JP2009261185A - Electric motor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an electric motor, capable of reducing a quantity of an operation fluid stored in a liquid chamber which leaks from the liquid chamber. <P>SOLUTION: The electric motor 10 has inside and outside rotors 22, 21 magnetized respectively, a phase changing mechanism 13 changing the relative phase of the inside and outside rotors 22, 21 by rotating at least one of the inside and outside rotors 22, 21 by working fluid pressures around the rotational axis within an operation chamber 46, a pair of inner side plates 15A, 15B covering an inside space of the inside rotor 22 on both sides in an axial direction of the operation chamber 46, and capable of integratedly turning together with the inside rotor 22, and outer side plates 14A, 14B arranged in the outside of the inner side plates 15A, 15B, and capable of integratedly turning together with the outside rotor 21. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

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

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

  The phase changing mechanism of the electric motor includes an annular housing having a plurality of partition walls on the inner periphery, and a vane rotor disposed on the inner side of the annular housing and having vanes protruding between the partition walls on the outer periphery. The annular housing and the vane rotor are rotated relative to each other by appropriately supplying and discharging hydraulic fluid to and from the working chamber formed between the vane rotors.

In the electric motor described in Patent Document 1, the axially opposite ends of the outer rotor and the vane rotor are connected to each other by a pair of drive plates, and thus the inner rotor is formed in an annular space formed between the outer rotor and the vane rotor. And an annular housing are rotatably accommodated. In this structure, it is necessary to support the annular housing in a floating state in an annular space formed between the outer rotor and the vane rotor. Therefore, cylindrical protrusions are integrally formed at both ends in the axial direction of the annular housing, An annular groove for slidably supporting the cylindrical convex portion is formed on the inner peripheral surfaces of the drive plates on both sides facing the housing.
JP 2007-244042 A

  However, in the case of an electric motor employing such a structure, the annular housing constituting the phase changing mechanism is formed of a ferrous magnetic material having high mechanical strength, while the outer peripheral edge portion is coupled to the outer rotor. The drive plate with the inner peripheral edge straddling the axial end of the inner rotor with a minute gap needs to be formed of a nonmagnetic material from the viewpoint of preventing magnetic flux short-circuit between the outer peripheral permanent magnet and the inner peripheral permanent magnet. .

However, the linear expansion coefficient of the ferrous sintered metal (magnetic material) of the annular housing is about 10 × 10 ⁻⁶ , whereas the linear expansion coefficient of the nonmagnetic material of the drive plate is about 23.9 for aluminum. × 10 ⁻⁶ , stainless steel (SUS), which is a relatively large value of about 17 × 10 ⁻⁶ . For this reason, in an electric motor that generates heat during operation, the clearance between the cylindrical convex portion and the annular groove changes greatly due to a temperature change during operation. Furthermore, since the working chamber formed between the partition wall of the annular housing and the vane rotor needs a predetermined volume, the sliding contact portion between the inner rotor and the drive plate, that is, the cylindrical convex portion and the annular groove is rotated. It is arranged radially outward from the shaft. For this reason, there is a problem that the amount of hydraulic fluid stored in the working chamber leaks from the working chamber is increased when the centrifugal force is increased due to the influence of the centrifugal force due to the rotation of the electric motor.

  An object of this invention is to provide the electric motor which can reduce the quantity which the hydraulic fluid stored in the liquid chamber leaks from a liquid chamber.

  In order to achieve the above object, the invention according to claim 1 is directed to an inner side and an outer side rotor (for example, an inner side and an outer side rotor 22 in the embodiment) in which electric motors (for example, the electric motor 10 in the embodiment) are respectively magnetized. 21) and at least one of the inner and outer rotors is rotated by a working fluid pressure around a rotation axis in a working chamber (for example, the working chamber 46 in the embodiment), and the inner and outer rotors are relative to each other. A pair of phase change mechanisms (for example, the phase change mechanism 13 in the embodiment) that change the correct phase, and a pair that can rotate integrally with the inner rotor that covers the inner space of the inner rotor on both axial sides of the working chamber. Inner side plates (for example, the inner side plates 15A and 15B in the embodiment) and the outer side rotation of the inner side plate disposed on the outer side in the axial direction. Rotatable pair of outer side plates (e.g., outer side plates 14A, 14B in the embodiment) integrally and, characterized by comprising a.

    According to a second aspect of the present invention, the outer side plate includes an elongated hole 73 in which an end portion of a fastening member (for example, the bolt 17 in the embodiment) that fastens the inner side plate and the inner rotor is movable. It is characterized by that.

  According to a third aspect of the present invention, the outer surface of the inner side plate and the surface of the fastening member (for example, the flat head screw 95 or the rivet 96 in the embodiment) that fasten the inner side plate and the inner rotor are in a fastened state. One or the surface of the fastening member for fastening the inner rotor is located on the inner side in the axial direction from the outer surface of the inner side plate.

  The invention according to claim 4 is characterized in that an outer peripheral contact portion (for example, the outer peripheral contact portion 80 in the embodiment) between the inner rotor and the inner side plate is sealed.

  According to the first aspect of the invention, the inner space of the inner rotor is formed at both ends in the axial direction by the pair of inner side plates. In other words, since the working chamber is formed independently of the outer side plate that functions as a drive plate, the working fluid stored in the working chamber can be prevented from leaking from the working chamber due to the influence of temperature change. . In addition, since the inner side plate and the inner rotor can rotate integrally, the sliding contact portion with the member that can rotate integrally with the outer rotor is secured on the inner diameter side while securing a working chamber having a predetermined volume. Can be arranged. As a result, even if a large centrifugal force acts when the rotational speed is high, the hydraulic fluid stored in the working chamber leaks from the working chamber by arranging the sliding contact portion on the inner diameter side where the centrifugal force is relatively small. Can be prevented. Furthermore, by providing the sliding contact portion on the inner diameter side, the length of the sliding contact portion (circumference of the sliding contact portion) can be shortened, and leakage of the hydraulic fluid can be suppressed by a synergistic effect.

  According to the invention of claim 2, for example, a universal bolt can be used as a fastening member between the inner rotor and the inner side plate, and in this case, the head of the bolt is formed on the outer side plate. By moving the elongated hole, the inner rotor can rotate relative to the outer rotor. Furthermore, by detecting the differential rotation of the inner rotor with respect to the outer rotor during rotation, the sensor is integrated with the fastening member or fixed to the fastening member. Angle information of the inner rotor relative to the rotor can be obtained.

  According to the invention of claim 3, for example, a countersunk screw or a rivet can be used for the fastening member between the inner rotor and the inner side plate. In this case, the inner side plate and the surface of the fastening member are in a fastened state. The inner rotor can rotate relative to the outer rotor because the surface of the fastening member is flush with the outer surface of the inner side plate in the axial direction. In particular, even when the operating angle of the inner rotor with respect to the outer rotor is large, it is not necessary to consider the head relief portion of the fastening member.

  According to the invention which concerns on Claim 4, even if the centrifugal force with a large rotational speed acts by sealing the outer peripheral contact part of an inner side rotor and an inner side plate, the hydraulic fluid stored in the working chamber Can be prevented from leaking from the working chamber through the outer peripheral contact portion between the inner rotor and the inner side plate.

  Hereinafter, an electric motor according to an embodiment of the present invention will be described in detail with reference to the drawings. 1 is a cross-sectional view of an electric motor according to the present invention, FIG. 2 is a front view of the rotor unit shown in FIG. 1 viewed from the axial direction, and FIG. 3 is an exploded perspective view showing a part of the rotor unit shown in FIG. 4 is an assembly diagram of a part of the rotor unit shown in FIG. 3, FIG. 5 is an enlarged view of a main part for explaining the state of the strong field phase of the rotor unit, and FIG. 6 is a field weakening of the rotor unit. FIG. 7 is an explanatory view showing a sealing example of the outer peripheral contact portion between the inner rotor and the inner side plate of the electric motor of FIG. 1, and FIG. 8 is an illustration of the electric motor of FIG. FIG. 9 is an explanatory view showing a configuration example of a sliding portion of an inner side plate and a vane rotor, FIG. 9 is an explanatory view in which an angle sensor is attached to the electric motor of FIG. 1, and FIG. It is. 3 and 4 omits the yoke of the inner rotor and the outer rotor for the sake of explanation.

  Hereinafter, an embodiment of an electric motor according to the present invention will be described in detail with reference to the accompanying drawings. The drawings are viewed in the direction of the reference numerals.

  As shown in FIGS. 1 to 6, the electric motor 10 of the present embodiment is an inner rotor type brushless DC motor in which a rotor unit 20 is disposed on the inner peripheral side of an annular stator 11, for example, a hybrid vehicle And used as a driving source for electric vehicles and the like. The stator 11 has a multi-phase stator winding 11a, and the rotor unit 20 has a rotating shaft 12 at the shaft core. When the electric motor 10 is used as a vehicle driving source, the rotational force of the electric motor 10 is transmitted to a wheel drive shaft (not shown) via a transmission (not shown). In this case, if the electric motor 10 is caused to function as a power generator when the vehicle is decelerated, the generated power can be recovered as regenerative energy in the capacitor. In the hybrid vehicle, the rotating shaft 12 of the electric motor 10 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.

  The rotor unit 20 includes an annular outer rotor 21 and an annular inner rotor 22 disposed coaxially inside the outer rotor 21, and the outer rotor 21 and the inner rotor 22. Is capable of relative rotation within a set angle range.

  The outer rotor 21 and the inner rotor 22 are formed of laminated steel plates in which annular yokes 23 and 24, which are rotor bodies, are laminated in a direction along the rotating shaft 12, for example. In each yoke 23, 24, a plurality of magnet mounting slots 23a, 24a formed so as to penetrate in the axial direction are arranged at a predetermined interval (22.5 ° in the present embodiment) in the circumferential direction.

  Each of the magnet mounting slots 23a and 24a is mounted with a flat plate-like outer peripheral permanent magnet 25A and inner peripheral permanent magnet 25B magnetized in the thickness direction. And in this embodiment, 25 A of outer peripheral side permanent magnets are arrange | positioned so that the magnetization direction (thickness direction) may face a circumferential direction, and the inner peripheral side permanent magnet 25B has a magnetization direction (thickness direction) in radial direction. It is arranged to face. Therefore, the adjacent outer peripheral side permanent magnets 25A and 25A and the inner peripheral side permanent magnet 25B are arranged in a substantially U-shape.

  Further, the same number of outer peripheral side permanent magnets 25A and inner peripheral side permanent magnets 25B (8 pole pairs in the present embodiment) are provided, and as shown in FIG. The direction of the magnetic pole of the permanent magnet 25A is set in reverse, and the direction of the magnetic pole of the inner peripheral side permanent magnet 25B adjacent in the circumferential direction on the inner rotor 22 is also set in reverse.

  Then, as shown in FIG. 5, the same polarity, that is, the N pole (or S pole) of the inner peripheral permanent magnet 25 </ b> B is opposed to the opposite N pole (or S pole) of the adjacent outer peripheral permanent magnet 25 </ b> A. When the relative rotation angle between the outer rotor 21 and the inner rotor 22 is adjusted, the field of the entire rotor unit 20 is in the “strong field phase” state that is most strengthened. Further, as shown in FIG. 6, a different polarity of the inner peripheral side permanent magnet 25 </ b> B, that is, the S pole (or N pole) is opposed to the opposite N pole (or S pole) of the adjacent outer peripheral side permanent magnet 25 </ b> A. When the relative rotation angle between the outer rotor 21 and the inner rotor 22 is adjusted, the field of the entire rotor unit 20 is in the “weakening field phase” state that is most weakened.

  Further, the rotor unit 20 includes a rotation mechanism 30 for rotating the outer rotor 21 and the inner rotor 22 relative to each other. The rotating mechanism 30 constitutes a phase changing mechanism 13 for arbitrarily changing the relative phase of both the rotors 21 and 22, and is driven by the pressure of the working fluid that is an incompressible working fluid. . The phase change mechanism 13 includes the above-described rotation mechanism 30 and a hydraulic pressure control device (not shown) that controls supply / discharge of hydraulic fluid to / from the rotation mechanism 30 as main elements.

  As shown in FIGS. 1 to 4, the rotating mechanism 30 is a vane rotor 31 that is spline-fitted to the outer periphery of the rotary shaft 12 so as to rotate integrally therewith, and an annular ring that is disposed to be relatively rotatable on the outer peripheral side of the vane rotor 31. And a housing 32.

  As shown in FIG. 1, the vane rotor 31 includes the outer rotor 21 via outer side plates 14 </ b> A and 14 </ b> B that function as a pair of disk-shaped drive plates that straddle both end surfaces of the annular housing 32 and the inner rotor 22 in the axial direction. Connected to Accordingly, since the outer rotor 21, outer side plates 14A and 14B, the vane rotor 31, and the rotating shaft 12 are integrated, the driving force of the outer rotor 21 is transmitted to the rotating shaft 12 via the outer side plates 14A and 14B. Is done.

  Reference numeral 16 in the figure denotes a bolt that integrally connects the outer side plates 14A and 14B and the vane rotor 31, and a bolt insertion hole 72 formed in the outer side plates 14A and 14B and a bolt formed in the vane rotor 31. Screwed into the insertion hole 31a. The outer side plates 14A, 14 are formed with a plurality of elongated holes 73 (five places in the present embodiment) extending in the circumferential direction.

  As shown in FIG. 1, the annular housing 32 is arranged on the outer peripheral surface so as to sandwich the inner rotor 22 and the inner rotor 22 in the axial direction, and the inner peripheral permanent magnet 25 </ b> B comes out from the magnet mounting slot 24 a. A collar 34 that sandwiches the inner rotor 22 and the pair of end surface plates 33, 33 between a pair of end surface plates 33, 33 that prevent this and a flange portion 32 a formed at the axial end portion of the annular housing 32; A pair of inner side plates 15A and 15B provided at both ends so as to be substantially flush with the outer peripheral surface of the annular housing 32 are integrally fitted and fixed. Therefore, the annular housing 32, the inner rotor 22, and the pair of inner side plates 15A and 15B are integrated.

  In the vane rotor 31, a plurality of vanes 36 protruding radially outward are provided at equal intervals in the circumferential direction on the outer periphery of a cylindrical boss portion 35 that is spline-fitted to the rotary shaft 12. The annular housing 32 is provided with a plurality of recesses 37 at equal intervals in the circumferential direction on the inner peripheral surface, and the corresponding vanes 36 of the vane rotor 31 are accommodated in these recesses 37. Each recess 37 includes a bottom wall 38 having an arc surface that substantially matches the rotation trajectory of the tip of the vane 36, and a partition wall 39 that defines adjacent recesses 37, and the vane rotor 31 and the annular housing 32. At the time of relative rotation, the vane 36 moves between one partition wall 39 and the other partition wall 39.

  In addition, a seal member 40 constituted by a seal 40 a that slides in contact with the bottom wall 38 along the axial direction and a spring 40 b that presses the seal 40 a toward the bottom wall 38 is provided at the tip of each vane 36. The sealing member 40 is provided so as to liquid-tightly seal between the vane 36 and the bottom wall 38. In addition, a seal 41 a that is in sliding contact with the outer peripheral surface of the boss portion 35 along the axial direction and a spring 41 b that presses the seal 41 a toward the outer peripheral surface of the boss portion 35 are provided at the distal ends of the partition walls 39. A configured sealing member 41 is provided, and the sealing member 41 seals between the partition wall 39 and the outer peripheral surface of the boss portion 35 in a liquid-tight manner.

  In addition, a bolt insertion hole 39a for integrally attaching the inner side plates 15A and 15B and the annular housing 32 is provided at the base of the partition wall 39.

  The inner side plates 15 </ b> A and 15 </ b> B are integrally attached to the end surface in the axial direction of the annular housing 32 via the bolts 17, and respectively close the sides of the concave portions 37 of the annular housing 32. Accordingly, each concave portion 37 of the annular housing 32 forms an independent space together with the boss portion 35 of the vane rotor 31 and the inner side plates 15A and 15B on both sides, and this space becomes a working chamber 46 into which working fluid is introduced. ing. Each working chamber 46 is divided into two chambers by the corresponding vanes 36 of the vane rotor 31, one chamber being the advance side working chamber 42, and the other chamber being the retard side working chamber 43. Yes.

  The advance side working chamber 42 rotates the inner rotor 22 relative to the outer rotor 21 in the advance direction by the working fluid pressure of the working fluid introduced inside, and the retard side working chamber 43 The inner rotor 22 is rotated relative to the outer rotor 21 in the retard direction by the pressure of the hydraulic fluid introduced into In this case, “advance angle” refers to advancing the inner rotor 22 in the main rotation direction of the electric motor 10 indicated by the arrow R in FIG. 2 with respect to the outer rotor 21, and “retard angle” refers to the inner side It is assumed that the rotor 22 is advanced to the opposite side to the main rotation direction R of the electric motor 10 with respect to the outer rotor 21.

  Further, the supply and discharge of the hydraulic fluid to and from each of the advance side working chambers 42 and the retard side working chambers 43 are performed through the rotating shaft 12. Specifically, the advance side working chamber 42 has a passage hole 44 a formed in the rotating shaft 12, an annular groove 44 b formed in the outer peripheral surface of the rotating shaft 12 and connected to the passage hole 44 a, and the vane rotor 31. The boss portion 35 is connected to the hydraulic pressure control device through a plurality of conduction holes 44c formed in a substantially radial direction. Further, the retard side working chamber 43 is formed with a passage hole 45 a formed in the rotating shaft 12, an annular groove 45 b formed in the outer peripheral surface of the rotating shaft 12 and connected to the passage hole 45 a, and a boss portion 35 of the vane rotor 31. Are connected to the hydraulic pressure control device through a plurality of conduction holes 45c formed in a substantially radial direction.

  The outer rotor 21 and the outer side plates 14A, 14B are connected to each other by long holes formed at the center in the circumferential direction between the outer peripheral side permanent magnets 25A of the yoke 23 of the outer rotor 21 (at intervals of 22.5 °). The through-hole 51 having a shape and four through-holes 51 located at equal intervals (90 ° interval in the present embodiment) among the plurality of through-holes 51 are respectively inserted, and both end portions thereof are outer side plates 14A, The torque transmission pin 61 is inserted into or pressed into the pin holding hole 18 formed on the inner surface of 14B. Thereby, the torque transmission pins 61 are arranged uniformly (at intervals of 90 °) in the circumferential direction.

  As described above, in the generator 10 according to the present invention, the inner rotor 22 and the annular housing 32 of the rotor unit 20 are closed by the inner side plates 15 </ b> A and 15 </ b> B on both sides in the axial direction via the bolts 17. Are disposed in an annular space between the vane rotors 31 closed by the outer side plates 14A and 14B, but these are held in a floating state in the space. Further, the head of the bolt 17 is configured to be movable in a long hole 73 formed in the outer side plates 14A and 14B, and the inner side plates 15A and 15B are attached to the annular housing 32 at the outer peripheral end, and at the inner diameter end. It is in sliding contact with the vane rotor 31.

  Specifically, as shown in FIG. 7A, the outer peripheral contact portion 80 where the inner peripheral surface of the annular housing 32 and the outer peripheral surfaces of the inner side plates 15A and 15B are in contact is provided at both ends of the annular housing 32 in the axial direction. The outer diameter end portions of the inner side plates 15A and 15B are sealed by being attached to the annular portion 32a by in-row or press-fitting. Further, the annular housing 32, the inner rotor 22 and a pair of inner members are formed by bolts 17 inserted into bolt insertion holes 39a formed in the base of the partition wall 39 and bolt insertion holes 74 formed in the inner side plates 15A and 15B. The side plates 15A and 15B are fixed so as to be integrally rotatable.

  The outer peripheral contact portion 80 between the annular portion 32a of the annular housing 32 and the inner side plates 15A and 15B is shown in FIG. 7B in addition to the method of sealing by in-row or press fitting shown in FIG. As shown in FIG. 7C, the annular portion 32a and the inner side plates 15A and 15B may be welded to form a welded portion 82. It may be sealed using an O-ring 83 between 15B. In FIG. 7C, an annular recess 85 is provided at the outer diameter end portion of the inner side plates 15A and 15B and an O-ring 83 is attached to the annular recess 85, but an annular recess is provided at the inner diameter portion of the annular housing 32, An O-ring 83 can also be attached.

  As shown in FIGS. 3, 4 and 7, the outer side plates 14 </ b> A and 14 </ b> B are provided with an oil hole outlet 81 penetrating in the axial direction at a location corresponding to the outer diameter side end of the inner rotor 22. ing.

  Further, as shown in FIG. 8 (a), an annular step, which is an annular step portion substantially the same as the thickness (axial length) of the inner side plates 15A and 15B, is provided on both end sides in the axial direction of the vane rotor 31. A portion 31b is formed, and inner end portions of the inner side plates 15A and 15B are opposed to the annular step portion 31b to form a sliding contact portion. A predetermined clearance is provided between the annular step portion 31b and the inner diameter end portions of the inner side plates 15A and 15B to ensure proper sliding.

  Note that the annular step portion 31b of the vane rotor 31 and the inner diameter end portions of the inner side plates 15A and 15B are disposed between the annular step portion 31b and the inner side plates 15A and 15B as shown in FIG. You may seal using. In FIG. 8 (b), an annular recess 89 is provided at the outer diameter end of the annular step 31b and a seal ring 87 is attached to the annular recess 89. However, an annular recess is provided at the inner diameter of the inner side plates 15A and 15B. A seal ring 87 can also be attached.

Here, since the annular housing 32 is a component constituting the hydraulic phase change mechanism 13, it is formed of an iron-based sintered metal that is a magnetic material having high mechanical strength, and the outer side plates 14A and 14B are Since the outer peripheral side end is coupled to the outer rotor 21 and the radially inner region is closer to the axial end of the inner peripheral permanent magnet 25B than the coupled portion, In order to prevent magnetic flux short circuit between the permanent magnets 25A and 25B, the permanent magnets 25A and 25B are formed of a nonmagnetic material such as aluminum (linear expansion coefficient: 23.9 × 10 ⁻⁶ ) or stainless steel (linear expansion coefficient: 17 × 10 ⁻⁶ ). Yes. The inner side plates 15A and 15B are made of chromium steel (linear expansion coefficient: 12) having substantially the same linear expansion coefficient as the iron-based sintered metal (linear expansion coefficient: 10 × 10 ⁻⁶ ) constituting the annular housing 32. × 10 ⁻⁶ ) or carbon steel (linear expansion coefficient: 11 × 10 ⁻⁶ ) or the like. Various other materials can be used as the magnetic material constituting the inner side plates 15A and 15B. In this case, the linear expansion coefficient is in the range of 9 × 10 ^{−6 to} 12 × 10 ⁻⁶ . I just need it.

  In the electric motor 10 configured as described above, when changing the field characteristics, the hydraulic fluid is supplied to one of the advance side working chamber 42 and the retard side working chamber 43 by supplying and discharging the hydraulic fluid by the hydraulic pressure control device. And the hydraulic fluid is discharged from the other. When the supply and discharge of the hydraulic fluid is controlled in this way, the vane rotor 31 and the annular housing 32 are rotated relative to each other, and the relative phase between the outer rotor 21 and the inner rotor 22 is operated accordingly. At this time, as shown in FIG. 4, the heads of the bolts 17 that fix the annular housing 32 and the inner side plates 15A, 15B move in the elongated holes 73 formed in the outer side plates 14A, 14B, and the inner rotor 22 The annular housing 32 and the inner side plates 15A, 15B are integrally rotated with respect to the outer rotor 21, the vane rotor 31, and the outer side plates 14A, 14B.

  When the relative phase between the outer rotor 21 and the inner rotor 22 is manipulated, the magnetic field exerted on the stator 11 between the strong field phase state shown in FIG. 5 and the weak field phase state shown in FIG. The strength of changes. When the strength of the magnetic field changes, the induced voltage constant changes accordingly, and as a result, the characteristics of the electric motor 10 are changed. That is, when the induced voltage constant increases due to the strong field, the allowable rotational speed at which the motor 10 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 as the electric motor 10 decreases, the permissible rotational speed that can be operated increases.

  As described above, according to the electric motor 10 of the present embodiment, the inner space of the inner rotor 22 is formed at both ends in the axial direction by the pair of inner side plates 15A and 15B. In other words, since the working chamber 46 is formed independently of the outer side plates 14A and 14B functioning as drive plates, the working fluid stored in the working chamber 46 leaks from the working chamber 46 due to the influence of temperature change. Can be prevented. Further, since the inner side plates 15A and 15B and the inner rotor 22 can rotate integrally, the sliding contact portion between the outer rotor 21 and the vane rotor 31 has an inner diameter while ensuring a working chamber 46 having a predetermined volume. Can be placed on the side. As a result, even when a large centrifugal force is applied when the rotational speed is high, the hydraulic fluid stored in the working chamber 46 leaks from the working chamber 46 by arranging the sliding contact portion on the inner diameter side where the centrifugal force is small. Can be suppressed. Further, by providing a sliding contact portion between the vane rotor 31 and the inner side plates 15A and 15B on the inner diameter side, the length of the sliding contact portion (circumference of the sliding contact portion) can be shortened, and hydraulic fluid leaks due to a synergistic effect. Can be suppressed.

  Further, since the outer side plates 14A and 14B are formed with elongated holes 73 through which the heads of the bolts 17 that fasten the inner side plates 15A and 15B and the inner rotor 22 can move, the heads of the bolts 17 are connected to the outer side plates 14A and 14B. The inner rotor 22 can rotate relative to the outer rotor 21 by moving the elongated hole 73 formed in 14B. Thereby, the versatile bolt 17 can be used as what fixes inner side plate 15A, 15B and the inner side rotor 22. FIG.

  Further, in the electric motor 10 of the present embodiment, as shown in FIG. 7, by sealing the outer peripheral contact portion between the inner rotor 22 and the inner side plates 15A and 15B, a large centrifugal force is generated when the rotational speed is high. Even if it acts, the hydraulic fluid stored in the working chamber 46 can be prevented from leaking from the working chamber 46 through the outer peripheral contact portion between the inner rotor 22 and the inner side plates 15A and 15B.

  Further, in the electric motor 10 of the present embodiment, as shown in FIG. 8 (b), the annular step portion 31b of the vane rotor 31 and the inner diameter end portions of the inner side plates 15A, 15B are formed of the annular step portion 31b, the inner side plate 15A, When sealing is performed using the seal ring 87 between 15B and the hydraulic fluid stored in the working chamber 46, leakage from the working chamber 46 can be further suppressed. Furthermore, by providing the sliding contact portion between the vane rotor 31 and the inner side plates 15A and 15B on the inner diameter side, the axial vane rotor that is relatively easy to cut can be processed, and the workability is improved.

  In the electric motor 10 of the present embodiment, the oil hole outlet 81 is provided in the outer side plates 14 </ b> A and 14 </ b> B at a location corresponding to the outer diameter side end of the inner rotor 22, so that it is stored in the working chamber 46. Even if the working fluid leaks from the working chamber 46, the working fluid can be discharged from the oil hole outlet 81, and the working fluid leaked from the working chamber 46 does not stay inside the electric motor 10. .

  Further, in the electric motor 10 of the present embodiment, as shown in FIG. 9A, a pin 91 is press-fitted into the inner rotor 22 in order to detect a relative angle of the inner rotor 22 with respect to the outer rotor 21, that is, a differential rotation. In addition, the angle information can be detected by providing the outer rotor 21 with the relief hole 92. Thereby, the differential rotation of the inner rotor 22 with respect to the outer rotor 21 can be detected with high accuracy.

  Further, as shown in FIG. 9B, angle information can be detected by providing a screw pin 93 on the head of the bolt 17 that fixes the annular housing 32 and the inner side plates 15A and 15B. Furthermore, as shown in FIG. 9C, angle information can also be detected by attaching a non-contact type pin 94 to the head of the bolt 17 that fixes the annular housing 32 and the inner side plates 15A and 15B. As shown in FIGS. 9B and 9C, the outer side plate 14 </ b> A can be obtained by integrating a part of the members constituting the rotation sensor in this way with the bolt 17 that is the fastening member or by fixing to the bolt 17. , 14B is not required to be newly processed, and the angle information of the inner rotor 22 with respect to the outer rotor 21 can be easily obtained.

  Further, in the electric motor 10 of the present embodiment, the annular housing 32 and the inner side plates 15A and 15B are fixed by the bolts 17 and become escape holes so that the inner rotor 22 and the outer rotor 21 can be rotated relative to each other. Although the elongated hole 73 is formed, as shown in FIG. 10A, a flat head screw 95 can be used to fix the annular housing 32 and the inner side plates 15A and 15B. Further, as shown in FIG. 8B, a rivet 96 can be used to fix the annular housing 32 and the inner side plates 15A and 15B. As a result, versatile countersunk screws and rivets can be used for the fastening members between the inner rotor 22 and the inner side plates 15A and 15B. In this case, the surfaces of the inner side plates 15A and 15B and the fastening members are The inner rotor 22 can rotate relative to the outer rotor 21 when the fastening state is flush or the surface of the fastening member is axially inner than the outer surfaces of the inner side plates 15A and 15B. Thereby, even when the operating angle of the inner rotor 22 with respect to the outer rotor 21 is large or when it is necessary to increase the number of vanes 36, it is not necessary to consider the head relief portion of the fastening member.

  In addition, this invention is not limited to what was illustrated to the said embodiment, In the range which does not deviate from the summary of this invention, it can change suitably. For example, in the above embodiment, the phase change mechanism 13 rotates the inner rotor 22 so that the relative phase between the outer rotor 21 and the inner rotor 22 can be changed. The relative phase between the rotors 21 and 22 may be changed by rotating 21.

It is sectional drawing of the electric motor which concerns on this invention. It is the front view which looked at the rotor unit shown in FIG. 1 from the axial direction, and is a figure corresponded in the AA arrow sectional drawing of FIG. FIG. 3 is an exploded perspective view showing a part of the rotor unit shown in FIG. 2. FIG. 4 is an assembly diagram showing a part of the rotor unit shown in FIG. 3. It is a principal part enlarged view for demonstrating the state of the strong field phase of a rotor unit. It is a principal part enlarged view for demonstrating the state of the field weakening phase of a rotor unit. It is explanatory drawing which shows the sealing example of the outer periphery contact part of the inner side rotor and inner side plate of the electric motor of FIG. 1, (a) is a principal part enlarged view of the electric motor of FIG. 1, (b) and (c). It is a principal part enlarged view which shows the modification of the electric motor of FIG. It is explanatory drawing which shows the structural example of the sliding part of the inner side plate and vane rotor of the electric motor of FIG. 1, (a) is a principal part enlarged view of the electric motor of FIG. 1, (b) is a modification of the electric motor of FIG. It is a principal part enlarged view shown. Is an explanatory diagram in which an angle sensor is attached to the electric motor of FIG. These are explanatory drawings which show the modification of the fastening member of the electric motor of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Electric motor 11 Stator 12 Rotating shaft 13 Phase change mechanism 14A, 14B Outer side plate 15A, 15B Inner side plate 17 Bolt
20 rotor unit 21 outer rotor 22 inner rotor 23 yoke 24 yoke 25A outer peripheral side permanent magnet 25B inner peripheral side permanent magnet 30 rotating mechanism 31 vane rotor 32 annular housing 73 oblong hole
80 Outer peripheral contact area

Claims (4)

The relative phases of the inner and outer rotors are changed by rotating at least one of the magnetized inner and outer rotors and at least one of the inner and outer rotors around the rotation axis by working fluid pressure. A phase change mechanism to
A pair of inner side plates that can rotate integrally with the inner rotor, covering the inner space of the inner rotor on both axial sides of the working chamber;
An electric motor including a pair of outer side plates that are disposed on the outer side in the axial direction of the inner side plate and that can rotate integrally with the outer rotor.   The electric motor according to claim 1, wherein the outer side plate includes an elongated hole through which an end of a fastening member that fastens the inner side plate and the inner rotor can move.   The outer surface of the inner side plate and the surface of the fastening member that fastens the inner side plate and the inner rotor are flush with each other, or the surface of the fastening member that fastens the inner rotor is outside the inner side plate. The electric motor according to claim 1, wherein the electric motor is located on the inner side in the axial direction from the surface.   The electric motor according to any one of claims 1 to 3, wherein an outer peripheral contact portion between the inner rotor and the inner side plate is sealed.

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