JP2015070656A - Rotary electric machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary electric machine that can cool the inside suitably.SOLUTION: Coolant supply means 30 of a rotary electric machine 12 supplies coolant fluid 42 to a bottom surface 70 of a cylindrical member 52 from a point closer to one end of a rotation axis 50 than the bottom surface 70. The bottom surface 70 has a first penetration hole 86 and a second penetration hole 88 that penetrate in the axial direction of the rotation axis 50, through which the coolant fluid 42 is supplied into the cylindrical member 52. In the inner side of the cylindrical member 52, an exit opening 92 of the first penetration hole 86 is formed on the outer side of the rotation axis 50 in the radial direction; and an exit opening 96 of the second penetration hole 88 is formed on the outer side of the exit opening 92 of the first penetration hole 86 in the radial direction.

Description

  The present invention relates to a rotating electrical machine capable of suitably cooling the inside.

  Patent Document 1 discloses a plurality of configurations for cooling an electric motor (FIGS. 1 to 11). Among these configurations, as a configuration for supplying the cooling oil from the inside of the electric motor toward the outside in the radial direction, there is a configuration in which the cooling oil is circulated through the inside of the shaft 28 (FIGS. 7 and 8).

  Patent Document 2 shows a configuration in which lubricating oil as cooling oil is supplied from the inner side of the electric motor 7 toward the outer side in the radial direction. Specifically, in Patent Document 2, the oil supply hole 11b of the first main shaft 11 with respect to the planetary gear mechanism 30 of the transmission 20 disposed inside the rotor 72 (that is, inside the fixing portion 72c that fixes the rotor yoke 72b). The lubricating oil discharged from is supplied (FIG. 2, FIG. 9, [0036], [0079]).

JP 2003-324901 A International Publication No. 2012/046307 Pamphlet

  As shown in FIGS. 7 and 8 of Patent Document 1, in the configuration in which the cooling oil is supplied to the inside of the rotating electrical machine through the inside of the rotating shaft, the specifications of the refrigerant supply path such as the number, position, and size of the holes are rotated. Limited by the relationship with the strength of the shaft. For this reason, there is still room for improvement from the viewpoint of cooling the inside of the rotating electrical machine.

  Further, as in Patent Document 2, when the planetary gear mechanism 30 is arranged inside the rotor 72, the lubricating oil as cooling oil is supplied to the rotor 72 after absorbing the heat of the planetary gear mechanism 30. Become. For this reason, the rotor 72 may not be sufficiently cooled.

  The present invention has been made in view of such problems, and an object thereof is to provide a rotating electrical machine capable of suitably cooling the inside.

  A rotating electrical machine according to the present invention includes a rotating shaft, a cylindrical member having a bottom surface formed on one end side of the rotating shaft and an opening formed on the other end side, and connected to an outer periphery of the rotating shaft by the bottom surface, A motor rotor having a rotor core fixed to the outer periphery of the cylindrical member, and a refrigerant supply means for supplying a cooling fluid for cooling the motor rotor, wherein the refrigerant supply means is formed from a bottom surface of the cylindrical member. Also, the cooling fluid is supplied from one end side of the rotating shaft to the bottom surface of the cylindrical member, and the bottom surface of the cylindrical member includes a first through hole and a second through hole, and the first through hole and the first through hole are provided. The cooling fluid is supplied to the inside of the cylindrical member through two through holes, and inside the cylindrical member, a cooling target drive component connected to the rotating shaft is disposed, and inside the cylindrical member, Exit side opening of the first through hole Is formed radially outside the rotating shaft, and the outlet side opening of the second through hole is formed radially outside the outlet side opening of the first through hole. To do.

  According to the present invention, the cooling fluid is supplied to the bottom surface (outside) of the cylindrical member and enters the inside of the cylindrical member via the first through hole and the second through hole. Therefore, it becomes possible to cool the member (cooling target drive component) arranged inside the cylindrical member or the rotor core fixed to the outer periphery of the cylindrical member.

  Moreover, the cylindrical member has an opening formed on the side opposite to the bottom surface (the other end side of the rotating shaft). For this reason, the cooling fluid supplied to the inside of the cylindrical member from the bottom side can be discharged from the cylindrical member via the opening. Therefore, it is possible to prevent the cooling fluid from entering the air gap between the motor rotor and the motor stator facing the motor rotor, and to suppress an increase in the rotational resistance of the rotating electrical machine.

  Furthermore, the 1st through-hole and 2nd through-hole which guide a cooling fluid to the inside of a cylindrical member are formed in the bottom face of a cylindrical member. For this reason, it is possible to diversify the path for supplying the cooling fluid to the inside of the cylindrical member, as compared with the case where such a through hole is formed only on the rotating shaft. Further, for example, when a through hole is formed only in the rotating shaft, various specifications (for example, the flow rate or supply pressure of the cooling fluid) that have been difficult to select due to the limitations of the specifications such as the size and strength of the rotating shaft. ) Can be improved.

  Furthermore, on the inner side of the cylindrical member, the outlet side opening of the first through hole is formed on the radially outer side than the rotation shaft, and the outlet side opening of the second through hole is on the outlet side of the first through hole. It is formed radially outside the opening. For this reason, the cooling fluid via the first through hole is easily supplied to the cooling target drive component connected to the rotating shaft, while the cooling fluid via the second through hole does not pass through the cooling target drive component. It becomes easy to be supplied to the inner peripheral surface (that is, the rotor core side) of the cylindrical member at a relatively low temperature. Therefore, both the cooling target drive component and the rotor core can be efficiently cooled.

  On the bottom surface of the cylindrical member, an annular outer protruding wall portion that protrudes to one end side of the rotating shaft is formed on the outer side in the radial direction from the inlet side opening portion of the first through hole. The entrance-side opening is formed radially inward of the inner peripheral surface of the outer protruding wall or the outer protruding wall, and the second through hole extends in the radial direction from one end side to the other end side of the rotating shaft. You may incline toward the outer side.

  According to the above configuration, the centrifugal force acts on the cooling fluid when the motor rotor rotates, whereby the cooling fluid reservoir is formed on the radially inner side of the outer protruding wall portion, and the first through hole and the second through hole are formed from the reservoir. It becomes possible to supply a cooling fluid to the inside of the cylindrical member through the hole. For this reason, even when the supply pressure of the refrigerant supply means is relatively small, the cooling fluid can be supplied to the inside of the cylindrical member via the first through hole and the second through hole. As a result, when an electric pump is used as the refrigerant supply means, the work amount of the electric pump can be reduced.

  Further, when a pump mechanically connected to the rotating electrical machine and operated by the driving force of the rotating electrical machine is used as the refrigerant supply means, the output of the pump is reduced and the cooling fluid supply amount is reduced or reduced at the time of low rotation of the rotating electrical machine. Supply pressure decreases. Even in such a case, since it becomes possible to store the cooling fluid in the annular outer protruding wall portion, it becomes easy to guide the cooling fluid to the first through hole and the second through hole, and the inside of the cylindrical member It becomes possible to suppress the supply shortage of the cooling fluid. In other words, the amount of cooling fluid supplied by the pump is less affected by driving conditions such as the rotational speed of the rotating electrical machine.

  Further, the second through hole is inclined radially outward from one end side to the other end side of the rotating shaft. For this reason, when the centrifugal force increases with the increase in the rotational speed of the motor rotor, the supply amount of the cooling fluid through the second through hole can be increased accordingly. Therefore, when the amount of heat generated in the rotor core increases with an increase in the number of rotations of the motor rotor, it is possible to increase the cooling efficiency by increasing the amount of cooling fluid to be supplied.

  The cooling fluid is a cooling oil that is a lubricating oil, the cooling target drive component is a gear mechanism or friction engagement means connected to the rotating shaft, and the first through hole is one end of the rotating shaft. The second through hole extends from the side to the other end side, and the cross-sectional area of the second through hole is smaller than the cross-sectional area of the first through hole.

  In the above configuration, the first through hole extends along the rotation axis from one end side to the other end side of the rotation shaft, whereas the second through hole is a radial direction from one end side to the other end side of the rotation shaft. Inclined outward. For this reason, the 2nd through-hole tends to increase the passage quantity of cooling fluid according to the increase in the number of rotations of a motor rotor.

  Here, the loss in the rotor is the sum of the iron loss of the permanent magnet or the rotor core and the eddy current loss, but the eddy current loss increases with the square of the rotation speed of the motor rotor. For this reason, according to the above configuration, when the motor rotor rotates at a high speed, it becomes easy to increase the amount of cooling fluid supplied to the rotor core without passing through the cooling target drive parts. Therefore, the rotor core can be efficiently adjusted according to the heat generation state of the rotor core. It becomes possible to cool it. In addition, it is possible to stably supply the cooling oil as the lubricating oil to the gear mechanism or the friction engagement means regardless of the rotation speed of the motor rotor.

  On the bottom surface of the cylindrical member, an inner projecting wall portion projecting to the other end side of the rotating shaft is formed on the outer side in the radial direction from the outlet side opening portion of the first through hole. The outlet side opening may be formed on a radially outer side than the inner protruding wall or on an outer peripheral surface of the inner protruding wall.

  Thereby, it becomes easy to supply the cooling fluid that has passed through the first through hole to the cooling target drive component, and it is easy to supply the cooling fluid that has passed through the second through hole to the rotor core. Therefore, it is possible to efficiently cool the cooling target drive component and the rotor core. Further, when the cooling fluid is a cooling oil that is a lubricating oil, and the cooling target drive component is a gear mechanism or friction engagement means that is coupled to the rotating shaft, the cooling oil that has passed through the first through hole is used as the gear. It becomes possible to supply more reliably to the mechanism or the frictional engagement means.

  When viewed in the radial direction of the motor rotor, the tip of the inner protruding wall portion may overlap a part of a gear constituting the gear mechanism or a part of the friction engagement means. As a result, the cooling oil that has passed through the first through hole can be more reliably supplied to the gear mechanism or the friction engagement means.

  On the bottom surface of the cylindrical member, an annular first outer projecting wall portion projecting toward one end side of the rotation shaft is formed on the outer side in the radial direction from the inlet side opening of the first through hole, and the first outer side is formed. A radial through hole penetrating from the radially inner side to the radially outer side is formed in the protruding wall portion, and further, the bottom surface of the tubular member is formed on the bottom surface of the rotating shaft at a radially outer side than the radial through hole. An annular second outer projecting wall portion projecting to one end side is formed, and the inlet side opening of the second through hole is radially outward from the first outer projecting wall portion and from the second outer projecting wall portion. May also be formed at a position that is radially inward.

  According to the above configuration, the inlet side opening of the first through hole is disposed radially inward of the first outer protruding wall portion, and the inlet side opening of the second through hole is more than the first outer protruding wall portion. Are also arranged on the radially outer side and on the radially inner side of the second outer protruding wall portion. For this reason, the amount of the cooling fluid that passes through the first through hole is not affected by the amount of the cooling fluid that passes through the second through hole. Therefore, the amount of cooling fluid supplied to the cooling target drive component through the first through hole is stabilized and, for example, the amount of cooling fluid supplied to the rotor core is increased by increasing the cross-sectional area of the second through hole. It can be increased.

  In addition, the cooling fluid that has passed through the radial through hole can be reliably supplied to the rotor core at a relatively low temperature while reliably avoiding the cooling target drive component.

  Furthermore, since the radial through hole penetrates from the radially inner side to the radially outer side, it is easy to increase the passing amount of the cooling fluid in accordance with the increase in the number of rotations of the motor rotor. The loss in the rotor core increases, for example, by the square of the rotational speed of the motor rotor. Therefore, according to the above configuration, the rotor core can be efficiently cooled according to the heat generation state of the rotor core.

  A rotating electrical machine according to the present invention includes a rotating shaft, a cylindrical member having a bottom surface formed on one end side of the rotating shaft and an opening formed on the other end side, and connected to an outer periphery of the rotating shaft by the bottom surface, A motor rotor having a rotor core fixed to the outer periphery of the cylindrical member, and a refrigerant supply means for supplying a cooling fluid for cooling the motor rotor, wherein the refrigerant supply means is formed from a bottom surface of the cylindrical member. The cooling fluid is also supplied from one end side of the rotating shaft to the bottom surface of the cylindrical member, and the bottom surface of the cylindrical member includes a through hole that guides the cooling fluid into the cylindrical member. A cooling target drive component connected to the rotating shaft is disposed inside the shaped member, and the through hole is inclined radially outward from one end side to the other end side of the rotating shaft. To do.

  According to the present invention, the inside can be suitably cooled.

It is a fragmentary sectional view which pays attention to a cooling system and shows a vehicle carrying a motor as a rotary electric machine concerning a 1st embodiment of the present invention. It is a partial expanded sectional view which shows the flow of the cooling oil in the said motor which concerns on 1st Embodiment. It is an external appearance perspective view of the side cover which functions as a part of said cooling system. It is the external appearance perspective view which looked at the cylindrical member of a 1st embodiment from the X2-Y1-Z2 direction. It is the external appearance perspective view which looked at the said cylindrical member of 1st Embodiment from the X1-Y1-Z2 direction. It is the external appearance rear view which looked at the said cylindrical member of 1st Embodiment from X1 direction. It is a front view which simplifies a motor rotor and shows the position of a through-hole. It is a partial expanded sectional view which shows the flow of the cooling oil in the motor which concerns on a comparative example. In a comparative example, it is a figure which shows an example of the relationship between a motor rotation speed, the flow volume of the cooling oil supplied to a storage part from a side cover, and the flow volume of the cooling oil which passes a 1st through-hole. It is a figure which shows an example of the relationship between the motor speed in the motor which concerns on 1st Embodiment and a comparative example, and the heat loss of a rotor core. An example of the relationship between the motor rotation speed in the motor according to the first embodiment and the comparative example, the flow rate of cooling oil necessary for the reduction gear (required lubrication flow rate), and the flow rate of cooling oil necessary for the rotor core (required flow rate of rotor core cooling) FIG. An example of the relationship between the motor rotation speed in the motor which concerns on 1st Embodiment and a comparative example, and the supply flow rate (rotor core supply flow rate) of the cooling oil supplied to a rotor core via a 1st through-hole and a 2nd through-hole is shown. FIG. It is a figure which shows an example of the relationship between the motor rotation speed in the motor which concerns on 1st Embodiment and a comparative example, and the temperature of a rotor core. It is a partial expanded sectional view which shows the flow of the cooling oil in the motor which concerns on 2nd Embodiment. It is the external appearance perspective view which looked at the cylindrical member of 2nd Embodiment from the X2-Y1-Z2 direction. It is the external appearance perspective view which looked at the said cylindrical member of 2nd Embodiment from the X1-Y1-Z2 direction. It is the external appearance front view which looked at the said cylindrical member of 2nd Embodiment from X2 direction. It is the external appearance rear view which looked at the cylindrical member which concerns on a modification from X1 direction.

A. First Embodiment 1. FIG. Explanation of overall configuration [1-1. overall structure]
FIG. 1 is a partial cross-sectional view showing a vehicle 10 equipped with a motor 12 as a rotating electrical machine according to a first embodiment of the present invention, paying attention to a cooling system (refrigerant supply means). FIG. 2 is a partial enlarged cross-sectional view showing the flow of the cooling oil 42 in the motor 12 according to the first embodiment. In FIG. 2, a solid line, a broken line, and an alternate long and short dash line arrow (however, excluding a lead line for a reference symbol) indicates the flow of the cooling oil 42. That is, the solid line arrows indicate the flow of the cooling oil 42 supplied from the side cover 30 (described later) and the flow of the cooling oil 42 supplied into the rotary shaft 50. The dashed arrow indicates the flow of the cooling oil 42 that passes through or has passed through the first through-hole 86, and the dashed-dotted arrow indicates the flow of the cooling oil 42 that passes through or passes through the second through-hole 88.

  For ease of understanding, FIGS. 1 and 2 are cross-sectional views taken along line II in FIG. 7 described later, and the side cover 30 (described later) in FIGS. 1 and 2 is introduced later. It should be noted that this is a cross-sectional view (cross-sectional view taken along the line I-I in FIG. 3) that passes through the hole 32 and the first to third discharge holes 36, 38, and 40.

  As shown in FIG. 1, the vehicle 10 includes a speed reducer 14 (cooling target drive component) as a gear mechanism in addition to the motor 12. A part of the speed reducer 14 is arranged so as to enter the inside of the motor 12.

  The motor 12 is a drive source for generating the driving force F of the vehicle 10. The motor 12 is a three-phase AC brushless type, and generates a driving force F of the vehicle 10 based on electric power supplied from a battery (not shown) via an inverter (not shown). In addition, the motor 12 charges the battery by outputting power (regenerative power Preg) [W] generated by performing regeneration to the battery. The regenerative power Preg may be output to a 12 volt system or an auxiliary machine (not shown).

  As shown in FIGS. 1 and 2, the motor 12 includes a motor rotor 20 (hereinafter also referred to as “rotor 20”), a motor stator 22 (hereinafter also referred to as “stator 22”), a resolver rotor 24, and a resolver stator. 26, a motor housing 28, and a side cover 30. The resolver rotor 24 and the resolver stator 26 constitute a resolver 31.

[1-2. Cooling system]
(1-2-1. Side cover 30)
FIG. 3 is an external perspective view of the side cover 30 that functions as a part of the cooling system. As shown in FIGS. 1 to 3, the side cover 30 has a single introduction hole 32, a flow path 34, a single first discharge hole 36, a single second discharge hole 38, and a plurality of third discharges. A hole 40 is formed. Cooling oil 42 is supplied to the first to third discharge holes 36, 38, 40 from a pump (not shown). The pump may be either electric or mechanical.

  As shown in FIGS. 1 to 3, in this embodiment, cooling oil 42 is injected or discharged from the side cover 30 to the rotor 20 and the stator 22.

  Specifically, the first discharge hole 36 mainly injects or discharges the cooling oil 42 with respect to the rotating shaft 50 of the rotor 20. The second discharge holes 38 mainly inject or discharge the cooling oil 42 with respect to the cylindrical member 52 of the rotor 20. The third discharge holes 40 mainly inject or discharge the cooling oil 42 with respect to the stator 22. Each discharge hole 36, 38, 40 is nozzle-shaped, and can inject or discharge the cooling oil 42.

(1-2-2. Motor rotor 20)
(1-2-2-1. Rotating shaft 50)
As shown in FIGS. 1 and 2, the rotary shaft 50 of the rotor 20 includes a shaft opening 53 for supplying the cooling oil 42 to the inside of the rotary shaft 50, and axial directions X <b> 1 and X <b> 2 (FIG. 1 and the like). A plurality of second shafts that communicate with the first shaft channel 54 that extends and the first shaft channel 54 and the outside of the rotary shaft 50 toward the radial directions R1 and R2 (FIG. 6 and the like) of the motor 12. An axial flow path 56 is formed.

  The cooling oil 42 supplied from the first discharge holes 36 of the side cover 30 is guided to the respective second axial flow paths 56 via the first axial flow paths 54, and the rotating shafts are transmitted via the respective second axial flow paths 56. 50 is released. The discharged cooling oil 42 is supplied to the inside of the rotor 20 or a part of the speed reducer 14.

(1-2-2-2. Cylindrical member 52)
(1-2-2-2-1. Overview)
As shown in FIGS. 1 and 2, the rotor 20 includes a bottomed cylindrical tubular member 52 and a rotor core 62 including a permanent magnet 60 in addition to the rotating shaft 50. The rotor 20 may be configured by a rotor core 62 that does not include the permanent magnet 60, such as a reluctance motor type rotor.

  FIG. 4 is an external perspective view of the cylindrical member 52 of the first embodiment viewed from the X2-Y1-Z2 direction. FIG. 5 is an external perspective view of the cylindrical member 52 of the first embodiment viewed from the X1-Y1-Z2 direction. FIG. 6 is an external rear view of the cylindrical member 52 of the first embodiment viewed from the X1 direction. 5 and 6, the one-dot chain line and two-dot chain line arrows indicate the flow of the cooling oil 42. That is, the one-dot chain line arrow indicates the flow of the cooling oil 42 that passes through the second through-hole 88 and travels toward the inner peripheral surface 64 of the cylindrical member 52, and the two-dot chain line arrow reaches the inner peripheral surface 64. The flow of the subsequent cooling oil 42 (relative movement accompanying the rotation of the motor 12) is shown.

  As shown in FIGS. 2, 4 to 6, etc., the cylindrical member 52 extends in the axial direction X <b> 2 from the bottom surface 70 fixed to the outer periphery of the rotating shaft 50 on the side cover 30 side and the outer edge of the bottom surface 70. Side surface 72. The side of the side surface 72 opposite to the bottom surface 70 is open. In other words, the opening 74 is formed on the side 72 opposite to the bottom 70. As shown in FIG. 2, a planetary gear 76 constituting the speed reducer 14 is disposed inside the cylindrical member 52.

(1-2-2-2. Bottom 70)
(1-2-2-2-1. Overview of the bottom surface 70)
As shown in FIGS. 2 and 4 to 6, the bottom surface 70 includes a base 80, a first protruding wall portion 82 (outer protruding wall portion), and a second protruding wall portion 84 (inner protruding wall portion). The base 80 is a part extending along the radial direction R1. A plurality of first through holes 86 (inner through holes or rotary shaft side through holes) and a plurality of second through holes 88 (outer through holes or outer peripheral side through holes) are formed in part of the base 80. The first through hole 86 is mainly used for directly supplying the cooling oil 42 to the speed reducer 14. The second through hole 88 is mainly used to supply the cooling oil 42 directly to the permanent magnet 60 or the rotor core 62.

  As shown in FIG. 2, the first through hole 86 penetrates the bottom surface 70 (base 80) along the axial directions X1 and X2. In addition, the first through hole 86 is formed such that the entrance-side opening 90 is formed on the inner side (rotation shaft 50 side) than the first projecting wall 82, and the outlet-side opening 92 is disposed on the inner side than the second projecting wall 84 ( Formed on the rotating shaft 50 side). Accordingly, the cooling oil 42 that has passed through the first through hole 86 can be supplied to a portion of the speed reducer 14 that is close to the rotating shaft 50.

  As shown in FIG. 2, the second through-hole 88 is inclined with respect to the axial directions X1 and X2 and penetrates the bottom surface 70 (base 80). That is, the angle α formed by the virtual center axis Ax2 of the second through hole 88 with respect to the virtual center axis Ax1 of the rotation shaft 50 is an acute angle (for example, any angle of 30 to 60 °). In the second through-hole 88, the inlet side opening 94 is formed in the first protruding wall 82 itself (the inner peripheral surface of the first protruding wall 82), and the outlet side opening 96 is more than the second protruding wall 84. It is formed on the outside (radially outside). Accordingly, the cooling oil 42 that has passed through the second through hole 88 can be supplied to the permanent magnet 60 or the rotor core 62 without passing through a part or all of the speed reducer 14.

  In FIG. 2, a part of the speed reducer 14 exists on the virtual center axis Ax <b> 2 of the second through hole 88, but the virtual center axis Ax <b> 2 avoids the speed reducer 14 and is more rotor core 62 than the speed reducer 14. You may face the side (namely, radial direction outer side R1).

  Both the first through hole 86 and the second through hole 88 of the present embodiment are based on a columnar shape. Alternatively, other shapes (for example, a rectangular parallelepiped shape) may be used as the basic tone. In the present embodiment, the cross-sectional area of the second through hole 88 is smaller than the cross-sectional area of the first through hole 86. However, the cross-sectional area of the second through-hole 88 can be made equal to or larger than the cross-sectional area of the first through-hole 86.

  FIG. 7 is a front view showing the position of the first through hole 86 by simplifying the motor rotor 20. In addition, since the 2nd through-hole 88 is formed in the internal peripheral surface of the 1st protrusion wall part 82 (refer FIG.2 and FIG.4), it does not appear in FIG.

  As shown in FIGS. 4, 6, and 7, four first through holes 86 and two second through holes 88 in the present embodiment are provided at equal intervals. As shown in FIG. 6, the first through holes 86 and the second through holes 88 are arranged in the same virtual straight line in the radial directions R1 and R2, and the phases of the through holes 86 and 88 are the same. The cooling oil 42 sprayed from the side cover 30 to the bottom surface 70 is supplied into the cylindrical member 52 through the first through hole 86 and the second through hole 88. The operation and effect of the first through hole 86 and the second through hole 88 will be described later.

(1-2-2-2-2. First projecting wall portion 82)
The first protruding wall portion 82 protrudes toward the side cover 30 (X1 direction) on the radially outer side (R1 direction) than the first through hole 86. A second through hole 88 is formed in the inner peripheral surface of the first protruding wall portion 82. Further, the first protruding wall portion 82 is formed in an annular shape. Therefore, when the cooling oil 42 injected or discharged from the side cover 30 to the bottom surface 70 during the rotation of the rotor 20 does not directly enter the first through hole 86 or the second through hole 88, the cooling oil 42 has a centrifugal force. By acting, it accumulates on the inner peripheral side of the first protruding wall portion 82 (region surrounded by the base 80 and the first protruding wall portion 82). In other words, the reservoir 80 (FIG. 2) for the cooling oil 42 is formed by the base 80 and the first projecting wall 82. Therefore, even when the cooling oil 42 does not directly enter the first through-hole 86 or the second through-hole 88, after temporarily staying in the storage portion 89, the tubular member is removed from the first through-hole 86 or the second through-hole 88. It becomes possible to supply the inside of 52.

  Further, when viewed in the radial directions R <b> 1 and R <b> 2 of the rotor 20, a part of the first projecting wall portion 82 overlaps the shaft opening 53 of the rotating shaft 50. For this reason, the cooling oil 42 overflowing from the first shaft flow path 54 via the shaft opening 53 also accumulates on the inner peripheral side of the first protruding wall portion 82 by the action of centrifugal force or gravity, and then the first It becomes possible to be supplied into the cylindrical member 52 from the through hole 86 or the second through hole 88. Therefore, the cooling oil 42 overflowing from the first shaft flow path 54 via the shaft opening 53 can be efficiently used for cooling the permanent magnet 60 or the rotor core 62.

  In addition, as shown in FIG. 2, the first protruding wall portion 82 is formed with a diameter-expanded portion 100 that increases in diameter from the side cover 30 toward the base portion 80 of the bottom surface 70 (that is, in the X2 direction). Yes. As a result, the storage portion 89 is easily formed on the radially inner side (R2 direction) of the first projecting wall portion 82, and once supplied to the radially inner side (R2 direction) of the first projecting wall portion 82. Regardless, it is possible to reduce the cooling oil 42 that does not enter the cylindrical member 52. In FIG. 2, both the radially inner side and the radially outer side of the first projecting wall portion 82 are expanded in diameter. However, the above-described operations and effects can be achieved as long as the radially inner side is expanded. It is.

  Furthermore, the resolver rotor 24 (rotor of the rotation sensor) is fixed on the radially outer side (R1 direction) of the first protruding wall portion 82. As a result, the first projecting wall portion 82 has a function of forming the storage portion 89 of the cooling oil 42 and a function of holding the resolver rotor 24. Therefore, it is possible to make the motor 12 simpler than in the case where a member for holding the resolver rotor 24 is provided separately from the first projecting wall portion 82.

(1-2-2-2-2-3. Second protruding wall portion 84)
As shown in FIGS. 2, 5, and 6, the second protruding wall portion 84 is radially outer than the first through hole 86 (R1 direction) and radially inner than the second through hole 88 (R2 direction). 1 project toward the opening 74 (in the axial direction X2 in FIG. 2). As shown in FIG.5 and FIG.6, the 2nd protrusion wall part 84 is carrying out the cyclic | annular form along the circumferential directions C1 and C2. For this reason, the cooling oil 42 introduced into the cylindrical member 52 through the first through hole 86 is mainly guided to the second projecting wall portion 84 and supplied to the rotor core 62 after passing through the speed reducer 14. (A dashed arrow in FIG. 2).

  When viewed on the radially outer side (R1 direction) of the rotor 20, the tip of the second protruding wall portion 84 overlaps a part of the planetary gear 76. Thus, the cooling oil 42 guided by the second projecting wall portion 84 is supplied to a part of the planetary gear 76 when discharged toward the radially outer side (R1 direction) under the action of the centrifugal force. It becomes.

(1-2-2-2-3. Side surface 72)
As shown in FIGS. 1, 2, and 7, the rotor core 62 is fixed to the radially outer side (R1 direction) of the side surface 72 of the cylindrical member 52. As described above, the cooling oil 42 from the side cover 30 is supplied to the inside of the cylindrical member 52 via the rotary shaft 50 or the bottom surface 70 of the cylindrical member 52. Thereafter, when the cooling oil 42 moves along the side surface 72 under the rotating action of the rotor 20, the rotor core 62 is cooled.

  The cooling oil 42 reaching the side surface 72 moves toward the opening 74 along the side surface 72 and is discharged from the opening 74. The cooling oil 42 discharged from the opening 74 is then stored in the bottom (not shown) of the motor housing 28 and then injected or discharged from the side cover 30 to the rotor 20 or the stator 22 again by the pump. The The cooling oil 42 may be heat exchanged by a cooler or a warmer (not shown) before being injected or discharged again.

(1-2-3. Motor stator 22)
The cooling oil 42 supplied from the third discharge holes 40 of the side cover 30 passes through the interior of the stator 22 and cools down to the bottom of the motor housing 28 while cooling each part of the stator 22.

  Further, as shown in FIG. 2 and the like, a resolver stator 26 is disposed in the motor stator 22 on the radially outer side (R1 direction) of the resolver rotor 24. Thereby, the resolver stator 26 outputs according to the rotation angle of the resolver rotor 24. Therefore, the rotation angle of the motor rotor 20 can be detected.

[1-3. Action and Effect of Second Through Hole 88 (Comparison with Comparative Example)]
(1-3-1. Problems when the second through-hole 88 is not provided)
FIG. 8 is a partial enlarged cross-sectional view showing the flow of the cooling oil 42 in the motor 312 according to the comparative example. In FIG. 8, a solid line and a broken line arrow (except for a lead line for reference numerals) indicate the flow of the cooling oil 42. FIG. 9 shows the motor rotation speed Nm, the flow rate of the cooling oil 42 supplied from the side cover 30 to the storage unit 89 (hereinafter also referred to as “storage unit supply flow rate Qsp” or “supply flow rate Qsp”) and the comparative example. 6 is a diagram illustrating an example of a relationship with a flow rate of cooling oil 42 passing through a first through hole 86 (hereinafter also referred to as “passage flow rate Qp1”). FIG. In the motor 312 according to the comparative example, the first through hole 86 is formed, but the second through hole 88 is not formed.

  As shown in FIG. 9, the difference (Qsp−Qp1) between the reservoir supply flow rate Qsp and the passage flow rate Qp1 increases as the motor rotation speed Nm increases. This means that as the motor rotation speed Nm increases, the amount of the cooling oil 42 that cannot pass through the first through hole 86 and flows down from the storage portion 89 increases.

  FIG. 10 is a diagram illustrating an example of the relationship between the motor rotation speed Nm in the motors 12 and 312 and the heat loss of the rotor core 62 (hereinafter referred to as “heat loss Lc”) according to the first embodiment and the comparative example. FIG. 11 shows the motor rotation speed Nm in the motors 12 and 312 according to the first embodiment and the comparative example, the flow rate of the cooling oil 42 required for the reduction gear 14 (hereinafter referred to as “lubrication required flow rate Rl”), and the rotor core 62. It is a figure which shows an example of the relationship with the flow volume (henceforth "cooling required flow volume Rc") of the required cooling oil.

  As shown in FIG. 10, the heat loss Lc of the rotor core 62 increases as the motor rotation speed Nm increases. Further, as shown in FIG. 11, the required cooling flow rate Rc has a larger increase corresponding to the increase in the motor rotation speed Nm than the required lubrication flow rate Rl.

  In the comparative example, as the motor rotation speed Nm increases, the heat loss Lc of the rotor core 62 increases (FIG. 10), while the flow rate of the cooling oil 42 flowing down from the storage unit 89 increases (FIG. 9). For this reason, in the comparative example, when the motor rotation speed Nm increases, the rotor core 62 may not be sufficiently cooled.

  In addition, in the comparative example, the cooling oil 42 that has passed through the first through hole 86 is once supplied to the speed reducer 14 and then supplied to the rotor core 62. For this reason, the cooling oil 42 supplied to the speed reducer 14 cools the rotor core 62 after cooling the speed reducer 14. In the comparative example, the rotor core 62 may not be sufficiently cooled from this point.

(1-3-2. Action and effect of second through-hole 88)
In the comparative example, there is a problem as described above. In the first embodiment, a second through hole 88 is provided in addition to the first through hole 86 (see FIG. 2 and the like). For this reason, it becomes possible to solve the above problems in the comparative example.

  12 shows the motor rotation speed Nm in the motors 12 and 312 according to the first embodiment and the comparative example, and the supply flow rate of the cooling oil 42 supplied to the rotor core 62 via the bottom surface 70 of the cylindrical member 52 (hereinafter referred to as “rotor core”). It is a figure showing an example of relation to supply flow rate Rsc. The rotor core supply flow rate Rsc in the comparative example is the supply flow rate of the cooling oil 42 supplied to the rotor core 62 through the first through hole 86, and the rotor core supply flow rate Rsc in the first embodiment is the first through hole 86 and the first flow rate. 2 is a supply flow rate of the cooling oil 42 supplied to the rotor core 62 through the through-hole 88. FIG. 13 is a diagram illustrating an example of the relationship between the motor rotation speed Nm in the motors 12 and 312 and the temperature Tc of the rotor core 62 according to the first embodiment and the comparative example.

  In the first embodiment, the cooling oil 42 that has passed through the second through-hole 88 is supplied to the rotor core 62 without passing through part or all of the speed reducer 14 (see the dashed line arrow in FIG. 2). In addition, the center axis Ax2 of the second through hole 88 is away from the center axis Ax1 of the rotation shaft 50 toward the opening 74 of the cylindrical member 52 (toward the right side in FIG. 2). Inclined. For this reason, the flow rate of the cooling oil 42 passing through the second through hole 88 (hereinafter referred to as “passing flow rate Rp2”) increases as the motor rotation speed Nm increases and the centrifugal force applied to the cooling oil 42 of the reservoir 89 increases. .) Increases, and as a result, the rotor core supply flow rate Rsc also increases (see FIG. 12). Therefore, compared to the comparative example, in the first embodiment, even if the motor rotation speed Nm increases, it is possible to suppress the temperature rise of the rotor core 62 (including the permanent magnet 60) (FIG. 13). reference). Thereby, the demagnetization of the permanent magnet 60 accompanying a temperature rise can be prevented, for example.

2. Effects of First Embodiment As described above, according to the first embodiment, the cooling oil 42 is supplied to the bottom surface 70 (outside) of the cylindrical member 52, and the first through hole 86 and the second through hole 88 are provided. Through the inside of the cylindrical member 52. Therefore, it is possible to cool the member disposed inside the cylindrical member 52 (the planetary gear 76 of the speed reducer 14 as a cooling target drive component) or the rotor core 62 fixed to the outer periphery of the cylindrical member 52.

  Further, the cylindrical member 52 has an opening 74 on the side opposite to the bottom surface 70 (the other end side of the rotating shaft 50). For this reason, the cooling oil 42 supplied to the inside of the cylindrical member 52 from the bottom surface 70 side can be discharged from the cylindrical member 52 through the opening 74. Therefore, it is possible to prevent the cooling oil 42 from entering the air gap between the motor rotor 20 and the motor stator 22 facing the motor rotor 20 and to suppress an increase in the rotational resistance of the motor 12.

  Further, the first through hole 86 and the second through hole 88 that guide the cooling oil 42 to the inside of the cylindrical member 52 are formed in the bottom surface 70 of the cylindrical member 52. For this reason, it is possible to diversify the paths for supplying the cooling oil 42 to the inside of the cylindrical member 52 as compared to the case where such a through hole is formed only on the rotating shaft 50. Further, for example, when the through hole (the first shaft flow path 54 and the second shaft flow path 56) is formed only in the rotation shaft 50, the selection may be made based on the restrictions of the specifications such as the size and strength of the rotation shaft 50. It becomes possible to improve the degree of freedom of various specifications that have been difficult (for example, setting of the flow rate or supply pressure of the cooling oil 42).

  Furthermore, on the inner side of the cylindrical member 52, the outlet side opening 92 of the first through hole 86 is formed on the radially outer side (R1 direction) than the rotation shaft 50, and the outlet side opening of the second through hole 88 is formed. 96 is formed radially outward from the outlet side opening 92 of the first through hole 86 (see FIG. 2 and the like). Therefore, the cooling oil 42 (cooling fluid) through the first through hole 86 is easily supplied to the speed reducer 14 (cooling target drive component) connected to the rotating shaft 50, while the second through hole 88 is passed through. The cooled oil 42 is easily supplied to the inner peripheral surface 64 (in other words, the rotor core 62 side) of the cylindrical member 52 at a relatively low temperature without passing through the speed reducer 14. Therefore, both the speed reducer 14 and the rotor core 62 can be efficiently cooled.

  In the first embodiment, on the bottom surface 70 of the cylindrical member 52, an annular first protruding wall portion 82 that protrudes to one end side of the rotation shaft 50 on the radially outer side than the inlet-side opening 90 of the first through hole 86. (Outer protruding wall portion) is formed, the inlet side opening 94 of the second through hole 88 is formed on the inner peripheral surface of the first protruding wall portion 82, and the second through hole 88 is one end side of the rotating shaft 50. It inclines toward the radial direction outer side from the other end side (refer FIG. 2).

  According to the above configuration, the centrifugal oil acts on the cooling oil 42 when the motor rotor 20 rotates, whereby the reservoir portion 89 for the cooling oil 42 is formed on the radially inner side of the first projecting wall portion 82. The cooling oil 42 can be supplied into the cylindrical member 52 through the first through hole 86 and the second through hole 88. For this reason, even when the supply pressure of the cooling system (refrigerant supply means) is relatively small, the cooling oil 42 can be supplied to the inside of the cylindrical member 52 via the first through hole 86 and the second through hole 88. It becomes. As a result, when the electric pump is used as a part of the cooling system (refrigerant supply means), the work amount of the electric pump can be reduced.

  Further, when a pump mechanically connected to the motor 12 (rotary electric machine) and operated by the driving force of the motor 12 is used as the refrigerant supply means, the output of the pump becomes small when the motor 12 is rotating at low speed, and the cooling oil 42 The supply amount is small or the supply pressure is small. Even in such a case, the cooling oil 42 can be stored in the annular first protruding wall portion 82 (outside protruding wall portion), and therefore the cooling oil 42 is supplied to the first through hole 86 and the second through hole. It becomes easy to guide to the hole 88, and it becomes possible to suppress insufficient supply of the cooling oil 42 to the inside of the cylindrical member 52. In other words, the supply amount of the cooling oil 42 by the pump is not easily affected by driving conditions such as the number of revolutions of the motor 12.

  Further, the second through-hole 88 is inclined toward the radially outer side (in the R1 direction) toward the axial direction X2 of the rotary shaft 50 (from one end side to the other end side of the rotary shaft 50) (see FIG. 2 and the like). ). For this reason, when the centrifugal force increases as the motor rotation speed Nm increases, the supply amount of the cooling oil 42 through the second through hole 88 can be increased accordingly. Therefore, when the heat loss Lc in the rotor core 62 increases as the motor rotation speed Nm increases, the cooling efficiency can be improved by increasing the passage flow rate Rp2 of the cooling oil 42.

  In the first embodiment, the cooling fluid is the cooling oil 42 that is lubricating oil, the cooling target drive component is the speed reducer 14 (gear mechanism) connected to the rotary shaft 50, and the first through hole 86 is The rotary shaft 50 extends along the rotary shaft 50 from one end side to the other end side, and the cross-sectional area of the second through hole 88 is smaller than the cross-sectional area of the first through hole 86.

  In the above configuration, the first through hole 86 extends along the rotation shaft 50 in the axial direction X2 of the rotation shaft 50 (from one end side to the other end side of the rotation shaft 50), whereas the second through hole 86 The hole 88 is inclined toward the axial direction X2 and the radially outer side (R1 direction) (see FIG. 2). For this reason, the 2nd through-hole 88 tends to increase the passage amount of the cooling oil 42 according to the increase in motor rotation speed Nm.

  Here, the loss in the rotor 20 is the sum of the iron loss of the permanent magnet 60 or the rotor core 62 and the eddy current loss, but the eddy current loss increases with the square of the motor rotation speed Nm. Therefore, according to the above configuration, when the motor rotor 20 rotates at a high speed, the flow rate of the cooling oil 42 (passing flow rate Rp2) supplied to the rotor core 62 without passing through the speed reducer 14 is easily increased. The rotor core 62 can be efficiently cooled according to the state. In addition, it becomes possible to stably supply the cooling oil 42 as the lubricating oil to the speed reducer 14 regardless of the motor rotation speed Nm.

  In the first embodiment, the bottom surface 70 of the cylindrical member 52 is radially outside the outlet side opening 92 of the first through hole 86 and radially inside the outlet side opening 96 of the second through hole 88. A second protruding wall portion 84 (inner protruding wall portion) that protrudes to the other end side of the rotating shaft 50 is formed (see FIG. 2 and the like).

  This makes it easy to supply the cooling oil 42 that has passed through the first through hole 86 to the speed reducer 14 (cooling target drive component), and it is easy to supply the cooling oil 42 that has passed through the second through hole 88 to the rotor core 62. . Therefore, the reduction gear 14 and the rotor core 62 can be efficiently cooled. In addition, when the cooling fluid is the cooling oil 42 that is the lubricating oil and the cooling target drive component is the speed reducer 14 (gear mechanism) connected to the rotating shaft 50, the cooling oil that has passed through the first through hole 86. 42 can be more reliably supplied to the speed reducer 14.

  In the first embodiment, when viewed in the radial direction R <b> 1 of the motor rotor 20, the tip of the second protruding wall portion 84 (inner protruding wall portion) overlaps with a part of the gear 76 that constitutes the speed reducer 14 (gear mechanism). (Refer to FIG. 2 etc.). As a result, the cooling oil 42 that has passed through the first through hole 86 can be more reliably supplied to the speed reducer 14.

B. Second Embodiment 1. FIG. Description of overall configuration (difference from the first embodiment)
In 2nd Embodiment, the shape of the cylindrical member 52a differs from the cylindrical member 52 of 1st Embodiment. About the same component as 1st Embodiment, the same referential mark is attached | subjected and description is abbreviate | omitted.

  FIG. 14 is a partially enlarged cross-sectional view showing the flow of the cooling oil 42 in the motor 12a according to the second embodiment. In FIG. 14, solid line, broken line, and alternate long and short dash line arrows (except for a lead line for reference signs) indicate the flow of the cooling oil 42. That is, solid arrows indicate the flow of the cooling oil 42 supplied from the side cover 30 and the flow of the cooling oil 42 supplied into the rotary shaft 50. The broken arrow indicates the flow of the cooling oil 42 that passes through or has passed through the first through hole 86, and the alternate long and short dashed line arrow indicates that the cooling oil 42 that has passed through or passed through the radial through hole 110 or the second through hole 88 a. Shows the flow. The positions of the parts shown in FIG. 14 correspond to those in FIG.

  FIG. 15 is an external perspective view of the cylindrical member 52a of the second embodiment viewed from the X2-Y1-Z2 direction. FIG. 16 is an external perspective view of the cylindrical member 52a of the second embodiment viewed from the X1-Y1-Z2 direction. FIG. 17 is an external front view of the cylindrical member 52a of the second embodiment as viewed from the X2 direction. 15-17, the dashed-dotted line and the dashed-two dotted line arrow show the flow of the cooling oil 42. That is, the one-dot chain line arrow indicates the flow of the cooling oil 42 that passes through the radial through hole 110 or the second through hole 88a and travels toward the inner peripheral surface 64 of the cylindrical member 52a. The flow (the relative movement accompanying rotation of the motor 12a) of the cooling oil 42 after reaching the peripheral surface 64 is shown.

  In the cylindrical member 52 of the first embodiment, the inlet side opening 94 of the second through hole 88 is formed on the inner peripheral surface of the first protruding wall 82 (outer protruding wall), and the outlet side opening 96 is The second protruding wall portion 84 (inner protruding wall portion) is formed on the outer side (outer peripheral side) (see FIG. 2 and the like). Then, the cooling oil 42 that passed through the second through hole 88 was directly supplied to the rotor core 62 without passing through part or all of the speed reducer 14.

  On the other hand, in the cylindrical member 52a of the second embodiment, the cooling oil 42 is supplied to the rotor core 62 via the path different from that of the first embodiment without using the speed reducer 14. That is, as shown in FIGS. 14 and 15, in the cylindrical member 52 a, the cooling oil 42 supplied directly to the rotor core 62 is the radial through hole of the first protruding wall portion 82 (first outer protruding wall portion). 110 (hereinafter also referred to as “through hole 110”). The central axis Ax2 of the through hole 110 is perpendicular to the central axis Ax1 of the rotation shaft 50.

  Thereafter, the cooling oil 42 reaches the annular third protruding wall portion 112 (second outer protruding wall portion) formed on the radially outer side (R1 direction) than the first protruding wall portion 82. A second through hole 88a is formed in the bottom surface 70 on the radially inner side (R2 direction) than the third protruding wall portion 112. Therefore, the cooling oil 42 that has reached the third protruding wall portion 112 is directly supplied to the rotor core 62 via the second through hole 88a.

2. Effects of Second Embodiment According to the second embodiment as described above, the following effects can be obtained in addition to or instead of the effects of the first embodiment.

  That is, in the second embodiment, the bottom surface 70 of the cylindrical member 52a is located on one end side (X1 direction) of the rotary shaft 50 on the radially outer side (R1 direction) than the inlet side opening 90 of the first through hole 86. A projecting annular first projecting wall portion 82 (first outer projecting wall portion) is formed, and the first projecting wall portion 82 has a diameter penetrating from the radially inner side (R2 direction) to the radially outer side (R1 direction). A directional through hole 110 is formed (see FIGS. 14 and 15). Further, on the bottom surface 70 of the cylindrical member 52a, an annular third protruding wall portion 112 (projecting in the axial direction X1 (one end side of the rotating shaft 50) on the radially outer side (R2 direction) than the radial through hole 110 ( A second outer protruding wall portion) is formed, and the inlet side opening 94 of the second through hole 88a is radially outward (R1 direction) and third than the first protruding wall portion 82 (first outer protruding wall portion). It is formed at a position that is radially inner (R2 direction) than the protruding wall 112 (second outer protruding wall) (see FIG. 14 and the like).

  According to the above configuration, the inlet-side opening 90 of the first through hole 86 is disposed radially inward (R2 direction) with respect to the first protruding wall 82 (first outer protruding wall), and the second through hole The inlet side opening 94 of 88a is disposed radially outside the first projecting wall 82 and radially inward from the third projecting wall 112 (second outer projecting wall). For this reason, the flow rate (passage flow rate Rp1) of the cooling oil 42 (cooling fluid) passing through the first through hole 86 is not affected by the flow rate (passage flow rate Rp2) of the cooling oil 42 passing through the second through hole 88a. Accordingly, the flow rate of the cooling oil 42 that passes through the first through hole 86 and is supplied to the speed reducer 14 (cooling target drive component) is stabilized, and, for example, the rotor core is increased by increasing the cross-sectional area of the second through hole 88a. The supply flow rate of the cooling oil 42 to 62 can be increased.

  Further, the cooling oil 42 that has passed through the radial through hole 110 can be reliably supplied to the rotor core 62 at a relatively low temperature while avoiding the speed reducer 14 (cooling target drive component).

  Furthermore, since the radial through hole 110 penetrates from the radially inner side to the radially outer side, it is easy to increase the passage amount of the cooling oil 42 according to the increase in the motor rotation speed Nm. Since the loss in the rotor core 62 increases, for example, by the square of the motor rotation speed Nm (see FIG. 10), according to the second embodiment, the rotor core 62 can be efficiently cooled according to the heat generation state of the rotor core 62. It becomes possible.

C. Modifications Note that the present invention is not limited to the above-described embodiments, and various configurations can be adopted based on the description of the present specification. For example, the following configuration can be adopted.

1. Applicable object In each of the above-described embodiments, the motors 12 and 12a are mounted on the vehicle 10. However, the present invention is not limited to this and can be applied to other uses using the motors 12 and 12a. For example, in each of the above embodiments, the motors 12 and 12a are used for driving the vehicle 10. However, the motors 12 and 12a may be used for other purposes in the vehicle 10 (for example, an electric power steering, an air conditioner, an air compressor, etc.). . Alternatively, the motors 12 and 12a can be used for devices such as industrial machines and home appliances.

2. Motor 12, 12a
In each of the embodiments described above, the motors 12 and 12a are three-phase AC systems. However, from the viewpoint of cooling with a cooling fluid or miniaturization of the motors 12 and 12a, other AC systems or DC systems may be used. . In each said embodiment, although the motors 12 and 12a were made into the brushless type, it is good also as a brush type. In each of the embodiments described above, the motor stator 22 is disposed on the radially outer side (R1 direction) of the motor rotor 20 (see FIG. 1 and the like), but not limited thereto, the motor stator 22 is disposed on the radially inner side of the motor rotor 20 (R2). (Direction).

3. Resolver 31
In each of the above embodiments, the resolver rotor 24 is formed on the first projecting wall portion 82. However, from the viewpoint of supplying the cooling oil 42 from the bottom surface 70 of the cylindrical member 52 to the inside of the cylindrical member 52, the present invention is not limited thereto. Instead, the resolver rotor 24 may be fixed to a portion other than the first protruding wall portion 82.

4). Cooling system [4-1. Cooling fluid]
In each of the above embodiments, the cooling oil 42 is used as the cooling fluid. However, from the viewpoint of the cooling function, a cooling fluid (for example, water) other than the cooling oil 42 may be used. However, there is a possibility that the gear mechanism such as the planetary gear 76 cannot be used for lubrication.

[4-2. Cylindrical member 52]
(4-2-1. First Through Hole 86 and Second Through Hole 88, 88a)
In the first embodiment, when viewed in the radial direction R1, the first through hole 86 and the second through hole 88 are arranged in the same virtual straight line, and the phases of the through holes 86 and 88 are the same (FIG. 6 and the like). reference). However, the first through hole 86 and the second through hole 88 when viewed in the radial direction R1 are not arranged in the same virtual straight line, and the phases of the through holes 86 and 88 can be made different.

  FIG. 18 is an external rear view of the cylindrical member 52b according to the modification viewed from the X1 direction. In the cylindrical member 52b of FIG. 18, the first through holes 86 and the second through holes 88 when viewed in the radial direction R1 are not arranged in the same virtual straight line, but the phases of the through holes 86 and 88 are different. Yes.

  In each of the above embodiments, the first through hole 86 is formed along (in parallel with) the rotation shaft 50 (see FIGS. 2 and 14). However, for example, from the viewpoint of supplying the cooling oil 42 directly to the speed reducer 14, the present invention is not limited to this. For example, you may arrange | position the exit side opening part 92 to the radial direction inner side (R2 direction) or radial direction outer side (R1 direction) rather than the inlet side opening part 90 of the 1st through-hole 86. FIG.

  In the first embodiment, the inlet side opening 94 of the second through-hole 88 is provided on the inner peripheral surface of the first protruding wall 82 (see FIG. 2 and the like). However, for example, if attention is paid to the configuration in which the inlet-side opening 94 faces the storage part 89, the present invention is not limited to this. For example, the entrance-side opening 94 may be disposed radially inward (R2 direction) with respect to the first projecting wall 82.

  In 1st Embodiment, the exit side opening part 96 of the 2nd through-hole 88 was provided in the radial direction outer side (R1 direction) rather than the 2nd protrusion wall part 84 (refer FIG. 2 etc.). However, for example, from the viewpoint of avoiding part or all of the speed reducer 14 and supplying the cooling oil 42 to the permanent magnet 60 or the rotor core 62, the present invention is not limited to this. For example, the outlet side opening 96 may be disposed on the outer peripheral surface of the second protruding wall 84.

  In the first embodiment, the inlet-side opening 90 of the first through-hole 86 is disposed radially inward (R2 direction) with respect to the inlet-side opening 94 of the second through-hole 88 (see FIG. 2 and the like). However, for example, from the viewpoint of disposing the outlet side opening 96 of the second through-hole 88 radially outward (R1 direction) with respect to the outlet-side opening 92 of the first through-hole 86, the first through-hole 86 It is also possible to arrange the inlet side opening 90 on the radially outer side (R1 direction) than the inlet side opening 94 of the second through-hole 88. In this case, as in the example of FIG. 18, the first through holes 86 and the second through holes 88 are not arranged in the same virtual straight line, and it is necessary to make the phases of the two through holes 86 and 88 different.

  In each said embodiment, the 1st through-hole 86 and the 2nd through-hole 88 were made into the shape (shape where most cross-sectional shapes are the same) based on a column shape. However, for example, from the viewpoint of passing the cooling oil 42, the present invention is not limited to this. For example, the first through hole 86 and the second through hole 88 may have a shape based on a rectangular parallelepiped or a truncated cone.

(4-2-2. 1st protrusion wall part 82 and 2nd protrusion wall part 84)
In 1st Embodiment, the 1st protrusion wall part 82 (outer protrusion wall part) and the 2nd protrusion wall part 84 (inner protrusion wall part) were provided (refer FIG.2 and FIG.14). However, for example, if attention is paid to the relative positional relationship between the outlet-side opening 92 of the first through-hole 86 and the outlet-side opening 96 of the second through-hole 88, the first protruding wall 82 and the second protruding wall One or both of 84 may be omitted.

(4-2-3. Radial direction through-hole 110 (radial direction flow path))
In the second embodiment, the virtual center axis Ax2 of the radial through hole 110 is perpendicular to the virtual center axis Ax1 of the rotation shaft 50 (see FIG. 14). However, for example, from the viewpoint of supplying the cooling oil 42 to the third protruding wall portion 112, the angle formed by the virtual central axes Ax1 and Ax2 is a value other than 90 ° (for example, any value of 75 to 105 °). It may be.

  In the second embodiment, cooling oil is supplied from the radially inner side (rotary shaft 50 side) of the first protruding wall portion 82 (first outer protruding wall portion) to the third protruding wall portion 112 (second outer protruding wall portion). A radial through hole 110 was used as a configuration for supplying 42. However, for example, from the viewpoint of supplying the cooling oil 42 to the third projecting wall 112 from the radially inner side of the first projecting wall 82, the first projecting wall 82 is used instead of the radial through hole 110. It is also possible to provide a groove portion or a notch portion (not shown).

[4-3. Reduction gear 14 (cooling target drive part)]
In each of the above embodiments, the planetary gear 76 connected to the rotating shaft 50 is disposed inside the cylindrical member 52, but other gear mechanisms can also be disposed. Alternatively, from the viewpoint of cooling with the cooling fluid, other members can be arranged inside the cylindrical member 52. For example, friction engagement means (clutch mechanism) connected to the rotation shaft 50 may be disposed.

  When the friction engagement means is arranged inside the cylindrical member 52, the dimensions of the motor 12 in the axial directions X1 and X2 can be reduced. Further, in addition to the cooling of the rotor core 62, the friction engagement means can be cooled or lubricated (when the cooling fluid also serves as the lubricating oil). For this reason, compared with the case where the cooling structure of the rotor core 62 and the cooling structure of a friction engagement means are provided separately, it can be set as a simple structure.

[4-4. Others]
In the first embodiment, the inside of the cylindrical member 52 is cooled via the flow path (the first axial flow path 54 and the second axial flow path 56) of the rotating shaft 50, the first through hole 86, and the second through hole 88. Oil 42 was supplied. However, for example, from the viewpoint of efficiently performing both the lubrication or cooling of the speed reducer 14 (cooling target drive component) and the cooling of the rotor core 62, the present invention is not limited to this. For example, the flow path of the rotating shaft 50 and the second through hole 88 are provided and the first through hole 86 is not provided, or the first through hole 86 and the second through hole 88 are provided and the flow path of the rotating shaft 50 is provided. No configuration is possible. Alternatively, for example, if it is a configuration in which the need to supply the cooling oil 42 to a member disposed inside the cylindrical member 52 such as the speed reducer 14 is low, the flow path of the rotating shaft 50 and the first through hole 86 are provided. Alternatively, a configuration in which the second through-hole 88 is provided is also possible.

10 ... Vehicle 12 ... Motor (Rotating electric machine)
14 ... Reducer (cooling target drive parts, gear mechanism)
20 ... Motor rotor 30 ... Side cover (part of refrigerant supply means)
42 ... Cooling oil (cooling fluid) 50 ... Rotating shaft (part of refrigerant supply means)
52, 52a, 52b ... cylindrical member 62 ... rotor core 70 ... bottom surface of cylindrical member 74 ... opening 76 of cylindrical member ... planetary gear (gear)
82 ... 1st protrusion wall part (outside protrusion wall part, 1st outside protrusion wall part)
84 ... 2nd protrusion wall part (inner protrusion wall part)
86 ... first through hole 88, 88a ... second through hole 90 ... first through hole inlet side opening 92 ... first through hole outlet side opening 94 ... second through hole inlet side opening 96 ... first 2 through-hole outlet side opening 110 ... radial through-hole 112 ... third protruding wall (second outer protruding wall)

Claims (7)

A rotating shaft, a cylindrical member having a bottom surface formed on one end side of the rotating shaft and an opening formed on the other end side, coupled to the outer periphery of the rotating shaft by the bottom surface, and fixed to the outer periphery of the cylindrical member A motor rotor having a rotor core,
A rotary electric machine comprising: refrigerant supply means for supplying a cooling fluid for cooling the motor rotor;
The refrigerant supply means supplies the cooling fluid from one end side of the rotating shaft to the bottom surface of the cylindrical member from the bottom surface of the cylindrical member,
The bottom surface of the cylindrical member includes a first through hole and a second through hole,
The cooling fluid is supplied to the inside of the cylindrical member through the first through hole and the second through hole,
Inside the tubular member, a cooling target drive component connected to the rotating shaft is disposed,
On the inner side of the cylindrical member, the outlet side opening of the first through hole is formed radially outside the rotating shaft, and the outlet side opening of the second through hole is formed on the first through hole. The rotating electrical machine is characterized by being formed radially outward from the outlet side opening. The rotating electrical machine according to claim 1, wherein
On the bottom surface of the cylindrical member, an annular outer protruding wall portion that protrudes to one end side of the rotating shaft at a radially outer side than the inlet side opening portion of the first through hole is formed,
The inlet-side opening of the second through hole is formed radially inward from the inner peripheral surface of the outer protruding wall or the outer protruding wall.
The rotating electrical machine, wherein the second through hole is inclined radially outward from one end side to the other end side of the rotating shaft. In the rotating electrical machine according to claim 2,
The cooling fluid is a cooling oil that is a lubricating oil;
The cooling target drive component is a gear mechanism or friction engagement means connected to the rotating shaft,
The first through hole extends along the rotation shaft from one end side to the other end side of the rotation shaft,
The rotary electric machine characterized in that a cross-sectional area of the second through hole is smaller than a cross-sectional area of the first through hole. In the rotary electric machine according to claim 2 or 3,
On the bottom surface of the cylindrical member, an inner protruding wall portion that protrudes to the other end side of the rotary shaft at a radially outer side than an outlet side opening portion of the first through hole is formed,
The outlet side opening of the second through hole is formed on a radially outer side than the inner protruding wall portion or on an outer peripheral surface of the inner protruding wall portion. The rotating electrical machine according to claim 4, which is dependent on claim 3,
When viewed in the radial direction of the motor rotor, the tip of the inner projecting wall portion overlaps a part of a gear constituting the gear mechanism or a part of the friction engagement means. The rotating electrical machine according to claim 1, wherein
On the bottom surface of the cylindrical member, an annular first outer protruding wall portion that protrudes to one end side of the rotating shaft at a radially outer side than an inlet side opening portion of the first through hole is formed.
In the first outer protruding wall portion, a radial through hole penetrating from the radially inner side to the radially outer side is formed,
Furthermore, an annular second outer projecting wall portion projecting to one end side of the rotation shaft is formed on the bottom surface of the cylindrical member at a radially outer side than the radial through hole,
The entrance-side opening of the second through hole is formed at a position that is radially outward from the first outer protruding wall and radially inner than the second outer protruding wall. Rotating electric machine. A rotating shaft, a cylindrical member having a bottom surface formed on one end side of the rotating shaft and an opening formed on the other end side, coupled to the outer periphery of the rotating shaft by the bottom surface, and fixed to the outer periphery of the cylindrical member A motor rotor having a rotor core,
A rotary electric machine comprising: refrigerant supply means for supplying a cooling fluid for cooling the motor rotor;
The refrigerant supply means supplies the cooling fluid from one end side of the rotating shaft to the bottom surface of the cylindrical member from the bottom surface of the cylindrical member,
The bottom surface of the cylindrical member includes a through hole that guides the cooling fluid inside the cylindrical member, and inside the cylindrical member, a cooling target drive component connected to the rotating shaft is disposed,
The rotating electrical machine characterized in that the through hole is inclined radially outward from one end side to the other end side of the rotating shaft.

Images