JP5095129B2 - 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 of this type, an inner circumferential rotor and an outer circumferential rotor each having a permanent magnet are coaxially arranged, and both rotors are relatively rotated in the circumferential direction (of both rotors). It is known that the field characteristics of the entire rotor can be changed by changing the relative 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 according to the speed of the rotating magnetic field generated in the stator, a control current is applied to the stator winding in a state where each rotor maintains the rotation speed due to inertia. The relative position in the circumferential direction of the outer peripheral side rotor and the inner peripheral side rotor is changed by energizing and changing the rotating magnetic field speed.

In this electric motor, the permanent magnets of the outer rotor and the inner rotor 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. On the contrary, 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.
JP 2002-204541 A

  However, in the case of this conventional electric motor, the conditions under which the relative phase between the outer peripheral rotor and the inner peripheral rotor can be changed are limited, and the relative phase can be freely changed when the motor is stopped or rotated arbitrarily. I can't. 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 the supply and discharge of the working fluid to and from these working chambers is controlled by an electromagnetic flow path switching valve.

  However, in the case of this phase changing means, the working fluid is supplied and discharged by the flow path switching valve to the advance side working chamber and the retard side working chamber, so that the operation response is determined by the allowable flow rate of working fluid in the flow path switching valve Therefore, unless the passage allowable flow rate is set large, it becomes impossible to respond to a sudden phase change request. And in order to increase the passage allowable flow rate, it is necessary to increase the size of the valve body and the electromagnetic actuator part of the flow path switching valve. However, increasing the size of the flow path switching valve increases the occupied space in the system. The manufacturing cost will rise.

  Therefore, the present invention intends to provide an electric motor capable of improving the degree of freedom of phase change control and improving the operation response at the time of phase change without causing an increase in occupied space or an increase in manufacturing cost. It is.

As means for solving the above-mentioned problems, the invention according to claim 1 is directed to an inner peripheral rotation in which a permanent magnet (for example, a permanent magnet 9 in an embodiment described later) is disposed along the circumferential direction. A rotor (for example, an inner circumferential rotor 6 in an embodiment described later) and an outer circumferential side of the inner circumferential rotor are arranged coaxially and relatively pivotably, and are permanent along the circumferential direction. An outer peripheral rotor (for example, an outer peripheral rotor 5 in an embodiment described later) on which a magnet is disposed, and the inner peripheral rotor and the outer peripheral rotor are rotated relative to each other so that the relative phases of the two are changed. A phase change means for changing (for example, a phase change means 12 in an embodiment to be described later), wherein the phase change means changes the inner rotor by the pressure of the working fluid introduced therein. Rotate relative to the outer rotor in the advance direction A corner side working chamber (for example, an advance side working chamber 24 in an embodiment to be described later) and a pressure of working fluid introduced into the inner side rotor are rotated relative to the outer side rotor in a retarded direction. A retarding-side working chamber to be moved (for example, a retarding-side working chamber 25 in an embodiment to be described later), a fluid supply source for supplying the working fluid (for example, an oil pump 32 in an embodiment to be described later), and a phase change A flow path switching valve (for example, a flow path switching valve 37 in an embodiment to be described later) for distributing the supply and discharge of the working fluid to the advance side working chamber and the retard side working chamber according to demand, and the fluid supply source And a bypass passage provided between the fluid supply source and the retarding side working chamber so as to bypass the flow path switching valve (for example, implementation described later) Advance side bypass passage in the configuration 5, the retard-side bypass passage 46), interposed the on-off valve in the bypass passage (e.g., on-off valve 47A will be described in the exemplary embodiment, 47B) and a phase detector for outputting a detection value of the relative phase A phase detector (e.g., phase detector 81 in an embodiment described later) and phase control means (e.g., phase control unit 62 in an embodiment described later) for outputting the relative phase command value, The phase changing means opens the on-off valve when a difference between the detected value of the relative phase and the command value is out of a predetermined range .
In this case, the on-off valve closes the bypass passage during normal phase change, and the flow path switching valve supplies and discharges the working fluid to the advance side working chamber and the retard side working chamber in response to a phase change request from the controller. I do. Further, for example, when there is a request for a sudden phase change on the advance side or the retard side, the on-off valve opens the bypass passage, and the hydraulic fluid of the fluid supply source flows in the flow path switching valve and the bypass passage. It is introduced into the advance side working chamber or the retard side working chamber. In this case, the working fluid flows into one working chamber at a large flow rate, and the phase is quickly changed.

According to a second aspect of the present invention, in the first aspect of the present invention, a first member (for example, a vane rotor 14 and a drive plate 16 in an embodiment described later) that rotates integrally with the outer circumferential rotor and the inner circumferential surface. A working fluid introduction space (for example, an introduction space 23 in a later-described embodiment) is provided between a second member (for example, an annular housing 15 in the later-described embodiment) that rotates integrally with the side rotor, and the first One of the member and the second member is provided with a vane (for example, a vane 18 in an embodiment described later) that is slidably disposed in the introduction space and separates the introduction space into two chambers. The advance side working chamber and the retard side working chamber are constituted by two chambers separated by the vane.
Thereby, for example, when the working fluid is supplied to the advance side working chamber and the working fluid is discharged from the retard side working chamber, the vane receives the pressure difference between the front and rear, and the inside of the introduction space is relatively moved from one side to the other side. The first member and the second member rotate relative to each other. As a result, the inner circumferential rotor rotates relative to the outer circumferential rotor in the advance direction. On the other hand, when the working fluid is supplied to the retard side working chamber and the working fluid is discharged from the advance side working chamber, the vane receives the differential pressure before and after this and relatively At this time, the inner rotor rotates relative to the outer rotor in the retarding direction via the first member and the second member.

According to a third aspect of the present invention, an inner peripheral rotor on 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 phase change means, wherein the phase change means causes the inner rotor to rotate relative to the outer rotor in the advance direction by the pressure of the working fluid introduced therein. Advancing side working chamber, a retarding side working chamber for rotating the inner circumferential side rotor relative to the outer circumferential side rotor in a retarding direction by the pressure of the working fluid introduced therein, and supplying the working fluid The fluid supply source to be operated and the operation for the advance side working chamber and the retard side working chamber in response to the phase change request. A flow path switching valve for distributing supply and discharge of fluid, and the flow path between at least one of the fluid supply source and the advance side working chamber, and between the fluid supply source and the retard side working chamber. A first member (for example, in an embodiment to be described later) that includes a bypass passage provided so as to bypass the switching valve, and an on-off valve interposed in the bypass passage, and rotates integrally with the outer peripheral rotor. An inner cylinder member 112, a drive plate 114) and a second member (for example, an outer cylinder member 113 in an embodiment described later) that rotates integrally with the inner peripheral rotor are provided with a shaft portion (for example, an operation described later). A shaft portion 112b) is provided, and a cylindrical portion (for example, a thick portion 113a in an embodiment described later) is provided on the other of the first member and the second member to surround the outside of the shaft portion. Inner and outer circumference Is provided with a ring gear (for example, a ring gear 118 in an embodiment described later) that engages with the shaft portion and the cylindrical portion, respectively, and a working fluid introduction space (for example, described later) is provided between the first member and the second member. In this embodiment, an introduction space 115) is provided, and a piston (for example, a piston 122 in the embodiment described later) is provided that is slidably received in the introduction space and separates the introduction space into two chambers. The piston is connected to the ring gear so as to be integrally displaceable, and the advance side working chamber and the retard side working chamber are constituted by two chambers separated by the piston.
In this case, for example, when the working fluid is supplied to the advance side working chamber and the working fluid is discharged from the retard side working chamber, the piston receives a differential pressure between the front and rear, and the inside of the introduction space is relatively moved from one side to the other side. At this time, the ring gear connected to the piston moves from one side to the other side between the shaft portion and the cylindrical portion. When the ring gear moves in this manner between the shaft portion and the tube portion, the ring gear applies one side relative rotational force to the shaft portion and the tube portion via the helical spline. As a result, the first member and the second member rotate relative to each other, and the inner circumferential rotor rotates relative to the outer circumferential rotor in the advance direction. On the other hand, when the working fluid is supplied to the retarded-side working chamber and the working fluid is discharged from the advanced-side working chamber, the piston receives a differential pressure before and after that and is relatively moved in the opposite direction. At this time, the ring gear moves in the same direction as the piston, and applies a relative rotational force in the opposite direction to the shaft portion and the cylindrical portion via the helical spline. As a result, the first member and the second member rotate relative to the other, and the inner circumferential rotor rotates relative to the outer circumferential rotor in the retard direction.

The invention according to claim 4 is an inner peripheral rotor in which permanent magnets are disposed along the circumferential direction, and is disposed coaxially and relatively rotatably on the outer peripheral side of the inner peripheral rotor. 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 phase change means, wherein the phase change means causes the inner rotor to rotate relative to the outer rotor in the advance direction by the pressure of the working fluid introduced therein. Advancing side working chamber, a retarding side working chamber for rotating the inner circumferential side rotor relative to the outer circumferential side rotor in a retarding direction by the pressure of the working fluid introduced therein, and supplying the working fluid The fluid supply source to be operated and the operation for the advance side working chamber and the retard side working chamber in response to the phase change request. A flow path switching valve for distributing supply and discharge of fluid, and the flow path between at least one of the fluid supply source and the advance side working chamber, and between the fluid supply source and the retard side working chamber. A first member (for example, in an embodiment to be described later) that includes a bypass passage provided so as to bypass the switching valve, and an on-off valve interposed in the bypass passage, and rotates integrally with the outer peripheral rotor. An inner block 212) and a second member that rotates integrally with the inner rotor (for example, an outer block 213 in an embodiment described later) are arranged in a direction substantially tangential to the circumference centered on the rotation axis. A first cylinder (for example, a first cylinder 214 in an embodiment to be described later) and a second cylinder (for example, a second cylinder 215 in an embodiment to be described later) are provided. In addition, a first piston (for example, a first piston 216 in an embodiment described later) and a second piston (for example, a second piston 217 in an embodiment described later) are connected to the first cylinder and the second cylinder. Are provided so as to be capable of advancing and retreating, and the first member and the second member are in contact with the tops of the first piston and the second piston, respectively, along the substantially radial direction of the two rotors. Load transmission walls (for example, a first load transmission wall 218 in an embodiment described later) and a second load transmission wall (for example, a second load transmission wall 219 in an embodiment described later) are provided. The advance side working chamber and the retard side working chamber are configured between the cylinder and the first piston and between the second cylinder and the second piston, respectively.
In this case, for example, when the working fluid is supplied to the advance side working chamber and the working fluid is discharged from the retard side working chamber, the first piston protrudes while the second piston moves backward. At this time, the first piston presses the first load transmission wall, the first load transmission wall is separated from the first cylinder side, and the second load transmission wall is close to the second cylinder side. As a result, the first member and the second member rotate relative to one side. As a result, the inner circumferential rotor rotates relative to the outer circumferential rotor in the advance direction. On the other hand, when the working fluid is supplied to the retard side working chamber and the working fluid is discharged from the advance side working chamber, the second piston protrudes while the first piston moves backward, The piston presses the second load transmission wall. As a result, the first member and the second member rotate relative to the other side, and the inner circumferential rotor rotates relative to the outer circumferential rotor in the retard direction.

According to a fifth aspect of the present invention, in the electric motor according to any one of the first to fourth aspects, the signal pressure is generated by switching between introduction and discharge of the pressure of the working fluid supplied from the fluid supply source. An electromagnetic valve (for example, electromagnetic valves 48A and 48B in the embodiments described later) is provided, and the on-off valve is opened and closed by a signal pressure generated by the electromagnetic valve.
In this case, since the solenoid valve only switches between the introduction and discharge of the pressure of the working fluid from the fluid supply source, the solenoid valve can be operated with a relatively small magnetic force, while the on-off valve is introduced from the fluid supply source. The bypass passage is operated with a relatively large signal pressure based on the pressure.

According to the invention of this application, a configuration is adopted in which the relative phases of the outer circumferential rotor and the inner circumferential rotor are changed by appropriately supplying and discharging working fluid to and from the advance side working chamber and the retard side working chamber. In addition, according to the phase change request, the flow path switching valve distributes the supply and discharge of the working fluid to the advance side working chamber and the retard side working chamber, and in addition to the passage through the flow path switching valve, A bypass passage that bypasses the path switching valve and connects one of the working chambers to the fluid supply source is provided, and an on-off valve is interposed in the bypass passage, so that when there is a sudden phase change request, the bypass passage By opening the on-off valve interposed in the working fluid, the working fluid can be supplied to the corresponding working chamber at a large flow rate.
Therefore, according to the present invention, the phase of the rotor can be freely changed at an arbitrary timing, and it is possible to respond quickly to a sudden phase change request without using a large solenoid valve. . Therefore, an increase in occupied space and an increase in manufacturing cost are not caused.

According to the fifth aspect of the present invention, since the signal pressure is generated by the solenoid valve using the pressure of the working fluid supplied from the fluid supply source, and the on-off valve is operated by the signal pressure, the solenoid valve is relatively small. The on-off valve can be reliably controlled with magnetic force.
Therefore, according to the present invention, the solenoid valve can be further downsized, the occupied space can be reduced, and the manufacturing cost can be further reduced.

In addition, according to the inventions described in claims 2 to 4 , the relative phases of the inner and outer rotors can be accurately determined at any timing by the supply and discharge control of the working fluid with a relatively simple configuration. Therefore, it is possible to reduce the size of the electric motor while increasing the degree of freedom in changing the relative phase.

  Embodiments of the present invention will be described below with reference to the drawings. First, the first embodiment shown in FIGS. 1 to 8 will be described.

  The electric motor 1 of this embodiment is an inner rotor type brushless motor in which a rotor unit 3 is disposed on the inner peripheral side of an annular stator 2 as shown in FIGS. 1 to 4, for example, a hybrid vehicle or an electric vehicle. It is used as a traveling drive source. The stator 2 has a multi-phase stator winding 2a, and the rotor unit 3 has a rotating shaft 4 at the shaft core. When used as a vehicle driving source, the rotational force of the electric motor 1 is transmitted to a wheel drive shaft (not shown) via a transmission (not shown). In this case, if the electric motor 1 functions as a generator when the vehicle is decelerated, it can be recovered as regenerative energy in the electric storage device. Further, in the hybrid vehicle, the rotating shaft 4 of the electric motor 1 can be further connected to a crankshaft (not shown) of the internal combustion engine so that it can be used for power generation by the internal combustion engine.

FIG. 6 shows an example of a control system of the electric motor 1 when the electric motor 1 is used as a travel drive source of the vehicle. In this control system, the drive operation and regenerative operation of the electric motor 1 are performed by a power drive unit 41 (hereinafter referred to as “PDU41”) in response to a control command output from the controller 40.
The PDU 41 includes a PWM inverter that performs pulse width modulation (PWM) using a bridge circuit in which transistor switching elements are bridge-connected, and is connected to a high-voltage battery 42 that exchanges electric energy with the electric motor 1. .
The PDU 41 is based on a gate signal (that is, a PWM signal) that is a switching command input from the controller 40 at the time of driving the electric motor 1 or the like. By switching the (shutoff) state, the DC power supplied from the battery 42 is converted into three-phase AC power, and the energization to the stator winding 2a of the electric motor 1 is sequentially commutated, whereby the stator of each phase. AC winding U-phase current Iu, V-phase current Iv and W-phase current Iw are passed through winding 2a.

  As shown in FIGS. 1 to 4, 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 5B) in which the field of the entire field is most weakened, and the magnet mounting slots 7a of the outer peripheral rotor 5 and the inner peripheral rotor 6. , 8a, the pair of permanent magnets 9 are opposed to each other with different polarities (with the same polarity arrangement), so that the field of the entire rotor unit 3 is most strongly strengthened (see FIGS. 2 and 5). (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 a hydraulic control device 13 shown in FIG. 7 for controlling the pressure of the hydraulic fluid supplied to the turning mechanism 11.

  As shown in FIGS. 1 to 4, the rotation mechanism 11 can be relatively rotated on the outer peripheral side of the vane rotor 14 and the vane rotor 14 (first member) that is spline-fitted to the outer periphery of the rotary shaft 4 so as to be integrally rotatable. An annular housing 15 (second member) disposed, and the annular housing 15 is integrally fitted and fixed to the inner peripheral surface of the inner rotor 6, and the vane rotor 14 is connected to the inner periphery of the annular housing 15. The outer rotor 5 is integrally coupled to the outer rotor 5 via a pair of disk-like drive plates 16 and 16 (first member) straddling the side end portions on both sides of the side rotor 6. Therefore, the vane rotor 14 is integrated with the rotary 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 rotary 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.

  Further, the base portion 15a of the annular housing 15 fixed to the inner peripheral rotor 6 is formed in a cylindrical shape having a constant thickness, and is also provided with respect to the inner peripheral rotor 6 and the partition wall 21 as shown in FIG. Projects outward in the axial direction. Each end projecting outward of the base portion 15a is slidably held in an annular guide groove 16a formed in the drive plate 16, and the annular housing 15 and the inner peripheral rotor 6 are connected to the outer peripheral rotor. 5 and the rotating shaft 4 are supported in a floating state.

  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 circumferential rotor 6 is advanced relative to the outer circumferential rotor 5 in the rotational direction of the electric motor 1 indicated by an arrow R in FIGS. 2 and 4. “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 rotating shaft 4. Specifically, 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. 7 and the retard side working chamber 25 is connected to the retard side supply / discharge passage of the hydraulic control device 13. Although connected to the exhaust passage 27, a part of the advance side supply / exhaust passage 26 and the retard side supply / exhaust passage 27 are respectively formed on the rotary shaft 4 along the axial direction as shown in FIG. It is constituted by passage holes 26a and 27a. The end portions of the passage holes 26a and 27a are respectively connected to an annular groove 26b and an annular groove 27b formed at two positions offset in the axial direction of the outer peripheral surface of the rotary shaft 4, and the respective annular grooves 26b and 27b. Are connected to a plurality of conduction holes 26c... 27c formed in the boss portion 17 of the vane rotor 14 along the substantially radial direction. 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.

Here, 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 outer circumferential rotor 5 and the inner circumferential rotor 6 are permanent. The magnets 9 are opposed to each other with different polarities and are in a strong field state (see FIGS. 2 and 5A), and the inner circumferential rotor 6 is at the most advanced position with respect to the outer circumferential rotor 5. Sometimes, the permanent magnets 9 of the outer circumferential rotor 5 and the inner circumferential rotor 6 are set so as to face each other with the same poles to form a field weakening state (see FIGS. 4 and 5B). Yes.
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.

On the other hand, as shown in FIG. 7, the hydraulic control device 13 sucks the hydraulic fluid from an oil tank (not shown) and discharges it to the passage, and the oil pump 32 is discharged from the oil pump 32. The hydraulic pressure of the hydraulic fluid was adjusted and introduced into the high-pressure line passage 33, and the excess hydraulic fluid was introduced into the low-pressure passage 34 for lubricating and cooling various devices, and the hydraulic fluid was introduced into the line passage 33. A flow in which the working fluid is distributed to the advance side supply / discharge passage 26 and the retard side supply / discharge passage 27, and unnecessary working fluid is discharged to the drain passage 36 through the advance side supply / discharge passage 26 and the retard side supply / discharge passage 27. And a path switching valve 37.
The regulator valve 35 receives the pressure of the line passage 33 as a control pressure, and distributes the hydraulic fluid according to the balance with the reaction force spring 38.
Further, the flow path switching valve 37 has an electromagnetic solenoid 37 b that moves the control spool 37 a forward and backward, and the electromagnetic solenoid 37 b is controlled by the controller 40.

  The hydraulic control device 13 further includes an advance side bypass passage 45 that bypasses the flow path switching valve 37 from the upstream position of the flow path switching valve 37 in the line passage 33 and is connected to the advance side supply / discharge passage 26. The retard side bypass passage 46, which bypasses the flow path switching valve 37 from the upstream position of the flow path switching valve 37 in the line passage 33 and is connected to the retard side supply / discharge passage 27, and the advance side bypass passage 45 and the delay side. Normally-closed on-off valves 47A and 47B that open and close the passages 45 and 46, respectively, and electromagnetic valves 48A and 48B that generate signal pressures to open and close the on-off valves 47A and 47B. And a solenoid valve 50 for fixing the valve for introducing the pressure of the line passage 33 into the reaction force chamber 49 of the regulator valve 35 by turning on the solenoid.

  The electromagnetic valves 48A and 48B of the bypass passages 45 and 46 are respectively connected to the corresponding on-off valves 47A and 47B, the signal port P1 conducting to the line passage 33, the pressure introducing port P2 conducting to the line passage 33, and the drain port P3 conducting to the drain passage 44. In response to a control signal (ON / OFF signal) from the controller 40 (see FIG. 6), the signal port P1 is selectively conducted to the pressure introduction port P2 and the drain port P3. Specifically, each of the solenoid valves 48A and 48B is normally turned off, and the corresponding on-off valves 47A and 47B are maintained in the closed state by causing the signal port P1 to be connected to the drain port P3. When a signal is input, the signal port P1 is electrically connected to the pressure introduction port P2, and the corresponding on-off valves 47A and 47B are opened.

  Further, the reaction force chamber 49 of the regulator valve 35 applies the pressure introduced from the line passage 33 to the regulator valve 35 as a force in the same direction as the urging direction of the reaction force spring 38, and is a solenoid valve for fixing the valve. The on / off operation of 50 controls the introduction and shut-off of the pressure in the line passage 33. The electromagnetic valve 50 has a signal port P4 that conducts to the reaction force chamber 49, a pressure introduction port P5 that conducts to the line passage 33, and a drain port P6 that conducts to the drain passage 44, and the electromagnetic valves 48A and 48B. In the same manner as described above, a control signal (ON / OFF signal) is received from the controller 40 (see FIG. 6), and the signal port P4 is selectively conducted to the pressure introduction port P5 and the drain port P6. Specifically, the solenoid valve 50 is normally turned off, the signal port P4 is electrically connected to the drain port P6, and the reaction force chamber 49 is maintained in an atmospheric pressure state, and an on signal is input from the controller 40. Then, the signal port P4 is conducted to the pressure introduction port P5 to introduce the pressure of the line passage 33 into the reaction force chamber 49. When pressure is introduced into the reaction force chamber 49 in this way, the regulator valve 35 substantially disables spool control in accordance with the pressure in the line passage 33 and completely shuts off the low-pressure passage 34 (the total flow rate is reduced to the line passage 33). Switch to the fixed state.

  The solenoid valves 48A and 48B and the solenoid valve 50 for fixing the valve described above are turned off when the normal phase change of the electric motor 1 is performed, and the controller 40 determines that a sudden phase change is necessary (requesting a sudden phase change). For example, when the vehicle is rapidly accelerating or decelerating, when the viscosity of the hydraulic fluid is high in a low temperature environment (when the flow of hydraulic fluid cannot catch up with the phase change request), the ON operation is performed.

  Here, the configuration of the controller 40 shown in FIG. 6 will be described.

  The controller 40 performs current feedback control on the dq coordinates that form the rotation orthogonal coordinates. For example, the d-axis current command is based on the torque command Tq that is set according to the accelerator opening degree related to the accelerator operation of the driver. Idc and q-axis current command Iqc are calculated, and each phase output voltage Vu, Vv, Vw is calculated based on d-axis current command Idc and q-axis current command Iqc, and according to each phase output voltage Vu, Vv, Vw Obtained by outputting a PWM signal as a gate signal to the PDU 41 and converting any two phase currents of the phase currents Iu, Iv, and Iw actually supplied from the PDU 41 to the current on the dq coordinate. Current control is performed such 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 controller 40 also controls the hydraulic control device 13 (of the flow path switching valve 37) to change the phase based on the request command such as the torque command Tq and the actual feedback value of the phase difference between the rotors 6 and 5. and controls the electromagnetic solenoid 37b), further, if the difference command value θc and the feedback value theta ₀ of the phase control is out of allowable setting range, the hydraulic pressure control is determined that there is a request for sudden phase changes Additional control (on-control of the solenoid valves 48A, 48B, 50) is performed on the device 13.

  Specifically, the controller 40 includes a target current setting unit 51, a current deviation calculation unit 52, a field control unit 53, a power control unit 54, a current control unit 55, a dq-3 phase conversion unit 56, and a PWM. Signal generator 57, filter processor 58, 3-phase-dq converter 59, rotation speed calculator 60, induced voltage constant command output unit 83, induced voltage constant calculator 82, and induced voltage constant difference calculation Unit 84, phase control unit 62, required phase difference calculation unit 63, change request determination unit 64, and second phase control unit 65.

  The controller 40 then detects current sensors 71 and 71 for detecting a two-phase U-phase current Iu and a W-phase current Iw among the three-phase currents Iu, Iv, and Iw output from the PDU 41 to the electric motor 1. Detection signals Ius and Iws output from the battery 42, a detection signal output from the voltage sensor 72 for detecting the terminal voltage (power supply voltage) VB of the battery 42, and the rotation angle θM of the rotor unit 3 of the motor 1 (that is, A detection signal output from a resolver 73 (rotation sensor) that detects a rotation angle of a magnetic pole of the rotor unit 3 from a predetermined reference rotation position, a torque command Tq output from an external control device (not shown), and A shift command that is a control command for the transmission gear ratio of the transmission T / M and a control command for a vehicle driving state (for example, a front wheel driving state or a total wheel driving state) That the drive wheel selection command and are inputted.

The target current setting unit 51 is, for example, for causing the electric motor 1 to generate a torque command Tq (for example, a torque required according to the amount by which the driver depresses the accelerator pedal) input from an external control device (not shown). ), The rotational speed NM of the electric motor 1 input from the rotational speed calculation unit 60, and the induced voltage constant Ke, each phase current Iu, Iv, Iw supplied from the PDU 41 to the electric motor 1 is specified. The current command is output to the current deviation calculation unit 52 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 41 to each phase of the electric motor 1.

The current deviation calculation unit 52 includes a d-axis current deviation calculation unit 52a 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 53 and the d-axis current Id, A q-axis target current Iqc to which the q-axis correction current input from the control unit 54 is added and a q-axis current deviation calculating unit 52a that calculates a deviation ΔIq from the q-axis current Iq are configured.
The field control unit 53 performs field weakening control that controls the current phase so as to weaken the field amount of the rotor 23 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 is output as the d-axis correction current.
Further, the power control unit 54 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 18.

  The current control unit 55 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 rotational speed NM, and controls and amplifies the deviation ΔIq to thereby q-axis voltage command. The value Vq is calculated.

  The dq-3 phase conversion unit 56 uses the rotor rotation angle θM input from the rotation speed calculation unit 60 to convert the d-axis voltage command value Vd and the q-axis voltage command value Vq on the dq coordinate in a stationary 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 a certain three-phase AC coordinate.

  For example, the PWM signal generation unit 57 turns on each switching element of the PWM inverter of the PDU 13 by pulse width modulation based on each phase output voltage Vu, Vv, Vw of a sine wave, 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 58 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 71 and 71 to obtain the phase currents Iu and Iw as physical quantities. Extract.

  The three-phase-dq conversion unit 59 uses the phase currents Iu and Iw extracted by the filter processing unit 58 and the rotation angle θM of the rotor unit 3 input from the rotation number calculation unit 60 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 60 extracts the rotation angle θM of the rotor unit 3 of the electric motor 1 from the detection signal output from the resolver 73, 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 calculator 82 receives the detection value θ ₀ from the phase detector 81 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 51 and also input to the induced voltage constant difference calculation unit 84. As the phase detector 81, for example, a sensor that detects a differential pressure between the advance side supply / discharge passage 26 (advance side working chamber 24) and the retard side supply / exhaust passage 27 (retard side operation 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 calculation unit 84 calculates a deviation between the induced voltage constant command value Kec output from the induced voltage constant command output unit 83 and the actual induced voltage constant Ke obtained by the induced voltage constant calculation unit 82. Therefore, the calculated deviation ΔKe of the induced voltage constant is output to the phase controller 62.

  The phase control unit 62 calculates a phase command value θc corresponding to the induced voltage constant deviation ΔKe, and outputs the phase command value θc to the flow path switching valve 37 (electromagnetic solenoid 37b) of the hydraulic control device 13.

The request phase difference calculation unit 63 calculates a difference Δθ between the phase command value θc output from the phase control unit 62 and the detection value θ ₀ output from the phase detector 81, and the change request determination unit 64 It is determined whether or not the difference Δθ calculated by the phase difference calculation unit 63 is out of the set allowable value range.
When the change request determination unit 64 determines that the difference Δθ is out of the set allowable value range, the second phase control unit 65 controls the electromagnetic valves 48A, 48B, 50 of the hydraulic control device 13 to receive control signals (ON signals). Is output.

A control flow in the change request determination unit 64 and the second phase control unit 65 is, for example, as shown in FIG. Hereinafter, this flow will be described. In this flow, it is assumed that the direction in which the inner circumferential rotor 6 advances from the advance side to the retard side is a positive direction.
First, in step S1, reads the difference Δθ of the actual and phase detection value theta ₀ and phase command value .theta.c, in the following step S2, whether the difference Δθ is greater than the phase difference setting value θ1 upper side (positive value) If it is larger than the phase difference set value θ1, the process proceeds to step S3, and if not larger, the process proceeds to step S4.
When the routine proceeds to step 3, the inner circumferential rotor 6 is controlled in the retarding direction, and the deviation width between the phase command value θc and the current phase is out of the set allowable range (that is, in the retarding direction). Since the phase change request is abrupt, an ON signal is output to the solenoid valve 50 and the solenoid valve 48B shown in FIG. As a result, the regulator valve 35 is fixed and the retard side bypass passage 46 is opened.
When the process proceeds to step S4, it is further determined whether or not the difference Δθ is smaller than the lower limit side phase difference set value θ2 (negative value). If the difference Δθ is smaller than the phase difference set value θ2, step S5 is performed. If not, return.
When the process proceeds to step S4, the inner rotor 6 is controlled in the advance direction, and the deviation width between the phase command value θc and the current phase is out of the set allowable range (that is, in the advance direction). Since the phase change request is abrupt, an ON signal is output to the solenoid valve 50 and the solenoid valve 48A shown in FIG. As a result, the regulator valve 35 is fixed and the advance side bypass passage 45 is opened.

Next, the operation of changing the phase of the electric motor 1 will be described.
When the phase of the electric motor 1 is changed to the strong field side, the flow path switching valve 37 shown in FIG. 7 is controlled by a command from the controller 40, and the hydraulic fluid in the line passage 33 is retarded from the flow path switching valve 37. The retarded-side working chamber 25 is supplied to the retarded-side working chamber 25 through the side-feeding / discharging passage 27, and the working fluid in the advance-side working chamber 24 is discharged to the drain passage 36 through the advance-side feeding / discharging passage 26 and the flow path switching valve 37. As a result, the inner rotor 6 and the annular housing 15 shown in FIGS. 1 to 4 are rotated relative to the outer rotor 5 and the vane rotor 14 in the retarded direction, and the electric motor 1 includes both rotors 5. , 6 permanent magnets 9 are phase-shifted in the direction of the strong magnetic field facing each other at different polar surfaces.

  Further, when the phase of the electric motor 1 is changed to the strong field side and the phase change request is abrupt, the solenoid valve 50 and the solenoid valve 48B are turned on by the command from the controller 40 as described above. Then, the regulator valve 35 is fixed in a state where the low pressure passage 34 is closed, and the retard side bypass passage 46 is opened. As a result, the hydraulic fluid supplied from the oil pump 32 side is divided into the main passage on the flow path switching valve 37 side of the line passage 33 and the retard side bypass passage 46, and enters the retard side working chamber 25 with a large flow rate. Supplied. Therefore, as a result, the phase of the electric motor 1 is quickly changed to the strong field side.

  On the other hand, when the phase of the electric motor 1 is changed to the field weakening side, the flow path switching valve 37 is controlled by a command from the controller 40, and the hydraulic fluid in the line passage 33 is supplied to the flow path switching valve 37 and the advance side. The hydraulic fluid is supplied to the advance side working chamber 24 through the exhaust passage 26, and the working fluid in the retard side working chamber 25 is discharged to the drain passage 36 through the retard side supply / exhaust passage 27 and the flow path switching valve 37. As a result, the annular housing 15 rotates relative to the vane rotor 14 in the retarded direction, and the electric motor 1 changes the phase in the field-weakening direction in which the permanent magnets 9 of the rotors 5 and 6 face each other at the same pole surfaces. Is done.

  Also in this case, when the phase change request is abrupt, the solenoid valve 50 and the solenoid valve 48A are turned on, the regulator valve 35 is fixed in the closed state of the low pressure passage 34, and the advance side bypass passage 46 is be opened. As a result, the hydraulic fluid supplied from the oil pump 32 side is divided into the main passage on the flow path switching valve 37 side and the advance side bypass passage 45, and is supplied to the advance side working chamber 24 with a large flow rate. As a result, the phase of the electric motor 1 is rapidly changed to the field weakening side.

  As described above, in the electric motor 1, the flow path switching valve 37 controls the supply and discharge of the hydraulic fluid to the advance side working chamber 24 and the retard side working chamber 25 in response to a request for phase change, and the phase change is performed. When the demand is abrupt, the corresponding bypass passages 45 and 46 can be opened by the electromagnetic valve 48A or 48B, and the flow rate of the working fluid introduced into the working chambers 24 and 25 can be increased. Without using a large solenoid valve (flow path switching valve), the phase of the rotor unit 3 can be freely changed at an arbitrary timing, and it is possible to quickly respond to a sudden phase change request.

  In the case of the electric motor 1, the electromagnetic valves 48A and 48B that control the opening and closing of the bypass passages 45 and 46 do not directly open and close the bypass passages 45 and 46, but the pressure of the line passage 33 is controlled by the electromagnetic valves 48A and 48B. Since the signal pressure is applied to the on-off valves 47A and 47B, a small one having a relatively weak magnetic force can be employed. Therefore, the system of the electric motor 1 can be reduced in size and the manufacturing cost can be reduced.

  Furthermore, in the case of the electric motor 1 of this embodiment, since the valve-fixing electromagnetic valve 50 is provided, the bypass passage 45 or 46 is opened at the time of a sudden phase change request to rapidly increase the introduction flow rate of the working chambers 24 and 25. In this case, a sufficient supply flow rate in the line passage 33 can be stably maintained.

  In the embodiment described above, the bypass passages 45 and 46 and the corresponding on-off valves 47A and 47B and electromagnetic valves 48A and 48B are provided on both the retard side and the advance side. It may be provided only on either the advance side or the retard side according to the specifications of the vehicle. In this case, the solenoid valve for fixing the valve can be shared with the solenoid valve for operating the on-off valve.

9 and 10 show a second embodiment and a third embodiment of the present invention, respectively.
The electric motors 1 of these embodiments are different from those of the first embodiment in the configuration of the rotation mechanisms 111 and 211 of the phase changing means 12, and the other configurations are substantially the same as those in the first embodiment. The same is said. Accordingly, the same parts as those in the first embodiment are denoted by the same reference numerals, and the description of the overlapping parts is omitted.

  The rotating mechanism 111 of the second embodiment shown in FIG. 9 includes a bobbin-shaped inner cylinder member 112 (first member) that is spline-fitted to the outer surface of the rotating shaft 4 so as to be integrally rotatable, and the inner cylinder member 112. A cylindrical outer cylinder member 113 (second member) disposed on the outer peripheral side, and the outer cylinder member 113 is integrally fitted and fixed to the inner peripheral surface of the inner peripheral side rotor 6. Both side walls 112a, 112a on the axially outer side of the member 112 are on the outer peripheral side through a pair of drive plates 114, 114 (first member) straddling the outer cylindrical member 113 and the side end portions on both sides of the inner peripheral side rotor 6. The rotor 5 is integrally connected. In the case of the rotating mechanism 111, the inner cylinder member 112 is integrated with the rotating shaft 4 and the outer rotor 5, and the outer cylinder member 113 is integrated with the inner rotor 6.

  A cylindrical introduction space in which an outer cylinder member 113 is slidably fitted to the outer peripheral surfaces of both side walls 112 a of the inner cylinder member 112 and hydraulic fluid is introduced between the inner cylinder member 112 and the outer cylinder member 113. 115 is formed. A thick portion 113a (cylindrical portion) protruding radially inward is formed at a substantially intermediate position in the axial direction of the inner peripheral surface of the outer cylindrical member 113. The inner peripheral surface of the thick portion 113a and the inner cylindrical member 112 Helical splines 116 and 117 having opposite directions are formed on the outer peripheral surface of a substantially half portion (left region in the drawing) of the shaft portion 112b. Between the shaft portion 112a of the inner cylinder member 112 and the outer cylinder member 113, a ring gear 118 that is engaged with the helical splines 117 and 116 on the inner periphery and outer periphery thereof is interposed. In addition, helical splines that mesh with the helical splines 117 and 116 of the inner cylindrical member 112 and the outer cylindrical member 113 are formed on the inner peripheral surface and the outer peripheral surface of the ring gear 118. These helical splines are denoted by the reference numerals in the figure. Shall be omitted.

  Further, the ring gear 118 is formed in a double cylindrical shape having one end connected by a sealing wall 119, and one end of the outer peripheral wall on the side where the sealing wall 119 of the ring gear 118 is extended to a cylindrical shape, Is provided with a flange 120 projecting radially outward. The outer peripheral surface of the flange portion 120 is slidably fitted to the inner peripheral surface of a substantially half portion of the outer cylinder member 113 where the helical spline 116 is not formed via a seal ring 121. A piston 122 that divides the inside of the introduction space 115 into two front and rear chambers is formed from the sealing wall 119 at one end of the ring gear 118 to the flange portion 120, and thus one of the chambers separated by the piston 122 operates on the advance side. The chamber 24 and the other chamber are set as the retard side working chamber 25. The advance side working chamber 24 and the retard side working chamber 25 are respectively connected to an advance side supply / discharge passage 26 and a retard side supply / discharge passage 27 formed from the inner cylinder member 112 to the rotating shaft 4. ing. The advance side supply / discharge passage 26 and the retard side supply / discharge passage 27 are connected to a hydraulic control device (not shown) similar to that of the first embodiment.

  In the case of the rotation function 111 of this embodiment, when the working fluid is supplied to one of the advance side working chamber 24 and the retard side working chamber 25 and the working fluid is discharged from the other, the ring gear 118 including the piston 122 is The inside of the introduction space 115 moves from one side to the other in accordance with the differential pressure across the front and back. At this time, the inner cylinder member 112 and the outer cylinder member 113 engaged with the ring gear 118 by the helical splines 117 and 116 rotate relative to one side. Thus, the inner rotor 6 is rotated forward or retarded with respect to the outer rotor 5. Conversely, when the hydraulic fluid is supplied to the other of the advance side working chamber 24 and the retard side working chamber 25 and the hydraulic fluid is discharged from one, the ring gear 118 including the piston 122 causes the differential pressure between the front and rear. Accordingly, the inside of the introduction space 115 is moved from the other side to the other side, and similarly, the inner circumferential rotor 6 is rotated to the retard side or the advanced side with respect to the outer circumferential rotor 5.

In the case of the rotation mechanism 111, the inner rotor 5 and the outer rotor 6 can be reliably rotated relative to each other at a desired position by the hydraulic pressure controlled by the hydraulic control device, although having a simple structure. .
In the embodiment shown in FIG. 9 described here, the piston 122 that divides the introduction space 115 into two chambers is formed integrally with the ring gear 118, but the piston and the ring gear are formed separately from each other, You may make it couple | bond both by a connection member.

  Further, the rotation mechanism 211 of the third embodiment shown in FIG. 10 includes an inner block 212 (first member) that is spline-fitted to the outer surface of the rotating shaft 4 so as to be integrally rotatable, and an outer peripheral side of the inner block 212. A substantially cylindrical outer block 213 (second member) disposed on the inner block 212, and the outer block 213 is integrally fitted and fixed to the inner peripheral surface of the inner rotor 6 and the shaft of the inner block 212 is fixed. The end in the direction is integrally coupled to the outer rotor 5 via a drive plate (first member) (not shown) that straddles the outer block 213 and the side end of the inner rotor 6. In the case of this rotating mechanism 211, the inner block 212 is integrated with the rotating shaft 4 and the outer peripheral rotor 5, and the outer block 213 is integrated with the inner peripheral rotor 6.

  The inner block 212 is provided with a pair of arms 212a projecting outward in the radial direction, and the ends of the arms 212a are opposite to each other along the substantially tangential direction of the circumference around the rotation shaft 4. A first cylinder 214 and a second cylinder 215 are formed. A first piston 216 and a second piston 217 are fitted to the first cylinder 214 and the second cylinder 215 of both arm portions 212a so as to be able to advance and retract, and correspond to the cylinders 214 and 215. The hydraulic fluid for moving the pistons 216 and 217 forward and backward is supplied and discharged. The first cylinder 214 opens toward the main rotation direction of the electric motor 1 to form an advance side working chamber 24 with the first piston 216, and the second cylinder 215 is opposite to the main rotation direction. The retard side working chamber 25 is formed between the second piston 217 and the second piston 217. The advance side working chamber 24 and the retard side working chamber 25 are connected via a supply / exhaust passage (only the retard side supply / exhaust passage 27 is shown in the figure) formed from the inner block 212 to the rotating shaft 4. Are connected to the same hydraulic control apparatus as in the first embodiment. The pistons 216, 217 are formed in a substantially cylindrical shape with the top portions 216a, 217a sealed, and the outer surfaces of the top portions 216a, 217a are formed in a spherical shape.

  On the other hand, the outer block 213 includes a cylindrical base portion 213a that is fitted and fixed to the inner peripheral rotor 6, and a pair of raised portions 213b and 213b that bulge radially inward from the inner peripheral surface of the base portion 213a. Is provided. Each of the raised portions 213b has a first load transmission wall 218 that is in contact with the top 216a of the first piston 216 of the inner block 212 along the radial direction of the rotation shaft 4, and similarly to the radial direction of the rotation shaft 4. A second load transmission wall 219 is formed along the top block 217a of the second piston 217 of the inner block 212.

  In the case of this embodiment, for example, when the working fluid is supplied to the advance side working chamber 24 and the working fluid is discharged from the retard side working chamber 25, the first piston of the inner block 212 as shown in FIG. 216 protrudes while the second piston 217 is retracted. At this time, the first piston 216 presses the first load transmission wall 218 of the outer block 213 and advances the outer block 213 relative to the inner block 212. Rotate in the angular direction. As a result, the inner circumferential rotor 6 integral with the outer block 213 rotates in the advance direction with respect to the outer circumferential rotor 5 integral with the inner block 212. On the other hand, when the working fluid is supplied to the retard side working chamber 25 and the working fluid is discharged from the advance side working chamber 24 from this state, the second piston 217 protrudes while the first piston 216 is projected. Retreats, and the second piston 217 presses the second load transmission wall 219 of the outer block 213 to rotate the inner rotor 6 in the retard direction with respect to the outer rotor 5.

  Even in the case of the rotation mechanism 211, the inner rotor 5 and the outer rotor 6 can be reliably rotated relative to each other by hydraulic pressure, though the structure is simple.

  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.

1 is a cross-sectional view of a main part of an electric motor according to a first embodiment of the present invention. 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 disassembled perspective view of the rotor unit 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 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 phase change means of the embodiment. The hydraulic circuit diagram of the phase change means of the embodiment. The flow chart which shows a part of flow of the phase change control of the embodiment. Sectional drawing of the principal part of the electric motor of 2nd Embodiment of this invention. Sectional drawing of the principal part of the electric motor of 3rd Embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Electric motor 5 ... Outer peripheral side rotor 6 ... Inner peripheral side rotor 9 ... Permanent magnet 12 ... Phase change means 14 ... Vane rotor (1st member)
15 ... Annular housing (second member)
16 ... Drive plate (first member)
18 ... Vane 23 ... Introduction space 24 ... Advance side working chamber 25 ... Delay side working chamber 32 ... Oil pump (fluid supply source)
37 ... Flow path switching valve 45 ... Advance side bypass passage (bypass passage)
46 ... retard side bypass passage (bypass passage)
47A, 47B ... open / close valve 48A, 48B ... solenoid valve
62 ... Phase control section (phase control means)
81 ... Phase detector 112 ... Inner cylinder member (first member)
112a ... Shaft 113 ... Outer cylinder member (second member)
113a ... Thick part (cylinder part)
114 ... Drive plate (first member)
115: Introduction space 118 ... Ring gear 122 ... Piston 212 ... Inner block (first member)
213 ... Outer block (second member)
214 ... 1st cylinder 215 ... 2nd cylinder 216 ... 1st piston 217 ... 2nd piston 218 ... 1st load transmission wall 218 ... 2nd load transmission wall

Claims (5)

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;
A phase changing means for changing the relative phase of the inner and outer rotors by relatively rotating the inner rotor and the outer rotor,
The phase changing means is
An advance side working chamber for rotating the inner circumference side rotor relative to the outer side rotor in the advance direction by the pressure of the working fluid introduced inside;
A retarding-side working chamber that rotates the inner circumferential rotor relative to the outer circumferential rotor in the retarding direction by the pressure of the working fluid introduced therein;
A fluid supply source for supplying the working fluid;
A flow path switching valve for distributing the supply and discharge of the working fluid to the advance side working chamber and the retard side working chamber in response to a request for phase change;
A bypass passage provided between the fluid supply source and the advance side working chamber and at least one of the fluid supply source and the retard side working chamber so as to bypass the flow path switching valve;
An on-off valve interposed in the bypass passage;
A phase detector for outputting a detected value of the relative phase;
Phase control means for outputting a command value of the relative phase;
With
The electric motor characterized in that the phase changing means opens the on-off valve when a difference between the detected value of the relative phase and the command value is out of a predetermined range . A working fluid introduction space is provided between a first member that rotates integrally with the outer circumferential rotor and a second member that rotates integrally with the inner circumferential rotor,
One of the first member and the second member is provided with a vane that is slidably disposed in the introduction space and separates the introduction space into two chambers,
The electric motor according to claim 1, wherein the advance side working chamber and the retard side working chamber are configured by two chambers separated by the vane. 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;
A phase changing means for changing the relative phase of the inner and outer rotors by relatively rotating the inner rotor and the outer rotor,
The phase changing means is
An advance side working chamber for rotating the inner circumference side rotor relative to the outer side rotor in the advance direction by the pressure of the working fluid introduced inside;
A retarding-side working chamber that rotates the inner circumferential rotor relative to the outer circumferential rotor in the retarding direction by the pressure of the working fluid introduced therein;
A fluid supply source for supplying the working fluid;
A flow path switching valve for distributing the supply and discharge of the working fluid to the advance side working chamber and the retard side working chamber in response to a request for phase change;
A bypass passage provided between the fluid supply source and the advance side working chamber and at least one of the fluid supply source and the retard side working chamber so as to bypass the flow path switching valve;
An on-off valve interposed in the bypass passage,
A shaft portion is provided on one of a first member that rotates integrally with the outer circumferential rotor and a second member that rotates integrally with the inner circumferential rotor,
The other of the first member and the second member is provided with a cylindrical portion surrounding the outside of the shaft portion,
A ring gear is provided in which an inner peripheral surface and an outer peripheral surface are helically spline-engaged with the shaft portion and the cylindrical portion, respectively.
A working fluid introduction space is provided between the first member and the second member,
A piston that is slidably accommodated in the introduction space and that separates the introduction space into two chambers is provided,
This piston is connected to the ring gear so as to be integrally displaceable,
The electric motor characterized in that the advance side working chamber and the retard side working chamber are constituted by two chambers separated by the piston. 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;
A phase changing means for changing the relative phase of the inner and outer rotors by relatively rotating the inner rotor and the outer rotor,
The phase changing means is
An advance side working chamber for rotating the inner circumference side rotor relative to the outer side rotor in the advance direction by the pressure of the working fluid introduced inside;
A retarding-side working chamber that rotates the inner circumferential rotor relative to the outer circumferential rotor in the retarding direction by the pressure of the working fluid introduced therein;
A fluid supply source for supplying the working fluid;
A flow path switching valve for distributing the supply and discharge of the working fluid to the advance side working chamber and the retard side working chamber in response to a request for phase change;
A bypass passage provided between the fluid supply source and the advance side working chamber and at least one of the fluid supply source and the retard side working chamber so as to bypass the flow path switching valve;
An on-off valve interposed in the bypass passage,
One of the first member that rotates integrally with the outer circumferential rotor and the second member that rotates integrally with the inner circumferential rotor is mutually reciprocal along a substantially tangential direction of the circumference around the rotation axis. A first cylinder and a second cylinder facing the rotating direction are provided,
A first piston and a second piston are respectively provided in the first cylinder and the second cylinder so as to freely advance and retract,
The other of the first member and the second member is provided with a first load transmission wall and a second load abutting on tops of the first piston and the second piston, respectively, along a substantially radial direction of the two rotors. A load transmission wall is provided,
The advance side working chamber and the retard side working chamber are respectively configured between the first cylinder and the first piston and between the second cylinder and the second piston. Electric motor. An electromagnetic valve for generating a signal pressure by switching between introduction and discharge of the pressure of the working fluid supplied from the fluid supply source is provided, and the on-off valve is opened and closed by the signal pressure generated by the electromagnetic valve. Item 5. The electric motor according to any one of Items 1 to 4.

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