JP5031351B2 - Electric motor - Google Patents

Description

  The present invention relates to an electric motor having a permanent magnet in a rotor, and more particularly to an electric motor capable of changing the field characteristics of a permanent magnet of a rotor.

  As an electric motor, an inner circumferential rotor and an outer circumferential rotor each having a permanent magnet are arranged coaxially, and both rotors are rotated relative to each other in the circumferential direction (relative to both rotors). It is known that the field characteristics of the entire rotor can be changed by changing the phase) (see, for example, Patent Document 1).

  In this electric motor, when the relative phase of both rotors is changed according to the rotational speed of the electric motor, the outer rotor and the inner rotor are rotated by a member that is displaced along the radial direction by the action of centrifugal force. Either one of the children is rotated in the circumferential direction with respect to the other. In addition, when the relative phase of both rotors is changed by the rotating magnetic field generated in the stator, each rotor is rotated by passing a control current to the stator winding while maintaining the rotation speed due to inertia. By changing the magnetic field velocity, one of the outer peripheral side rotor and the inner peripheral side rotor is rotated in the circumferential direction with respect to the other.

  In this electric motor, the permanent magnets of the outer and inner rotors are opposed to each other with different polarities (with the same polarity arrangement), thereby strengthening the field of the entire rotor and increasing the induced voltage constant. Conversely, the permanent magnets of the outer and inner rotors are opposed to each other with the same polarity (with a counter electrode arrangement), thereby weakening the field of the entire rotor and reducing the induced voltage constant. .

  Also known is a valve timing control device that changes the relative phase of a crankshaft of an internal combustion engine and a camshaft driven by the crankshaft by hydraulic pressure (see, for example, Patent Document 2).

In this valve timing control device, a hydraulic phase changing mechanism is incorporated in a chain sprocket that transmits power from the crankshaft to the camshaft, and the cam sprocket is attached to the camshaft by operating the phase changing mechanism with hydraulic pressure. Is to be changed arbitrarily. In this case, the hydraulic fluid is supplied to and discharged from the phase change mechanism through the camshaft, but the hydraulic fluid is appropriately supplied to the advance side working chamber and the retard side working chamber in the phase change mechanism. Two systems of supply and discharge passages on the advance side and the retard side are formed in relation to the exhaust.
JP 2002-204541 A Japanese Patent Laid-Open No. 9-60508

  In the case of the conventional motor, the conditions for changing the relative phase between the outer rotor and the inner rotor are limited, and the relative phase cannot be freely changed when the motor is stopped or at any rotation. . In particular, when used for driving a hybrid vehicle or an electric vehicle, it is desired to instantaneously change to a desired motor characteristic according to the driving situation of the vehicle. It is important to increase the degree of freedom. For this reason, the present applicant has conceived of incorporating phase changing means using a working fluid, and is currently studying efficient supply / discharge control of the working fluid.

  Specifically, the phase changing means includes an advance side working chamber for rotating the inner side rotor relative to the outer side rotor in the advance direction, and the inner side rotor as the outer side rotor. On the other hand, a retarding-side working chamber that is relatively rotated in the retarding direction is provided, and it is considered to supply and discharge the working fluid to and from these working chambers through the output shaft of the motor.

  In this case, as in the valve timing control device, there are two systems of supply and discharge passages on the advance side and retard side in the output shaft. In the valve timing control device, on the advance side The axial path of the supply / discharge passage and the axial path of the retarding side supply / discharge passage are provided in parallel along the camshaft, and the radial path of each supply / discharge passage is asymmetric with respect to the axis of the camshaft. Therefore, if this technology is applied as it is to the phase changing means of the electric motor, the rotation of the output shaft of the electric motor becomes unbalanced. As a result, an increase in load acting on the bearing supporting the output shaft is increased. There is a concern that vibration, noise, fluid controllability, etc. may be reduced. In particular, when this type of electric motor is used for driving a hybrid vehicle or an electric vehicle, the above-mentioned tendency is expected to be promoted because the use rotation range becomes high.

  Therefore, the present invention allows the relative phase between the outer rotor and the inner rotor to be arbitrarily changed using the working fluid without causing an imbalance in the rotation of the output shaft. An object of the present invention is to provide an electric motor capable of simultaneously improving the degree of freedom and improving durability, quietness and control stability.

According to the first aspect of the present invention, an inner peripheral rotor in which a permanent magnet is disposed along the circumferential direction, and an outer peripheral side of the inner peripheral rotor are coaxially and relatively rotatable. At the same time, the outer peripheral rotor on which the permanent magnets are arranged along the circumferential direction, and the inner peripheral rotor and the outer peripheral rotor are relatively rotated to change the relative phase between them. An electric motor comprising: a phase changing unit; and an output shaft that is integrally coupled to the outer peripheral side rotor or the inner peripheral side rotor and is supported by a bearing to rotate, wherein the phase changing unit is introduced inside An advancing-side working chamber for rotating the inner-side rotor relative to the outer-side rotor in an advancing direction by the pressure of the working fluid, and the inner-side rotor by the pressure of the working fluid introduced therein A retard-side working chamber that rotates relative to the outer circumferential rotor in the retard direction, and The force shaft is provided with an advance side supply / discharge passage and a retard side supply / discharge passage for supplying / discharging working fluid to and from the advance side working chamber and the retard side working chamber. Of the advance side axial path extending along the axial direction of the output shaft (for example, the advance side axial path 26a in the embodiment described later) and the retard side supply / exhaust path. A retard side axial path extending along the axial direction of the output shaft (for example, a retard side axial path 27a in an embodiment described later) extends concentrically from opposite ends of the output shaft in the axial direction. It is provided.
As a result, when the working fluid is supplied to one of the advance side supply / discharge passage and the retard side supply / discharge passage, and the working fluid is discharged from the other side, the inner circumferential rotor advances to the outer circumferential rotor. Rotate to one of the side and the retard side. Thus, while the control by the phase changing means is performed, the working fluid flows through the advance side axial path and the retard side axial path, but both the axial paths are provided concentrically on the output shaft. Therefore, the working fluid in both axial paths balances during rotation of the output shaft.

According to the second aspect of the present invention, an inner peripheral rotor in which a permanent magnet is disposed along the circumferential direction, and an outer peripheral side of the inner peripheral rotor are coaxially and relatively rotatable. At the same time, the outer peripheral rotor on which the permanent magnets are arranged along the circumferential direction, and the inner peripheral rotor and the outer peripheral rotor are relatively rotated to change the relative phase between them. An electric motor comprising: a phase changing unit; and an output shaft that is integrally coupled to the outer peripheral side rotor or the inner peripheral side rotor and is supported by a bearing to rotate, wherein the phase changing unit is introduced inside An advancing-side working chamber for rotating the inner-side rotor relative to the outer-side rotor in an advancing direction by the pressure of the working fluid, and the inner-side rotor by the pressure of the working fluid introduced therein A retard-side working chamber that rotates relative to the outer circumferential rotor in the retard direction, and The force shaft is provided with an advance side supply / discharge passage and a retard side supply / discharge passage for supplying / discharging working fluid to and from the advance side working chamber and the retard side working chamber, and the output shaft along the axial center portion. Thus, a base hole (for example, a base hole 303 in an embodiment described later) is formed, and a hollow pipe (for example, described later) that divides the base hole into an inner axial passage and an outer cylindrical passage in the base hole. In the embodiment, the hollow pipe 308) is coaxially installed, and the advance side axial path (e.g., an embodiment described later) of the advance side supply / discharge passage extends along the axial direction of the output shaft. Is formed on one side of the axial passage and the cylindrical passage, and extends along the axial direction of the output shaft of the retard-side supply / discharge passage. Retarded side axial path (for example, retarded side axial path 27a in an embodiment described later) But characterized in that it is configured on the other side of the axis passage and cylindrical passage.
Thus, when the inner peripheral side rotor is rotated by one relative to the outer peripheral side rotor by the phase changing means, one of the cylindrical passage between the base hole and the pipe and the axial passage in the pipe. Is supplied from the working fluid and discharged from the other. While the control by the phase changing means is performed in this way, the working fluid flows through the cylindrical passage and the axial passage, but both axial passages are provided concentrically inside and outside the pipe on the output shaft. The working fluid in both passages is balanced during the rotation of the output shaft.

According to a third aspect of the present invention, in the electric motor according to the first or second aspect , an advance side radial path extending substantially along a radial direction of the output shaft in the advance side supply / discharge passage. (E.g., a radial hole 205 in an embodiment described later) and a retarded-side radial path (e.g., described later) extending substantially along the radial direction of the output shaft of the retarded-side supply / discharge passage. The radial path 206) in the embodiment is arranged to be rotationally symmetric around the axis when projected onto a plane orthogonal to the axis of the output shaft.
As a result, the working fluid in both radial paths is balanced during the rotation of the output shaft.

According to a fourth aspect of the present invention, in the electric motor according to the second aspect , the end portion of the cylindrical passage is a seal member interposed between the pipe and the base hole (for example, a seal member 209 in an embodiment described later). ).
Thereby, the leakage of the working fluid from between the pipe and the base hole is suppressed by the seal member.

According to a fifth aspect of the present invention, in the electric motor according to the second or fourth aspect , the pipe has an annular protrusion (for example, described later) that forms a restriction with the base hole in the vicinity of the end of the cylindrical passage. An annular protrusion 321) in the embodiment is formed.
Thereby, the annular protrusion on the pipe hole functions as a throttle in the vicinity of the end of the cylindrical passage, and the surge pressure acting on the end of the cylindrical passage is suppressed.

A sixth aspect of the present invention is the electric motor according to any one of the second to fifth aspects, wherein a hollow first pipe (for example, an intermediate hollow pipe 414 in an embodiment described later) is provided inside the base hole. Is disposed coaxially, and a further hollow second pipe (for example, a hollow pipe 408 in an embodiment described later) is disposed coaxially within the first pipe, and is disposed between the base hole and the first pipe. One of the advance side axial path and the retard side axial path is configured by the formed cylindrical passage, and the advance side is formed by the axial passage formed inside the second pipe. One of the axial path and the retarded-side axial path is configured, and a lubricating liquid supply path (for example, in an embodiment described later) is formed by an intermediate cylindrical path formed between the first pipe and the second pipe. Jun Wherein the fluid passage 441) is formed.
Thus, when the inner peripheral side rotor is rotated in one direction with respect to the outer peripheral side rotor by the phase changing means, the cylindrical passage between the base hole and the first pipe, and the axial center passage inside the second pipe. Is supplied from one side and discharged from the other. Further, the cylindrical passage that is the control pressure passage and the axial passage are separated by the lubricating liquid passage between the first pipe and the second pipe.

According to a seventh aspect of the present invention, in the electric motor according to any one of the first to sixth aspects, distribution of supply and discharge of the working fluid to the advance side working chamber and the retard side working chamber according to a spool position. The pressure of the working fluid supplied from a fluid supply source (for example, an oil pump 32 in an embodiment described later) is provided. And an electromagnetic pressure regulating valve (for example, a pressure regulating valve 39 in an embodiment described later) that controls the spool position of the flow path switching valve by the pressure of the regulated working fluid is provided. To do.
Thus, when the electromagnetic pressure regulating valve is operated, the pressure of the working fluid acting on the spool of the flow path switching valve from the fluid supply source is adjusted. Thus the pressure of the working fluid acting on spool is adjusted, the spool position is controlled in accordance with the pressure, distribution of the working fluid that is supplied to and discharged from the advance angle side operating chamber and the retard angle side operating chamber is carried out .

According to the first aspect of the present invention, the phase changing means can be quickly controlled by the working fluid at an arbitrary timing, and the advance side axial direction path and the retard side axial direction path are connected to the axis of the output shaft. Since it extends concentrically from the opposite ends of the direction, the rotation balance of the output shaft can be improved, and the durability of the bearing portion can be improved, and the quietness and control stability can be improved. In the present invention, since the advance side axial path and the retard side axial path extend from opposite ends of the output shaft in the axial direction, the operation between the advance side and the retard side passages is performed. Fluid leakage can be reliably prevented, and control can be further stabilized.

According to the second aspect of the present invention, the phase changing means can be quickly controlled by the working fluid at an arbitrary timing, and a hollow pipe is arranged in the base hole of the output shaft so that the shaft can be inserted into and out of the pipe. Because the central passage and the cylindrical passage are formed, one of the axial passage and the cylindrical passage arranged concentrically, and the other is the advance side axial passage and the other is the retard side axial passage. Thus, it is possible to improve the rotation balance of the output shaft, improve the durability of the bearing portion, and improve the silence and control stability. In addition, the present invention has an advantage that a compact layout is possible because the advance side axial path and the retard side axial path can be concentrated on one side in the axial direction of the output shaft.

According to the third aspect of the present invention, when the advance side radial path and the retard side radial path are projected onto a plane orthogonal to the axis of the output shaft, the rotational symmetry is made about the axis. Therefore, in the invention described in claim 1 or 2 , the rotational balance can be further improved.

According to the fourth aspect of the present invention, since the seal member that suppresses leakage of the working fluid is interposed between the pipe and the base hole, the advance side axial path and the retard side axial path are arranged concentrically. The structure can be easily and compactly formed.

According to the fifth aspect of the present invention, the annular protrusion is formed in the vicinity of the end portion of the cylindrical passage among the pipes arranged in the base hole, and the restriction is configured between the base hole and the annular protrusion. Therefore, the surge pressure can be effectively suppressed by adding simple processing.

According to the sixth aspect of the present invention, the first pipe is disposed in the base hole, the second pipe is further disposed in the first pipe, and the outer peripheral side of the first pipe and the inner peripheral side of the second pipe. Since one of the advance side axial path and the retard side axial path is formed at the same time, and the lubricating liquid passage is formed between the first pipe and the second pipe, the phase changing means Can be quickly controlled by the working fluid at any timing, and the rotation balance of the output shaft can be improved to improve the durability of the bearing section and improve the quietness and control stability. Liquid leakage between the advance side axial path and the retard side axial path can be effectively prevented.

According to the seventh aspect of the present invention, the pressure of the working fluid is regulated by the electromagnetic pressure regulating valve, and the spool position of the flow path switching valve is controlled by the pressure of the regulated working fluid. A large flow rate of working fluid can be supplied to the phase changing means without using a valve.

  Embodiments of the present invention will be described below with reference to the drawings. First, the first embodiment shown in FIGS. 1 to 15 will be described.

FIG. 1 is a schematic configuration diagram of a power transmission system of a hybrid vehicle using an electric motor 1 according to the present invention.
In this hybrid vehicle, the engine 170 and the electric motor 1 are used as power sources, and the driving forces of these power sources are selectively selected or used together and transmitted to the drive wheels 171.

  A crankshaft 170a of the engine 170 is directly connected to a rotor shaft 173a of a generator 173 that also serves as a cell motor via a flywheel 172, and the rotor shaft 173a is a clutch for transmitting the driving force of the engine 170 to the drive wheels 171 side. 174. An engine output gear 176 is provided at the end of the driven engine output shaft 175 connected to the clutch 174, and this engine output gear 176 is meshed with an idle gear 178 provided on one end side of the idle shaft 177. Yes. A pinion gear 179 is provided on the other end side of the idle shaft 177, and the pinion gear 179 is connected to a differential device 180 that distributes power to the left and right drive wheels 171 and 171. The driving force of the engine 170 is transmitted to the driving wheels 171 and 171 through the above path.

  On the other hand, the electric motor 1 is supplied with electric power from the battery 181 or the generator 173 via a power drive unit 182 (hereinafter referred to as “PDU 182”), and rotates the output shaft 4 according to the supplied electric power. The output shaft 4 is provided with a motor gear 183, and the motor gear 183 is meshed with an idle gear 178 at one end of the idle shaft 177. The driving force of the electric motor 1 is transmitted to the left and right driving wheels 171 and 171 through the idle shaft 177 and the differential device 180.

  The PDU 182 interposed between the electric motor 1 and the generator 173 and the battery 181 is controlled by the hybrid ECU 184, and the output characteristics of the engine 170 are controlled by the engine ECU 185. In the hybrid ECU 184, an ignition switch 186, a shift position sensor 187, an accelerator pedal sensor 188, a brake pedal sensor 189, a vehicle speed sensor 190, and the like are connected to an input unit, input signals from these sensors, and various inputs from the battery 181. The PDU 182 and the operation actuator 174a of the clutch 174 are appropriately controlled in accordance with signals (signals such as voltage, current, and temperature). The hybrid ECU 184 and the engine ECU 185 are connected by a communication line, and various signals are exchanged between them.

  In this hybrid vehicle, the hybrid ECU 184 disconnects the clutch 174 and separates the engine power from the drive system during low vehicle speed traveling and when going uphill including when the vehicle starts, and also from the battery 181 via the PDU 182 to the electric motor 1. The power supplied to the vehicle is controlled, and the vehicle is driven by the driving force of the electric motor 1. If the remaining capacity of the battery 181 is reduced at this time, the engine ECU 184 starts the engine 170 while the clutch 174 is disengaged, and the electric motor 1 is driven by the electric power generated by the generator 173 (series operation). mode).

  Further, during steady running at medium and high vehicle speeds, the hybrid ECU 184 stops power supply to the electric motor 1 under the control of the PDU 182 and connects the clutch 174 with the engine 170 activated to drive the driving force of the engine 170. Transmission to the wheel 171 (engine drive cruise mode).

  Further, when the vehicle accelerates at medium and high vehicle speeds, the hybrid ECU 184 connects the clutch 174 to transmit the driving force of the engine 170 to the drive wheels 171 and simultaneously drives the motor 1 by the control of the PDU 182. Are also transmitted to the drive wheels 171 in parallel (parallel operation mode).

  The electric motor 1 is an inner rotor type brushless motor. As shown in FIG. 2, a rotor unit 3 is rotatably provided on an inner peripheral side of an annular stator 2 having a plurality of stator windings 2a. The output shaft 4 is integrally coupled to the axial center portion of the rotor unit 3.

  As shown in FIGS. 2 to 5, the rotor unit 3 includes an annular outer circumferential rotor 5 and an annular inner circumferential rotor 6 disposed coaxially inside the outer circumferential rotor 5. The outer peripheral side rotor 5 and the inner peripheral side rotor 6 are rotatable within a set angle range.

  The outer rotor 5 and the inner rotor 6 are formed by, for example, sintered rotor cores 7 and 8 made of sintered metal, and are biased toward the outer periphery of the rotor cores 7 and 8. A plurality of magnet mounting slots 7a, 8a are formed at equal intervals in the circumferential direction. In each of the magnet mounting slots 7a and 8a, two flat plate-like permanent magnets 9 and 9 magnetized in the thickness direction are mounted in parallel. Two permanent magnets 9, 9 mounted in the same magnet mounting slot 7a, 8a are magnetized in the same direction, and a pair of permanent magnets 9 mounted in each adjacent magnet mounting slot 7a, 7a and 8a, 8a. The magnetic poles are set so that the directions of the magnetic poles are opposite to each other. That is, in each of the rotors 5 and 6, a pair of permanent magnets 9 whose outer peripheral side is an N pole and a pair of permanent magnets 9 that are an S pole are alternately arranged in the circumferential direction. A notch 10 for controlling the flow of magnetic flux of the permanent magnet 9 is rotated between the adjacent magnet mounting slots 7a, 7a and 8a, 8a on the outer peripheral surfaces of the rotors 5, 6. It is formed along the axial direction of the children 5 and 6.

  The same number of magnet mounting slots 7a, 8a of the outer rotor 5 and inner rotor 6 are provided, and the permanent magnets 9 of the rotors 5, 6 correspond to each other on a one-to-one basis. Therefore, by making the pair of permanent magnets 9 in each of the magnet mounting slots 7a and 8a of the outer peripheral rotor 5 and the inner peripheral rotor 6 face each other with the same polarity (with different polar arrangement), the rotor unit 3 is able to obtain a field-weakening state (see FIGS. 4 and 7B) in which the entire field is weakened most, and the magnet mounting slots 7a of the outer circumferential rotor 5 and the inner circumferential rotor 6. , 8a, the pair of permanent magnets 9 are opposed to each other with different polarities (arranged with the same polarity), so that the field of the entire rotor unit 3 is strengthened most strongly (see FIGS. 3 and 7). (See (a)) can be obtained.

  The rotor unit 3 includes a rotation mechanism 11 for relatively rotating the outer peripheral rotor 5 and the inner peripheral rotor 6. The rotating mechanism 11 constitutes a part of phase changing means 12 for arbitrarily changing the relative phase of the two rotors 5 and 6, and is based on the pressure of the working fluid that is an incompressible working fluid. It is designed to be operated. The phase changing means 12 is composed mainly of the turning mechanism 11 and the hydraulic control device 13 shown in FIG. 9 for controlling the pressure of the hydraulic fluid supplied to the turning mechanism 11.

  As shown in FIGS. 2 to 5, the rotation mechanism 11 includes a vane rotor 14 that is spline-fitted to the outer periphery of the output shaft 4 and an annular housing that is relatively rotatable on the outer periphery side of the vane rotor 14. 15, and the annular housing 15 is integrally fitted and fixed to the inner peripheral surface of the inner peripheral rotor 6, and the vane rotor 14 is provided on both side end portions of the annular housing 15 and the inner peripheral rotor 6. Are integrally coupled to the outer circumferential rotor 5 via a pair of disk-shaped drive plates 16, 16 straddling each other. Therefore, the vane rotor 14 is integrated with the output shaft 4 and the outer peripheral rotor 5, and the annular housing 15 is integrated with the inner peripheral rotor 6.

  In the vane rotor 14, a plurality of vanes 18 projecting radially outward are provided at equal intervals in the circumferential direction on the outer periphery of a cylindrical boss portion 17 that is spline-fitted to the output shaft 4. On the other hand, the annular housing 15 is provided with a plurality of concave portions 19 on the inner peripheral surface at equal intervals in the circumferential direction, and the corresponding vanes 18 of the vane rotor 14 are accommodated in the concave portions 19. Each recess 19 is constituted by a bottom wall 20 having an arc surface that substantially matches the rotational trajectory of the tip of the vane 18 and a substantially triangular partition wall 21 that separates the adjacent recesses 19, 19. The vane 18 can be displaced between the one partition wall 21 and the other partition wall 21 during relative rotation of the annular housing 15. In the case of this embodiment, the partition wall 21 also functions as a stopper that restricts the relative rotation of the vane rotor 14 and the annular housing 15 by contacting the vane 18. A seal member 22 is provided along the axial direction at the tip of each vane 18 and the tip of the partition wall 21, and the vane 18, the bottom wall 20 of the recess 19, and the partition wall 21 are provided by these seal members 22. And the outer peripheral surface of the boss portion 17 are liquid-tightly sealed.

  In addition, cylindrical protrusions 15a are provided at both axial ends of the annular housing 15 as shown in FIG. The protrusion 15 a is slidably held in an annular guide groove 16 a formed in the drive plate 16, and the annular housing 15 and the inner peripheral rotor 6 are in a floating state on the outer peripheral rotor 5 and the output shaft 4. Has come to be supported.

  The drive plates 16 and 16 on both sides connecting the outer rotor 5 and the vane rotor 14 are slidably in close contact with both side surfaces (both end surfaces in the axial direction) of the annular housing 15, and the side of each recess 19 of the annular housing 15. Respectively. Therefore, each recessed part 19 forms the independent space part by the boss | hub part 17 of the vane rotor 14, and the drive plates 16 and 16 of both sides, and this space part is the introduction space 23 into which a hydraulic fluid is introduce | transduced. Each introduction space 23 is divided into two chambers by the corresponding vanes 18 of the vane rotor 14, and one room is an advance side working chamber 24 and the other room is a retard side working chamber 25. The advance side working chamber 24 rotates the inner circumferential side rotor 6 relative to the outer circumferential side rotor 5 in the advance direction by the pressure of the working fluid introduced inside, and the retard side working chamber 25 is The inner rotor 6 is rotated relative to the outer rotor 5 in the retard direction by the pressure of the working fluid introduced therein. In this case, “advance angle” means that the inner rotor 6 is advanced in the rotation direction of the electric motor 1 indicated by the arrow R in FIGS. 3 and 4 with respect to the outer rotor 5. “Angle” means that the inner rotor 6 is advanced to the opposite side of the rotation direction R of the electric motor 1 with respect to the outer rotor 5.

  Further, the supply and discharge of the hydraulic fluid to and from each of the advance side working chambers 24 and the retard side working chambers 25 is performed through the output shaft 4. That is, the advance side working chamber 24 is connected to the advance side supply / discharge passage 26 of the hydraulic control device 13 shown in FIG. 9, and the retard side operation chamber 25 is connected to the retard side supply / discharge passage 27 of the hydraulic control device 13. However, a part of the advance side supply / exhaust passage 26 and the retard side supply / exhaust passage 27 are respectively formed on the output shaft 4 along the axial direction as shown in FIG. An axial path 26a and a retard side axial path 27a are configured. And the edge part of each axial path 26a, 27a is connected to the annular groove 26b, 27b formed in the position offset in the axial direction of the outer peripheral surface of the output shaft 4, and each said annular groove 26b, 27b is a vane rotor. Are connected to a plurality of conduction holes 26c... 27c formed substantially along the radial direction in the 14 boss portions 17. Each conduction hole 26c of the advance side supply / discharge passage 26 connects the annular groove 26b and each advance side working chamber 24, and each conduction hole 27c of the retard side supply / exhaust passage 27 connects to the annular groove 27b and each retard side. The working chamber 25 is connected.

  The output shaft 4 will be described in more detail. The output shaft 4 penetrates the axial center portion of the vane rotor 14, and both end portions thereof are supported by the support blocks 202A and 202B on the vehicle body side via bearings 201A and 201B. Here, in the output shaft 4, the side having a long protruding length from the vane rotor 14 is referred to as “front side”, and the side having a short protruding length is referred to as “rear side”. The motor gear 183 is coupled to the part side by spline fitting, and the power of the motor 1 is output to the power transmission system (see FIG. 1) via the motor gear 183. Note that a portion of the output shaft 4 between the motor gear 183 and the vane rotor 14 is supported by a support block 202C on the vehicle body side via an intermediate bearing 201C.

  In addition, base holes 203 and 204 are formed in the shaft center portion of the output shaft 4 from the end face on the front side and the end face on the rear side, respectively, and the vicinity of the bottoms of the base holes 203 and 204 are respectively in the radial holes 205. , 206 communicates with the respective annular grooves 26b, 27b on the advance side and the retard side.

The front support block 202A is provided with an advance side supply / discharge port 207 connected to the hydraulic circuit of the hydraulic control device 13, and one end is connected to the advance side supply / discharge port 207 and the other end is connected to the output shaft. A metal hollow pipe 208 that is loosely inserted into the four base holes 203 is provided. An annular seal member 209 is attached to the outer periphery on the front end side of the hollow pipe 208, and the seal member 209 is in sliding contact with the inner peripheral surface of the base hole 203 so that the space between the hollow pipe 208 and the base hole 203 is sealed. It has become.
Similarly, the support block 202B on the rear side is provided with a retard side supply / discharge port 210 connected to the hydraulic circuit of the hydraulic control device 13, and one end is connected to the retard side supply / discharge port 210 and the other end is output. A metal hollow pipe 211 that is loosely inserted into the base hole 204 on the rear side of the shaft 4 is projected. An annular seal member 209 is also attached to the outer periphery on the tip side of the hollow pipe 211, and the space between the hollow pipe 211 and the base hole 204 is sealed by the seal member 209.
In this embodiment, the front side base hole 203 and the hollow pipe 208 of the output shaft 4 constitute the advance side axial path 26a, and the rear side base hole 204 and the hollow pipe 211 constitute the retard side axis. A direction path 27a is configured. Further, the advance side radial path and the retard side radial path are constituted by radial holes 205 and 206 of the output shaft 4, respectively.

Here, the two base holes 203 and 204 on the output shaft 4 are formed coaxially from the opposite direction of the output shaft 4 and have substantially the same diameter. A pair of radial holes 205 and 206 communicating with the respective front and rear base holes 203 and 204 are provided. When projected onto a plane perpendicular to the axis of the output shaft 4, these holes are arranged around the axis. Are arranged so as to be rotationally symmetric.
Specifically, as shown in FIG. 6, a pair of radial holes 205 and 206 communicating with the respective base holes 203 and 204 is formed so as to be straight in the radial direction across the base holes 203 and 204. However, pairs of radial holes 205, 205 and 206, 206 forming straight lines are arranged so as to be orthogonal to each other.

  Further, an outer hollow pipe 212 is provided on the front support block 202A so as to surround the outer periphery of the hollow pipe 208 on the base portion side with a predetermined gap. An annular seal member 209 is attached to the outer periphery on the front end side of the outer hollow pipe 212, and the seal member 209 is in sliding contact with the inner peripheral surface of the base hole 203. A cylindrical passage 220 formed between the hollow pipe 208 and the outer hollow pipe 212 connects the inflow port 213 provided in the support block 202A and the lubrication port 214 formed in the vicinity of the meshing portion of the motor gear 183, and flows in. The lubricating liquid introduced into the port 213 can be supplied to the meshing portion of the motor gear 183.

By the way, in the case of the electric motor 1 of this embodiment, when the inner circumferential rotor 6 is at the most retarded position with respect to the outer circumferential rotor 5, the permanent magnets of the outer circumferential rotor 5 and the inner circumferential rotor 6 are used. When 9 is opposed to different poles and is in a strong field state (see FIGS. 3 and 7A), the inner rotor 6 is at the most advanced angle position with respect to the outer rotor 5 Further, the permanent magnets 9 of the outer peripheral rotor 5 and the inner peripheral rotor 6 are set so as to face each other with the same poles and to have a field weakening state (see FIGS. 4 and 7B). .
The electric motor 1 can arbitrarily change the state of the strong field and the state of the weak field by controlling the supply and discharge of the hydraulic fluid to the advance side working chamber 24 and the retard side working chamber 25. Thus, when the strength of the magnetic field is changed, the induced voltage constant is changed accordingly, and as a result, the characteristics of the electric motor 1 are changed. That is, when the induced voltage constant increases due to the strong field, the allowable rotational speed at which the motor 1 can be operated decreases, but the maximum torque that can be output increases. Conversely, when the induced voltage constant decreases due to the weak field, Although the maximum torque that can be output from the electric motor 1 decreases, the allowable rotational speed at which the motor 1 can operate increases.

  Further, as shown in FIG. 9, the hydraulic control device 13 controls the oil pump 32 that sucks up and discharges the hydraulic fluid in the oil tank 31, and adjusts the hydraulic fluid discharged from the oil pump 32 to adjust the high-pressure line passage. The regulator valve 35 is introduced into the low pressure passage 34 for lubricating and cooling various devices, and the hydraulic fluid introduced into the line passage 33 is delayed with respect to the advance side supply / discharge passage 26. A spool-type flow path switching valve 37 for distributing unnecessary hydraulic fluid to the drain passage 36 in the advance side supply / discharge passage 26 and the retard side supply / discharge passage 27, and a line passage 33. And an electromagnetic pressure regulating valve 39 for regulating the position of the spool 38 of the flow path switching valve 37 by regulating the pressure introduced from

  As shown in FIG. 13, the regulator valve 35 is formed on a control spool 41 slidably accommodated in the valve accommodating chamber 40 and an inner peripheral surface of a substantially central portion of the valve accommodating chamber 40, and is connected to the pump side passage. 42, the annular supply port 43 that always communicates with the line passage 33, the annular discharge port 44 that is formed at a position adjacent to the supply port 43 of the valve housing chamber 40 and communicates with the low pressure passage 34, and the valve housing chamber 40 A spring 45 disposed on one end side (left side in the figure) and urging the control spool 41 toward the other end side (right side in the figure), and provided near the other end of the valve housing chamber 40 and spring 45 on the control spool 41 The spool control chamber 46 that applies the pressure of the line passage 33 in a direction against the force of the valve and the valve housing chamber 40 in which the spring 45 is housed are provided at one end side to introduce an adjustment pressure described later. It includes a reaction force adjusting chamber 47, the being.

The control spool 41 is formed with an annular discharge guide groove 48 having a groove width spanning the supply port 43 and the discharge port 44 on the valve accommodating chamber 40 side in the substantially axial center of the outer peripheral surface, and is supplied through the discharge guide groove 48. Excess hydraulic fluid can be discharged from the port 43 to the discharge port 44 (low pressure passage 34). In the initial state where the pressure of the line passage 33 is low, the control spool 41 receives the urging force of the spring 45 and moves to the other end side (right side in the drawing) of the valve housing chamber 40, and the discharge guide groove 48 is connected to the supply port 43. And the communication between the discharge port 44 is blocked. When the control spool 41 moves to one end side (left side in the figure) against the force of the spring 45 from this state, the discharge guide groove 48 is supplied according to the amount of movement (according to the position of the control spool 41). The opening area for communicating the port 43 and the discharge port 44 is increased. The position of the control spool 41 is basically controlled by the balance between the pressure of the line passage 33 introduced into the spool control chamber 46 and the reaction force of the spring 45, and the pressure of the line passage 33 is controlled according to the movement position. To do. However, since an adjustment pressure, which will be described later, is appropriately introduced into the reaction force adjustment chamber 47 according to the operating state of the electric motor 1, the reaction force of the spring 45 is applied when a pressure higher than atmospheric pressure is introduced into the reaction force adjustment chamber 47. The reaction force due to the adjustment pressure is added to.
9 and 13, reference numeral 49 denotes an atmospheric pressure port provided at the other end of the spool housing chamber 46.

  On the other hand, as shown in FIGS. 10 and 12, the flow path switching valve 37 and the spool 38 slidably accommodated in the valve accommodating chamber 50 and the two positions separated in the axial direction of the valve accommodating chamber 50. Positions adjacent to the first introduction port 52 between the first and second introduction ports 52, 53 of the annular shape and the annular first and second introduction ports 52, 53 formed and respectively conducted to the line passage 33. Adjacent to the annular advance angle supply / discharge port 54 formed in the connection with the advance angle supply / discharge passage 26 and between the first and second introduction ports 52, 53 of the valve storage chamber 50. At an intermediate position between the annular retard side supply / exhaust port 55 formed in the position and conducting to the retard side supply / exhaust passage 25, and the advance side supply / exhaust port 54 and the retard side supply / exhaust port 55 of the valve storage chamber 50. An annular discharge port 57 formed and connected to the drain passage 36; A spring 58 disposed on one end side (right side in the figure) of the valve housing chamber 50 and biasing the spool 38 toward the other end side (left side in the figure), and provided on the other end portion of the valve housing chamber 50 And a control chamber 59 for applying a spool control pressure to the end face.

  The spool 38 has an annular first guide groove 60 having a groove width spanning the first introduction port 52 and the advance side supply / exhaust port 54 and a second introduction at two spaced apart positions in the vicinity of the substantially axial center of the outer peripheral surface. An annular second guide groove 61 having a groove width extending over the port 53 and the retard side supply / discharge port 55 is formed. The separation width between the first introduction port 52 and the advance side supply / discharge port 54 and the separation width between the advance side supply / discharge port 54 and the discharge port 57 are substantially the same. The separation width of the retard side supply / discharge port 55 and the separation width of the retardation side supply / discharge port 55 and the discharge port 57 are also substantially the same. In the spool 38, the first guide groove 60 increases or decreases the communication opening area of the advance side supply / discharge port 54 with respect to the first introduction port 52 and the discharge port 57 according to the movement position in the valve accommodating chamber 50, and at the same time. The second guide groove 61 increases or decreases the communication opening area of the retard side supply / discharge port 55 with respect to the second introduction port 53 and the discharge port 57. The spool 38 reciprocally increases or decreases the pressures of the advance side supply / discharge port 54 and the retard side supply / discharge port 55 according to the movement position in the valve storage chamber 50.

  In the flow path switching valve 37, the advance / retreat position of the spool 38 is basically determined by the balance between the urging force of the spring 58 and the spool control pressure introduced into the control chamber 59. However, in this embodiment, the pressure of the advance side supply / discharge passage 26 (advance side working chamber 24) is introduced into the flow path switching valve 37, and the spool 38 serves as a thrust in the same direction as the urging force of the spring 58. The retard angle applied to the spool 38 as a thrust opposite to the urging force of the spring 58 by introducing the pressure of the advance angle feedback chamber 62 and the retard angle supply / discharge passage 27 (retard angle working chamber 25). A side feedback chamber 63 is provided, and the pressure in these feedback chambers 62 and 63 is one of the factors for determining the advance / retreat position of the spool 38.

  Specifically, the advance side feedback chamber 62 is formed facing a step surface 64 provided near one end portion of the spool 38, and the retard side feedback chamber 63 is provided a step provided near the other end portion of the spool 38. It is formed facing the surface 65. The stepped surfaces 64 and 65 facing both the feedback chambers 62 and 63 have the same pressure receiving area, and a force corresponding to the pressure difference between the two feedback chambers 62 and 63 acts on the entire spool 38.

That is, the pressure receiving area of the end surface of the spool 38 facing the control chamber 59 is now S1, the pressure receiving areas of the stepped surfaces 64 and 65 of the feedback chambers 62 and 63 are S2, and the pressure and force of each part are
Spool control pressure: Psol
Pressure in retard side working chamber 25: Pr
Pressure in advance side working chamber 24: Pa
Reaction force of spring 58: Fs
Then, the balance of force during the position control of the spool 38 is
(Psol × S1) + (Pr × S2) = (Pa × S2) + Fs
Then, when this is organized,
(Pa-Pr) * S2 = Psol * S1-Fs.
Accordingly, a force corresponding to the differential pressure between the advance side working chamber 24 and the retard side working chamber 25 (the differential pressure between both feedback chambers 62 and 63) acts on the spool 38, and the advance side working chamber 24 and the retard angle are retarded. The differential pressure in the side working chamber 25 is controlled in proportion to the spool control pressure.

  Further, as shown in FIGS. 9 and 11, the pressure regulating valve 39 includes a spool 71 slidably accommodated in the valve accommodating chamber 70, an electromagnetic solenoid 72 that moves the spool 71 forward and backward, and the valve accommodating chamber 70. An annular control port 74 formed substantially at the center in the axial direction and connected to the control chamber 59 of the flow path switching valve 37 through the connection passage 73, and a position adjacent to one side of the control port 74 of the valve storage chamber 70. An annular line pressure port 75 that is formed to be connected to the line passage 33, and an annular discharge port 77 that is formed at a position adjacent to the other side of the control port 74 of the valve storage chamber 70 and is connected to the drain passage 76. And a control pressure introducing port 78 formed at a position close to the electromagnetic solenoid 72 of the valve accommodating chamber 70 and conducting to the connecting passage 73.

The spool 71 is formed with an annular guide groove 79 that is always connected to the control port 74 at a substantially central position in the axial direction of the outer peripheral surface. The overlap amount of the guide groove 79 with respect to the line pressure port 75 and the discharge port 77 is the amount of the spool 71. It is adjusted continuously according to the moving position. Further, the spool 71 basically has its advance / retreat position determined by the balance between the magnetic force of the electromagnetic solenoid 72 and the force of a reaction force spring (not shown), and the position of the spool 71 is changed according to the increase of the magnetic force of the electromagnetic solenoid 72. It is like that. Specifically, in the initial state in which the electromagnetic solenoid 72 is turned off, the control port 74 conducts only to the discharge port 77 and maintains the pressure in the control chamber 59 of the flow path switching valve 37 at atmospheric pressure. When the electromagnetic solenoid 72 is turned on from the state and the magnetic force increases, the spool 71 moves in accordance with the increase of the magnetic force, and the connection opening area of the control port 74 and the line pressure port 75 increases. As a result, the pressure in the control chamber 59 of the flow path switching valve 37 increases in accordance with the amount of movement of the spool 71 and is the same as the pressure in the line passage 33 at the maximum. Therefore, the pressure in the control chamber 59 is regulated by the pressure regulating valve 39 in the range of 0 to line pressure (pressure in the line passage 33).
Further, a step surface 80 is provided on the proximal end side of the spool 71, and the pressure of the connection passage 73 acts on the step surface 80 via the control pressure introduction port 78.

  Further, a branch passage 81 is provided in the connection passage 73, and this branch passage 81 is connected to the reaction force adjustment chamber 47 of the regulator valve 35. In the reaction force adjusting chamber 47, the pressure of the connection passage 73, that is, the spool control pressure of the flow path switching valve 37 is introduced as the adjusting pressure. Therefore, the reaction force against the pressure of the spool control chamber 46 of the regulator valve 35 is obtained by adding the spool control pressure of the flow path switching valve 37 to the reaction force of the spring 45, and the spool is changed when the phases of the rotors 5 and 6 are changed. When the control pressure increases, the adjustment pressure of the regulator valve 35 increases accordingly, and the pressure of the line passage 33 increases.

By the way, in the case of the electric motor 1, when the inner rotor 6 is on the retard side with respect to the outer rotor 5, the permanent magnets 9 face each other with different polarities and become a strong field state. When the inner circumferential rotor 6 is on the advance side with respect to the outer circumferential rotor 5, the permanent magnets 9 face each other with the same poles and become a field weakening state. However, the inner circumferential rotor 6 When displacing from the retard angle side to the advance angle side, the rotational reaction force between the inner circumferential rotor 6 and the outer circumferential rotor 5 increases substantially linearly.
Various means for linearly increasing the rotational reaction force can be considered. For example, it can be realized by adopting the means shown in FIG. Since FIG. 14 is an image, it is drawn slightly differently from those shown in FIGS.

14 will be briefly described. FIG. 14A shows a state where the inner circumferential rotor 6 is at the most retarded position (the rotational angle θ ₀ of the inner circumferential rotor 6), and FIG. the state in which the inner periphery side rotor 6 proceeds rotation angle theta ₁ to the advance direction from the most retarded angle position, FIG. 14 (C) the inner periphery side rotor 6 to the most advanced angle position from the most retarded position advanced rotation angle θ ₂ state respectively shown.

In the means shown in FIG. 14, an elastic member 86 is provided between the outer circumferential rotor 5 and the inner circumferential rotor 6. The elastic member 86 is constituted by a tension spring having one end connected to the outer rotor 5 by a fixed pin 87 and the other end connected to the inner rotor 6 by a movable pin 85. The movable pin 85 is slidably held in a long hole-like holding groove 88 provided in the inner circumferential side rotor 6.
Thus, in the means shown in FIG. 14, as shown in FIG. 14A, the permanent magnets 9 of the outer peripheral rotor 5 and the inner peripheral rotor 6 face each other with different poles to be in a strong field state. When the inner circumferential rotor 6 rotates relative to the advance direction from the most retarded angle position, the inner circumferential rotor 6 rotates at a rotational angle θ with respect to the outer circumferential rotor 5 as shown in FIG. between ₀ and displaced in the rotation angle theta ₁ slides movable pin 85 along the holding groove 88, the urging force of the elastic member 86 at this time does not act almost.
Then, as shown in FIG. 14B, when the inner rotor 6 is displaced to the rotation angle θ _{1 with} respect to the outer rotor 5, the movable pin 85 is positioned at the end of the holding groove 88, and its sliding Movement is regulated. When the inner rotor 6 further rotates relative to the advance direction from here, as shown in FIG. 14C, the inner rotor 6 pulls and deforms the elastic member 86 in accordance with the rotation angle. . Thus, when the elastic member 86 is pulled, the reaction force increases approximately in proportion to the increase in the rotation angle as shown in the characteristic diagram B of FIG. When the relative rotation angle of the inner rotor 6 reaches θ ₂ and reaches the most advanced position, the outer rotor 5 and the permanent magnet 9 of the inner rotor 6 face each other with the same polarity. Weak field state.

On the other hand, when the inner circumferential rotor 6 advances in the advance direction from the most retarded position, the permanent magnet 9 of the inner circumferential rotor 6 facing the permanent magnet 9 of the outer circumferential rotor 5 with the different magnetic poles is opposed. The magnetic reaction force gradually increases in proportion to the rotation angle θ while the inner rotor 6 advances to the rotation angle θ _{1 in the} advance direction as shown in A of the characteristic diagram of FIG. _The magnetic reaction force gradually decreases until the rotation angle θ ₂ is reached after ₁ is reached.

In the case of the electric motor 1 employing this means, only the magnetic reaction force by the permanent magnet 9 acts while the inner circumferential rotor 6 advances from the most retarded position to the rotation angle θ ₁ , and the rotation angle θ ₁ changes to θ ₂ . Until the movement, the reaction force of the tension spring by the elastic member 86 is added to the magnetic reaction force by the permanent magnet 9. Therefore, the total rotational reaction force obtained by combining the magnetic reaction force and the spring reaction force increases substantially linearly with respect to the increase in the rotation angle of the inner rotor 6 as shown by the characteristic C in FIG. .

  As described above, in the electric motor 1, the rotational reaction force between the rotors 5 and 6 increases almost linearly in accordance with the relative rotation in the advance direction of the inner circumferential rotor 6. By controlling the differential pressure between the advance side working chamber 24 and the retard side working chamber 25 as described above, the relative rotation angle between the inner peripheral side rotor 6 and the outer peripheral side rotor 5 can be arbitrarily controlled. That is, when the spool control pressure of the flow path switching valve 37 is controlled by the pressure regulating valve 39, the relative rotation angle between the rotors 5 and 6 is controlled to an angle corresponding to the spool control pressure.

When the inner rotor 6 is maintained at the most retarded position in order to operate the electric motor 1 in the strong field state, the electromagnetic solenoid 72 of the pressure regulating valve 39 is turned off as shown in FIG. 74 and the discharge port 77 are made conductive. Thereby, the pressure in the control chamber 59 of the flow path switching valve 37 is released to the outside through the connection passage 73, and the pressure in the control chamber 59 is maintained at atmospheric pressure.
At this time, in the flow path switching valve 37, the spool 38 is displaced to the maximum in the direction of the control chamber 59 as shown in FIG. 9 and FIG. The corner side supply / discharge port 55 is electrically connected to the second introduction port 53, and the pressure of the line passage 33 is introduced into the retard side working chamber 25. Thereby, the inner peripheral rotor 6 and the annular housing 15 are maintained on the most retarded angle side with respect to the outer peripheral rotor 5 and the vane rotor 14.

On the other hand, when the inner rotor 6 is displaced to the most advanced angle position in order to operate the electric motor 1 in the field weakening state, the electromagnetic solenoid 72 of the pressure regulating valve 39 is turned on and controlled as shown in FIG. Port 74 is conducted to line pressure port 75. As a result, the hydraulic fluid in the line passage 33 is introduced into the control chamber 59 of the flow path switching valve 37 via the connection passage 73, and the pressure in the control chamber 59 increases.
At this time, in the flow path switching valve 37, the spool 38 is displaced in the direction opposite to the control chamber 59 as shown in FIG. 12, and the advance side supply / discharge port 54 is electrically connected to the first introduction port 52 and the retard side discharge. Port 55 conducts to discharge port 57. At this time, the pressure in the line passage 33 is introduced into the advance side working chamber 24 and the working fluid in the retard side working chamber 25 is discharged to the drain passage 36. As a result, the inner rotor 6 and the annular housing 15 rotate relative to the outer rotor 5 and the vane rotor 14 toward the advance side. When the electric motor 1 is maintained in the field weakening state, the pressure of the line passage 33 is continuously applied to the control chamber 59 by the control of the pressure regulating valve 39.

  Further, when the inner rotor 6 is controlled to an arbitrary position between the most retarded position and the most advanced position, the spool control pressure (introduced into the control chamber 59) is controlled by the electromagnetic solenoid 72 of the pressure regulating valve 39. To a pressure corresponding to the target rotation angle. Thus, when the spool control pressure is controlled, the relative rotational force of the inner rotor 6 due to the differential pressure between the advance side working chamber 24 and the retard side working chamber 25 and the rotation between the rotors 5 and 6. The relative rotation of the inner rotor 6 stops at a rotation angle that balances the reaction force.

Here, the configuration of the motor control unit of hybrid ECU 184 (hereinafter referred to as “ECU 184”) shown in FIG. 8 will be described.
The ECU 184 mainly performs feedback control of current on the dq coordinate forming the rotation orthogonal coordinate. For example, the d-axis current is based on the torque command Tq set according to the accelerator opening degree related to the accelerator operation of the driver. The command Idc and the q-axis current command Iqc are calculated, and the phase output voltages Vu, Vv, and Vw are calculated based on the d-axis current command Idc and the q-axis current command Iqc, and the phase output voltages Vu, Vv, and Vw are calculated. This is obtained by outputting a PWM signal as a gate signal to the PDU 182 and converting any two of the phase currents Iu, Iv, Iw actually supplied from the PDU 182 to the electric motor 1 into currents on the dq coordinate. The current control is performed so that each deviation between the d-axis current Id and the q-axis current Iq and the d-axis current command Idc and the q-axis current command Iqc becomes zero.

  The ECU 184 controls the hydraulic control device 13 (pressure regulating valve 39) to change the phase based on a request command such as the torque command Tq and the actual feedback value of the phase difference between the rotors 6 and 5. Do.

  Specifically, the ECU 184 includes a target current setting unit 120, a current deviation calculation unit 121, a field control unit 122, a power control unit 123, a current control unit 124, a dq-3 phase conversion unit 125, and a PWM signal. Generation unit 126, filter processing unit 127, three-phase-dq conversion unit 128, rotation speed calculation unit 129, induced voltage constant command output unit 130, induced voltage constant number calculation unit 131, and induced voltage constant difference calculation unit 132 and a phase control unit 133.

  The ECU 184 receives current sensors 135 and 135 that detect a two-phase U-phase current Iu and a W-phase current Iw from the three-phase currents Iu, Iv, and Iw output from the PDU 182 to the electric motor 1. Each detection signal Ius, Iws that is output, a detection signal that is output from the voltage sensor 136 that detects the terminal voltage (power supply voltage) VB of the battery 181, and the rotation angle θM of the rotor unit 3 of the motor 1 (that is, a predetermined value) The detection signal output from the resolver 137 (rotation sensor) that detects the rotation angle of the magnetic pole of the rotor unit 3 from the reference rotation position of the rotor and the torque command Tq output from the external control device (not shown) are input. Is done.

For example, the target current setting unit 120 causes the motor 1 to generate a torque command Tq (for example, a torque required according to the amount of depression of the accelerator pedal by the driver) input from an external control device (not shown). ), The rotational speed NM of the electric motor 1 input from the rotational speed calculation unit 129, and the induced voltage constant Ke, each phase current Iu, Iv, Iw supplied from the PDU 182 to the electric motor 1 is specified. The current command is output to the current deviation calculation unit 121 as the d-axis target current Idc and the q-axis target current Iqc on the rotating orthogonal coordinates.
The dq coordinates forming the rotation orthogonal coordinates are, for example, the field magnetic flux direction of the permanent magnet 9 of the rotor unit 3 as a d axis (field axis), and the direction orthogonal to the d axis as a q axis (torque axis). And is rotating in synchronization with the rotation phase of the electric motor 1. As a result, the d-axis target current Idc and the q-axis target current Iqc, which are DC signals, are given as current commands for the AC signal supplied from the PDU 182 to each phase of the electric motor 1.

The current deviation calculation unit 121 includes a d-axis current deviation calculation unit 121a that calculates a deviation ΔId between the d-axis target current Idc input with the d-axis correction current input from the field control unit 122 and the d-axis current Id, A q-axis target current Iqc to which the q-axis correction current input from the control unit 123 is added, and a q-axis current deviation calculation unit 121b that calculates a deviation ΔIq from the q-axis current Iq are configured.
The field control unit 122 is a weakening that controls the current phase so as to weaken the field quantity of the rotor unit 3 equivalently in order to suppress an increase in the counter electromotive voltage accompanying an increase in the rotational speed NM of the electric motor 1, for example. The target value for the field weakening current of the field control is output as the d-axis correction current.
Further, the power control unit 123 outputs a q-axis correction current for correcting the q-axis target current Iqc according to appropriate power control according to, for example, the remaining capacity of the battery 181.

  The current control unit 124 controls and amplifies the deviation ΔId to calculate the d-axis voltage command value Vd by, for example, a PI (proportional integration) operation according to the motor rotation speed NM, and controls and amplifies the deviation ΔIq to control and amplify the deviation ΔIq. The value Vq is calculated.

  The dq-3 phase conversion unit 125 uses the rotation angle θM of the rotor unit 3 input from the rotation number calculation unit 129 to convert the d-axis voltage command value Vd and the q-axis voltage command value Vq on the dq coordinate, It is converted into a U-phase output voltage Vu, a V-phase output voltage Vv, and a W-phase output voltage Vw, which are voltage command values on the three-phase AC coordinates that are stationary coordinates.

  For example, the PWM signal generation unit 126 turns on each switching element of the PWM inverter of the PDU 182 by pulse width modulation based on each phase output voltage Vu, Vv, Vw having a sine wave shape, a carrier signal composed of a triangular wave, and a switching frequency. A gate signal (that is, a PWM signal) that is a switching command including each pulse to be driven off / off is generated.

  The filter processing unit 127 performs filter processing such as removal of high-frequency components on the detection signals Ius and Iws for the phase currents detected by the current sensors 135 and 135 to obtain the phase currents Iu and Iw as physical quantities. Extract.

  The three-phase-dq conversion unit 128 uses the phase currents Iu and Iw extracted by the filter processing unit 127 and the rotation angle θM of the rotor unit 3 input from the rotation number calculation unit 129 to rotate the rotation phase of the electric motor 1. The d-axis current Id and the q-axis current Iq on the rotation coordinates by dq, that is, the dq coordinates are calculated.

  The rotation speed calculation unit 129 extracts the rotation angle θM of the rotor unit 3 of the electric motor 1 from the detection signal output from the resolver 137, and calculates the rotation speed NM of the electric motor 1 based on the rotation angle θM.

  The induced voltage constant command output unit 83 outputs an induced voltage constant command value Kec (induced voltage constant command) based on, for example, the torque command Tq, the rotation speed NM of the electric motor 1, the shift command, and the drive wheel selection command. .

The induced voltage constant calculating unit 131 receives the detection value θ ₀ from the phase detector 138 that detects the relative phase between the inner circumferential rotor 6 and the outer circumferential rotor 5 and calculates the actual induced voltage constant Ke of the electric motor 1. . The induced voltage constant Ke calculated here is input to the target current setting unit 120 and is also input to the induced voltage constant difference calculation unit 132. As the phase detector 138, for example, a sensor for detecting a differential pressure between the advance side supply / discharge passage 26 (advance side working chamber 24) and the retard side supply / discharge passage 27 (retard side working chamber 25), A sensor or the like that directly detects the phase difference between the inner circumferential rotor 6 and the outer circumferential rotor 5 can be used.

  The induced voltage constant difference calculating unit 132 calculates a deviation between the induced voltage constant command value Kec output from the induced voltage constant command output unit 130 and the actual induced voltage constant Ke obtained by the induced voltage constant calculating unit 131, Therefore, the calculated deviation ΔKe of the induced voltage constant is output to the phase control unit 133.

  The phase control unit 133 calculates a phase command value θc corresponding to the induced voltage constant deviation ΔKe, and outputs the phase command value θc to the pressure regulating valve 39 of the hydraulic control device 13.

  Since the electric motor 1 configured as described above changes the relative phase between the inner circumferential rotor 6 and the outer circumferential rotor 5 by the hydraulic fluid supplied and discharged from the hydraulic control device 13, the electric motor 1 is used as a hybrid vehicle. Or when used as a drive source for an electric vehicle, the motor characteristics can be quickly changed to the optimum motor characteristics according to the driving requirements.

  Further, in the electric motor 1, the radial holes 205 and 206 forming part of the advance side supply / discharge passage 26 and the retard side supply / discharge passage 27 on the output shaft 4 are rotationally symmetric as shown in FIG. Therefore, the rotation balance of the output shaft 4 during rotation is good, and the vibration of the output shaft 4 is less likely to occur. For this reason, it is advantageous in terms of durability of the bearings 201A, 201B, 201C that support the output shaft 4, and the quietness at the time of operation is enhanced, and the control is stable even when the control pressure of the phase changing means 12 is high. It can be made.

Furthermore, in this electric motor 1, since the advance side axial path 26a and the retard side axial path 27a are concentrically extended from the reciprocal direction so as to be concentric, these axial directions The paths 26a and 27a do not hinder the rotation balance of the output shaft 4. Therefore, in this electric motor 1, the rotation balance of the output shaft 4 becomes better.
Further, since the advance side axial path 26a and the retard side axial path 27a are formed inside the base holes 203 and 204 formed from the opposite directions of the output shaft 4, the distance between the axial paths 26a and 27a is reduced. In this case, there is no concern that the hydraulic fluid leaks, and this makes it possible to stabilize the control.

  Further, the phase changing means 12 of the electric motor 1 distributes the supply and discharge of the hydraulic fluid to the advance side working chamber 24 and the retard side working chamber 25 of the rotating mechanism 11 by the spool type flow switching valve 37, and Since the spool position of the flow path switching valve 37 is controlled by the pressure of the hydraulic fluid produced by the electromagnetic pressure regulating valve 39 based on the line pressure, a relatively large flow rate can be obtained without using a large solenoid valve. The relative phases of the rotors 5 and 6 that require a working fluid can be reliably changed at an arbitrary timing.

  FIGS. 16, 17, 18 and 19 show the second and third embodiments of the present invention, respectively. The electric motors 301 and 401 of these embodiments are different from the first embodiment in the configuration of the output shafts 304 and 404 fitted and fixed to the vane rotor, and the other configurations are substantially the same as those in the first embodiment. ing. Hereinafter, the second and third embodiments will be described in order, but the same parts as those in the first embodiment are denoted by the same reference numerals, and the description of the overlapping parts will be omitted.

  In the electric motor 301 of the second embodiment shown in FIGS. 16 and 17, the advance side supply / discharge port 207 and the retard side supply / exhaust port 210 are provided in the support block 202A at the front end, and the output shaft 304 is arranged in the axial direction. The hydraulic fluid is supplied to and discharged from the advance side supply / discharge passage 26 and the retard side supply / discharge passage 27 from one end side.

  Specifically, a base hole 303 is formed in the shaft center portion of the output shaft 304 so as to reduce the diameter in two steps from the front end surface toward the bottom portion. A pair of radial holes 206 are formed in the minimum diameter portion 303a so as to be connected to the retarded-side annular groove 27b. A pair of radial holes 206b connected to the advanced-angle-side annular groove 26b are formed in the intermediate diameter portion 303b of the base hole 303. The radial hole 205 is formed. Similar to the first embodiment, these retarded and advanced radial holes 206 and 205 are rotationally symmetric about the axis when projected onto a plane orthogonal to the axis of the output shaft 304. Are arranged as follows.

  A hollow pipe 308 having one end connected to the retard side supply / exhaust port 210 protrudes from the support block 202A on the front side, and the other end of the hollow pipe 308 is in the smallest diameter portion 303a of the base hole 303. Has been inserted. An annular seal member 209 slidably contacting the inner peripheral surface of the minimum diameter portion 303 a is attached to the outer periphery of the other end portion of the hollow pipe 308, and the inner peripheral surface of the minimum diameter portion 303 a and the hollow pipe 308 are attached by this seal member 209. The space is sealed in a liquid-tight manner, and the retarded-side axial path 27 a is configured by the axial center path 380 in the hollow pipe 308 and the bottom of the base hole 303.

In addition, an outer hollow pipe 312 is provided on the front support block 202A so as to surround the outer periphery of the hollow pipe 308 on the base portion side with a predetermined gap. The outer hollow pipe 312 has a gap between the outer hollow pipe 312 and the hollow pipe 308 connected to the advance side supply / discharge port 207 of the support block 202A and the other end extending to the intermediate diameter portion 303b of the base hole 303. ing. An annular seal member 209 slidably contacting the inner peripheral surface of the intermediate diameter portion 303b is attached to the outer periphery of the other end portion of the outer hollow pipe 312, and the inner peripheral surface of the intermediate diameter portion 303b and the outer hollow pipe are attached by this seal member 209. Between 312 is liquid-tightly sealed.
A cylindrical gap is formed between the hollow pipe 308 and the outer hollow pipe 312, and this cylindrical gap is continuous with the cylindrical gap between the intermediate diameter portion 303 b of the base hole 303 and the hollow pipe 308. The cylindrical passage formed by the continuous gap constitutes the advance side axial path 26 a that connects the advance side supply / discharge port 207 and the radial hole 205.
A cylindrical passage 320 is formed between the maximum diameter portion 303c of the base hole and the outer hollow pipe 312 to connect the inflow port 213 of the support block 202A and the lubrication port 214 of the output shaft 304.

Furthermore, an annular protrusion 321 is formed on the outer periphery on the other end side of the hollow pipe 308 by bulging as shown in an enlarged view in FIG. The annular projection 321 is provided on the side of the hollow pipe 308 facing the advance side axial path 26a across the mounting portion of the seal member 209, and connects the base hole 303 (the intermediate diameter portion 303b and the minimum diameter portion 303a). An annular minute gap d is formed with the inner peripheral surface of the part. The minute gap d functions as an orifice that attenuates the surge pressure acting on the advance side axial path 26a.
Similarly, an annular protrusion 322 is formed on the outer periphery of the other end of the outer hollow pipe 312 by bulging, and this annular protrusion 322 is formed in the base hole 303 (the connecting portion of the intermediate diameter portion 303b and the maximum diameter portion 303c). A minute gap d is formed with the peripheral surface.

  Since this electric motor 301 employs a structure in which the relative phase between the inner circumferential rotor 6 and the outer circumferential rotor 5 is controlled by the phase changing means 12 that is operated by hydraulic fluid, it serves as a drive source for hybrid vehicles and electric vehicles. When used, it is possible to quickly change to the optimum motor characteristics according to the operation requirements.

In the case of the electric motor 301 as well, the radial holes 205 and 206 forming part of the advance side supply / discharge passage 26 and the retard side supply / exhaust passage 27 on the output shaft 304 are rotationally symmetrical. The rotation balance of the output shaft 304 becomes good.
Further, since the advance side axial path 26a and the retard side axial path 27a are formed by concentric spaces separated in the base hole 303 by the hollow pipe 308, both the axial paths 26a and 27a are formed. The rotational balance of the output shaft 304 is not hindered.
Therefore, in this electric motor 301, since the rotational vibration of the output shaft 304 can be suppressed by these, it is possible to reduce the load acting on the bearings 201A, 201B, 201C, and to reduce and control vibration noise during operation. It is also possible to stabilize.

  Further, the electric motor 301 has a structure in which a hollow pipe 308 is disposed in the base hole 303 of the output shaft 304, and inner and outer double axial paths 27a and 26a are formed from one side in the shaft center portion of the output shaft 304. Therefore, the flow path of the hydraulic fluid is concentrated on one side of the output shaft 304 in the axial direction. Therefore, it is possible to improve the in-vehicle performance by making the whole into a compact layout.

  Further, in the electric motor 301 of this embodiment, a seal member 209 is attached to the outer periphery on the other end side of the hollow pipe 308, and the space between the base hole 303 and the hollow pipe 308 is sealed with the seal member 209 in a liquid-tight manner. Therefore, the structure in which the advance side axial path 26a and the retard side axial path 27a are arranged concentrically on the output shaft 304 can be easily and compactly formed.

  In the case of the electric motor 301, an annular protrusion 321 is formed on the hollow pipe 308 by bulge processing, and an annular minute gap d that functions as a throttle is formed between the annular protrusion 321 and the base hole 303. Therefore, the surge pressure acting on the advance side axial path 26a and the retard side axial path 27a is attenuated by the throttling function of the annular protrusion 321, and the leakage of the hydraulic fluid between the axial paths 26a, 27a is further effective. Can be prevented. Further, since the annular protrusion 321 can be easily formed on the hollow pipe 308 by bulging, there is an advantage that the manufacturing cost can be suppressed.

  As in the second embodiment, the electric motor 401 of the third embodiment shown in FIGS. 18 and 19 is provided with an advance side supply / discharge port 207 and a retard side supply / discharge port 210 on the support block 202A at the front end. The hydraulic fluid is supplied to and discharged from the advance side supply / discharge passage 26 and the retard side supply / discharge passage 27 from one end side of the output shaft 404 in the axial direction. The support block 202A is provided with an inflow port 213 for supplying the lubricating liquid to the lubricating port 214 and the front side bearing 201A, and an inflow port 440 for supplying the lubricating liquid to the rear side bearing 201B.

  A base hole 403 is formed in the shaft center portion of the output shaft 404 so as to reduce the diameter in two steps from the front end surface toward the bottom portion, and the minimum diameter portion 403a on the bottom side of the base hole 403 has a delay. A pair of radial holes 206 conducting to the angular annular groove 27b are formed, and a pair of radial holes 205 conducting to the advanced annular groove 26b are formed in the intermediate diameter portion 403b of the base hole 403. . These radial holes 206 and 205 are arranged so as to be rotationally symmetric about the axis when projected onto a plane orthogonal to the axis of the output shaft 404, as in the first and second embodiments. Yes.

  A hollow pipe 408 (second pipe) whose one end is connected to the retarded-side supply / discharge port 210 protrudes from the support block 202A on the front side, and the other end of the hollow pipe 408 is the outermost end of the base hole 403. It is inserted into the small diameter part 403a. An annular seal member 209 is attached to the outer periphery of the other end of the hollow pipe 408 so as to be in sliding contact with the inner peripheral surface of the minimum diameter portion 303a. The seal member 209 allows the inner peripheral surface of the minimum diameter portion 303a and the hollow pipe 408 to The space is sealed in a liquid-tight manner, and the retarded-side axial path 27 a is configured by the axial path 380 in the hollow pipe 408 and the bottom of the base hole 403.

  The support block 202A on the front side includes an intermediate hollow pipe 414 (first pipe) that surrounds the outer periphery of the hollow pipe 408 with a predetermined gap, and an outer side that similarly surrounds the outer periphery of the intermediate hollow pipe 414 with a predetermined gap. A hollow pipe 415 is protruded.

  One end of the intermediate hollow pipe 414 is connected to the advance side supply / discharge port 207 of the support block 202A at the gap with the outer hollow pipe 415, and the other end is the shaft of the intermediate diameter portion 403b of the base hole 403. It extends to the approximate center position in the direction. An annular seal member 209 slidably contacting the inner peripheral surface of the intermediate diameter portion 403b of the base hole 403 is attached to the outer periphery of the other end portion of the intermediate hollow pipe 414, and the inner peripheral surface of the intermediate diameter portion 403b is attached by the seal member 209. And the intermediate hollow pipe 414 are sealed in a liquid-tight manner.

  The outer hollow pipe 415 is connected at one end to the inflow port 213 of the support block 202A with the gap between the base hole 403 and the maximum diameter portion 403c, and the other end is the deepest of the maximum diameter portion 403c of the base hole 403. It extends to the vicinity of the part. An annular seal member 209 slidably contacting the inner peripheral surface of the maximum diameter portion 403c of the base hole 403 is attached to the outer periphery of the other end portion of the outer hollow pipe 415, and the inner peripheral surface of the maximum diameter portion 403c is attached by this seal member 209. And the outer hollow pipe 415 are liquid-tightly sealed.

  Here, the cylindrical passage between the intermediate hollow pipe 414 and the outer hollow pipe 415 is an advance side axial path 26 a that communicates the advance side supply / discharge port 207 and the advance side radial hole 205, and the hollow pipe 408. The cylindrical passage between the intermediate hollow pipe 414 is a part of the lubrication passage 441 communicating with the inflow port 440.

  The lubrication passage 441 includes a cylindrical passage 441a between the hollow pipe 408 and the intermediate hollow pipe 414, a large-diameter cylindrical passage 441c provided between the output shaft 404 and the vane rotor 14, and a support block 202B on the rear side. The shaft passage 441e that conducts to the bearing 201B portion, the cylindrical passages 441a and 441c, and the radial passages 441b and 441d that connect the cylindrical passage 441c and the shaft passage 441e respectively. The bearing 201B is supplied.

  A cylindrical passage 420 is formed between the maximum diameter portion 403c of the base hole 403 and the outer hollow pipe 415 to connect the inflow port 213 of the support block 202A and the lubrication port 214 of the output shaft 404. The hydraulic fluid introduced from the inflow port 213 is directly supplied to the front bearing 201 </ b> A and is also supplied to the motor gear 183 through the cylindrical passage 420 and the lubrication port 214.

  Since the electric motor 401 controls the relative phase between the inner circumferential rotor 6 and the outer circumferential rotor 5 by hydraulic fluid supply / discharge control, similarly to the first and second embodiments, any timing is possible. In addition, the motor characteristics can be changed quickly, and the axial passages 26a and 27a of the advance side supply / discharge passage 26 and the retard side supply / discharge passage 27 are coaxially arranged on the output shaft 404, and Since the radial holes 205 and 206 are disposed rotationally symmetrically, the balance of the output shaft 404 during rotation can be improved, the durability of the bearings 201A, 201B, and 201C can be improved, and vibration and noise can be reduced. Reduction and stabilization of control can also be achieved.

  In the case of the electric motor 401 of this embodiment, the hollow pipe 408 that forms the retard side axial path 27a on the inner peripheral side and the intermediate hollow pipe 414 that forms the advance side axial path 26a on the outer peripheral side are coaxial. Since the two pipes 408 and 414 are arranged as a lubricating liquid passage 441 for supplying the lubricating liquid to the bearing 201B, the retard side axial path 27a and the advance side axial direction in which the pressure difference of the hydraulic fluid becomes large The passages 26a are not disposed directly adjacent to each other, and as a result, it is possible to effectively prevent leakage of hydraulic fluid between the two axial passages 27a and 26a.

  The present invention is not limited to the above embodiments, and various design changes can be made without departing from the scope of the invention.

BRIEF DESCRIPTION OF THE DRAWINGS The schematic block diagram of the motive power system of the vehicle to which the electric motor of 1st Embodiment of this invention is applied. The longitudinal cross-sectional view of the electric motor of the embodiment. The side view which abbreviate | omitted some components of the rotor unit controlled to the most retarded angle position of the electric motor of the embodiment. The side view which abbreviate | omitted some components of the rotor unit controlled to the most advanced angle position of the electric motor of the embodiment. The disassembled perspective view of the rotor unit of the electric motor of the embodiment. The expanded sectional view corresponding to the AA section of Drawing 2 showing the embodiment. The figure (a) which shows typically the strong field state where the permanent magnet of the inner circumference side rotor and the permanent magnet of the outer circumference side rotor are arranged in the same polarity, and the permanent magnet and outer circumference side rotation of the inner circumference side rotor The figure which also described the figure (b) which shows typically the field-weakening state by which the permanent magnet of a child was arrange | positioned differently. The schematic block diagram of the control system of the electric motor of the embodiment. The hydraulic circuit diagram centering on the hydraulic control apparatus of the phase change means of the embodiment. Typical sectional drawing of the flow-path switching valve of the embodiment. The typical sectional view of the pressure regulation valve of the embodiment. Typical sectional drawing of the flow-path switching valve of the embodiment. The typical sectional view of the regulator valve of the embodiment. FIG. 4 is a schematic cross-sectional view showing the embodiment, in which the operation of the means for linearly increasing the rotational reaction force is sequentially divided into (A), (B), and (C). The characteristic view which showed the mode of the change of the rotational reaction force with respect to the increase in the relative rotation angle of the inner peripheral side rotor of the embodiment. The longitudinal cross-sectional view of the electric motor of 2nd Embodiment of this invention. The expanded sectional view of the B section of Drawing 16 showing the embodiment. The longitudinal cross-sectional view of the electric motor of 3rd Embodiment of this invention. The expanded sectional view of the C section of Drawing 18 showing the embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1,301,401 ... Electric motor 4,304,404 ... Output shaft 5 ... Outer peripheral side rotor 6 ... Inner peripheral side rotor 9 ... Permanent magnet 12 ... Phase change means 24 ... Advance angle side working chamber 25 ... Delay angle side operation Chamber 26 ... Advance side supply / discharge passage 26a ... Advance side axial passage 27 ... Delay angle supply / discharge passage 27a ... Delay angle axial passage 32 ... Oil pump (fluid supply source)
37 ... Flow path switching valve 39 ... Pressure control valve 201A, 201B ... Bearing 205 ... Diameter hole (advanced side radial path)
206: Radial hole (retarded radial path)
209 ... Seal member 303, 403 ... Base hole 308 ... Hollow pipe 321 ... Annular projection 380 ... Axial passage 408 ... Hollow pipe (second pipe)
414 ... Intermediate hollow pipe (first pipe)

Claims (7)

An inner rotor on which permanent magnets are arranged along the circumferential direction;
An outer peripheral rotor disposed coaxially and relatively rotatably on the outer peripheral side of the inner peripheral rotor, and a permanent magnet disposed along the circumferential direction;
Phase changing means for changing the relative phase of the inner and outer rotors by relatively rotating the inner and outer rotors;
An output shaft that is integrally coupled to the outer circumferential rotor or the inner circumferential rotor and is supported by a bearing and rotates;
An electric motor with
The phase changing means includes an advance side working chamber for rotating the inner circumference side rotor relative to the outer circumference side rotor in the advance direction by the pressure of the working fluid introduced therein, and the working fluid introduced into the inside. A retard-side working chamber that rotates the inner-side rotor relative to the outer-side rotor in a retarded direction by the pressure of
The output shaft is provided with an advance side supply / discharge passage and a retard side supply / discharge passage for supplying / discharging working fluid to and from the advance side working chamber and the retard side working chamber,
Advancing side axial passage extending along the axial direction of the output shaft in the advance side supply / discharge passage, and Axis direction of the output shaft in the retarding side supply / discharge passage. The retarding-side axial path extending in a manner extends concentrically from the axially opposite ends of the output shaft. An inner rotor on which permanent magnets are arranged along the circumferential direction;
An outer peripheral rotor disposed coaxially and relatively rotatably on the outer peripheral side of the inner peripheral rotor, and a permanent magnet disposed along the circumferential direction;
Phase changing means for changing the relative phase of the inner and outer rotors by relatively rotating the inner and outer rotors;
An output shaft that is integrally coupled to the outer circumferential rotor or the inner circumferential rotor and is supported by a bearing and rotates;
An electric motor with
The phase changing means includes an advance side working chamber for rotating the inner circumference side rotor relative to the outer circumference side rotor in the advance direction by the pressure of the working fluid introduced therein, and the working fluid introduced into the inside. A retard-side working chamber that rotates the inner-side rotor relative to the outer-side rotor in a retarded direction by the pressure of
The output shaft is provided with an advance side supply / discharge passage and a retard side supply / discharge passage for supplying / discharging working fluid to and from the advance side working chamber and the retard side working chamber,
A base hole is formed in the output shaft along the axial center portion, and a hollow pipe that divides the base hole into an inner axial passage and an outer cylindrical passage is coaxially installed in the base hole,
Among the advance angle side supply / discharge passages, an advance angle side axial path extending along the axial direction of the output shaft is configured on one side of the axial path and the cylindrical path,
Of the retarded side supply / exhaust passage, a retarded side axial path extending along the axial direction of the output shaft is formed on the other side of the axial passage and the cylindrical passage. Electric motor. Of the advance angle side supply / discharge passage, the advance angle side radial path extending substantially along the radial direction of the output shaft, and in the radial direction of the output shaft of the retard angle side supply / discharge passage, The retard-angle-side radial path extending substantially along is disposed so as to be rotationally symmetric about an axis when projected onto a plane orthogonal to the axis of the output shaft. The electric motor according to 1 or 2 . The electric motor according to claim 2 , wherein an end portion of the cylindrical passage is partitioned by a seal member interposed between the pipe and a base hole. The pipe, in the vicinity of the end portion of the cylindrical passage, the electric motor according to claim 2 or 4, characterized in that the annular projection is formed which forms a stop between the base hole. A hollow first pipe is coaxially arranged inside the base hole, and a further hollow second pipe is coaxially arranged inside the first pipe,
Either one of the advance side axial path and the retard side axial path is constituted by a cylindrical passage formed between the base hole and the first pipe,
One of the advance side axial path and the retard side axial path is configured by an axial passage formed inside the second pipe,
The electric motor according to any one of claims 2 to 5, characterized in that lubricating liquid supply passage by an intermediate cylindrical passage formed between the first pipe and the second pipe is constructed. A spool-type flow path switching valve that distributes the supply and discharge of the working fluid to the advance side working chamber and the retard side working chamber according to the spool position is provided,
An electromagnetic pressure regulating valve that regulates the pressure of the working fluid supplied from the fluid supply source and controls the spool position of the flow path switching valve by the pressure of the regulated working fluid is provided. The electric motor of any one of Claims 1-6 .

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