JP4494354B2 - Electric motor - Google Patents

Description

  The present invention relates to an electric motor.

Conventionally, for example, first and second rotors provided concentrically around a rotation axis of an electric motor are provided, and the first and second rotors are provided according to the rotational speed of the electric motor or the rotational magnetic field generated in the stator. An electric motor that controls the relative position of the second rotor in the circumferential direction, that is, the phase difference is known (see, for example, Patent Document 1).
In this electric motor, for example, when the phase difference between the first and second rotors is controlled according to the rotational speed of the electric motor, the first and second elements are displaced via a member that is displaced along the radial direction by the action of centrifugal force. The relative position in the circumferential direction of the rotor is changed. For example, when the phase difference between the first and second rotors is controlled in accordance with the speed of the rotating magnetic field generated in the stator, the stator windings are kept in a state where each rotor maintains the rotation speed due to inertia. The relative position in the circumferential direction of the first and second rotors is changed by passing a control current and changing the rotating magnetic field velocity.
JP 2002-204541 A

By the way, in the electric motor according to the above prior art, for example, when controlling the phase difference between the first and second rotors according to the rotational speed of the electric motor, the centrifugal force according to the operating state of the electric motor, that is, the rotational speed is There is a problem in that the phase difference between the first and second rotors can be controlled only in the operating state, and the phase difference cannot be controlled at an appropriate timing including the stop state of the electric motor. In addition, when the electric motor is mounted on a vehicle as a drive source, etc., when the external vibration is likely to act on the electric motor, the phase difference between the first and second rotors is determined only by the centrifugal force. The problem is that it is difficult to control properly. In addition, in this case, since the phase difference is controlled regardless of the fluctuation of the power supply voltage at the power supply to the motor, for example, the magnitude relationship between the power supply voltage and the counter electromotive voltage of the motor is reversed. May occur.
For example, when the phase difference between the first and second rotors is controlled according to the speed of the rotating magnetic field generated in the stator, the rotating magnetic field speed is changed, which complicates the motor control process. Problem arises.

  The present invention has been made in view of the above circumstances, and by making the induced voltage constant variable easily and appropriately while suppressing the complexity of the electric motor, the operable rotation speed range and torque range are expanded. An object of the present invention is to provide an electric motor capable of improving the operation efficiency and expanding the operable range with high efficiency.

In order to achieve the above object, an invention according to claim 1 is directed to an inner circumferential rotor (including an inner circumferential permanent magnet (for example, the inner circumferential permanent magnet 11a in the embodiment) disposed along the circumferential direction. For example, the outer peripheral side rotor (for example, the outer peripheral side rotation in the embodiment) including the inner peripheral side rotor 11 in the embodiment and the outer peripheral side permanent magnet (for example, the outer peripheral side permanent magnet 12a in the embodiment) arranged along the circumferential direction. The rotation axes of the rotor 12) are coaxially arranged, and at least one of the inner circumferential rotor and the outer circumferential rotor is rotated around the rotational axis to thereby rotate the inner circumferential rotor and the An electric motor (for example, the electric motor 10 in the embodiment) provided with a rotating means (for example, the rotating mechanism 14 in the embodiment) capable of changing a relative phase with the outer peripheral side rotor. The means includes a first member (for example, a vane rotor 32 in the embodiment) provided so as to be integrally rotatable with respect to the outer circumferential rotor, and is fixed integrally to the inner side of the inner circumferential rotor and the first member. And a second member (for example, the housing 33 in the embodiment) that defines a pressure chamber (for example, the first pressure chamber 56 and the second pressure chamber 57 in the embodiment) inside the inner circumferential rotor, Supplying a working fluid to the pressure chamber changes a relative phase between the inner circumferential rotor and the outer circumferential rotor, and the second member is moved from the pressure chamber to the second chamber . A through hole (for example, the through hole 33b in the embodiment) penetrating on the outer peripheral side of the member is formed, and a flow path (for example, in the embodiment) communicating with the through hole between the inner peripheral rotor and the second member. channels 51) is outside of said second member It is formed so as to extend along the surface, an end portion of said flow path, characterized in that is open at an end surface of the inner periphery side rotor (the end surface 33B of the example embodiment).

  The invention according to claim 2 is the invention according to claim 1, wherein the first member is disposed inside the inner circumferential rotor and has a plurality of blade portions (for example, the blade portion 36 in the embodiment). The vane rotor is provided integrally with the outer circumferential rotor, and the second member defines the pressure chamber with the vane portion while rotatably accommodating the vane portion of the vane rotor. A housing having a plurality of recesses (for example, the recesses 48 in the embodiment) and integrally provided inside the inner circumferential rotor, and communicating with the flow path for each of the plurality of pressure chambers. The through hole is formed.

Invention, in the invention according to claim 2, wherein the flow path forms a spiral shape extending in the circumferential direction, Tei Rukoto communicates with a plurality of the pressure chamber the through holes formed in each of the claims 3 It is characterized by.

  According to the first aspect of the present invention, permanent magnets are arranged along the circumferential direction on the inner circumferential rotor and the outer circumferential rotor, so that, for example, the field magnetic flux by the permanent magnet of the outer circumferential rotor is fixed. The amount of interlinkage magnetic flux interlinking the child windings can be efficiently increased or decreased by the field magnetic flux generated by the permanent magnet of the inner circumferential rotor. In the field-enhanced state, the torque constant (that is, the torque / phase current) of the motor can be set to a relatively high value without reducing current loss during motor operation or the stator. The maximum torque value output by the electric motor can be increased without changing the maximum value of the output current of the inverter that controls energization of the windings.

In addition, the rotating means rotates on the inner peripheral side by a first member provided so as to be integrally rotatable with respect to the outer peripheral rotor and a second member provided so as to be integrally rotatable with respect to the inner peripheral rotor. Since the working fluid is supplied to the pressure chamber defined inside the rotor, the relative phase between the inner rotor and the outer rotor is changed, which complicates the electric motor. The induced voltage constant can be made variable easily and appropriately at a desired timing while suppressing this, and as a result, the operable speed range and torque range can be expanded to improve operating efficiency and increase the operating efficiency. It is possible to expand the operating range with efficiency.
Furthermore, the relative phase between the inner peripheral side rotor and the outer peripheral side rotor can be set to a desired phase by controlling the supply amount of the working fluid to the pressure chamber.

  Further, when the outer circumferential rotor and the inner circumferential rotor rotate, a through hole formed through the second member from the pressure chamber to the outer circumferential side and a flow path between the inner circumferential rotor and the second member are formed. Accordingly, the working fluid can be discharged from the pressure chamber together with the impurities (contamination) contained in the working fluid, and accumulation of impurities contained in the working fluid on the wall surface of the pressure chamber can be suppressed. Further, since the working fluid discharged from the pressure chamber is discharged through the flow path between the inner circumferential rotor and the second member, the inner circumferential rotor and the second member can be cooled.

According to the invention of claim 2, the first member is a vane rotor having a plurality of blade portions, and the second member defines the pressure chambers with the blade portions while rotatably accommodating the blade portions of the vane rotor. In the case of the housing having a plurality of recesses formed, through holes communicating with the flow paths are formed for the plurality of pressure chambers, so that the accumulation of impurities can be suppressed for each of the plurality of pressure chambers.
In addition, since the vane rotor and the housing define the pressure chamber inside the inner circumferential rotor, an increase in the thickness in the direction of the rotation axis can be suppressed, and the size can be reduced.

  According to the invention of claim 3, since the flow path has a spiral shape extending in the circumferential direction, when the outer circumferential rotor and the inner circumferential rotor rotate, the through holes of each of the plurality of pressure chambers are rotated by the rotational force. Thus, the working fluid is sucked out and discharged from the end face of the inner circumferential rotor. Thus, since the spiral flow path functions as a screw pump and sucks out and discharges the working fluid in the pressure chamber together with the impurities, the accumulation of impurities can be effectively suppressed. In addition, since the working fluid discharged from the pressure chamber is discharged through the spiral flow path between the inner circumferential rotor and the second member, the entire inner circumferential rotor and the second member are averaged. Can be cooled.

Hereinafter, an electric motor according to an embodiment of the present invention will be described with reference to the drawings.
As shown in FIGS. 1 to 3, the electric motor 10 according to the present embodiment includes a substantially annular inner circumferential rotor 11 provided to be rotatable around the rotation axis of the electric motor 10, and the inner circumferential side. A substantially annular outer circumferential rotor 12 provided on the outer side in the radial direction with respect to the rotor 11 so as to be rotatable around a coaxial rotational axis, and aligned with the position in the rotational axis direction, and an inner circumferential side A stator 13 having the stator winding 13a shown in FIG. 1 for generating a rotating magnetic field for rotating the rotor 11 and the outer rotor 12 is connected to the inner rotor 11 and the outer rotor 12. And a rotation mechanism that changes the relative phase between the inner rotor 11 and the outer rotor 12 with the hydraulic pressure (fluid pressure) of hydraulic oil (working fluid) that is an incompressible fluid. Moving means) 14 and hydraulic pressure (not shown) for controlling the hydraulic pressure to the rotation mechanism 14. A brushless DC motor and a control device. The electric motor 10 is mounted as a drive source in a vehicle such as a hybrid vehicle or an electric vehicle, and its output shaft (rotating shaft) 16 is connected to an input shaft of a transmission (not shown). The driving force of the electric motor 10 is transmitted to driving wheels (not shown) of the vehicle via the transmission.

  When the driving force is transmitted from the driving wheel side to the electric motor 10 during deceleration of the vehicle, the electric motor 10 functions as a generator to generate a so-called regenerative braking force, and the kinetic energy of the vehicle body is used as electric energy (regenerative energy). to recover. Further, for example, in a hybrid vehicle, the rotation axis of the electric motor 10 is connected to a crankshaft of an internal combustion engine (not shown), and the electric motor 10 is used as a generator even when the output of the internal combustion engine is transmitted to the electric motor 10. Functions to generate power generation energy.

  The inner circumferential rotor 11 is arranged so that the rotation axis thereof is coaxial with the rotation axis of the electric motor 10, and has a substantially cylindrical inner circumferential rotor core 21 as shown in FIG. The inner circumferential rotor core 21 is provided with a plurality (specifically, 16 locations) of inner circumferential side magnet mounting portions 23,..., 23 at a predetermined equal pitch in the circumferential direction on the outer circumferential portion. ing. On the outer peripheral surface 21A of the inner rotor core 21, a concave groove 21a extending in parallel to the rotation axis is provided in the radial direction at a position between all the inner peripheral magnet mounting portions 23, 23 adjacent in the circumferential direction. It is formed to be recessed. The inner circumferential rotor core 21 is formed by, for example, sintering.

  Each of the inner peripheral side magnet mounting portions 23,..., 23 includes a pair of magnet mounting holes 23a, 23a penetrating the inner peripheral side rotor core 21 in parallel to the rotation axis. The pair of magnet mounting holes 23a, 23a have a substantially rectangular cross section in the direction parallel to the rotation axis, and are arranged in the same plane so as to be adjacent to each other in the circumferential direction via the center rib 23b. This plane is orthogonal to the radial line connecting the center rib 23b and the rotation axis. Each magnet mounting hole 23a, 23a is mounted with a substantially plate-like permanent magnet 11a extending parallel to the rotation axis.

The permanent magnets 11a mounted in the magnet mounting holes 23a,..., 23a are all magnetized in the same manner in the thickness direction (that is, the radial direction of the rotors 11 and 12). The pair of permanent magnets 11a, 11a mounted in the pair of magnet mounting holes 23a, 23a provided in the head 23 is set so that the magnetization directions thereof are the same. And in all the inner peripheral side magnet mounting parts 23, ..., 23, the inner peripheral side magnet mounting parts 23, 23 adjacent in the circumferential direction are mounted on a pair of permanent magnets 11a, 11a mounted on one side and the other. The paired permanent magnets 11a, 11a are set so that their magnetization directions are different from each other. That is, the inner peripheral side where the pair of permanent magnets 11a, 11a whose outer peripheral side is the S pole is mounted on the inner peripheral side magnet mounting portion 23 where the pair of permanent magnets 11a, 11a whose outer peripheral side is the N pole is mounted. The magnet mounting portion 23 is adjacent in the circumferential direction via the concave groove 21a.
As described above, the inner circumferential rotor 11 includes a plurality of permanent magnets 11a,..., 11a arranged along the circumferential direction.

  The outer circumferential rotor 12 is also arranged so that its rotational axis is coaxial with the rotational axis of the electric motor 10, and has a substantially cylindrical outer circumferential rotor core 22. The outer peripheral side magnet mounting portions 24,..., 24 are provided in the outer peripheral portion at a predetermined equal pitch in the circumferential direction as many as the inner peripheral side magnet mounting portions 23,. On the outer peripheral surface 22A of the outer rotor core 22, a groove 22a extending parallel to the rotation axis is recessed in the radial direction at a position between all the outer magnet mounting portions 24, 24 adjacent in the circumferential direction. Is formed. Further, bolts shown in FIG. 1 are inserted in positions between the inner diameter sides of the concave grooves 22a,..., 22a of the outer rotor core 22, that is, between adjacent ones of the outer magnet mounting portions 24,. A hole 22b is formed penetrating along the axial direction. The outer rotor core 22 is also formed by, for example, sintering.

  Each outer magnet mounting portion 24,..., 24 includes a pair of magnet mounting holes 24a, 24a penetrating in parallel with the rotation axis. The pair of magnet mounting holes 24a and 24a have a substantially rectangular cross section in the direction parallel to the rotation axis, and are arranged in the same plane so as to be adjacent to each other in the circumferential direction via the center rib 24b. This plane is orthogonal to the radial line connecting the center rib 24b and the rotation axis. Each magnet mounting hole 24a, 24a is mounted with a substantially plate-like permanent magnet 12a extending parallel to the rotation axis.

The permanent magnets 12a mounted in the magnet mounting holes 24a,..., 24a are all magnetized in the same manner in the thickness direction (that is, the radial direction of the rotors 11 and 12). The pair of permanent magnets 12a, 12a mounted in the pair of magnet mounting holes 24a, 24a provided in 24 are set so that the magnetization directions thereof are the same. And in all the outer peripheral side magnet mounting parts 24, ..., 24, the outer peripheral side magnet mounting parts 24, 24 adjacent in the circumferential direction are mounted on the pair of permanent magnets 12a, 12a mounted on one side and the other. The pair of permanent magnets 12a, 12a is set so that the magnetization directions are different from each other. In other words, the outer peripheral side magnet mounting portion 24 having the pair of permanent magnets 12a, 12a having the N pole on the outer peripheral side is mounted on the outer side magnet mounting having the pair of permanent magnets 12a, 12a having the S pole on the outer peripheral side. The parts 24 are adjacent to each other in the circumferential direction via the concave groove 22a.
As described above, the outer rotor 12 also includes a plurality of permanent magnets 12a, ..., 12a arranged along the circumferential direction.

  The inner peripheral magnet mounting portions 23 of the inner peripheral rotor 11 and the outer peripheral magnet mounting portions 24 of the outer peripheral rotor 12 are the diameters of the rotors 11 and 12, respectively. It arrange | positions so that it can mutually oppose in a direction. In this opposed arrangement state, all of the pair of permanent magnets 11a, 11a are in a state of being in one-to-one alignment with the corresponding pair of permanent magnets 12a, 12a. Further, each of the concave grooves 21a,..., 21a of the inner circumferential rotor 11 and each of the concave grooves 22a,. The phase in the rotational direction is in a one-to-one correspondence with the concave groove 22a.

  Thereby, according to the relative position of the inner peripheral side rotor 11 and the outer peripheral side rotor 12 around the rotation axis, the state of the electric motor 10 is changed to all the permanent magnets 11a, ..., 11a of the inner peripheral side rotor 11. In all the permanent magnets 12a,..., 12a of the outer circumferential rotor 12, the magnetic poles of the same polarity as the paired permanent magnets 11a, 11a and the paired permanent magnets 12a, 12a are opposed to each other (that is, the pair The paired permanent magnets 11a and 11a are paired with the permanent magnets 11a and 11a that make a pair from the weakened field state shown in FIG. The field in which the magnetic poles of the opposite polarities of the permanent magnets 12a and 12a are arranged opposite to each other (that is, the permanent magnets 11a and 11a that make a pair and the permanent magnets 12a and 12a that make a pair have the same polarity) and the field is strengthened most. Strength shown in 4 And it is capable of setting the appropriate state over the magnetic state.

  Here, the stator 13 shown in FIG. 1 is formed in a substantially cylindrical shape facing the outer peripheral portion of the outer peripheral rotor 12, and is fixed to, for example, a housing (not shown) of a vehicle transmission.

  Next, the rotation mechanism 14 that changes the relative phase between the inner circumferential rotor 11 and the outer circumferential rotor 12 as described above will be described.

  As shown in FIG. 1, the rotation mechanism 14 of the present embodiment includes a pair of disk-shaped drives that are fixed on both sides in the axial direction of the outer rotor 12 so as to cover the space inside the outer rotor 12. Plates (end plates) 31, 31, a vane rotor (first member) 32 provided integrally inside the outer peripheral rotor 12 by being sandwiched between the drive plates 31, 31, and the inner peripheral rotor 11 A housing (second member) 33 that is integrally fixed to the inner side and disposed between the inner rotor 11 and the vane rotor 32, the outer rotor 12, and the drive plates 31, 31 is provided. The vane rotor 32 and the housing 33 are formed by, for example, sintering.

  In the pair of drive plates 31, 31, a plurality of bolt insertion holes 31 a,..., 31 a penetrating in the axial direction (equal to the number of bolt insertion holes 22 b) are provided at equal intervals on the same circumference. An annular groove 31b shown in FIG. 1 that is recessed in the axial direction is formed on one side inside these bolt insertion holes 31a,..., 31a. The drive plate 31 is formed with a plurality of bolt insertion holes 31c,..., 31c penetrating in the axial direction inside the annular groove 31b so as to be equally spaced on the same circumference. Further, at the center position of the drive plate 31 that is inside the bolt insertion holes 31c,..., 31c, a cylindrical portion 31d that protrudes in a cylindrical shape along the axial direction is formed on the same side as the formation side of the annular groove 31b. The inside is a central hole 31e penetrating in the axial direction.

  As shown in FIGS. 2 and 3, the vane rotor 32 includes a cylindrical boss portion 35 and a plurality of the above-described bolts extending outward in the radial direction from circumferentially equidistant positions on the outer peripheral surface of the boss portion 35. The number of blade portions 36,..., 36 is the same as the number of insertion holes 31c (specifically, six locations).

  On both sides in the axial direction of the boss portion 35, a sandwiching base portion 37 having the same axial length as the blade portions 36,... 36 is formed on the outer peripheral side, and a stepped portion 38 is recessed in a stepped shape inward in the axial direction from the sandwiching base portion 37. Has a shape formed on the inner peripheral side. A connecting spline 35b shown in FIG. 1 is formed on the inner diameter side of the boss portion 35 in the axial direction intermediate position, and each vane portion is arranged on one side in the axial direction from the connecting spline 35b as shown in FIG. Passage holes 35c,..., 35c are formed penetrating on the same side in the rotational direction of the proximal end of the blade portion 36 closest to the inner peripheral side of the position of 36,. On the opposite side, passage holes 35d,..., 35d are formed penetrating on the same opposite side in the rotational direction of the proximal end of the blade part 36 closest to the inner peripheral side of the position of each blade part 36,. .

  As shown in FIG. 1, an output shaft 16 to which the driving force of the outer rotor 12 is transmitted is attached to the inner diameter side of the vane rotor 32. The output shaft 16 is connected to a spline 16a for connection to the connection spline 35b of the boss part 35, and an annular communication for connecting all the passage holes 35c of the boss part 35 in a state of being connected by the connection spline 16a. It has a groove 16b, an annular communication groove 16c that allows all the passage holes 35d to communicate with each other in the same state, and seal grooves 16d,..., 16d formed at both outer positions of the communication grooves 16b, 16c. These seal grooves 16d,..., 16d are provided with seal rings (not shown) that seal the gaps with the vane rotor 32, respectively. The output shaft 16 has a passage hole 16e for supplying and discharging hydraulic oil to and from the communication groove 16b through the inside, and a passage hole 16f for supplying and discharging hydraulic oil to and from the communication groove 16c. Is formed. The output shaft 16 has a bearing fitting portion 16g for fitting, for example, a pair of bearings 42, 42 held in a housing of a vehicle transmission to a portion protruding outward in the axial direction from the drive plates 31, 31. Are formed, and a gear 43 for transmitting the rotation of the output shaft 16 is splined to the drive plate 31 side of one bearing fitting portion 16g.

  Each of the blade portions 36,... 36 has a substantially plate shape, and a screw hole 36a penetrating in the axial direction is formed at an intermediate position as shown in FIG. In addition, a pair of concave portions 36b, 36b are formed on both sides in the circumferential direction over the entire length in the axial direction on the outer peripheral side from the position where the screw hole 36a is formed, and the position where the screw hole 36a is formed The concave portions 36c and 36c are also formed on the inner side over the entire length in the axial direction. Furthermore, a seal holding groove 36d that is recessed from the outer peripheral surface toward the center side is formed on the outer peripheral surface of each blade portion 36,... 36 over the entire length in the axial direction. Spring seals 44 that seal the gaps with the housing 33 are disposed on the seal holding portions 36d,. Each of the spring seals 44,..., 44 includes a seal 44a that is provided on the outer side and that is in sliding contact with the housing 33, and a spring 44b that is provided on the inner side and presses the seal 44a toward the housing 33 radially outward. Yes.

  A housing 33 that is integrally fitted inside the inner peripheral rotor 11 so as to have a predetermined phase relationship includes a cylindrical base portion 46 having a small radial thickness and an inner peripheral surface of the base portion 46. It has protrusions 47,..., 47 that are the same number as the blades 36 and protrude radially inward from circumferentially equidistant positions. Here, as shown in FIG. 1, the base portion 46 projects over the entire circumference on both sides in the axial direction from the projecting portion 47. As shown in FIG. 2, each of the protrusions 47,..., 47 has a substantially isosceles triangular shape that is tapered in the axial direction, and all the protrusions 47,. A concave portion 48 in which the vane portion 36 of the vane rotor 32 described above can be disposed is formed between the adjacent projecting portions 47 and 47. Each of the projecting portions 47,..., 47 is formed with a seal holding groove 47b that is recessed toward the outer diameter side on the inner end surface thereof over the entire length in the axial direction. Spring seals 50 for sealing a gap with the outer peripheral surface of the boss portion 35 of the vane rotor 32 are disposed in the seal holding portions 47b,. These spring seals 50,..., 50 are provided on the inner peripheral side and are in contact with the boss portion 35 of the vane rotor 32, and the seal spring 50b is provided on the outer diameter side and presses the seal 50a toward the vane rotor 32. It consists of and. The housing 33 may be integrally connected to the inner circumferential rotor 11 by fastening bolts or the like.

  In the present embodiment, the housing 33 has a spiral flow path that extends along the circumferential direction on the outer circumferential surface 33A and is gradually displaced toward one side in the axial direction toward the distal end in the extending direction. A formation groove 33a is formed. As shown in FIGS. 1 and 3, the flow path forming groove 33a is formed from an end surface 33B on one side in the axial direction of the housing 33, and rotates around the outer peripheral surface 33A of the housing 33 a plurality of times so as to end on the other side in the axial direction. Is formed. Further, as shown in FIG. 2, the housing 33 penetrates along the radial direction at the center position in the circumferential direction of the bottom wall surface 48 a on the radially outer side of each of the recesses 48,. A through hole 33b communicating with the formation groove 33a is formed. Each of the through holes 33b,..., 33b communicates with the spiral flow path forming groove 33a, so that the position of the housing 33 in the axial direction is different. When the housing 33 is fitted inside the inner circumferential rotor 11, the flow passage forming groove 33a and the inner circumferential surface 11A of the inner circumferential rotor 11 communicate with the through holes 33b, ..., 33b. A spiral channel 51 is formed. The flow path 51 is formed between the inner circumferential rotor 11 and the housing 33, has a spiral shape extending in the circumferential direction of the housing 33, and both end portions are housings of the inner circumferential rotor 11. An opening is formed at an end face 33B in the axial direction of 33.

  When assembling each of the above components, for example, by fitting the cylindrical portion 31d of one drive plate 31 to one stepped portion 38 of the vane rotor 32, the drive plate 31 and the vane rotor 32 are combined with each other. The bolts 54 are inserted into the respective bolt insertion holes 31c,..., 31c of the plate 31 and screwed into the screw holes 36a of the blade portion 36 of the vane rotor 32, respectively. Then, with the spring seals 44 attached to the blades 36,... 36 of the vane rotor 32, the blades 36,. The inner circumferential rotor 11 into which the housing 33 is press-fitted is aligned with one drive plate 31 with the spring seals 50,. Then, after the outer rotor 12 is aligned with one drive plate 31 so as to cover the outer side of the inner circumferential rotor 11, the other drive plate 31 is connected to the other fitting portion 38 of the vane rotor 32 with the center hole 31e. , 31a, the bolt insertion holes 31a, ..., 31a of the drive plate 31, the bolt insertion holes 22b, ..., 22b of the outer peripheral rotor 12, and the one drive plate 31 described above. The bolts 52 are inserted into the bolt insertion holes 31a,..., 31a, and the nuts 53 are screwed into the bolts 52,. Further, the bolts 54 are inserted into the bolt insertion holes 31c,..., 31c of the other drive plate 31, respectively, and the bolts 54,..., 54 are respectively screwed into the screw holes 36a of the blade portion 36 of the vane rotor 32.

  As a result, the drive plates 31, 31 fixed to both end faces in the axial direction of the outer rotor 12 are integrally fixed by the vanes 36,..., 36 of the vane rotor 32 and the bolts 54,. The bolts 54,..., 54 for fixing the blade portions 36,... 36 to the drive plate 31 are smaller in number and size than the bolts 52,. A large one is used.

  Thereafter, the output shaft 16 is fitted inside the vane rotor 32, and at that time, the connecting spline 16a and the connecting spline 35b are coupled. As a result, the output shaft 16 is fixed to the vane rotor 32 integrally. Of course, the above assembling procedure is an example, and it is possible to assemble in a procedure different from the above.

  As described above, the inner peripheral rotor 11 integrated with the housing 33 is provided in the space 58 between the drive plates 31 and 31 inside the outer peripheral rotor 12 and outside the vane rotor 32. The drive plates 31 and 31 are rotatably held at both sides in the axial direction of the base portion 46 entering the annular grooves 31b and 31b. Furthermore, the blade | wing part 36 of the vane rotor 32 is arrange | positioned 1 each in the recessed part 48 of the housing 33, ..., 48. Further, the output shaft 16 that is spline-coupled to the vane rotor 32 can rotate integrally with the outer peripheral rotor 12, the drive plates 31, 31, and the vane rotor 32, and specifically, is fixed integrally. In addition, since it becomes rotatable with respect to the outer peripheral rotor 12 and the drive plates 31, 31 provided integrally, both end surfaces in the axial direction of the inner peripheral rotor 11 are in contact with the opposing drive plate 31. A gap 59 shown in FIG. 1 can be formed therebetween, and the outer peripheral surface 21 </ b> A also has a slight gap 60 between the outer peripheral rotor 12.

  Here, when the permanent magnets 12a,..., 12a of the outer peripheral rotor 12 and the permanent magnets 11a,. In this way, all the impellers 36,..., 36 are in contact with the protrusions 47 adjacent to the same side in the rotation direction in the corresponding recesses 48, and the first pressure is between the protrusions 47 in contact with each other. The chamber 56 is formed, and a second pressure chamber 57 wider than the first pressure chamber 56 is formed between the protrusions 47 adjacent to each other on the same opposite side in the rotation direction (in other words, the recess 48. , ... and the impellers 36, ..., 36 accommodated in the recesses 48, ..., 48 form first pressure chambers 56, ..., 56 and second pressure chambers 57, ..., 57). As a result, the first pressure chambers 56,..., 56 and the second pressure chambers 57,... 57 are defined inside the inner circumferential rotor 11.

  On the contrary, when the permanent magnets 12a,..., 12a of the outer peripheral rotor 12 and the permanent magnets 11a,. Thus, all the impellers 36,..., 36 are brought into contact with the protrusions 47 adjacent to the same opposite side in the rotation direction in the corresponding recesses 48, respectively, and the second pressure chambers 57 are reduced. Expands the first pressure chamber 56 between the protrusions 47 adjacent to the same one side in the rotation direction. The passage holes 35c,..., 35c of the vane rotor 32 are provided in the first pressure chambers 56,..., 56 so as to always open one-to-one, and the vane rotor 32 is provided in the second pressure chambers 57,. Each of the passage holes 35d,..., 35d is provided so as to always open one-on-one.

  Each of the through holes 33b,..., 33b formed in the housing 33 is switched between a state of opening to the first pressure chamber 56 and a state of opening to the second pressure chamber 57 depending on the position of the impeller 36. In the state opened to the first pressure chamber 56, the first pressure chamber 56 penetrates from the first pressure chamber 56 to the outer peripheral surface 33 </ b> A side, and is formed for all the first pressure chambers 56,. Each of the through holes 33b,..., 33b penetrates from the second pressure chamber 57 to the outer peripheral surface 33A side of the housing 33 in a state of opening to the second pressure chamber 57, and all the second pressure chambers 57,. 57 is formed for each.

  Here, the outer circumferential rotor 12 and the inner circumferential rotor 11 are made of the strong field shown in FIG. 4 in which the permanent magnets 12a,..., 12a and the permanent magnets 11a,. The positions are set to the origin positions when the first pressure chambers 56,..., 56 and the second pressure chambers 57,. The first pressure chambers 56,..., 56 and the second pressure chambers 57,. Then, from this state of the origin, hydraulic oil is introduced into each first pressure chamber 56,..., 56 through each passage hole 35c,. When the hydraulic oil is discharged from the second pressure chambers 57,..., 57 through the passage holes 35d,..., 35d at the same time, the outer circumferential rotor 12 and the inner circumferential rotor 11 are Relative rotation against the magnetic force causes a field weakening state. Conversely, hydraulic oil is introduced into the second pressure chambers 57,..., 57 through the passage holes 35d,..., 35d, and at the same time, the passage holes 35c,. When the hydraulic oil is discharged through the outer circumferential rotor 12, the outer circumferential rotor 12 and the inner circumferential rotor 11 return to the origin position and enter a strong field state. At this time, the permanent magnet 12 a of the outer circumferential rotor 12 is used. ,..., 12a and the permanent magnets 11a,..., 11a of the inner rotor 11 are attracted by magnetic force, so that the pressure of the hydraulic oil introduced into the second pressure chambers 57,. The pressure may be lower than that required when the phase is changed to the field-weakening state, and in some cases, only supply and discharge of hydraulic oil is required without introducing hydraulic pressure.

  Here, the electric motor 10 starts from the weakened state in which the inner circumferential rotor 11 has the permanent magnets 12a,..., 12a and the permanent magnets 11a,. The direction of rotation when returning to the position coincides with the direction of the moment of inertia that occurs during decelerating rotation. That is, the electric motor 10 is set so as to rotate the outer circumferential rotor 12 and the inner circumferential rotor 11 in the clockwise direction in FIGS. 2 and 4 when the vehicle travels forward. When the outer rotor 12 is decelerated from the magnetic state, an inertia moment is generated in the inner rotor 11 in the floating state to return to the strong field state shown in FIG.

  Here, since the hydraulic oil is incompressible, the phase change to both limit ends of the strong field state and the weak field state as described above is of course an intermediate position between these limit ends. However, the hydraulic control device (not shown) supplies and discharges hydraulic fluid from all the first pressure chambers 56,..., 56 and the second pressure chambers 57,. By stopping, the outer circumferential rotor 12 and the inner circumferential rotor 11 maintain the phase relationship at that time, and the phase change can be stopped in an arbitrary field state.

  As described above, the vane rotor 32 described above is integrally fixed to the outer circumferential rotor 12 and can rotate integrally, and is disposed inside the inner circumferential rotor 11. Moreover, the vane rotor 32 is connected to the outer rotor 12 via drive plates 31 and 31 fixed to the outer rotor 12 so as to cover both end faces of the outer rotor 12 and the inner rotor 11 in the axial direction. And an output shaft 16 that outputs the driving force of the outer rotor 12 is also provided integrally. Further, the housing 33 described above is integrally fitted to the inner peripheral rotor 11 so as to be integrally rotatable, and the concave portion 48 allows the first pressure chamber 56 and the second pressure chamber 57 to be connected to the inner periphery with the vane rotor 32. It is defined inside the side rotor 11. Further, the relative phase of the vane rotor 32 with respect to the housing 33 is changed by supplying and discharging the hydraulic oil to and from the first pressure chamber 56 and the second pressure chamber 57, that is, the introduction control of the hydraulic pressure. The relative phase between the child 11 and the outer peripheral rotor 12 is changed. Here, the relative phase between the inner circumferential side rotor 11 and the outer circumferential side rotor 12 can be changed to the advance side or the retard side by at least 180 ° of the electrical angle, and the state of the electric motor 10 is A field-weakening state in which the same magnetic poles of the permanent magnet 11a of the inner rotor 11 and the permanent magnet 12a of the outer rotor 12 are arranged to face each other, and the permanent magnet 11a and outer periphery of the inner rotor 11 It is possible to set an appropriate state between the strong magnetic field state in which the magnetic poles of different polarities with respect to the permanent magnet 12a of the side rotor 12 are arranged to face each other.

  In addition, these outer peripheral rotors surrounded by drive plates 31 that transmit the driving force of the outer peripheral rotor 12 to the output shaft 16 are fixed to both end surfaces in the axial direction of the outer peripheral rotor 12 and the vane rotor 32, respectively. 12, the inner peripheral rotor 11 and the housing 33, which are integrated, are disposed in a space 58 shown in FIG. 2 between the vane rotor 32 and the drive plates 31, 31 so as to be rotatable in the circumferential direction. The integral part of the inner circumferential rotor 11 and the housing 33 is rotatably provided in the space 58 in a floating state (that is, not fixed to the drive plates 31 and 31 and the output shaft 16).

  For example, as shown in FIG. 5A, a strong field state in which the permanent magnet 11a of the inner rotor 11 and the permanent magnet 12a of the outer rotor 12 are arranged in the same polarity, for example, FIG. In the field-weakening state in which the permanent magnet 11a of the inner circumferential rotor 11 and the permanent magnet 12a of the outer circumferential rotor 12 are arranged as a counter electrode as shown in FIG. 6B, for example, as shown in FIG. Since the magnitude of the voltage changes, the induced voltage constant Ke is changed by changing the state of the electric motor 10 between the strong field state and the weak field state.

  This induced voltage constant Ke is the ratio of the number of revolutions of the induced voltage induced at the winding end of the stator winding 13a due to the rotation of the rotors 11 and 12, for example. The product of R, motor product thickness L, magnetic flux density B, and number of turns T can be described as Ke = 8 × p × R × L × B × T × π. Thereby, the field of the permanent magnet 11a of the inner peripheral side rotor 11 and the permanent magnet 12a of the outer peripheral side rotor 12 is changed by changing the state of the electric motor 10 between the strong field state and the weak field state. The magnitude of the magnetic flux density B of the magnetic flux changes, and the induced voltage constant Ke is changed.

Here, for example, as shown in FIG. 7A, the torque of the electric motor 10 is proportional to the product of the induced voltage constant Ke and the current passed through the stator winding 13a (torque ∝ (Ke × current)).
For example, as shown in FIG. 7B, the field weakening loss of the electric motor 10 is proportional to the product of the induced voltage constant Ke and the rotational speed (field weakening loss ∝ (Ke × rotational speed)). The allowable rotational speed of the electric motor 10 is proportional to the inverse of the product of the induced voltage constant Ke and the rotational speed (allowable rotational speed ∝ (1 / (Ke × rotational speed)).

That is, for example, as shown in FIG. 8, in the electric motor 10 having a relatively large induced voltage constant Ke, the operable rotational speed is relatively reduced, but a relatively large torque can be output. In the electric motor 10 having a relatively small constant Ke, the outputable torque is relatively reduced, but the motor 10 can be operated up to a relatively high rotational speed, and the operable range for the torque and the rotational speed depends on the induced voltage constant Ke. Change.
For this reason, as in the embodiment shown in FIG. 9A, for example, the induced voltage constant Ke changes in a decreasing trend as the rotational speed of the electric motor 10 increases (for example, A, B (<A), By setting so as to change to C (<change to B), the operable range for the torque and the rotational speed is expanded as compared with the case where the induced voltage constant Ke is not changed (for example, the first to third comparative examples). To do.

  The output of the electric motor 10 is proportional to the value obtained by subtracting the field weakening loss and other losses from the product of the induced voltage constant Ke and the current passed through the stator winding 13a and the rotational speed (output ∝ (Ke x current x rotational speed-field weakening loss-other loss). That is, for example, as shown in FIG. 9B, in the electric motor 10 having a relatively large induced voltage constant Ke, the operable speed is relatively reduced, but the output in the relatively low speed range is high. On the other hand, in the electric motor 10 in which the induced voltage constant Ke is relatively small, although the output in the relatively low rotational speed region is reduced, the motor 10 can be operated up to a relatively high rotational speed and has a relatively high rotational speed. The output in number increases, and the operable range for the output and the rotational speed changes according to the induced voltage constant Ke. For this reason, it is set so that the induced voltage constant Ke changes in a decreasing tendency (for example, changes to A, B (<A), C (<B) sequentially) as the rotational speed of the electric motor 10 increases. As a result, compared with the case where the induced voltage constant Ke is not changed (for example, the first to third comparative examples), the operable range for the output and the rotational speed is expanded.

The efficiency of the motor 10 is proportional to the value obtained by dividing the input power to the stator winding 13a by subtracting the copper loss, field weakening loss and other losses by the input power (efficiency ∝ ((Input power-copper loss-field weakening loss-other losses) / input power)).
For this reason, in the relatively low speed range to the medium speed range, by selecting a relatively large induced voltage constant Ke, the current required to output the desired torque is reduced, and the copper Loss is reduced.

In the relatively high rotational speed region from the medium rotational speed region, by selecting a relatively small induced voltage constant Ke, the field weakening current is reduced and the field weakening loss is reduced.
Accordingly, for example, as in the embodiment shown in FIG. 10A, the induced voltage constant Ke is set so that the induced voltage constant Ke changes in a decreasing tendency as the rotational speed of the electric motor 10 increases. Compared to the case where the change is not made (for example, the second comparative example shown in FIG. 10B), the rotation speed and the operable range for the rotation speed are expanded, and the efficiency of the electric motor 10 is equal to or higher than a predetermined efficiency. And the maximum achievable value increases.

  As described above, according to the present embodiment, first, the permanent magnet 11a and the permanent magnet 12a are arranged in the circumferential direction on the inner circumferential rotor 11 and the outer circumferential rotor 12, for example, on the outer circumferential side. It is possible to efficiently increase or decrease the amount of interlinkage magnetic flux in which the field magnetic flux generated by the permanent magnet 12a of the rotor 12 links the stator winding 13a by the field magnetic flux generated by the permanent magnet 11a of the inner circumferential rotor 11. it can. In the field-enhanced state, the torque constant (that is, torque / phase current) of the electric motor 10 can be set to a relatively high value without reducing the current loss during motor operation or fixed. The maximum torque value output from the electric motor 10 can be increased without changing the maximum value of the output current of the inverter that controls the energization of the child winding 13a.

  Moreover, the rotation mechanism 14 is rotated on the inner peripheral side by the vane rotor 32 provided so as to be integrally rotatable with respect to the outer peripheral rotor 12 and the housing 33 provided so as to be integrally rotatable with respect to the inner peripheral rotor 11. The first and second pressure chambers 56,... 56 and the second pressure chambers 57,. Therefore, the induced voltage constant can be made variable easily and appropriately at a desired timing while suppressing the complication of the electric motor 10. As a result, it is possible to expand the operable rotation speed range and torque range, improve the operation efficiency, and expand the operable range with high efficiency.

Further, by controlling the amount of hydraulic oil supplied to the first pressure chambers 56,..., And the second pressure chambers 57,. The phase can be changed steplessly within an electric angle of 180 ° between the field weakening state and the field strengthening state.
In addition, the vane rotor 32 and the housing 33 define the first pressure chambers 56,..., 56 and the second pressure chambers 57,. The increase in thickness can be suppressed and downsizing can be achieved.

  Specifically, the second pressure chamber is supplied to the first pressure chambers 56, ..., 56 defined by the vane portions 36, ..., 36 of the vane rotor 32 and the recesses 48, ..., 48 of the housing 33 while supplying hydraulic oil. When the hydraulic oil is discharged from 57,..., 57, the relative phase between the housing 33 and the vane rotor 32 is changed in the direction in which the first pressure chambers 56,. The relative phase between the inner peripheral rotor 11 provided integrally with the outer side of the housing 33 and the outer peripheral rotor 12 provided integrally with the vane rotor 32 is changed, and the field weakening state It becomes. On the other hand, when the hydraulic oil is discharged from the first pressure chambers 56,..., While supplying the hydraulic oil to the second pressure chambers 57,... 57, the second pressure chambers 57,. In the direction, the relative phase between the housing 33 and the vane rotor 32 is changed, and as a result, the relative phase between the inner circumferential rotor 11 and the outer circumferential rotor 12 is changed. It becomes a strong field state. As described above, since a simple vane actuator mechanism having the vane rotor 32 and the housing 33 is used as the rotation mechanism 14, it is easily and appropriately induced at a desired timing while reliably suppressing the complication of the electric motor 10. The voltage constant can be made variable.

  In addition, the vane rotor 32 is provided integrally with the outer rotor 12 via drive plates 31 and 31 fixed to the outer rotor 12 so as to cover the end face in the axial direction. Since the output shaft 16 that outputs the driving force is also provided integrally, the rotation of the outer peripheral rotor 12 can be directly connected to the output shaft 16, while the first pressure chambers 56,. The pressure of the hydraulic oil introduced into the two pressure chambers 57,... 57 is a relative phase between the housing 33 and the vane rotor 32 integrally provided inside the inner circumferential rotor 11, that is, the inner circumferential side. It is mainly used for changing the relative phase between the rotor 11 and the outer rotor 12. Therefore, the pressure that needs to be generated with the hydraulic oil can be kept low.

  Further, since the hydraulic oil is supplied to and discharged from the first pressure chambers 56,..., 56 and the second pressure chambers 57,. The increase in height can be suppressed.

  In addition, in the present embodiment, when the outer peripheral side rotor 12 and the inner peripheral side rotor 11 are rotated, the first pressure chamber is caused by centrifugal force from all the through holes 33b,. 56,..., Or the hydraulic oil in the second pressure chambers 57,..., 57 moves to the outer peripheral side by a small amount together with impurities (contamination) contained therein, and the inner peripheral rotor 11 and the housing 33 It is discharged through a spiral flow path 51 therebetween. Thereby, accumulation of impurities contained in hydraulic oil on the bottom wall surface 48a of the recesses 48,..., 48 forming the first pressure chamber 56 and the second pressure chamber 57 can be suppressed. Moreover, since the through holes 33b communicating with the flow path 51 are formed in all the first pressure chambers 56,..., 56 or all the second pressure chambers 57,. Deposition can be suppressed. Further, the hydraulic oil discharged from the first pressure chambers 56,..., 56 or the second pressure chambers 57,... 57 is discharged through the flow path 51 between the inner peripheral rotor 11 and the housing 33. Therefore, the inner peripheral side rotor 11 and the housing 33 can be cooled.

  Here, since the flow path 51 has a spiral shape extending in the circumferential direction, when the outer circumferential rotor 12 and the inner circumferential rotor 11 rotate, all the first pressure chambers 56,. Alternatively, the hydraulic oil is sucked out from the through holes 33b communicating with all the second pressure chambers 57,..., 57 and discharged from the end face 33B corresponding to the rotation direction of the housing 33 of the inner circumferential rotor 11. In this way, the spiral flow path 51 functions as a screw pump, and the hydraulic oil is sucked out and discharged from the first pressure chambers 56,..., 56 or the second pressure chambers 57,. It can be effectively suppressed. Further, since the hydraulic oil is discharged through the spiral flow path 51 between the inner circumferential rotor 11 and the housing 33, the entire inner circumferential rotor 11 and the housing 33 are cooled on average. Can do. Furthermore, the hydraulic fluid discharged from the end surface 33B of the housing 33 of the inner circumferential rotor 11 is a gap 59 between the inner circumferential rotor 11 and each of the drive plates 31, 31, and the inner circumferential rotor 11 and the outer circumferential side. It will pass the gap 60 with the rotor 12, and the outer peripheral side rotor 12 is also cooled. In addition, the hydraulic oil is discharged to the outside through a gap between the pair of drive plates 31 and 31 and the outer rotor 12 by centrifugal force, and is applied mainly to the stator winding 13a of the stator 13. The stator 13 is also cooled.

  Further, since the flow path 51 has a spiral shape extending in the circumferential direction, it becomes a screw orifice so that air can be vented well at the time of dry start, for example, and the first pressure chambers 56,. The pressure chambers 57,..., 57 can be immediately filled with the hydraulic oil, and the discharge flow rate of the hydraulic oil can be suppressed to a minimum discharge flow rate that is necessary for discharging impurities and does not affect the operation.

If there is no need to function as a screw pump, the flow path 51 may be a plurality of flow paths that extend along the axial direction and communicate with the through holes 33b,.
In addition, the rotation mechanism 14 is integrally fixed to the inner side of the inner peripheral side rotor 11 with the first member provided so as to be integrally rotatable with respect to the outer peripheral side rotor 12, and the first member is a pressure chamber. And a second member that defines the inside of the inner circumferential rotor 11, and at least one of the inner circumferential rotor 11 and the outer circumferential rotor 12 is rotated by the supply of the working fluid to the pressure chamber. What is necessary is just to be able to change the relative phase between the inner periphery side rotor 11 and the outer periphery side rotor 12 by rotating around. For example, a ring gear serving as a first member that is coupled by a helical spline is provided inside a second member that is integrally fixed to the inside of the inner circumferential rotor 11, and the ring gear is axially supplied by supplying hydraulic oil to the pressure chamber. The present invention can also be applied to those in which the inner circumferential rotor 11 is rotated relative to the outer circumferential rotor 12 by sliding in the direction and twisting of the helical spline.

It is principal part sectional drawing which shows the electric motor which concerns on one Embodiment of this invention. It is a front view which abbreviate | omitted the near drive plate which shows the field-weakening state of the inner peripheral side rotor of an electric motor which concerns on one Embodiment of this invention, an outer peripheral side rotor, and a rotation mechanism. It is a disassembled perspective view which shows the inner peripheral side rotor of an electric motor which concerns on one Embodiment of this invention, an outer peripheral side rotor, and a rotation mechanism. It is a front view which abbreviate | omitted the near drive plate which shows the strong field state of the inner peripheral side rotor of an electric motor which concerns on one Embodiment of this invention, an outer peripheral side rotor, and a rotation mechanism. FIG. 5A is a diagram schematically showing a strong field state in which the permanent magnets of the inner circumferential rotor and the permanent magnets of the outer circumferential rotor are arranged in the same polarity, and FIG. It is a figure which shows typically the field-weakening state by which the permanent magnet of the side rotor and the permanent magnet of the outer peripheral side rotor were arrange | positioned with a counter electrode. It is a graph which shows the induced voltage in the strong field state and weak field state shown in FIG. FIG. 7A is a graph showing the relationship between the current and torque of the motor that changes according to the induced voltage constant Ke, and FIG. 7B shows the rotation speed of the motor that changes according to the induced voltage constant Ke. It is a graph which shows the relationship with a field weakening loss. It is a figure which shows the driving | operation possible area | region with respect to the rotation speed and torque of an electric motor which change according to the induced voltage constant Ke. FIG. 9A is a graph showing the relationship between the rotational speed and torque of the motor that changes according to the induced voltage constant Ke, and FIG. 9B shows the rotational speed of the motor that changes according to the induced voltage constant Ke. It is a graph which shows the relationship between output. FIG. 10 (a) is a diagram showing an operable region and efficiency distribution with respect to the rotational speed and torque of the motor that change in accordance with the induced voltage constant Ke in the embodiment, and FIG. 10 (b) shows the distribution in the second comparative example. It is a figure which shows the driveable area | region and efficiency distribution with respect to the rotation speed and torque of an electric motor which change according to the induced voltage constant Ke.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Electric motor 11 Inner peripheral side rotor 11a Inner peripheral side permanent magnet 12 Outer peripheral side rotor 12a Outer peripheral side permanent magnet 14 Rotation mechanism (rotation means)
32 Vane rotor (first member)
33 Housing (second member)
33b Through-hole 33B End face 36 Blade part 48 Recessed part 51 Flow path 56 First pressure chamber (pressure chamber)
57 Second pressure chamber (pressure chamber)

Claims (3)

The rotation axes of the inner circumferential rotor having the inner circumferential permanent magnet arranged along the circumferential direction and the outer circumferential rotor having the outer circumferential permanent magnet arranged along the circumferential direction are coaxially arranged. The relative phase between the inner circumferential rotor and the outer circumferential rotor by rotating at least one of the inner circumferential rotor and the outer circumferential rotor about the rotation axis. An electric motor provided with rotating means capable of changing
The rotating means is integrally fixed to the inner side of the inner peripheral side rotor and a first chamber provided so as to rotate integrally with the outer peripheral side rotor, and the first member forms a pressure chamber. A second member defined inside the inner circumferential rotor, and a relative phase between the inner circumferential rotor and the outer circumferential rotor by supplying a working fluid to the pressure chamber. Is to change
A through hole penetrating from the pressure chamber to the outer peripheral side of the second member is formed in the second member ,
A flow path communicating with the through hole is formed between the inner peripheral rotor and the second member so as to extend along an outer peripheral surface of the second member, and an end of the flow path is An electric motor having an opening at an end face of an inner circumferential rotor . The first member is a vane rotor that is disposed inside the inner circumferential rotor and has a plurality of blade portions and is provided integrally with the outer circumferential rotor,
The second member has a plurality of recesses that respectively define the pressure chambers with the vane portion while rotatably accommodating the vane portion of the vane rotor, and is integrated with the inner peripheral rotor. A housing provided in
The electric motor according to claim 1, wherein the through hole communicating with the flow path is formed for each of the plurality of pressure chambers. The flow path forms a spiral shape extending in the circumferential direction, the electric motor according to claim 2, characterized in communicating Tei Rukoto a plurality of the pressure chamber the through holes formed, respectively.

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