JP2011015523A - Motor unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a motor unit which is miniaturized and changes an induction voltage without being affected by the number of revolutions.SOLUTION: The motor unit 10 includes a shaft 24 which transmits a drive force to a driven body, a rotor 22, permanent magnets 30, a stator 21, and a housing 11 accommodating the rotor and the stator. The rotor is divided into a first rotor 51 and a second rotor 52 in the axial direction, the first rotor is fixed to the shaft, the second rotor has a hydraulic turning mechanism 99, and the second rotor is supported so as to be turnable in the circumferential direction with respect to the shaft by the hydraulic turning mechanism.

Description

  The present invention relates to a motor unit.

  An inner rotor type motor is configured such that a rotor is disposed in a space formed inside a cylindrical stator, and the rotor is rotatable with respect to the stator. In addition, in this type of motor, a motor is known in which a permanent magnet is disposed on the rotor, a coil is disposed on the stator, a current is passed through the coil, a rotating magnetic field is generated in the stator, and the rotor is driven to rotate. . The motor configured as described above is used as a vehicle motor because it can achieve high output even if it is small.

  By the way, if a motor using the above-described permanent magnet is adopted as a motor for a vehicle, an excessive induced voltage is generated in the stator coil when the rotational speed of the rotor is increased. Since the rotational speed limit is determined by the induced voltage, a technique for changing the induced voltage by field-weakening control has been proposed (see, for example, Patent Documents 1 and 2).

Japanese Patent Laid-Open No. 2004-64942 JP 2002-262534 A

  However, in the motors (rotary electric machines) of Patent Documents 1 and 2, the rotor is divided into two parts in the axial direction, and as the rotational speed of the shaft (rotating shaft) increases, at least one of the divided rotors is moved in the axial direction of the shaft. It is configured to move along the circumferential direction and mechanically obtains the same effect as field weakening control. If the split rotor is configured to be movable along the axial direction of the shaft in this way, it is necessary to enlarge the housing accordingly, and there is a limit to downsizing the motor unit. Further, when the divided rotor is moved in the axial direction and the position thereof is shifted from the stator, there is a problem that the magnetic flux of the rotor turns around the axial end surface (side surface) of the stator and drag resistance increases.

  Accordingly, the present invention has been made in view of the above circumstances, and provides a motor unit capable of reducing the size and changing the induced voltage without being influenced by the rotational speed.

  In order to solve the above-described problems, the invention described in claim 1 is provided such that a shaft (for example, the shaft 24 in the embodiment) that transmits a driving force to a driven body and the shaft penetrates through a central portion. The formed cylindrical rotor (for example, the rotor 22 in the embodiment), a plurality of permanent magnets (for example, the permanent magnet 30 in the embodiment) provided along the outer periphery of the rotor, and the outer peripheral surface of the rotor A cylindrical stator (for example, the stator 21 in the embodiment) provided so as to house the rotor and the stator, and a housing (for example, the motor in the embodiment) provided to cover the outer peripheral surface of the stator. Housing 11) and a motor unit (for example, motor unit 10 in the embodiment), the rotor is axial Divided into a first rotor (for example, the first rotor 51 in the embodiment) and a second rotor (for example, the second rotor 52 in the embodiment), and the first rotor is fixed to the shaft, and the second rotor The rotor includes a hydraulic rotation mechanism (for example, the hydraulic rotation mechanism 99 in the embodiment), and the second rotor is supported by the hydraulic rotation mechanism so as to be rotatable in the circumferential direction with respect to the shaft. It is a feature.

  In the invention described in claim 2, a water jacket (for example, the water jacket 45 in the embodiment) is formed in the housing, and the oil (for example, the lubricating oil 14 in the embodiment) supplied to the hydraulic rotation mechanism is The water jacket is configured to be able to flow further on the outer peripheral side, and the oil is configured to be able to exchange heat in the water jacket before being supplied to the hydraulic rotation mechanism.

  According to a third aspect of the present invention, an oil pump (for example, the oil pump 15 in the embodiment) that is driven by the rotational force of the shaft is provided on the end side of the shaft where the first rotor is disposed. An oil passage (for example, oil passage 16 in the embodiment) is formed so that the oil discharged from the oil pump is heat-exchanged on the outer peripheral side of the water jacket and then supplied to the hydraulic rotation mechanism. It is characterized by being.

  According to a fourth aspect of the present invention, the shaft is supported and fixed to the housing via a bearing (for example, the bearings 26 and 27 in the embodiment), and the oil supplied to the hydraulic rotation mechanism is the bearing. The lubricating oil supplied to the

  According to a fifth aspect of the present invention, the second rotor covers a cylindrical first collar (for example, the first collar 63 in the embodiment) fixed to the shaft, and an outer peripheral surface of the first collar. A second collar configured to be rotatable in the circumferential direction with respect to the first collar (for example, the second collar 64 in the embodiment), covers an outer peripheral surface of the second collar, and is fixed to the second collar. A rotor yoke (for example, the second yoke 65 in the embodiment), and a hydraulic chamber (for example, the hydraulic chamber 91 in the embodiment) is formed between the first collar and the second collar. A biasing member (for example, the spring 90 in the embodiment) that connects the first collar and the second collar is provided, and supplies the oil to the hydraulic chamber against the biasing force of the biasing member. And said Is characterized in that second rotor is arranged to rotate in the circumferential direction with respect to the shaft.

  According to a sixth aspect of the present invention, in the state where the oil is not supplied to the hydraulic chamber, the second rotor is held in an advanced state, and the oil is supplied to the hydraulic chamber as the oil is supplied. The two-rotor is characterized in that it can be rotated in the retarding direction.

  According to a seventh aspect of the invention, the second rotor covers a cylindrical first collar fixed to the shaft, an outer peripheral surface of the first collar, and rotates in a circumferential direction with respect to the first collar. A second collar configured to be movable; and a rotor yoke that covers an outer peripheral surface of the second collar and is fixed to the second collar; and a first collar between the first collar and the second collar. A hydraulic chamber (for example, the first hydraulic chamber 191 in the embodiment) and a second hydraulic chamber (for example, the second hydraulic chamber 192 in the embodiment) are formed, and at least one of the first hydraulic chamber and the second hydraulic chamber. By supplying the oil to one side, the second rotor is configured to rotate in the circumferential direction with respect to the shaft.

According to the first aspect of the present invention, the rotor is divided into the first rotor and the second rotor in the axial direction, and the second rotor is configured to be rotatable in the circumferential direction by the hydraulic rotation mechanism. The phase difference between the permanent magnet provided in the first rotor and the permanent magnet provided in the second rotor is configured to be variable. That is, since it is possible to change the phase difference between the two rotors without moving the first rotor and the second rotor in the axial direction, it is not necessary to secure an extra space in the housing. Miniaturization can be achieved.
Further, since the phase difference between the first rotor and the second rotor can be adjusted by the hydraulic rotation mechanism without being affected by the rotational speed of the shaft, the induced voltage can be variably operated, and the motor The performance can be maximized. That is, it is possible to obtain a high torque by reducing the phase difference between the first rotor and the second rotor, while increasing the phase difference between the first rotor and the second rotor. Since the torque ripple is suppressed during low-speed rotation of the shaft, the starting NV (vibration) can be suppressed low, and the induced voltage can be suppressed low during high-speed rotation of the shaft, so that the maximum rotation speed can be increased.

  According to the second aspect of the present invention, since the cooled oil after heat exchange by the water jacket is supplied to the hydraulic rotation mechanism, the hydraulic rotation is performed without adversely affecting each member of the hydraulic rotation mechanism. The moving mechanism can function.

  According to the invention described in claim 3, by disposing the oil pump on the first rotor side, the oil passage for supplying oil to the hydraulic rotation mechanism can be efficiently arranged. Therefore, the motor unit can be reduced in size.

  According to the invention described in claim 4, since it is configured to share the lubricating oil for the bearing provided generally and the oil supplied to the hydraulic rotation mechanism, it is possible to install an extra pump or the like. Oil can be supplied to the hydraulic rotation mechanism with a simple configuration.

  According to the fifth aspect of the present invention, since the second collar can be rotated in the circumferential direction relative to the first collar by supplying oil to the hydraulic chamber, the first rotor and the second rotor A phase difference can be provided between the two. Further, the magnitude of the phase difference between the first rotor and the second rotor can be adjusted by adjusting the amount of oil supplied to the hydraulic chamber. Therefore, the phase difference between the first rotor and the second rotor can be adjusted without being affected by the rotational speed of the shaft, and motor efficiency can be improved by optimally controlling the phase difference.

  According to the sixth aspect of the present invention, when the motor unit is started, the phase difference between the first rotor and the second rotor is in the maximum state (advanced state), and the standby in which no oil is supplied to the hydraulic chamber. The motor can be smoothly started by configuring so that the state is an advanced angle state.

  According to the invention described in claim 7, by supplying oil to the first hydraulic chamber and the second hydraulic chamber, the second collar can be rotated in the circumferential direction with respect to the first collar. A phase difference can be provided between the first rotor and the second rotor. Moreover, the magnitude of the phase difference between the first rotor and the second rotor can be adjusted by adjusting the amount of oil supplied to the first hydraulic chamber and the second hydraulic chamber. Therefore, the phase difference between the first rotor and the second rotor can be adjusted without being affected by the rotational speed of the shaft, and motor efficiency can be improved by optimally controlling the phase difference.

It is a schematic structure sectional view of a motor unit in an embodiment of the present invention. It is a perspective view which shows the structure of the rotor and shaft in 1st embodiment of this invention. It is a cross-sectional perspective view which follows the AA line of FIG. It is sectional drawing which follows the BB line of FIG. It is a disassembled perspective view of the 2nd rotor in 1st embodiment of this invention. It is a perspective view of the shaft in a first embodiment of the present invention. It is a figure explaining the hydraulic rotation mechanism in a first embodiment of the present invention, and is a figure showing the state where the skew angle between the 1st rotor and the 2nd rotor is the minimum. It is a figure explaining the hydraulic rotation mechanism in 1st embodiment of this invention, and is a figure which shows the state with the largest skew angle between a 1st rotor and a 2nd rotor. It is a fragmentary sectional view of the motor unit in a first embodiment of the present invention, and is a figure explaining the oil passage of lubricating oil. It is a figure explaining the output characteristic of the motor unit in the embodiment of the present invention. It is a cross-sectional perspective view (equivalent to FIG. 3 of 1st embodiment) which shows the structure of the rotor and shaft in 2nd embodiment of this invention. It is sectional drawing (equivalent to FIG. 4 of 1st embodiment) which shows the structure of the rotor and shaft in 2nd embodiment of this invention. It is a disassembled perspective view of the 2nd rotor in 2nd embodiment of this invention. It is a perspective view of the shaft in 2nd embodiment of this invention. It is a fragmentary sectional view of the motor unit in a second embodiment of the present invention, and is a figure explaining the oil passage of the lubricating oil when the skew angle between the first rotor and the second rotor becomes the minimum state. It is a fragmentary sectional view of the motor unit in a second embodiment of the present invention, and is a figure explaining the oil passage of the lubricating oil when the skew angle between the first rotor and the second rotor reaches a maximum state. It is a figure explaining the rotation method of the 2nd rotor in 2nd embodiment of this invention, and is a figure which shows a state with the smallest skew angle with a 1st rotor. It is a figure explaining the rotation method of the 2nd rotor in 2nd embodiment of this invention, and is a figure which shows a state with the largest skew angle with a 1st rotor.

(First embodiment)
Next, a first embodiment of the present invention will be described with reference to FIGS. In the present embodiment, a motor employed in the vehicle drive motor unit will be described.

(Vehicle drive motor unit)
FIG. 1 is a schematic sectional view of a vehicle drive motor unit.
As shown in FIG. 1, a vehicle drive motor unit (hereinafter referred to as a motor unit) 10 is a motor that houses a motor 23 that includes a stator 21 around which a coil 17 is wound and a rotor 22 that includes a permanent magnet 30. A housing 11, a transmission housing 12 that is fastened to one end side in the axial direction of the motor housing 11, and that houses a power transmission unit (not shown) that transmits power from a shaft 24 that serves as a rotation shaft of the motor 23, And a sensor housing 13 that is fastened to the other end side in the axial direction and accommodates the rotation sensor 25 of the motor 23. The mission housing 12 includes a common housing 12A fastened to the motor housing 11 and a gear housing 12B fastened to the common housing 12A. The interior of the motor housing 11 is configured as a motor chamber 36, the interior of the mission housing 12 is configured as a mission chamber 37, and the interior of the sensor housing 13 is configured as a sensor chamber 38.

  The motor housing 11 is formed in a substantially cylindrical shape so as to cover the entire motor 23. The shared housing 12 </ b> A is connected to the motor housing 11, and a partition wall 41 that partitions the motor chamber 36 and the mission chamber 37 is formed. A through hole 40 penetrating in the thickness direction of the partition wall 41 is formed at a central portion in the radial direction of the partition wall 41. The through hole 40 is provided with a bearing 26 that rotatably supports one end side of the shaft 24 of the motor 23. At one end of the shaft 24, a helical gear (oblique gear) 28 that meshes with the power transmission unit in the mission housing 12 is formed.

  A boss portion 32 that protrudes toward one end in the axial direction is formed at the radial center of the sensor housing 13. A through hole 33 that penetrates in the axial direction and communicates with the sensor chamber 38 and the motor chamber 36 is formed in the central portion in the radial direction of the boss portion 32, and the shaft 24 is inserted through the through hole 33 and the sensor chamber 38. The other end side of the shaft 24 is arranged inside. The rotation angle of the motor 23 can be detected by detecting the rotation angle of the shaft 24 by the rotation sensor 25 arranged in the sensor chamber 38. On the other end side (the sensor chamber 38 side) of the inner peripheral surface of the through hole 33, an inner flange portion 34 is formed to project radially inward from the inner peripheral surface of the through hole 33. A bearing 27 that rotatably supports the other end side of the shaft 24 is disposed on one end side of the through hole 33 in a space surrounded by the inner peripheral surface of the through hole 33 and the end surface of the inner flange portion 34. ing. In this case, the forward rotation direction of the shaft 24 is counterclockwise when viewed from the one end side of the shaft 24 to the other end side (see arrow C in FIG. 1).

  In the motor unit 10 (the motor housing 11, the transmission housing 12, and the sensor housing 13), lubricating oil 14 for improving the lubricating performance of the bearings 26 and 27 and the like is introduced. The stator 21 is disposed in a state where a part of the stator 21 is immersed in the lubricating oil 14. An oil pump 15 is provided in the mission housing 12, and the lubricating oil 14 pumped up by the oil pump 15 is configured to circulate through the motor unit 10 through the oil passage 16. The lubricating oil 14 that circulates in the motor unit 10 is supplied to the bearings 26, 27, etc., so that the lubricating performance of the bearings 26, 27, etc. is improved.

  A water jacket 45 for cooling the motor 23 (stator 21) is provided in the wall portion 31 of the motor housing 11 so as to cover the entire circumference of the stator 21. The stator 21 is shrink-fitted into the motor housing 11 and is disposed so as to be in close contact with the inner peripheral surface of the motor housing 11.

(Rotor)
2 is a perspective view of the rotor and the shaft, FIG. 3 is a cross-sectional perspective view taken along the line AA in FIG. 2, FIG. 4 is a cross-sectional view taken along the line BB in FIG. It is a disassembled perspective view of a 2nd rotor.

  As shown in FIGS. 2 to 5, the rotor 22 is formed in a substantially cylindrical shape, and a shaft 24 is inserted through the central axis thereof. The rotor 22 of the present embodiment is divided into two along the axial direction of the shaft 24, and a first rotor 51 disposed on one end side in the axial direction and a second rotor 52 disposed on the other end side in the axial direction. It is equipped with. The first rotor 51 and the second rotor 52 are disposed on the shaft 24 so that their axial end faces are substantially in contact with each other.

  The first rotor 51 includes a substantially cylindrical fixed collar 53 that is press-fitted and fixed to the shaft 24, and a substantially cylindrical first yoke 54 that is disposed along the outer peripheral surface of the fixed collar 53. The first yoke 54 is press-fitted and fixed to the fixed collar 53, for example. That is, the first rotor 51 is fixed to the shaft 24 without moving in the circumferential direction with respect to the shaft 24. A plurality of through holes 55 are formed along the circumferential direction on the outer peripheral edge of the first yoke 54, and the permanent magnets 30 are disposed in the through holes 55. The permanent magnet 30 has magnets 30N and 30S with different magnetic poles arranged alternately in the circumferential direction.

  In addition, a presser plate portion 56 for preventing the permanent magnet 30 from falling out of the through hole 55 is formed on one end side in the axial direction of the fixed collar 53. The holding plate portion 56 is formed in a substantially ring shape extending from the one end side end portion of the fixed collar 53 toward the radially outer side. Further, the presser plate portion 56 is formed in a size that covers at least a part of the permanent magnet 30 when viewed from the axial direction. Further, in the fixed collar 53, a portion having no functional problem is cut out in order to reduce the weight.

  The second rotor 52 includes a substantially cylindrical first collar 63 that is press-fitted and fixed to the shaft 24, a substantially cylindrical second collar 64 that is disposed along the outer peripheral surface of the first collar 63, and a second collar 64. And a substantially cylindrical second yoke 65 disposed along the outer peripheral surface of the first yoke 65. For example, the second yoke 65 is press-fitted and fixed to the second collar 64. A plurality of through holes 66 are formed along the circumferential direction on the outer peripheral edge of the second yoke 65, and the permanent magnets 30 are disposed in the through holes 66. The permanent magnet 30 has magnets 30N and 30S having different magnetic poles arranged alternately in the circumferential direction.

  Further, a presser plate 67 for preventing the permanent magnet 30 from falling out of the through hole 66 is disposed on the other axial end side of the second rotor 52. The presser plate 67 is formed in a substantially ring shape extending from the outer peripheral surface near the other end of the first collar 63 toward the radially outer side. Further, the presser plate 67 is formed in such a size as to cover at least a part of the permanent magnet 30 when viewed from the axial direction. The presser plate 67 is fastened to the second collar 64 using bolts 68.

  The first collar 63 includes a cylindrical main body portion 70 having a through hole 71 through which the shaft 24 is inserted, a bulging portion 73 bulging in the radial direction near the axial center of the main body portion 70, and a bulging portion. And a plurality of locking pieces 74 (four in this embodiment) extending from the outer peripheral surface of the portion 73 toward the radially outer side. The bulging portion 73 and the locking piece 74 are configured to be disposed in a space formed between the second collar 64 and the presser plate 67 in a state where the second rotor 52 is assembled. Further, a plurality of through holes 75 are formed to communicate between the inner peripheral surface of the through hole 71 of the first collar 63 and the outer peripheral surface of the bulging portion 73. The through hole 75 is configured to allow the lubricating oil 14 to flow therethrough.

  The second collar 64 is a substantially cylindrical member in which an accommodation chamber 81 that can accommodate the first collar 63 is formed. An opening through which the first collar 63 can be inserted in the axial direction is formed on the other end side in the axial direction of the second collar 64. On the other hand, a wall 83 for positioning the first collar 63 inserted in the storage chamber 81 in the axial direction is formed on one axial end of the second collar 64. The wall 83 is formed with a through-hole through which the main body 70 of the first collar 63 can be inserted, and the bulging portion 73 of the first collar 63 and one axial end surface of the locking piece 74 are substantially in contact with each other. It is comprised so that.

  A plurality of restricting pieces 84 for restricting the circumferential movement range of the locking pieces 74 of the first collar 63 are formed on the inner peripheral surface of the second collar 64 so as to protrude radially inward. That is, the restricting piece 84 is formed so as to be disposed between the adjacent engaging pieces 74 and 74, and the engaging piece 74 can move between the adjacent restricting pieces 84 and 84. . A screw hole 85 into which the bolt 68 is screwed is formed along the axial direction on the other axial end side of the regulating piece 84.

  The second yoke 65 is a substantially cylindrical member arranged along the outer peripheral surface of the second collar 64. For example, the second yoke 65 is press-fitted and fixed to the second collar 64. That is, the second yoke 65 rotates together when the second collar 64 rotates in the circumferential direction with respect to the first collar 63. Therefore, the first rotor 51 and the second rotor 52 can be skewed.

  As shown in FIG. 6, an oil introduction hole 93 for introducing the lubricating oil 14 is formed on the peripheral surface near the other end of the shaft 24. In addition, the oil introduction groove 94 is formed in the circumferential surface of the shaft 24 in which the oil introduction hole 93 is formed over the entire circumference. Since the shaft 24 is rotated during driving, the lubricating oil 14 is temporarily supplied from the oil passage 16 to the oil introduction groove 94 and guided from the oil introduction groove 94 to the oil introduction hole 93 so that the shaft 24 rotates. The lubricating oil 14 can be guided into the shaft 24. The shaft 24 is formed in a substantially cylindrical shape in order to reduce the weight. Here, the oil introduction hole 93 is formed inward in the radial direction, and is connected to an oil introduction path 96 formed along the axial direction in the meat portion 95 constituting the outer periphery of the shaft 24. Note that the other end portion of the oil introduction path 96 is sealed by a sealing member (not shown) so that the lubricating oil 14 does not leak.

  An oil outlet hole 97 for discharging the lubricating oil 14 to the outside of the shaft 24 is formed in the vicinity of the end of the oil introduction path 96 opposite to the side where the oil introduction hole 93 is formed. In addition, the oil lead-out groove 98 is formed on the circumferential surface of the shaft 24 in which the oil lead-out hole 97 is formed over the entire circumference in the circumferential direction. Further, a through hole 75 of the first collar 63 is disposed at a position facing the oil lead-out groove 98. With this configuration, the lubricating oil 14 can be supplied to the plurality of through holes 75 substantially evenly.

Next, a method for skewing the second rotor 52 will be described more specifically.
As shown in FIG. 7, between the side surface 74 a on one circumferential side of the locking piece 74 of the first collar 63 and the side surface 84 a on the other circumferential side of the regulating piece 84 of the second collar 64 in the second rotor 52. Is provided with a spring 90. The spring 90 is biased in the contracting direction, in other words, biased in a direction in which the side surface 74a of the locking piece 74 to which both ends of the spring 90 are fixed and the side surface 84a of the regulating piece 84 abut. . Therefore, as shown in FIG. 8, when no external force is applied to the spring 90, the spring 90 is contracted to a minimum (not shown in FIG. 8), and the side surface 74 a of the locking piece 74 and the regulating piece 84. Is held in contact with the side surface 84a. In the present embodiment, this state is set so that the skew angle θ between the first rotor 51 and the second rotor 52 is maximized.

  Further, the through hole 75 formed in the first collar 63 opens between the side surface 74 a of the locking piece 74 and the side surface 84 a of the regulating piece 84, and by supplying the lubricating oil 14 from the through hole 75. The lubricating oil 14 is supplied between the side surface 74 a of the locking piece 74 and the side surface 84 a of the regulating piece 84. By supplying the lubricating oil 14, pressure (hydraulic pressure) is generated to push and spread between the side surface 74 a of the locking piece 74 and the side surface 84 a of the regulating piece 84, and the lubricating oil 14 is more than the biasing force of the spring 90. When the hydraulic pressure increases, the space between the side surface 74a of the locking piece 74 and the side surface 84a of the restricting piece 84 is expanded. That is, the second collar 64 rotates in the circumferential direction with respect to the first collar 63.

  A space surrounded by the side surface 74 a of the locking piece 74, the side surface 84 a of the regulating piece 84, the outer peripheral surface of the first collar 63 and the inner peripheral surface of the second collar 64 is configured as the hydraulic chamber 91. Further, a mechanism for supplying the lubricating oil 14 between the first collar 63 and the second collar 64 of the second rotor 52 to rotate the second rotor 52 with respect to the first rotor 51 is referred to as a hydraulic rotation mechanism 99. To do.

  The second collar 64 is configured to be rotatable until the side surface 74b circumferentially opposite to the side surface 74a of the locking piece 74 and the side surface 84a of the regulating piece 84 abut on the side surface 84b opposite to the circumferential direction. Has been. The state where the side surface 74b of the locking piece 74 and the side surface 84b of the restricting piece 84 are in contact is the state shown in FIG. 7, and at this time, the skew angle between the first rotor 51 and the second rotor 52 is minimum ( 0 °).

Next, a mechanism for supplying the lubricating oil 14 to the second rotor 52 will be specifically described.
As shown in FIG. 9, the lubricating oil 14 is configured to flow through an oil passage 16 formed in the motor housing 11, the mission housing 12, and the sensor housing 13. Since the oil passage 16 of the motor housing 11 is formed in the vicinity of the outer periphery of the water jacket 45, the lubricating oil 14 is configured to be heat-exchangeable and coolable. The oil passage 16 formed in the sensor housing 13 has an oil passage (not shown in FIG. 9) formed so as to open to the inner peripheral surface of the through hole 33 in order to lubricate the bearing 27, and the shaft 24. And an oil passage 16A formed so as to face the oil introduction hole 93 (oil introduction groove 94).

  The lubricating oil 14 supplied from the oil passage 16 </ b> A is once supplied to the oil introduction groove 94 of the shaft 24, and is guided from the oil introduction groove 94 to the oil introduction hole 93. With this configuration, the lubricating oil 14 can be guided into the shaft 24 that is rotationally driven. The lubricating oil 14 supplied from the oil introduction hole 93 to the oil introduction passage 96 is discharged from the oil lead-out hole 97 to the outside of the shaft 24 and filled in the oil lead-out groove 98. The lubricating oil 14 filled in the oil introduction groove 98 passes through the through hole 75 and is supplied to the hydraulic chamber 91 formed between the first collar 63 and the second collar 64. The skew angle θ between the first rotor 51 and the second rotor 52 can be adjusted by adjusting the amount (hydraulic pressure) of the lubricating oil 14 supplied to the hydraulic chamber 91. The hydraulic pressure can be adjusted, for example, by providing a valve (not shown) in the middle of the oil passage 16 and adjusting the opening of the valve.

  FIG. 10 shows an output characteristic diagram of the motor 23 configured as described above. In FIG. 10, the output characteristic line 100 (one-dot chain line) in a state where the first rotor 51 and the second rotor 52 are not skewed (state where the skew angle is minimum), the first rotor 51, and the second rotor 52 And an output characteristic line 200 (two-dot chain line) in a state where the space between the two is skewed (maximum skew angle).

  As shown in FIG. 10, the output characteristic line 100 can obtain a high torque value when the rotational speed is low, but the maximum rotational speed is kept low. On the other hand, the output characteristic line 200 can obtain only a lower torque value than the output characteristic line 100 when the rotational speed is low, but the maximum rotational speed is higher than that of the output characteristic line 100. That is, although the torque value decreases, the maximum speed can be increased. Therefore, by adjusting the skew angle between the first rotor 51 and the second rotor 52, optimal control corresponding to the vehicle operation mode can be performed, and motor efficiency and driving performance can be improved.

  According to the present embodiment, the rotor 22 is divided into the first rotor 51 and the second rotor 52 in the axial direction, and the second rotor 52 is configured to be rotatable in the circumferential direction by the hydraulic rotation mechanism 99. The phase difference between the permanent magnet 30 provided in the first rotor 51 and the permanent magnet 30 provided in the second rotor 52 is configured to be variable. That is, since the phase difference between the two rotors 51 and 52 can be changed without moving the first rotor 51 and the second rotor 52 in the axial direction, an extra space is provided in the housing such as the motor housing 11. Therefore, it is possible to reduce the size of the motor unit 10.

  In addition, since the phase difference between the first rotor 51 and the second rotor 52 can be adjusted by the hydraulic rotation mechanism 99 without being affected by the rotational speed of the shaft 24, the induced voltage is maintained in the entire rotational speed range. Can be variably operated, and the motor performance can be maximized. That is, it is possible to obtain a high torque by minimizing the phase difference between the first rotor 51 and the second rotor 52, while the phase difference between the first rotor 51 and the second rotor 52. Since the torque ripple is suppressed when the shaft 24 rotates at a low speed, the starting NV (vibration) can be suppressed low, and the induced voltage can be suppressed low when the shaft 24 rotates at a high speed so that the maximum rotational speed is increased. It becomes possible.

  Further, since the cooled oil after the heat exchange by the water jacket 45 is supplied to the hydraulic rotation mechanism 99, the hydraulic rotation mechanism 99 is appropriately set without adversely affecting each member of the hydraulic rotation mechanism 99. Can function.

  Further, by arranging the oil pump 15 on the first rotor 51 side, the oil passage 16 that supplies oil to the hydraulic rotation mechanism 99 can be efficiently arranged. Therefore, the motor unit 10 can be reduced in size.

  In addition, since the lubricating oil supplied to the bearings 26 and 27 and the oil supplied to the hydraulic rotation mechanism 99 are configured to be shared by the lubricating oil 14, a simple configuration without installing an extra pump, Oil (lubricating oil 14) can be supplied to the hydraulic rotation mechanism 99.

  Further, by supplying the lubricating oil 14 to the hydraulic chamber 91, the second collar 64 can be rotated in the circumferential direction with respect to the first collar 63, and therefore, between the first rotor 51 and the second rotor 52. Can be provided with a phase difference. Also, by adjusting the amount of oil supplied to the hydraulic chamber 91, the magnitude of the phase difference (skew angle θ) between the first rotor 51 and the second rotor 52 can be adjusted. Therefore, the phase difference between the first rotor 51 and the second rotor 52 can be adjusted without being affected by the rotational speed of the shaft 24, and motor efficiency can be improved by optimally controlling the phase difference. Can do.

  A spring 90 having an urging force is provided between the first collar 63 and the second collar 64 in the contracting direction. When the lubricating oil 14 is not supplied to the hydraulic chamber 91, the first rotor 51 and the second rotor are provided. 52, the phase difference between the first rotor 51 and the second rotor 52 is increased by supplying the lubricating oil 14 to the hydraulic chamber 91. It comprised so that it might become small gradually. Therefore, the phase difference between the first rotor 51 and the second rotor 52 is in the maximum state (advanced state) when the motor unit 10 is started (at low speed rotation), and the phase difference is minimum. Since the torque ripple is smaller than in the case of (retarded state), the vehicle can be started mildly. Further, even if the lubricating oil 14 is not supplied at the time of high speed rotation of the shaft 24 due to a malfunction of the oil pump 15, by suppressing the induced voltage to the drive control circuit (not shown) of the motor 23 by the above configuration, It is also possible to protect the drive control circuit.

  Further, when the motor 23 rotates at a medium speed, the motor efficiency can be improved by optimally controlling the phase difference between the first rotor 51 and the second rotor 52.

  Further, when the motor 23 rotates at a high speed, the torque value is decreased by adjusting the phase difference between the first rotor 51 and the second rotor 52 to the maximum state (advanced state) again, but the maximum rotational speed is decreased. Can be raised.

(Second embodiment)
Next, a second embodiment of the present invention will be described with reference to FIGS. The present embodiment is different from the first embodiment only in the configuration of the hydraulic rotation mechanism, and the other configurations are substantially the same as those in the first embodiment. Description is omitted.
As shown in FIGS. 11 to 13, the hydraulic rotation mechanism 199 of this embodiment is particularly different from the first embodiment in the configuration of the second rotor 152 and the shaft 124.

  The second rotor 152 includes a substantially cylindrical first collar 163 that is press-fitted and fixed to the shaft 124, a substantially cylindrical second collar 64 that is disposed along the outer peripheral surface of the first collar 163, and a second collar 64. A substantially cylindrical second yoke 65 disposed along the outer peripheral surface of the first yoke 65. For example, the second yoke 65 is press-fitted and fixed to the second collar 64. A plurality of through holes 66 are formed along the circumferential direction on the outer peripheral edge of the second yoke 65, and the permanent magnets 30 are disposed in the through holes 66. The permanent magnet 30 has magnets with different magnetic poles arranged alternately in the circumferential direction. A presser plate 67 is disposed on the other axial end side of the second rotor 152.

  The first collar 163 includes a cylindrical main body portion 70 in which a through hole 71 through which the shaft 124 is inserted, a bulging portion 73 that bulges radially in the vicinity of the central portion in the axial direction of the main body portion 70, and a bulging portion And a plurality of locking pieces 74 (four in this embodiment) extending from the outer peripheral surface of the portion 73 toward the radially outer side. The bulging portion 73 and the locking piece 74 are configured to be disposed in a space formed between the second collar 64 and the presser plate 67 in a state where the second rotor 152 is assembled. In addition, a plurality of through holes 75 that communicate between the inner peripheral surface of the through hole 71 of the first collar 163 and the outer peripheral surface of the bulging portion 73 are formed. The through hole 75 is configured to allow the lubricating oil 14 to flow therethrough.

  Here, the through hole 75 includes a first through hole 75A formed in the vicinity of one end side in the axial direction of the bulging portion 73, and a second through hole 75B formed in the vicinity of the other end side in the axial direction. Yes. The first through hole 75A opens at the boundary between the side surface 74a of the locking piece 74 and the outer peripheral surface of the bulging portion 73, and the second through hole 75B extends from the side surface 74b of the locking piece 74 and the bulging portion. 73 is open at the boundary with the outer peripheral surface. That is, each of the first through hole 75A and the second through hole 75B is formed at four locations.

  As shown in FIG. 14, an oil introduction hole 193 for introducing the lubricating oil 14 is formed on the peripheral surface near the other end side of the shaft 124. In addition, the oil introduction groove 194 is formed in the circumferential surface of the shaft 124 in which the oil introduction hole 193 is formed over the entire circumference.

  Here, two oil introduction holes 193 are formed at positions shifted in the axial direction and the circumferential direction, the first oil introduction hole 193A formed on the other end side in the axial direction, and one end side in the axial direction. And a second oil introduction hole 193B. The oil introduction groove 194 includes a first oil introduction groove 194A formed along the circumferential direction of the first oil introduction hole 193A and a second oil introduction formed along the circumferential direction of the second oil introduction hole 193B. And a groove 194B.

  Further, two oil introduction passages 196 are formed along the axial direction in the meat portion 95 constituting the outer periphery of the substantially cylindrical shaft 124, and are formed so as to communicate with the first oil introduction hole 193A. The first oil introduction path 196A and the second oil introduction path 196B formed so as to communicate with the second oil introduction hole 193B are configured (see FIG. 16).

  Further, a first oil lead-out hole 197A for discharging the lubricating oil 14 to the outside of the shaft 124 is provided near the end of the first oil introduction path 196A opposite to the side where the first oil introduction hole 193A is formed. Is formed. Similarly, in the vicinity of the end of the second oil introduction passage 196B opposite to the side where the second oil introduction hole 193B is formed, a second oil outlet hole for discharging the lubricating oil 14 to the outside of the shaft 124. 197B is formed.

  Note that the first oil outlet groove 198A is formed over the entire circumference in the circumferential direction of the shaft 124 in which the first oil outlet hole 197A is formed. Similarly, the second oil outlet groove 198B is formed over the entire circumference in the circumferential direction of the shaft 124 in which the second oil outlet hole 197B is formed. The first oil outlet groove 198A is formed on one end side in the axial direction, and the second oil outlet groove 198B is formed on the other end side in the axial direction.

  The first through hole 75A of the first collar 163 is arranged at a position facing the first oil lead-out groove 198A, and the second through-hole of the first collar 163 is placed at a position facing the second oil lead-out groove 198B. The hole 75B is arranged. By comprising in this way, the lubricating oil 14 can be supplied substantially equally with respect to several through-hole 75A, 75B, respectively.

  On the other hand, as shown in FIGS. 15 and 16, each of the housings 11, 12, and 13 is formed with an oil passage 16 through which the lubricating oil 14 can flow, but the oil passage 16 is branched in the sensor housing 13. The first oil passage 16A that can communicate with the first oil introduction hole 193A and the second oil passage 16B that can communicate with the second oil introduction hole 193B are formed.

Next, a method for skewing the second rotor 152 will be described more specifically.
As shown in FIGS. 17 and 18, the space surrounded by the side surface 74 a of the locking piece 74, the side surface 84 a of the regulating piece 84, the outer peripheral surface of the first collar 163 and the inner peripheral surface of the second collar 64 is first. A space surrounded by the side surface 74 b of the locking piece 74, the side surface 84 b of the restriction piece 84, the outer peripheral surface of the first collar 163, and the inner peripheral surface of the second collar 64 is referred to as the hydraulic chamber 191. .

  As shown in FIG. 17, the lubricating oil 14 is supplied to the first hydraulic chamber 191, and the state where the side surface 74 b of the locking piece 74 and the side surface 84 b of the regulating piece 84 are in contact with each other is the first rotor 51. And the second rotor 152 are configured to have a minimum skew angle (phase difference 0 °). On the other hand, as shown in FIG. 18, the lubricating oil 14 is supplied to the second hydraulic chamber 192 and the side surface 74a of the locking piece 74 and the side surface 84a of the regulating piece 84 are in contact with each other. And the second rotor 152 are configured to have a maximum skew angle θ.

  That is, by supplying the lubricating oil 14 from the first through hole 75 </ b> A of the first collar 163, the lubricating oil 14 is supplied to the first hydraulic chamber 191. By supplying the lubricating oil 14, pressure (hydraulic pressure) is generated to push and spread between the side surface 74 a of the locking piece 74 and the side surface 84 a of the regulating piece 84, and the side surface 74 a of the locking piece 74 and the regulating piece The space between the side surface 84a of 84 is expanded. Then, the second collar 64 is rotatable in the circumferential direction with respect to the first collar 163 until the side surface 74b of the locking piece 74 and the side surface 84b of the regulating piece 84 abut. It is configured.

  On the other hand, by supplying the lubricating oil 14 from the second through hole 75 </ b> B of the first collar 163, the lubricating oil 14 is supplied to the second hydraulic chamber 192. By supplying the lubricating oil 14, pressure (hydraulic pressure) is generated so as to push and spread between the side surface 74 b of the locking piece 74 and the side surface 84 b of the regulating piece 84, and the side surface 74 b of the locking piece 74 and the regulating piece. The space between the side surface 84b of 84 is expanded. Then, the second collar 64 rotates in the circumferential direction with respect to the first collar 163, and the second collar 64 is rotatable until the side surface 74 a of the locking piece 74 and the side surface 84 a of the regulating piece 84 abut. It is configured.

  Therefore, the skew angle θ between the first rotor 51 and the second rotor 152 is adjusted by adjusting the amount (hydraulic pressure) of the lubricating oil 14 supplied to the first hydraulic chamber 191 and the second hydraulic chamber 192. Can do. The amount of the lubricating oil 14 supplied to the first hydraulic chamber 191 and the second hydraulic chamber 192 is a valve (not shown) provided in the middle of the oil passage 16 (first oil passage 16A, second oil passage 16B). It can be adjusted by adjusting the opening degree. For example, a solenoid valve is provided as the valve.

  According to this embodiment, since the lubricating oil 14 is supplied to the first hydraulic chamber 191 and the second hydraulic chamber 192, the second collar 64 can be rotated in the circumferential direction with respect to the first collar 163. A phase difference can be provided between the first rotor 51 and the second rotor 152. Further, by adjusting the amount of the lubricating oil 14 supplied to the first hydraulic chamber 191 and the second hydraulic chamber 192, the magnitude of the phase difference (skew angle θ) between the first rotor 51 and the second rotor 152 is adjusted. can do. Therefore, the phase difference between the first rotor 51 and the second rotor 152 can be adjusted without being affected by the rotational speed of the shaft 124, and motor efficiency can be improved by optimally controlling the phase difference. Can do.

  Note that the present invention is not limited to the above-described embodiment, and includes various modifications made to the above-described embodiment without departing from the spirit of the present invention. That is, the specific structure and configuration described in the embodiment are merely examples, and can be changed as appropriate.

  For example, in the first embodiment, the phase difference between the first rotor and the second rotor is the maximum (advanced state) when the motor unit is started (a state in which no lubricating oil is supplied to the hydraulic chamber). However, the phase difference may be set to a minimum state (retarded state). By setting in this way, a high torque can be obtained when the vehicle starts. Therefore, for example, when a travel mode (sport mode) is selected to improve acceleration performance at the start like a sports car, the phase difference between the first rotor and the second rotor is minimized at the start. Is preferred.

  DESCRIPTION OF SYMBOLS 10 ... Motor unit 11 ... Motor housing 14 ... Lubricating oil 15 ... Oil pump 16 ... Oil path 21 ... Stator 22 ... Rotor 24 ... Shaft 26 ... Bearing 27 ... Bearing 30 ... Permanent magnet 45 ... Water jacket 51 ... 1st rotor 52 ... 2nd rotor 63 ... 1st collar 64 ... 2nd collar 65 ... 2nd yoke (rotor yoke) 90 ... Spring (biasing member) 91 ... Hydraulic chamber 99 ... Hydraulic rotation mechanism 152 ... 2nd rotor 191 ... 1st hydraulic chamber 192: Second hydraulic chamber 199: Hydraulic rotation mechanism

Claims (7)

A shaft that transmits driving force to the driven body;
A cylindrical rotor provided so that the shaft penetrates the center;
A plurality of permanent magnets provided along the outer periphery of the rotor;
A cylindrical stator provided to face the outer peripheral surface of the rotor;
A motor unit including the rotor and the stator, and a housing provided so as to cover an outer peripheral surface of the stator,
The rotor is divided into a first rotor and a second rotor in the axial direction;
The first rotor is fixed to the shaft;
The motor unit, wherein the second rotor includes a hydraulic rotation mechanism, and the second rotor is supported by the hydraulic rotation mechanism so as to be rotatable in the circumferential direction with respect to the shaft. A water jacket is formed on the housing;
The oil supplied to the hydraulic rotation mechanism is configured to be able to flow further on the outer peripheral side of the water jacket,
2. The motor unit according to claim 1, wherein the oil is configured to be able to exchange heat in the water jacket before being supplied to the hydraulic rotation mechanism. An oil pump that is driven by the rotational force of the shaft is provided on the end side of the shaft where the first rotor is disposed,
3. The oil passage is formed so that the oil discharged from the oil pump is heat-exchanged on the outer peripheral side of the water jacket and then supplied to the hydraulic rotation mechanism. The motor unit described in 1.   The shaft is supported and fixed to the housing via a bearing, and the oil supplied to the hydraulic rotation mechanism is lubricating oil supplied to the bearing. The motor unit according to crab. The second rotor is
A cylindrical first collar fixed to the shaft;
A second collar configured to cover an outer peripheral surface of the first collar and to be rotatable in a circumferential direction with respect to the first collar;
A rotor yoke that covers the outer peripheral surface of the second collar and is fixed to the second collar;
A hydraulic chamber is formed between the first collar and the second collar, and an urging member that connects between the first collar and the second collar is provided,
The second rotor is configured to rotate in the circumferential direction with respect to the shaft by supplying the oil to the hydraulic chamber against the urging force of the urging member. The motor unit according to claim 1. In a state where the oil is not supplied to the hydraulic chamber, the second rotor is held in an advanced state,
The motor unit according to claim 5, wherein the second rotor is configured to be rotatable in a retarding direction as the oil is supplied to the hydraulic chamber. The second rotor is
A cylindrical first collar fixed to the shaft;
A second collar configured to cover an outer peripheral surface of the first collar and to be rotatable in a circumferential direction with respect to the first collar;
A rotor yoke that covers the outer peripheral surface of the second collar and is fixed to the second collar;
A first hydraulic chamber and a second hydraulic chamber are formed between the first collar and the second collar;
By supplying the oil to at least one of the first hydraulic chamber and the second hydraulic chamber, the second rotor is configured to rotate in the circumferential direction with respect to the shaft. The motor unit according to claim 1.

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