JP2008259298A - Motor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a motor which changes the phase by turning two rotors, using the pressure of fluid such as hydraulic pressure, etc., and prevents the leakage of the fluid. <P>SOLUTION: The motor 10 includes first and second rotors 42a and 42b which are magnetized severally and a phase changing mechanism which changes a phase that shows the relative displacement angle of both by turning at least either the first rotor or the second rotor around the axis of rotation. The motor includes a working chamber (a leading angle side working chamber 54c) where the phase changing mechanism elongates or contracts, being supplied with pressure (hydraulic pressure) of fluid or discharged of it, thereby changing the above phase by rotating at least either the first rotor or the second rotor. The working chamber is provided with a bag-form body 72 which is connected fluid-tightly to a passage (oil path 62c, etc.) which supplies the pressure of fluid or discharges it. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an electric motor, and more specifically, to an electric motor in which two magnetized rotors are rotated to change a phase indicating a relative displacement angle therebetween.

  As an example of an electric motor in which two magnetized rotors are rotated to change the phase indicating the relative displacement angle between them, a technique described in Patent Document 1 below can be cited. In the technique described in Patent Document 1, when the phase of the two rotors is changed according to the rotational speed of the electric motor, the two rotations are performed via a member that is displaced along the radial direction by the action of centrifugal force. One of the children is configured to rotate in the circumferential direction.

Also, when the phase is changed according to the speed of the rotating magnetic field generated in the stator, the control current is supplied to the stator winding while the two rotors maintain the rotating speed due to inertia, and the rotating magnetic field speed is increased. By changing, the relative position in the circumferential direction is changed.
JP 2002-204541 A

  In the technology described in Patent Document 1, the conditions under which the phase can be changed are limited, and cannot be changed arbitrarily when the motor is stopped or rotated arbitrarily. Therefore, instead of mechanical force such as centrifugal force, It is conceivable to change the phase by rotating two rotors using the pressure of a fluid such as hydraulic pressure. However, if the phase is changed by using the pressure of a fluid such as hydraulic pressure, the fluid may leak. If the fluid leaks, new inconveniences such as lowering the accuracy and responsiveness of the phase change control occur. .

  Accordingly, an object of the present invention is to eliminate the above-described problem, and to change the phase by rotating two rotors using the pressure of fluid such as hydraulic pressure, and to prevent fluid leakage. It is to provide an electric motor.

  In order to achieve the above object, according to claim 1, the first and second rotors magnetized and at least one of the first and second rotors are centered on the rotation axis. And a phase change mechanism that changes the phase indicating the relative displacement angle of the both, and the phase change mechanism expands and contracts when fluid pressure is supplied and discharged, and thus the first and second A working chamber that changes the phase by rotating at least one of the rotors is provided, and a bag-like body that is liquid-tightly connected to a passage for supplying and discharging the fluid pressure is provided in the working chamber. did.

  The electric motor according to claim 2 is configured such that the bag-like body is formed of a bellows-like body that can expand and contract in the circumferential direction.

  The electric motor according to claim 3 is configured such that the bag-like body is formed of an elastic body.

  In the electric motor according to claim 4, the phase change mechanism is fixed to a vane fixed to one of the first and second rotors and to the other of the first and second rotors. A partition wall is provided, and the working chamber is formed between the vane and the partition wall.

  In the electric motor according to claim 1, the phase change mechanism expands and contracts by supplying and discharging the fluid pressure, and thus the working chamber changes the phase by rotating at least one of the first and second rotors. And a bag-like body that is liquid-tightly connected to the passage for supplying and discharging the fluid pressure is provided in the working chamber, so that the fluid can be prevented from leaking in or near the working chamber. Therefore, it is possible to avoid a decrease in accuracy and response of phase change control.

  In the electric motor according to claim 2, since the bag-like body is configured to be a bellows-like body that can expand and contract in the circumferential direction, in addition to the above effects, the bag-like body is bitten in the working chamber. There is nothing.

  In the electric motor according to claim 3, since the bag-like body is formed of an elastic body, in addition to the above-described effects, the discharge of fluid can be promoted, and the accuracy and responsiveness of phase change control can be promoted. Can be raised.

  In the electric motor according to claim 4, the phase changing mechanism includes a vane fixed to one of the first and second rotors and a partition wall fixed to the other of the first and second rotors. Since the working chamber is formed between the vane and the partition wall, in addition to the effects described above, a working chamber that is expanded and contracted by supplying and discharging the fluid pressure is formed between the vane and the partition wall. Thus, the phase can be changed by rotating the other rotor fixed to the partition wall with respect to the vane fixed to one rotor, so that the working chamber or The fluid can be prevented from leaking in the vicinity thereof.

  The best mode for carrying out the electric motor according to the present invention will be described below with reference to the accompanying drawings.

  FIG. 1 is a schematic diagram showing an overall configuration when an electric motor according to a first embodiment of the present invention is mounted on a hybrid vehicle. For simplification of illustration, the illustration of the sensor and the actuator is omitted in FIG.

  In FIG. 1, reference numeral 10 denotes an electric motor. More specifically, the electric motor 10 includes a brushless motor or an AC synchronous motor. Reference numeral 12 denotes a gasoline injection spark ignition type 4-cylinder engine (internal combustion engine), and its output is input to the transmission 16 via the drive shaft 14. The transmission 16 is composed of an automatic transmission, and is connected to drive wheels 20 of a hybrid vehicle (not shown) on which the electric motor 10 and the engine 12 are mounted, shifts engine output, and transmits it to the drive wheels 20 to transmit the hybrid vehicle. Let it run. Thus, in this embodiment, the electric motor 10 is mounted on a parallel hybrid vehicle.

  The electric motor 10 and the engine 12 are connected to the transmission 16 via a clutch (not shown). The electric motor 10 always rotates when the engine 12 rotates, and is energized at the time of starting to crank and start the engine 12, and is also energized at the time of acceleration or the like to assist the rotation of the engine 12 (acceleration). When the electric motor 10 is not energized, the motor 10 idles as the engine 12 rotates, and at the time of deceleration when the fuel supply to the engine 12 is stopped, the kinetic energy generated by the rotation of the drive shaft 14 is converted into electric energy and output. It functions as a generator having a function.

  The electric motor 10 is connected to a battery 24 via a power drive unit (referred to as “PDU”) 22. The PDU 22 includes an inverter, converts direct current (electric power) supplied (discharged) from the battery 24 to alternating current and supplies the alternating current to the electric motor 10, and converts alternating current generated by the regenerative operation of the electric motor 10 into direct current and converts the direct current (electric power) into direct current. To supply. In this way, driving / regeneration of the electric motor 10 is controlled via the PDU 22. This will be described later.

  Further, an engine control unit (referred to as “ENGECU”) 26 that controls the operation of the engine 12, a motor control unit (referred to as “MOTECU”) 30 that controls the operation of the electric motor 10, and a state of charge (SOC) of the battery 24. A battery control unit (referred to as “BATECU”) 32 that calculates charge and discharge and the like, and a shift control unit (referred to as “T / MECU”) that controls the operation of the transmission 16 are provided. All the ECUs (electronic control units) such as the above-described ENGECU 26 are composed of a microcomputer, and are connected to each other via a bus 36 so as to be able to communicate with each other.

  2 is a cross-sectional view of the main part of the electric motor 10 shown in FIG. 1, FIG. 3 is a side view of the rotor of the electric motor 10 shown in FIG. 2, and FIG. 4 is an exploded perspective view showing a phase change mechanism of the electric motor shown in FIG. FIG. 5 is a schematic view showing the orientation of the magnetic poles of the rotor magnet shown in FIG. 3 and the like, and FIG. 6 is a side view of the rotor of the electric motor 10 shown in FIG.

  As shown in the figure, the electric motor 10 includes an annular stator (stator) 40, a similarly annular rotor 42 housed therein, and a rotation shaft (rotation axis) 44. The stator 40 is formed by laminating thin plates manufactured from iron-based materials (or casting iron-based materials), and is arranged with three-phase (U, V, W-phase) stator windings 40a.

  The rotor 42 includes an outer peripheral side (first) rotor 42 a and an inner peripheral side (second) rotor 42 b that is relatively displaceable about a rotating shaft (rotating axis) 44. The rotors 42a and 42b are made of, for example, iron cores made of sintered metal, and a plurality of sets, more precisely 16 sets of permanent magnets 46 are arranged on the circumferential side at a slight distance from each other. . As shown in FIG. 5, each set of permanent magnets 46 is arranged so that the magnetic poles face each other.

  As shown in FIG. 4, the rotor 42 is provided with a phase changing mechanism 50. The phase changing mechanism 50 includes a vane rotor 52 that is fixed to the rotating shaft 44 via a spline (not shown), an annular housing 54 that is fitted and fixed to the inner peripheral surface of the rotor 42b on the inner peripheral side, The vane rotor 52 includes a pair of drive plates 56 that fix the vane rotor 52 to the outer rotor 42a with pins 56a, an operation chamber (described later) provided in the annular housing 54, and a hydraulic mechanism (described later) that supplies hydraulic pressure thereto.

  The vane rotor 52 is formed with a plurality of (six) vanes 52a protruding from the central boss portion at equal intervals in the radial direction, and protrudes at equal intervals to the center side inside the annular housing 54. A plurality (six) of partition walls 54a are formed. Seal members 52b and 54b are disposed at the tips of the vane 52a and the partition wall 54a, respectively, and provide a fluid-tight seal between the vane 52a and the inner wall surface of the annular housing 54 and between the partition wall 54a and the outer peripheral surface of the boss portion of the vane rotor 52. .

  As shown in FIG. 2, the annular housing 54 has an axial length (width) that is larger than that of the rotor 42 b on the inner peripheral side, and is freely movable in an annular groove 56 a formed in two drive plates 56. Therefore, the annular housing 54 and the inner peripheral rotor 42 b are rotatably supported by the outer peripheral rotor 42 a and the rotation shaft 44.

  The two drive plates 56 are slidably brought into close contact with both side surfaces of the annular housing 54, and a plurality of (6) sealed spaces are formed between the partition wall 54 a of the annular housing 54 and the outer peripheral surface of the boss portion of the vane rotor 52. )Form. This sealed space is divided into two by the vane 52a of the vane rotor 52 to form an advance side working chamber 54c and a retard side working chamber 54d. Here, the “advance angle” (ADV) means that the rotor 42b on the inner circumference side is in the same direction as the rotation direction of the electric motor 10 indicated by an arrow ADV (FIG. 3 or the like) with respect to the rotor 42a on the outer circumference side. “Delay” (RTD) means rotating in the opposite direction.

  In the advance side working chamber 54c and the retard side working chamber 54d, the operation of fluid pressure, specifically, incompressible fluid, more specifically, ATF of the transmission 16 (or lubricating oil of the engine 12), etc. Oil pressure, that is, oil pressure is supplied. The hydraulic oil is supplied from the rotary shaft 44 to the advance side working chamber 54c and the retard side working chamber 54d through two oil passages 62 and 64 formed in the vane rotor 52.

  The oil passages 62 and 64 are substantially parallel to each other. As shown in FIGS. 2 and 3, the oil passages 62 a and 64 a drilled in the axial direction of the rotating shaft 44 and the outer peripheral surface of the rotating shaft 44 are continuously formed. It consists of 62b and 64b drilled, and 62c and 64c radially drilled in the boss part of the vane rotor 52 continuously. The oil passage 62 is connected to the advance side working chamber 54c, and the oil passage 64 is connected to the retard side working chamber 54d, and hydraulic pressure is supplied to and discharged from a reservoir described later.

  The advance-side working chamber 54c and the retard-side working chamber 54d are expanded and contracted by supplying and discharging hydraulic pressure, so that the inner peripheral side integrated with the partition wall 54a with respect to the vane 42a fixed to the outer rotor 42a. The rotor 42b is rotated about the rotation axis (rotation axis) 44, so that the phase indicating the relative displacement angle between the outer rotor 42a and the inner rotor 42b is 0 to 180 degrees. The induced voltage of the electric motor 10 is changed accordingly.

  3 shows the retard side working chamber 54d (and the advance side working chamber 54c) when in the most retarded position, and FIG. 6 shows the advance side working chamber 54c (and the retard side) when in the most advanced position. The working chamber 54d) is shown.

  In the electric motor 10 according to this embodiment, when the inner circumferential side rotor 42b is at the most retarded angle position (phase 0 degree) with respect to the outer circumferential side rotor 42a, as shown in FIG. In addition, the permanent magnets 46 are opposed to each other and become a strong field (increasing field). On the other hand, when the inner circumferential side rotor 42b is at the most advanced angle position (phase 180 degrees) with respect to the outer circumferential side rotor 42a, as shown in FIG. They face each other and become field weakening (field reduction).

  Thereby, the induced voltage constant Ke of the electric motor 10 is changed, and the characteristics of the electric motor 10 are changed. That is, when the induced voltage constant Ke increases due to the strong field, the allowable rotational speed at which the motor 10 can operate decreases, but the maximum torque that can be output increases, and conversely, when the induced voltage constant Ke decreases due to the weak field. The maximum torque that can be output decreases, and the allowable rotational speed increases.

  The electric motor 10 according to this embodiment is stable when the inner rotor 42b is at the most retarded position (phase 0 degree) with respect to the outer rotor 42a. That is, when a failure occurs and the supply of hydraulic pressure becomes impossible, the rotor 42 is relatively displaced toward the most retarded position and stops at that position.

  FIG. 7 is a hydraulic circuit diagram of the above-described hydraulic mechanism (indicated by reference numeral 70) that supplies hydraulic pressure to the advance side working chamber 54c and the retard side working chamber 54d via the oil passages 62 and 64.

  As illustrated, the hydraulic mechanism 70 includes a hydraulic pump 70c that pumps hydraulic oil from the reservoir 70a through the filter 70b and discharges it as line pressure (high pressure), a second electric motor 70d that drives the hydraulic pump 70c, 4 port for supplying and discharging hydraulic pressure to the advance side working chamber 54c or the retard side working chamber 54d through the inverter circuit (INV) 70e for controlling the driving of the motor 70d and the oil passages 62 and 64 described above. It consists of a valve (direction switching valve) 70f and a linear solenoid valve 70g for switching the 4-port valve 70f.

  The linear solenoid valve 70g is inserted between the hydraulic pump 70c and the 4-port valve 70f, and the spool has a first position where the line pressure is applied to the spool (not shown) of the 4-port valve 70f, and the operating pressure is drained. It is possible to switch between the second positions, and outputs a hydraulic pressure adjusted by PWM control of the solenoid. A broken line shows a relief valve system.

  The 4-port valve 70f connects the line pressure to the advance side working chamber 54c, while the spool connects the first position to drain the retard side working chamber 54d, and connects the line pressure to the retard side working chamber 54d. In addition, it is configured to be switchable between a second position for draining the advance side working chamber 54c and a neutral position for closing the four ports between the second position and biasing to the second position with a spring. Is done.

  Specifically, for the 4-port valve 70f, the second position is selected when no hydraulic pressure is applied from the linear solenoid valve 70g, and the neutral position is selected when a relatively small hydraulic pressure is applied from the linear solenoid valve 70g. When the hydraulic pressure from the linear solenoid valve 70g increases, the first position is selected.

  More specifically, the most advanced angle position (phase 180 degrees) that is completely switched to the first position by adjusting the output pressure by PWM control of the energization of the linear solenoid valve 70g, between the first position and the neutral position Freely adjust the phase between any advance position, neutral position, any retard position between the neutral position and the second position, and the most retarded position (phase 0 degree) that can be completely switched to the second position. Can be changed.

  Note that the phase is controlled in accordance with command information such as the operating state of the motor 10, such as the rotational speed and power supply voltage, and the current command value, but the phase change control itself is not directly related to the gist of the present invention. The description is omitted.

  Next, the characteristics of this embodiment will be described. As described above, when the phase is changed by using the pressure of a fluid such as a hydraulic pressure, there is a risk that the hydraulic oil (hydraulic pressure) leaks, and the hydraulic oil leaks. This causes new inconveniences such as lowering the accuracy and responsiveness of the phase change control.

  The six advance-side working chambers 54c and the retard-side working chamber 54d are each formed in a space sealed by the vane 52a, the partition wall 54a, and the drive plate 56, and at the tips of the vane 52a and the partition wall 54a, respectively. Seal members 52b and 54b are arranged, and are configured to liquid tightly seal between the vane 52a and the inner wall surface of the annular housing 54 and between the partition wall 54a and the outer peripheral surface of the boss portion of the vane rotor 52. Easily leaks into the working chamber. Therefore, in this embodiment, the leakage is prevented from the intention.

  8 and 9 are enlarged partial sectional views in the vicinity of the advance side working chamber 54c shown in FIG. In the following description, the advance side working chamber 54c is taken as an example, but the same applies to the retard side working chamber 54d.

  As shown in the figure, the advance side working chamber 54c is configured to be provided with a bag-like body 72 that is liquid-tightly connected to a passage 62c that supplies and discharges hydraulic pressure. The bag-like body 72 is formed of a stretchable elastic body such as rubber. For convenience of illustration, the thickness of the bag 72 is exaggerated.

  FIG. 8 shows a case where the hydraulic oil is supplied and the advance side working chamber 54c, and thus the bag-like body 72 is extended (enlarged) to the most advanced position as indicated by an arrow. Since the bag-like body 72 is formed of an elastic body, the bag-like body 72 expands in accordance with the hydraulic pressure inside the advancing-side working chamber 54c having irregularities, and an oil pressure is applied to almost the entire wall surface of the partition wall 54a to thereby separate the partition wall. 54a is rotated (relatively displaced) with respect to the vane 52a.

  FIG. 9 shows a case where the hydraulic oil is discharged and the advance side working chamber 54c, and thus the bag-like body 72 is reduced to a medium advance position as indicated by an arrow. In this case, since the bag-like body 72 is contracted by the elastic force, the discharge of the hydraulic oil is promoted. The bag-like body 72 is provided in all of the six advance side working chambers 54c and the retard side working chambers 54d on the advance side and the retard side.

  Since the electric motor 10 according to this embodiment is configured as described above, hydraulic oil leaks in the vicinity of the advance side working chamber 54c (and the retard side working chamber 54d) or the oil passage 62c (and 64c). Therefore, it is possible to prevent the deterioration of the accuracy and response of the phase change control.

  Further, since the bag-like body 72 is configured to be formed of a stretchable elastic body, in addition to the effects described above, it is possible to promote the discharge of hydraulic oil, and to improve the accuracy and responsiveness of phase change control. it can.

  The phase changing mechanism 50 includes a vane 52a fixed to the outer rotor 42a, a partition wall 54a fixed to the inner rotor 42b, and an advance side working chamber 54c and a retard side. Since the working chamber 54d is configured to be formed between the vane 52a and the partition wall 54a, in addition to the above-described effects, the advance side working chamber 54c and the retard side working chamber 54d that are expanded and contracted by supplying and discharging fluid pressure. Is formed between the vane 52a and the partition wall 54a so that the inner peripheral rotor 42b fixed to the partition wall 54a is rotated with respect to the vane 52a fixed to the outer rotor 42a. The phase can be changed. Therefore, it is possible to prevent the fluid from leaking in the advance side working chamber 54c, the retard side working chamber 54d, or the vicinity thereof while changing the phase with certainty.

  FIG. 10 is an enlarged partial sectional view of the vicinity of the advance side working chamber 54c shown in FIG. 6, similarly to FIG. 8, showing the electric motor according to the second embodiment of the present invention.

  In the second embodiment, as shown in the figure, a bag-like body 72 is provided that is liquid-tightly connected to a passage 62c that supplies and discharges hydraulic pressure to the advance side working chamber 54c. The bellows-like body 72a can be expanded and contracted in the circumferential direction. The bellows-like body 72a is also formed of a stretchable elastic body such as rubber.

  FIG. 10 shows the case where the hydraulic oil is supplied and the advance side working chamber 54c, and therefore the bellows-like body 72a, extends (enlarges) to the most advanced position as indicated by the arrow. Since the bellows-like body 72a is formed of an elastic body, the bellows-like body 72a expands in accordance with the hydraulic pressure inside the advancing-side working chamber 54c having projections and depressions, and an oil pressure is applied to almost the entire wall surface of the partition wall 54a to cause the vane 52a The partition wall 54a is rotated (relatively displaced). Further, since the bellows-like body 72a can be expanded and contracted in the circumferential direction, the bellows-like body 72a is not caught between the vane 52a and the circumferential surface of the annular housing 54 or between the drive plate 56 and the like.

  Although the illustration of the state in which the hydraulic oil is discharged is omitted, the bellows-like body 72a contracts due to the elastic force, so that the discharge of the hydraulic oil is not different from the case of the first embodiment.

  Since the electric motor 10 according to the second embodiment is configured as described above, as in the first embodiment, the advance side working chamber 54c (and the retard side working chamber 54d) or the oil passage 62c (and 64c), etc. It is possible to reliably prevent the hydraulic oil from leaking in the vicinity of, so that it is possible to avoid deterioration of the accuracy and responsiveness of the phase change control.

  Further, since the bellows-like body 72a is formed of an elastic body that can be expanded and contracted, in addition to the above-described effects, it is possible to promote the discharge of hydraulic oil and to improve the accuracy and responsiveness of the phase change control. In addition, it is not caught between the vane 52a and other members.

  In the first and second embodiments, as described above, the first and second rotors (the outer peripheral side rotor and the inner peripheral side rotor) 42a and 42b, which are respectively magnetized, are provided. In the electric motor 10 including the phase change mechanism 50 that rotates at least one of the rotors about the rotation axis 44 and changes the phase indicating the relative displacement angle between the two, the phase change mechanism is configured to adjust the fluid pressure ( (Hydraulic pressure) is supplied and discharged to expand and contract, so that at least one of the first and second rotors is rotated to change the phase (the advance side working chamber 54c and the retard side working chamber 54d). ) And a bag-like body 72 (and a bellows-like body 72a) connected in a fluid-tight manner to passages (oil passages 62c, 64c, etc.) for supplying and discharging the fluid pressure. .

  Further, the bag-like body 72 is constituted by a bellows-like body 72a that can expand and contract in the circumferential direction.

  Further, the bag-like bodies 72, 72a are formed of an elastic body.

  The phase changing mechanism 50 includes a vane 52a fixed to one of the first and second rotors 42a and 42b, more specifically, the first rotor 42a, and the first and second rotors 42a and 42b. A partition wall 54a fixed to the other of the rotors, more specifically, the second rotor 42b is provided, and the working chamber (the advance side working chamber 54c and the retard side working chamber 54d) is connected to the vane 52a. It was comprised so that it might be formed between the partition walls 54a.

  In the above description, the bag-like body 72 is provided in all of the six working chambers 54c (54d) on the advance side (or on the retard side). Regarding the corner-side working chamber 54d, the bag-like body 72 (or the bellows-like body 72a) may not be provided in a part or all of the six chambers.

  In the above description, the electric motor according to the present invention has been described taking the electric motor mounted on the parallel hybrid vehicle as an example. However, the present invention is mounted on the electric motor mounted on the series hybrid vehicle, and further on the electric vehicle not including the internal combustion engine. Applicable to motors that have been made.

  Further, at least one of the first and second rotors, more specifically, the phase θ indicating the relative displacement angle between the second rotor 42b by rotating the second rotor 42b about the rotation axis (rotation shaft 44). However, the phase may be changed by rotating both the first and second rotors.

1 is a schematic diagram showing an overall configuration when an electric motor according to a first embodiment of the present invention is mounted on a hybrid vehicle. FIG. It is principal part sectional drawing of the electric motor shown in FIG. It is a side view of the rotor of the electric motor shown in FIG. It is a disassembled perspective view which shows the phase change mechanism of the electric motor shown in FIG. It is a schematic diagram which shows the direction of the magnetic pole of the magnet of the rotor shown in FIG. FIG. 4 is a side view of the rotor of the electric motor shown in FIG. 2, similar to FIG. 3. FIG. 4 is a hydraulic circuit diagram of a hydraulic mechanism that supplies hydraulic pressure to the working chamber of the phase change mechanism shown in FIG. 3 and the like. FIG. 7 is an enlarged partial cross-sectional view in the vicinity of an advance side working chamber of the electric motor shown in FIG. 6. Similarly, it is an enlarged partial sectional view of the vicinity of the advance side working chamber of the electric motor shown in FIG. FIG. 7 is an enlarged partial cross-sectional view of the electric motor according to the second embodiment of the present invention, similarly in the vicinity of the advance side working chamber of the electric motor shown in FIG. 6.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 Electric motor (electric motor), 12 Engine (internal combustion engine), 16 Transmission, 22 PDU (power drive unit), 30 Motor control unit, 40 Stator, 42 Rotor, 42a Outer peripheral side (first) rotor, 42b Inner peripheral side (second) rotor, 44 rotating shaft (rotating axis), 46 permanent magnet, 50 phase change mechanism, 52 vane rotor, 52a vane, 54 annular housing, 54a partition wall, 54c advance angle side working chamber, 54d Delay side working chamber, 56 drive plate, 62, 64 oil passage, 70 hydraulic mechanism, 70c hydraulic pump, 70f 4 port valve, 70g linear solenoid valve, 72 bag-like body, 72a bellows-like body

Claims (4)

  A phase that changes the phase indicating the relative displacement angle by rotating at least one of the first and second rotors magnetized with respect to each other about the rotation axis. In the electric motor including the change mechanism, the phase change mechanism expands and contracts when the fluid pressure is supplied and discharged, and thus the phase is changed by rotating at least one of the first and second rotors. An electric motor comprising a chamber and a bag-like body that is liquid-tightly connected to a passage that supplies and discharges the pressure of the fluid.   2. The electric motor according to claim 1, wherein the bag-like body is formed of a bellows-like body that can expand and contract in a circumferential direction.   The electric motor according to claim 1, wherein the bag-like body is formed of an elastic body.   The phase change mechanism includes a vane fixed to one of the first and second rotors and a partition wall fixed to the other of the first and second rotors, and the working chamber has the The electric motor according to any one of claims 1 to 3, wherein the electric motor is formed between the vane and the partition wall.

Images