JP4961257B2 - Electric motor - Google Patents

Description

  The present invention relates to an electric motor.

2. Description of the Related Art Conventionally, for example, there is known an electric motor including a rotor including an inner rotor and an outer rotor whose rotation axes are arranged coaxially and whose relative phases can be changed (see, for example, Patent Document 1).
JP 2004-72978 A

  By the way, in the electric motor according to the above-described prior art, in order to efficiently generate the magnetic interaction between the permanent magnets of the inner rotor and the outer rotor, the distance between the permanent magnets is shortened. Is desired. However, the yoke portion that holds the permanent magnet in each rotor needs to have a desired rigidity against stress generated when the motor rotates at a high speed. In particular, the yoke portion on the outer peripheral side of the inner rotor must be secured. It may be difficult to reduce the wall thickness, and it may be difficult to efficiently increase the variable width of the induced voltage constant of the motor.

  The present invention has been made in view of the above circumstances, and an object thereof is to provide an electric motor capable of efficiently increasing the variable width of the induced voltage constant of the electric motor.

  In order to solve the above-described problems and achieve the object, the electric motor according to the first aspect of the present invention includes an inner peripheral side permanent magnet (for example, a peripheral shaft disposed coaxially with each other's rotation shafts disposed coaxially) The inner peripheral rotor (for example, the inner peripheral rotor 11 in the embodiment) including the permanent magnet 11a in the embodiment and the outer peripheral permanent magnet (for example, the embodiment) arranged in the circumferential direction. And the outer peripheral side rotor (for example, the outer peripheral side rotor 12 in the embodiment) and at least the inner peripheral side rotor or the outer peripheral side rotor are rotated around the rotation axis. An electric motor comprising rotating means (for example, the rotating mechanism 14 in the embodiment) capable of changing the relative phase between the inner circumferential rotor and the outer circumferential rotor. The rotating means receives the pressure of the fluid supplied from the outside. A rotating actuator unit (for example, the vane rotor 32, the first pressure chamber 56, and the second pressure chamber 57 in the embodiment) is provided, and includes the actuator unit, the inner circumferential side rotor, and the outer circumferential side rotor. A fluid passage (for example, a fluid passage 59b in the embodiment) that communicates with a gap portion (for example, the gap portion 60 in the embodiment), and the rotation of the electric motor in the vicinity of the gap portion of the fluid passage. A centrifugal pressure chamber (for example, the centrifugal pressure chamber 59a in the embodiment) for accumulating the accompanying centrifugal fluid pressure is provided.

  Furthermore, in the electric motor according to the second aspect of the present invention, the actuator section is provided in any one of the inner circumferential rotor and the outer circumferential rotor and is supplied with the fluid (for example, an implementation chamber) The first pressure chamber 56 and the second pressure chamber 57) in the form of the above and the inner circumferential rotor and the outer circumferential rotor are configured integrally with the other and disposed in the working chamber, A vane rotor (for example, the vane rotor 32 in the embodiment) that rotates around the rotation axis under pressure of the pressure, and the vane rotor has a passage hole (circulates) the fluid supplied from the outside to the working chamber ( For example, the passage hole 35c and the passage hole 35d) in the embodiment are provided.

  Furthermore, in the electric motor according to the third aspect of the present invention, the wall portion of the working chamber includes a notch portion that can always open the fluid passage into the working chamber regardless of the relative position of the vane rotor.

  Furthermore, the electric motor according to the fourth aspect of the present invention is fixed integrally with the vane rotor and the outer rotor, and a pair of end plates (for example, covering both end surfaces in the axial direction of the inner rotor) The drive plates 31, 31) in the embodiment are provided, and the fluid passage is formed in at least one of the pair of end plates.

  Furthermore, in the electric motor according to the fifth aspect of the present invention, the centrifugal pressure chamber is formed by the end plate and the iron core portion of the inner circumferential rotor (for example, the inner circumferential rotor core 21 in the embodiment). Has been.

  Furthermore, in the electric motor according to the sixth aspect of the present invention, the centrifugal pressure chamber includes a screw orifice (for example, a screw orifice 31f in the embodiment) in the end plate.

  According to the electric motor according to the first aspect, in the centrifugal pressure chamber provided in the vicinity of the gap between the inner circumferential rotor and the outer circumferential rotor, pressure is accumulated as the rotational speed of the electric motor increases. Since the centrifugal fluid pressure changes in an increasing tendency and this centrifugal fluid pressure acts on the gap between the inner circumferential rotor and the outer circumferential rotor, the inner circumferential permanent magnet is particularly used in the inner circumferential rotor. In the yoke part (iron core part) that holds the rotor, centrifugal fluid pressure that is directed radially inward acts against the stress generated during high rotation of the electric motor, and the like. The thickness of the outer yoke portion can be reduced, the distance between the permanent magnets of the inner rotor and the outer rotor can be appropriately shortened, and the induced voltage constant of the motor can be reduced. The variable width can be increased efficiently.

Furthermore, according to the electric motor according to the second aspect, the actuator unit includes a simple vane actuator including a working chamber to which a fluid is supplied and a vane rotor that rotates around the rotation axis in the working chamber under the pressure of the fluid. As a result, the induced voltage constant can be easily made variable while suppressing the motor from becoming complicated.
Furthermore, according to the electric motor of the third aspect, fluid can be supplied to or discharged from the working chamber regardless of the relative position of the vane rotor, and the induced voltage constant can be easily made variable. Can do.

Furthermore, according to the electric motor which concerns on a 4th aspect, a fluid can be distribute | circulated between a working chamber and a space | gap part via the fluid channel | path formed in the end plate, suppressing the complication of an electric motor. The induced voltage constant can be easily made variable.
Furthermore, according to the electric motor which concerns on a 5th aspect, by forming a centrifugal pressure chamber with the iron core part of an end plate and an inner peripheral side rotor, it is easily induced voltage, suppressing complication of an electric motor. Constants can be variable.
Further, according to the electric motor of the sixth aspect, since the centrifugal pressure chamber is provided with the screw orifice in the end plate, for example, even when air or the like is mixed into the fluid, the air or the like is externally passed through the screw orifice. The contaminants can be discharged from the fluid.

Hereinafter, an embodiment of an electric motor of the present invention will be described with reference to the accompanying drawings.
As shown in FIGS. 1 and 2, for example, the electric motor 10 according to the present embodiment includes a substantially annular inner circumferential rotor 11 provided to be rotatable about the rotation axis of the electric motor 10, and an inner circumferential side of the inner circumferential rotor 11. A substantially annular outer peripheral rotor 12 provided to be rotatable about a coaxial rotation axis on the outer side in the radial direction with respect to the side rotor 11, and in alignment with the position in the rotation axis direction; The stator 13 having the stator winding 13a shown in FIG. 1 for generating a rotating magnetic field for rotating the side rotor 11 and the outer peripheral rotor 12, and the inner peripheral rotor 11 and the outer peripheral rotor 12 are provided. A rotating mechanism (which is connected and changes the relative phase between the inner rotor 11 and the outer rotor 12 with the hydraulic pressure (fluid pressure) of hydraulic fluid (working fluid) that is an incompressible fluid ( (Rotating means) 14 and the hydraulic pressure to the rotating mechanism 14 is controlled. A brushless DC motor and a hydraulic control device for 示略.
The electric motor 10 is mounted as a drive source in a vehicle such as a hybrid vehicle or an electric vehicle, and its output shaft (rotating shaft) 16 is connected to an input shaft of a transmission (not shown). The driving force of the electric motor 10 is transmitted to driving wheels (not shown) of the vehicle via the transmission.

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

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

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

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

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

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

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

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

  Thereby, according to the relative position of the inner peripheral side rotor 11 and the outer peripheral side rotor 12 around the rotation axis, the state of the electric motor 10 is changed to all the permanent magnets 11a, ..., 11a of the inner peripheral side rotor 11. In all the permanent magnets 12a,..., 12a of the outer circumferential rotor 12, the magnetic poles of the same polarity as the paired permanent magnets 11a, 11a and the paired permanent magnets 12a, 12a are opposed to each other (that is, the pair The paired permanent magnets 11a and 11a are paired with the paired permanent magnets 11a and 11a from the field-weakening state shown in FIG. 2 in which the permanent magnets 12a and 12a paired with the permanent magnets 11a and 11a are paired with each other. The field in which the magnetic poles of the opposite polarities of the permanent magnets 12a and 12a are arranged opposite to each other (that is, the permanent magnets 11a and 11a that make a pair and the permanent magnets 12a and 12a that make a pair have the same polarity) and the field is strengthened most. Strength shown in 4 And it is capable of setting the appropriate state over the magnetic state.

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

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

  As shown in FIG. 1, the rotation mechanism 14 according to the present embodiment includes shims 25 on the end faces 12A and 12A on both sides in the axial direction of the outer rotor 12 so as to cover the space inside the outer rotor 12. A pair of disk-shaped drive plates (end plates) 31 and 31 that are bonded and fixed together, and a vane rotor 32 that is directly provided between the drive plates 31 and 31 and provided integrally inside the outer rotor 12. , The vane rotor 32, the outer peripheral rotor 12, and the housing 33 constituting a part of the inner peripheral rotor 11 disposed between the drive plates 31 and 31. The vane rotor 32 and the housing 33 are formed by, for example, sintering.

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

And as shown in FIG. 3, the axial direction of the inner peripheral side rotor iron core 21 of the inner peripheral side rotor 11 which can be rotated with respect to the outer peripheral side rotor 12 and the drive plates 31 and 31 provided integrally. Both end surfaces form a centrifugal pressure chamber 59a having an appropriate gap between the opposite drive plates 31.
Further, as shown in FIG. 1, the drive plates 31, 31 are disposed between the first pressure chamber 56 and the second pressure chamber 57 between both end surfaces in the axial direction of the base portion 46 of the inner circumferential rotor 11 described later. The fluid passage 59b is formed of a slight gap that can communicate with the fluid passage 59b. The fluid passage 59b and the centrifugal pressure chamber 59a communicate with each other.
Further, the centrifugal pressure chamber 59 a is formed between the outer peripheral surface 21 A of the inner peripheral rotor core 21 of the inner peripheral rotor 11 and the inner peripheral surface 22 B of the outer peripheral rotor core 22 of the outer peripheral rotor 12. It communicates with the gap 60.
That is, the centrifugal pressure chamber 59a is provided in the vicinity of the gap 60 of the fluid passage 59b.
In addition, the drive plate 31 has screw orifices 31f,..., 31f communicating with the outermost peripheral portion of the centrifugal pressure chamber 59a and the outside at positions slightly shifted from the bolt insertion holes 31a,. Are formed at equal intervals on the same circumference. Here, these screw orifices 31f,..., 31f are all formed at positions (specifically, center positions) between the adjacent bolt insertion holes 31a, 31a. These screw orifices 31f,..., 31f prohibit passage of hydraulic oil, which will be described later, having a viscosity equal to or higher than a predetermined value, and allow passage of fluid and gas (for example, air) having a viscosity lower than the predetermined value. .

  As shown in FIG. 3, the pair of shims 25, 25 has an annular shape as a whole, and the annular flat plate portion 26 orthogonal to the central axis and the entire inner peripheral edge portion of the flat plate portion 26. It has a bead (bent portion) 27 extending inward while being bent stepwise in the axial direction from the periphery, and the flat plate portion 26 has a plurality of same numbers as the bolt insertion holes 31a penetrating in the axial direction. Bolt insertion holes 26a, ..., 26a are formed at equal intervals on the same circumference. Here, the bead 27 is a so-called half bead having a step shape from the flat plate portion 26 to one side in the axial direction, specifically, an annular tapered plate portion 27a extending obliquely inward from the flat plate portion 26; The taper plate portion 27a has an annular inner end plate portion 27b extending inward from the inner peripheral edge of the taper plate portion 27a in parallel with the flat plate portion 26. When the bead 27 is sandwiched between the drive plate 31 and the outer rotor 12, the bead 27 is deformed into the same flat plate shape as the flat plate portion 26 as a whole, and these drive plates are caused by the elastic force generated at that time. 31 and the outer peripheral rotor 12 are in close contact with each other to seal these gaps. In addition, you may employ | adopt what is called a full bead which makes a step shape in the axial direction both sides.

  As shown in FIG. 2, the vane rotor 32 includes a cylindrical boss portion 35 and a plurality of the above-described bolt insertion holes 31 c extending radially outward from the circumferentially equidistant positions on the outer peripheral surface of the boss portion 35. , And 36 blade portions 36,...

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

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

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

  The inner circumferential rotor 11 includes a ring-shaped inner circumferential rotor body 34 configured by mounting permanent magnets 11a, ..., 11a on the inner circumferential rotor core 21, and the inner circumferential rotor body. A housing 33 is integrally fitted inside 34 so as to have a predetermined phase relationship. A housing 33 that constitutes a part of the inner circumferential rotor 11 includes a cylindrical base portion 46 having a small radial thickness, and a radially inner position from a circumferentially equidistant position on the inner circumferential surface of the base portion 46. , 47 having the same number as the blade portion 36. Here, as shown in FIG. 1, the base portion 46 protrudes over the entire circumference on both sides in the axial direction from the protruding portion 47 and the inner circumferential rotor body 34. As shown in FIG. 2, each of the protrusions 47,..., 47 has a substantially isosceles triangular shape that is tapered in the axial direction, and all the protrusions 47,. A concave portion 48 in which the vane portion 36 of the vane rotor 32 described above can be disposed is formed between the adjacent projecting portions 47 and 47. Each of the projecting portions 47,..., 47 is formed with a seal holding groove 47b that is recessed toward the outer diameter side on the inner end surface thereof over the entire length in the axial direction. In these seal holding grooves 47b,..., 47b, spring seals 50 for sealing the gap with the outer peripheral surface of the boss portion 35 of the vane rotor 32 are arranged. These spring seals 50,..., 50 are provided on the inner peripheral side and are in contact with the boss portion 35 of the vane rotor 32, and the seal spring 50b is provided on the outer diameter side and presses the seal 50a toward the vane rotor 32. It consists of and. The housing 33 may be integrally connected to the inner circumferential rotor body 34 by fastening bolts or the like.

  The axial length of the outer peripheral rotor 12 is set to be shorter than the axial lengths of the vane portion 36 and the sandwiching base portion 37 of the vane rotor 32 even if a maximum allowable manufacturing error occurs. At the time of assembly, the actual axial length of the outer rotor 12 and the axial lengths of the vane rotor 36 and the clamping base 37 of the vane rotor 32 are measured.

  When assembling each component, first, for example, the axial length of the actual product of the outer rotor 12 measured as described above, the axis of the vane rotor 36 and the sandwiching base portion 37 of the actual product of the vane rotor 32 are used. Two shims 25 having a thickness that is half the difference from the direction length are selected from a plurality of types having different thicknesses prepared in advance.

  Next, by inserting the cylindrical portion 31d of one drive plate 31 into one fitting portion 38 of the vane rotor 32, the bolts of the drive plate 31 are inserted in a state where the drive plate 31 and the vane rotor 32 are combined. Bolts 54 are inserted into the holes 31c,..., 31c, respectively, and the bolts 54,..., 54 are respectively screwed into the screw holes 36a of the blade portion 36 of the vane rotor 32. Then, with the spring seals 44 attached to the blade portions 36,... 36 of the vane rotor 32, the blade portions 36,. The inner circumferential rotor 11 configured by press-fitting the housing 33 inside the side rotor main body 34 is aligned with one drive plate 31 with the spring seals 50,. Then, after aligning the end surface 12A of the outer peripheral rotor 12 with one drive plate 31 through the shim 25 so as to cover the outer side of the inner peripheral rotor 11, the end surface 12A on the opposite side of the outer peripheral rotor 12 is provided. Also, the shim 25 is arranged, and the other drive plate 31 is aligned from the opposite side by fitting the other fitting portion 38 of the vane rotor 32 into the center hole 31e, and each bolt insertion hole of the drive plate 31 is fitted. 31a, the bolt insertion holes 26a, ..., 26a of the shim 25, the bolt insertion holes 22b, ..., 22b of the outer rotor 12, the bolt insertion holes 26a, ..., 26a of the shim 25, and the above , 31a is inserted into each bolt insertion hole 31a,..., 31a of one drive plate 31, and a nut 53 is screwed into each bolt 52,. . Further, the bolts 54 are inserted into the bolt insertion holes 31c,..., 31c of the other drive plate 31, respectively, and the bolts 54,..., 54 are respectively screwed into the screw holes 36a of the blade portion 36 of the vane rotor 32.

  Here, the above-described bolt 52 and nut 53 are provided around the bolt insertion hole 31 a of one drive plate 31, the bolt insertion hole 26 a of one shim 25, and the bolt insertion hole 22 b of the outer rotor 12. A bolt fastening portion 63 for fastening the peripheral portion, the peripheral portion of the bolt insertion hole 26a of the other shim 25 and the peripheral portion of the bolt insertion hole 31a of the other drive plate 31 is configured. It is formed at predetermined intervals along the circumferential direction. Then, by fastening these bolt fastening portions 63,..., 63, both shims 25, 25 are connected to the drive plate 31 by an annular bead 27 on the axial center side of each bolt fastening portion 63,. It is sandwiched between the outer circumferential rotor 12 and deformed into a flat plate shape as a whole, and the drive plate 31 and the outer circumferential rotor 12 are brought into close contact with each other by a restoring force to seal these gaps. The screw orifices 31f,..., 31f of the drive plate 31 are formed between the adjacent bolt insertion holes 31a, 31a in the circumferential direction (specifically at the center position) as described above. It is formed between adjacent bolt fastening portions 63 and 63 inserted through the matching bolt insertion holes 31a and 31a (specifically, at the center position) (see FIG. 2).

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

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

As described above, the inner circumferential rotor 11 configured by integrating the housing 33 and the inner circumferential rotor body 34 is located inside the outer circumferential rotor 12 and outside the vane rotor 32 and on the drive plates 31, 31. Is provided in the space 58 between them, and is held rotatably at both side portions in the axial direction of the base portion 46 entering the annular grooves 31b, 31b of the drive plates 31, 31.
The fluid passages 59b and 59b are formed by slight gaps between both end surfaces of the base portion 46 in the axial direction and the annular grooves 31b and 31b of the opposing drive plates 31 and 31, respectively.
Furthermore, the blade | wing part 36 of the vane rotor 32 is arrange | positioned 1 each in the recessed part 48 of the housing 33, ..., 48. Further, the output shaft 16 that is spline-coupled to the vane rotor 32 can rotate integrally with the outer peripheral rotor 12, the drive plates 31, 31, and the vane rotor 32, and specifically, is fixed integrally.
The shims 25, 25 interposed between the both end faces 12A, 12A of the outer rotor 12 and the drive plates 31, 31 are formed within the range of the end face 12A of the outer rotor 12, respectively. And does not extend to the region of the gap 60 between the outer circumferential rotor 12 and the inner circumferential rotor 11. Further, the screw orifices 31f,..., 31f of the drive plate 31 are located on the axial center side of the shim 25 and on the side of the gap 60, specifically, along the central axis direction so as to open to the gap 60. It is formed on an extension line of the portion 60.

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

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

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

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

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

  As described above, the vane rotor 32 described above is integrally fixed to the outer circumferential rotor 12 and can rotate integrally, and is disposed inside the inner circumferential rotor 11. Moreover, the vane rotor 32 is connected to the outer rotor 12 via drive plates 31 and 31 fixed to the outer rotor 12 so as to cover both end faces of the outer rotor 12 and the inner rotor 11 in the axial direction. And an output shaft 16 that outputs the driving force of the outer rotor 12 is also provided integrally. Further, the housing 33 is integrally fitted to the inner circumferential rotor body 34 so as to be able to rotate integrally, and the concave portion 48 has the first pressure chamber 56 and the second pressure chamber 57 inside with the vane rotor 32. It is defined inside the circumferential rotor 11. Further, the relative phase of the vane rotor 32 with respect to the housing 33 is changed by supplying and discharging the hydraulic oil to and from the first pressure chamber 56 and the second pressure chamber 57, that is, the introduction control of the hydraulic pressure. The relative phase between the child 11 and the outer peripheral rotor 12 is changed. Here, the relative phase between the inner circumferential rotor 11 and the outer circumferential rotor 12 can be changed to the advance side or the retard side by at least 180 ° of the electrical angle, and the state of the electric motor 10 is A field-weakening state in which the same magnetic poles of the permanent magnet 11a of the inner rotor 11 and the permanent magnet 12a of the outer rotor 12 are arranged to face each other, and the permanent magnet 11a and outer periphery of the inner rotor 11 It is possible to set an appropriate state between the strong magnetic field state in which the magnetic poles of different polarities with respect to the permanent magnet 12a of the side rotor 12 are arranged to face each other.

  In addition, these outer peripheral rotors surrounded by drive plates 31 that transmit the driving force of the outer peripheral rotor 12 to the output shaft 16 are fixed to both end surfaces in the axial direction of the outer peripheral rotor 12 and the vane rotor 32, respectively. 12, the inner circumferential rotor 11 in which the inner circumferential rotor body 34 and the housing 33 are integrated in the space 58 shown in FIG. 2 between the vane rotor 32 and the drive plates 31 and 31 is rotatable in the circumferential direction. Is arranged. The inner circumferential rotor 11 in which the inner circumferential rotor body 34 and the housing 33 are integrated is rotatably provided in the space 58 in a floating state (that is, the drive plates 31 and 31 and the output shaft). 16 is not fixed).

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

And the hydraulic fluid which flowed out from the 1st pressure chamber 56 and the 2nd pressure chamber 57 with the centrifugal force at the time of rotation of the electric motor 10 consists of a slight clearance gap between the drive plates 31 and 31 and the inner peripheral side rotor 11. The fluid passes through the fluid passage 59b and is filled in a centrifugal pressure chamber 59a formed of an appropriate gap between the drive plates 31 and 31 and the inner rotor 11, and the centrifugal fluid caused by centrifugal force is filled in the centrifugal pressure chamber 59a. The pressure is accumulated.
Here, the centrifugal pressure chamber 59a is formed between the outer peripheral surface 21A of the inner peripheral rotor core 21 of the inner peripheral rotor 11 and the inner peripheral surface 22B of the outer peripheral rotor core 22 of the outer peripheral rotor 12. Therefore, the centrifugal fluid pressure due to the incompressible hydraulic oil acts on the gap 60.
Thereby, in particular, on the outer peripheral surface 21A of the inner peripheral rotor core 21 that holds the permanent magnets 11a,..., 11a in the inner peripheral rotor 11, it resists the stress generated during high rotation of the motor 10. Thus, a pressure directed radially inward acts.

As described above, according to the electric motor 10 according to the present embodiment, the rotation of the electric motor 10 is performed in the centrifugal pressure chamber 59a provided in the vicinity of the gap 60 between the inner peripheral rotor 11 and the outer peripheral rotor 12. As the number increases, the accumulated centrifugal fluid pressure changes in an increasing tendency, and this centrifugal fluid pressure acts on the gap 60 between the inner rotor 11 and the outer rotor 12. In particular, on the outer peripheral surface 21A of the inner peripheral rotor core 21 holding the permanent magnets 11a,..., 11a in the inner peripheral rotor 11, the stress generated during high rotation of the motor 10 is resisted. Then, the centrifugal fluid pressure directed radially inwardly acts, and the thickness of the outer peripheral side of the inner peripheral rotor core 21 of the inner peripheral rotor 11 can be reduced, and the inner peripheral rotor 11 and Each permanent magnet 11a, 12 of the outer rotor 12 The distance between each other can be shortened appropriately, the variable width of the induced voltage constant of the electric motor 10 can be increased efficiently.
Furthermore, since the centrifugal pressure chamber 59a includes the screw orifice 31f, for example, even when air or the like is mixed into the hydraulic oil, contaminants such as air can be discharged to the outside through the screw orifice 31f. .

  In the above-described embodiment, the hydraulic fluid flowing out from the first pressure chamber 56 and the second pressure chamber 57 flows through the fluid passage 59b by centrifugal force. However, the present invention is not limited to this. Regardless of the relative position, notches are provided in the respective walls of the first pressure chamber 56 and the second pressure chamber 57 so that the fluid passage 59b can always be opened in the first pressure chamber 56 and the second pressure chamber 57. May be.

  In the above-described embodiment, the fluid passages 59b and 59b are formed by the annular grooves 31b and 31b of the pair of drive plates 31 and 31, but the present invention is not limited thereto. The fluid passage 59b may be formed by at least one of the annular grooves 31b of the drive plates 31 and 31.

It is principal part sectional drawing which shows the electric motor which concerns on one Embodiment of this invention. It is a front view which abbreviate | omitted the near drive plate which shows the field-weakening state of the inner peripheral side rotor of an electric motor which concerns on one Embodiment of this invention, an outer peripheral side rotor, and a rotation mechanism. It is the elements on the outer peripheral side of the electric motor which concern on one Embodiment of this invention, and the bolt fastening part periphery of a drive plate, (a) Before an assembly | attachment, (b) The partial expanded sectional view after an assembly | attachment. It is a front view which abbreviate | omitted the near drive plate which shows the strong field state of the inner peripheral side rotor of an electric motor which concerns on one Embodiment of this invention, an outer peripheral side rotor, and a rotation mechanism. FIG. 5A is a diagram schematically showing a strong field state in which the permanent magnets of the inner circumferential rotor and the permanent magnets of the outer circumferential rotor are arranged in the same polarity, and FIG. It is a figure which shows typically the field-weakening state by which the permanent magnet of the side rotor and the permanent magnet of the outer peripheral side rotor were arrange | positioned with a counter electrode. It is a graph which shows the induced voltage in the strong field state and weak field state shown in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Electric motor 11 Inner peripheral side rotor 11a Permanent magnet (Inner peripheral side permanent magnet)
12 Outer peripheral rotor 12a Permanent magnet (outer peripheral permanent magnet)
14 Rotating mechanism (rotating means)
21 Inner rotor core (iron core)
31 Drive plate (end plate)
31f Screw orifice 32 Vane rotor (actuator part, vane rotor)
35c passage hole 35d passage hole 56 first pressure chamber (actuator section, working chamber)
57 Second pressure chamber (actuator section, working chamber)
59a Centrifugal pressure chamber 59b Fluid passage 60 Gap

Claims (6)

An outer peripheral side rotor having an inner peripheral side rotor having an inner peripheral side permanent magnet disposed in the circumferential direction and an outer peripheral side permanent magnet disposed in the circumferential direction, the rotation axes of which are arranged coaxially. ,
Rotation capable of changing the relative phase between the inner circumferential rotor and the outer circumferential rotor by rotating at least the inner circumferential rotor or the outer circumferential rotor about the rotation axis. An electric motor comprising means,
The rotating means includes an actuator unit that rotates by receiving the pressure of a fluid supplied from the outside,
A fluid passage that communicates the actuator section with a gap between the inner rotor and the outer rotor;
An electric motor comprising a centrifugal pressure chamber for accumulating centrifugal fluid pressure accompanying rotation of the electric motor in the vicinity of the gap portion of the fluid passage. The actuator unit is provided in any one of the inner circumferential rotor and the outer circumferential rotor and supplied with the fluid, and is either one of the inner circumferential rotor or the outer circumferential rotor. A vane rotor that is configured integrally with the other and disposed in the working chamber, and that rotates around the rotation shaft under the pressure of the fluid;
The electric motor according to claim 1, wherein the vane rotor includes a passage hole through which the fluid supplied from the outside to the working chamber flows. 3. The electric motor according to claim 2, wherein the wall portion of the working chamber includes a notch portion that allows the fluid passage to be always opened in the working chamber regardless of a relative position of the vane rotor. A pair of end plates that are fixed integrally with the vane rotor and the outer circumferential rotor and cover both end faces of the inner circumferential rotor in the axial direction;
The electric motor according to claim 3, wherein the fluid passage is formed in at least one of the pair of end plates. The electric motor according to claim 4, wherein the centrifugal pressure chamber is formed by the end plate and an iron core portion of the inner peripheral rotor. The electric motor according to claim 5, wherein the centrifugal pressure chamber includes a screw orifice in the end plate.

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