, the cross-sectional area of the oil passage, and the radius of the oil passage have a centrifugal force acting on the cooling oil flowing through the spiral oil passage, and the buoyancy of bubbles contained in the cooling oil. Rotating electric machine cooling device set to exceed. The cooling device for a rotary electric machine according to any one of claims 1 to 5.
The gas-liquid separation portion is formed by laminating plate materials in the axial direction.
The plate material has a rotary hole that can be rotated around the jig into which a jig is inserted, an annular portion that forms the tubular portion in a laminated state, and an annular portion that extends in the outer diameter direction from the annular portion. A cooling device for a rotary electric machine, which is provided with a rib forming a spiral vertical wall of the spiral oil passage in a laminated state, and a notch portion communicating inside and outside the annular portion in the radial direction. In the cooling device of the rotary electric machine according to claim 6.
The plate material is an engaging portion that engages with the rib of the plate material adjacent to the stacking direction at a position where the plate material is displaced and overlaps in the rotation direction when the plate material is rotated around the rotation hole. A rotating electric cooling device equipped with. In the cooling device of the rotary electric machine according to claim 6 or 7.
The plate material is a cooling device for a rotary electric machine formed of scraps on the inner circumference of an electromagnetic steel sheet forming the rotor of the rotary electric machine. The cooling device for a rotary electric machine according to any one of claims 1 to 8.
The housing is provided with a cooling water channel.
A cooling device for a rotary electric machine in which the housing oil passage is juxtaposed with the cooling water passage.

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