CN110277874B

CN110277874B - Variable magnetic field rotating electrical machine and vehicle provided with same

Info

Publication number: CN110277874B
Application number: CN201910202073.1A
Authority: CN
Inventors: 三浦雅哉; 久保田芳永
Original assignee: Honda Motor Co Ltd
Current assignee: Honda Motor Co Ltd
Priority date: 2018-03-16
Filing date: 2019-03-15
Publication date: 2021-06-29
Anticipated expiration: 2039-03-15
Also published as: JP2019161971A; CN110277874A

Abstract

The invention provides a variable magnetic field rotating motor which can easily adjust a magnetic field through a simple structure and realize miniaturization and a vehicle with the variable magnetic field rotating motor. The movable core displacement mechanism (20) comprises: cylinder chambers (46a, 46b) for storing working oil in accordance with the rotational speed of the rotor (16); a piston member (52) provided so as to be displaceable along the cylinder chamber; and a valve mechanism (21) capable of switching between discharge and accumulation of the hydraulic oil supplied into the cylinder chamber, wherein the valve mechanism (21) has a spool (82), the spool (82) is slidably housed in a valve holding chamber (80), and the spool (82) and the piston member (52) are displaced in the axial direction of the shaft (18) in accordance with increase and decrease in the amount of accumulated hydraulic oil in the cylinder chamber and the valve holding chamber (80), thereby displacing the movable core (40) in the axial direction of the shaft (18) in accordance with the piston member (52).

Description

Variable magnetic field rotating electrical machine and vehicle provided with same

Technical Field

The present invention relates to a variable field rotating electrical machine and a vehicle including the variable field rotating electrical machine.

Background

In general, in the case of a rotating electrical machine, when the torque density during low-speed rotation is increased by increasing the magnet interlinkage magnetic flux, the iron loss and the weak field copper loss increase during high-speed rotation. On the other hand, there is known a variable magnetic field rotating electrical machine capable of adjusting a magnetic field so as to obtain appropriate rotating electrical machine characteristics (for example, torque, output, etc.) according to a usage situation.

For example, patent document 1 discloses a variable field rotating electric machine in which a stator is axially drawn out with respect to a rotor by a wire-type traction device. Thus, in patent document 1, the magnet interlinkage magnetic flux can be reduced to suppress the iron loss to a low level.

Prior art documents

Patent document

Patent document 1: japanese laid-open patent publication No. 2010-57209

Problems to be solved by the invention

However, in the variable magnetic field rotating electrical machine disclosed in patent document 1, since the magnetic field is adjusted using the wire-type traction device that axially pulls out the stator, there are disadvantages that the structure becomes complicated and the rotating electrical machine becomes large.

Disclosure of Invention

The present invention has been made in view of the above problems, and an object of the present invention is to provide a variable magnetic field rotating electrical machine that can be easily adjusted in magnetic field with a simple configuration and can be reduced in size, and a vehicle including the variable magnetic field rotating electrical machine.

Means for solving the problems

In order to achieve the above object, the present invention is a variable magnetic field rotating electrical machine including a rotor provided so as to be integrally rotatable around an axis of a rotor shaft, the rotor having a movable core provided thereon, the variable magnetic field rotating electrical machine including a displacement mechanism for displacing the movable core in an axial direction of the rotor shaft, the displacement mechanism including: a cylinder chamber for storing working oil in accordance with the rotational speed of the rotor; a piston member coupled to one end portion of the movable core in the axial direction and provided to be displaceable along the cylinder chamber; a sealing member provided to the piston member; a cylinder portion including the piston member, the cylinder chamber, and the seal member; and a valve mechanism capable of switching between discharge and accumulation of the hydraulic oil supplied into the cylinder chamber, the valve mechanism including: a valve body slidably housed in the valve holding chamber; a valve biasing unit that is disposed at one end portion of the valve body in the axial direction and biases the valve body toward the other end side; and a hydraulic oil pressure receiving surface that is provided at the other end portion of the valve body in the axial direction, and displaces the valve body and the piston member in the axial direction of the rotor shaft in accordance with an increase or decrease in the amount of accumulated hydraulic oil in the cylinder chamber and the valve holding chamber, thereby displacing the movable core in the axial direction of the rotor shaft in accordance with the piston member.

The "working oil" is a fluid having both functions of a lubricating oil having a lubricating effect and a refrigerant having a cooling effect.

Effects of the invention

In the present invention, a variable magnetic field rotating electrical machine and a vehicle including the variable magnetic field rotating electrical machine, in which the magnetic field can be easily adjusted and the size can be reduced with a simple configuration, can be obtained.

Drawings

Fig. 1 is a longitudinal sectional view of the general structure of a variable magnetic field rotating electric machine according to an embodiment of the present invention.

Fig. 2 is a transverse sectional view of the variable magnetic field rotating electric machine shown in fig. 1.

Fig. 3 is a longitudinal sectional view of a spool valve constituting the valve mechanism shown in fig. 1 along the axial direction, and left and right side views showing one end surface and the other end surface of the spool valve along the axial direction.

Fig. 4 is an explanatory diagram illustrating operations of the movable core displacement mechanism and the valve mechanism when the rotor of the variable field rotating electric machine rotates at a low speed.

Fig. 5 is an explanatory diagram illustrating operations of the movable core displacement mechanism and the valve mechanism when the rotor of the variable field rotating electric machine rotates at high speed.

Fig. 6 is a partial cross-sectional view showing a modification of the hydraulic oil passage.

Description of the symbols:

10 variable magnetic field rotating electric machine

16 rotor

18-shaft

20 Displacement mechanism of movable iron core (Displacement mechanism)

21 valve mechanism

24 stator core

28 coil end

40 movable iron core

46. 46a, 46b cylinder chamber

52 piston component

58 piston seal (sealing component)

70 cylinder part

80 valve holding chamber

82 sliding valve (valve core)

84 spiral spring (valve force applying unit)

90 working oil pressure bearing surface

Axis of A shaft (rotation center)

Detailed Description

Next, embodiments of the present invention will be described in detail with reference to the drawings as appropriate.

Fig. 1 is a longitudinal sectional view of a general structure of a variable magnetic field rotating electric machine according to an embodiment of the present invention, and fig. 2 is a transverse sectional view of the variable magnetic field rotating electric machine shown in fig. 1.

As shown in fig. 1, a variable magnetic field rotating electrical machine 10 (hereinafter, simply referred to as a rotating electrical machine 10) according to an embodiment of the present invention is a traveling motor mounted on a vehicle such as a hybrid vehicle or an electric vehicle, for example. The rotating electric machine 10 includes a housing 12, a stator 14, a rotor 16, a shaft (rotor shaft) 18, a movable core displacement mechanism (displacement mechanism) 20, and a valve mechanism 21.

The housing 12 accommodates the stator 14, the rotor 16, the movable core displacement mechanism 20, and the valve mechanism 21, and is rotatably supported via a set of

bearings

22a and 22b attached to the housing 12.

As shown in fig. 2, the stator 14 includes a stator core 24, coils 26 of a plurality of phases (e.g., U-phase, V-phase, and W-phase) attached to the stator core 24, and coil ends 28 (see fig. 1). The stator 14 generates a magnetic field by flowing a current in the coil 26. The stator core 24 is formed in a cylindrical shape extending in the axial direction. The stator core 24 is formed by laminating a plurality of electromagnetic steel plates in the axial direction, for example.

In the stator core 24, coil slots 30 (see fig. 2) into which the coils 26 are inserted are arranged in parallel in the circumferential direction. The coil 26 is configured by, for example, inserting a plurality of conductor segments made of rectangular wires into the coil slots 30 of the stator core 24 and connecting the segments by segment coils at portions protruding from the stator core 24 in the axial direction.

The rotor 16 is formed as an embedded magnet. The rotor 16 is disposed radially inward of the stator 14. The rotor 16 includes a rotor core 32, a permanent magnet 34 embedded (mounted) in the rotor core 32, and a pair of

end plates

36a and 36b (see fig. 1) disposed to face one end surface and the other end surface of the rotor core 32, respectively.

The rotor core 32 is formed in a cylindrical shape extending in the axial direction, and is disposed to face the inner circumferential surface of the stator core 24. The rotor core 32 is configured by stacking a plurality of electromagnetic steel plates in the axial direction, for example.

The shaft 18 is inserted into the rotor core 32 in the radial direction, and the shaft 18 is fixed to the center portion of the rotor core 32 by press fitting or the like, for example. The shaft 18 and the rotor core 32 are provided so as to be integrally rotatable around an axis a (rotation center) of the shaft 18 (see fig. 1).

The rotor core 32 is provided with magnet mounting portions 38 (see fig. 2) for mounting the permanent magnets 34 in predetermined circumferential angular regions, respectively. The plurality of magnet attachment portions 38 are arranged at equal intervals along the circumferential direction with a predetermined distance apart on the outer peripheral portion of the rotor core 32. The magnet attachment portion 38 is formed in a rectangular shape having a longitudinal direction perpendicular to the radial direction when viewed from the axial direction.

The permanent magnet 34 is inserted into the magnet mounting portion 38 and fixed to the rotor core 32 by, for example, resin, adhesive, or the like.

The rotor core 32 is provided with a plurality of movable cores 40 arranged at equal angular intervals in the circumferential direction. Each of the plurality of movable cores 40 is disposed between a pair of circumferentially adjacent magnet mounting portions 38.

By disposing the movable core 40 in the housing slot 42 of the rotor core 32, the movable core 40 is disposed between a pair of permanent magnets 34 adjacent in the circumferential direction and having different polarities. The movable core 40 has a substantially elliptical shape in cross section perpendicular to the axis corresponding to the housing slot 42. The movable core 40 is provided so as to be displaceable in the axial direction in the housing slot 42 via a movable core displacement mechanism 20 described later.

Each of the

end plates

36a and 36b is formed of an annular plate having substantially the same shape as the rotor core 32. The

end plates

36a, 36b serve as escape prevention members for the permanent magnets 34 fitted in the magnet fitting portion 38 of the rotor core 32. A substantially circular through hole through which the shaft 18 passes is formed in the center of the

end plates

36a and 36 b.

As shown in fig. 1, a hole 44 is formed on the outer peripheral portion side of one end plate 36a when visually recognized from the axial direction, and the hole 44 has a larger diameter than the movable core 40 and penetrates the end plate 36 a. The hole 44 is formed in a shape corresponding to a cross section perpendicular to the axis of the movable core 40, that is, a substantially elliptical cross section in side view. The movable core 40 is disposed in the hole 44 so as to be able to advance and retreat.

The movable core displacement mechanism 20 displaces the plurality of movable cores 40 simultaneously or substantially simultaneously along the axial direction of the rotor shaft (axis a), and the plurality of movable cores 40 are arranged at equal angles in the circumferential direction on the outer peripheral portion side when the rotor core 32 is viewed from the side.

The movable core displacement mechanism 20 is disposed in the housing 12 protruding from one end plate 36a toward the outside in the axial direction of the rotor shaft on one end surface of the rotor core 32. The housing 12 includes an outer diameter wall portion 48a located on the outer side, an inner diameter wall portion 48b located on the inner side, a side annular wall portion 48c connecting a side surface of the outer diameter wall portion 48a and a side surface of the inner diameter wall portion 48b, a disc-shaped wall portion 48d facing the end plate 36a on one side, and an intermediate wall portion 48e disposed between the outer diameter wall portion 48a and the inner diameter wall portion 48b along the radial direction.

The outer diameter wall portion 48a is formed in a cylindrical shape along the outer diameter side of the rotor core 32. The inner diameter wall portion 48b is formed in a cylindrical shape along the inner diameter side of the rotor core 32 while having a diameter smaller than the outer diameter wall portion 48 a. The outer diameter wall portion 48a and the inner diameter wall portion 48b are formed to have the same width dimension substantially parallel to the axial direction of the shaft 18. The side annular wall portion 48c is formed of an annular body that connects a side portion of the outer diameter wall portion 48a and a side portion of the inner diameter wall portion 48b, and the side portion of the outer diameter wall portion 48a and the side portion of the inner diameter wall portion 48b are substantially parallel to each other while maintaining a predetermined separation distance in the radial direction.

An internal space, i.e., a cylinder chamber 46(46a, 46b), is formed by surrounding the intermediate wall portion 48e positioned on the upper side, the inner diameter wall portion 48b positioned on the lower side, and a side annular wall portion 48c connecting the intermediate wall portion 48e and one side of the inner diameter wall portion 48b in the vertical direction, in cross section. The cylinder chamber 46 is divided into a first (one) cylinder chamber 46a and a second (the other) cylinder chamber 46b by a piston member 52 described later. When both the one cylinder chamber 46a and the other cylinder chamber 46b are collectively referred to as "cylinder chamber 46". As will be described later, the hydraulic oil is stored in the cylinder chamber 46 in accordance with the rotation speed of the rotor 16. The "working oil" is a fluid having both functions of a lubricating oil having a lubricating effect and a refrigerant having a cooling effect.

A piston member 52 is housed in the cylinder chamber 46, and the piston member 52 is provided so as to be displaceable along the cylinder chamber 46. The piston member 52 is connected to one end portion of the movable core 40 in the axial direction, and is provided so as to be displaced integrally with the movable core 40. The piston member 52 is coupled to one end portion of the movable core 40 in the axial direction.

The piston member 52 includes: a piston main body formed of a plate body having a substantially rectangular shape in side view; a connecting portion protruding from the piston main body toward the movable core 40 and connected to one end portion of the movable core 40 in the axial direction; and a seal-fitted portion 54 formed continuously with the piston main body and located on the outer diameter side of the coupling portion and the movable core 40. The piston member 52 has a stroke amount (displacement amount) set in advance by a pair of stoppers (not shown) provided in the cylinder chamber 46.

The seal-fitted portion 54 is formed of an annular body extending substantially parallel to the outer peripheral portion of the rotor 16 in the circumferential direction. An annular groove 56 is formed in the seal fitted portion 54, and the annular groove 56 is formed in a substantially rectangular shape in cross section and opens toward the inner wall of the outer diameter wall portion 48 a. A piston seal (seal member) 58 is fitted to the annular groove 56.

The piston seal 58 is in sliding contact with the intermediate wall portion 48e and the inner diameter wall portion 48b when viewed in cross section, and functions to seal the cylinder chamber 46 into the one cylinder chamber 46a and the other cylinder chamber 46 b. The seal-fitted portion 54 formed of an annular body connects and connects the piston members 52 arranged in plurality along the outer peripheral portion of the rotor 16 in the circumferential direction. The piston seal 58 fitted in the annular groove 56 is located on the outer diameter side of the coupling portion and the movable core 40, is arranged substantially in parallel along the outer peripheral portion of the rotor 16, and is continuously formed in an annular shape.

The inner wall of the seal attached portion 54 facing the cylinder chamber 46 is pressed by the hydraulic oil accumulated on the outer diameter side of the cylinder chamber 46, and functions as a pressure receiving surface to which the pressing force of the hydraulic oil is applied to displace the piston member 52.

A disc-shaped wall portion 48d substantially perpendicular to the inner diameter wall portion 48b is provided radially inward of the inner diameter wall portion 48 b. A plurality of hydraulic oil passages 68 are formed in an inner wall of the circular plate-shaped wall portion 48d facing the end plate 36a, and the plurality of hydraulic oil passages 68 communicate with the

cylinder chambers

46a and 46b to supply hydraulic oil to the

cylinder chambers

46a and 46 b. Each of the hydraulic oil passages 68 is arranged to radially extend in the radial direction.

As shown in fig. 1, each of the hydraulic oil passages 68 extends continuously along the disc-shaped wall portion 48d, the inner diameter wall portion 48b, and the side annular wall portion 48 c. In the cross section, the inner diameter wall portion 48b is provided with a pair of

supply ports

69a, 69b, and the pair of

supply ports

69a, 69b communicate with the

cylinder chambers

46a, 46b to supply the working oil to the

cylinder chambers

46a, 46b, respectively. The supply port 69a is provided so as to be able to communicate with the cylinder chamber 46a on one side. The supply port 69b is provided so as to be able to communicate with the other side cylinder chamber 46 b. Further, a supply port 71 is provided on the outer diameter side of the side annular wall portion 48c, and the supply port 71 supplies the hydraulic oil to the valve holding chamber 80 at the end of each hydraulic oil passage 68.

The piston member 52, the cylinder chamber 46, and the piston seal 58 constitute a cylinder portion 70. The cylinder portion 70 is disposed on the inner diameter side of the coil end 28 of the coil 26.

The valve mechanism 21 switches between discharge and accumulation of the hydraulic oil supplied to each of the

cylinder chambers

46a and 46 b. The valve mechanism 21 includes a spool valve (valve body) 82 and a coil spring (valve biasing means) 84 (see fig. 1) housed in the valve holding chamber 80. The valve holding chamber 80 is located on the inner diameter side of the outer diameter wall portion 48a and is disposed on the outer diameter side of the cylinder chamber 46.

The spool 82 is housed so as to be slidable and displaceable along the valve holding chamber 80 (see fig. 1). As shown in fig. 3, the spool 82 has a valve body 83 having a substantially cylindrical shape. A first shoulder portion 86a, a second shoulder portion 86b, and a third shoulder portion 86c are arranged in this order along the axial direction on the outer peripheral surface of the valve main body 83. The first to third shoulder portions 86a to 86c have the same outer diameter. The outer diameters of the first to third shoulder portions 86a to 86c are formed to be substantially the same as the inner diameter of the holding hole forming the valve holding chamber 80.

An annular recess is formed between the first shoulder portion 86a and the second shoulder portion 86b of the valve main body 83, and a first small diameter portion 88a is provided by the annular recess. An annular recess is formed between the second shoulder portion 86b and the third shoulder portion 86c, and a second small diameter portion 88b is provided by the annular recess.

The coil spring 84 is disposed at one end portion of the spool 82 in the axial direction via the recessed portion, and presses (biases) the spool 82 toward the other end portion side (the side annular wall portion 48c side) (see fig. 1). A working oil pressure receiving surface 90 is provided on the other end portion side (the side opposite to the side on which the coil spring 84 is disposed) of the spool 82 in the axial direction, and the working oil pressure receiving surface 90 is pressed by the working oil supplied into the valve holding chamber 80. The hydraulic oil pressure receiving surface 90 is formed of an annular stepped portion having an annular convex portion 92 at the center.

As shown in fig. 1, the valve holding chamber 80 is formed by an internal space surrounded by the outer diameter wall portion 48a located on the upper side in cross section, the intermediate wall portion 48e located on the lower side, and the side annular wall portion 48c that vertically connects one side of the outer diameter wall portion 48a and the intermediate wall portion 48 e. Further, a pair of

discharge ports

94a, 94b are provided in the outer diameter wall portion 48a located on the upper side, and the pair of

discharge ports

94a, 94b discharge the working oil introduced into the valve holding chamber 80 to the outside of the valve holding chamber 80.

A set of

communication ports

96a, 96b are formed in the intermediate wall portion 48e, and the set of

communication ports

96a, 96b communicate the cylinder chamber 46 and the valve holding chamber 80 with each other. The

communication ports

96a and 96b lead out the hydraulic oil introduced into the cylinder chamber 46 into the valve holding chamber 80 in accordance with the slide position of the spool 82. The communication port 96a and the discharge port 94a are provided so as to be able to communicate with each other in accordance with the positional relationship of the spool 82 (see fig. 5 described later). Further, the communication port 96b and the discharge port 94b are provided so as to be able to communicate with each other in accordance with the positional relationship of the spool 82 (see fig. 4 described later).

The disc-shaped wall portion 48d has an inner diameter flange 72, and the inner diameter flange 72 is located near the inner diameter side of the shaft 18 and projects in the axial direction of the shaft 18. A resolver 74 for detecting the rotation angle of the rotating electric machine 10 is disposed in the inner diameter flange 72. The resolver 74 includes a resolver stator fixed to the housing 12 side and a resolver rotor press-fitted and fixed to the shaft 18 side and rotating integrally with the shaft 18.

The rotary electric machine 10 of the present embodiment is basically configured as described above, and its operational effects will be described below.

Fig. 4 is an explanatory diagram showing the operation of the movable core displacement mechanism and the valve mechanism at the time of low-speed rotation of the rotor of the variable-field rotary electric machine, and fig. 5 is an explanatory diagram showing the operation of the movable core displacement mechanism and the valve mechanism at the time of high-speed rotation of the rotor of the variable-field rotary electric machine. In the initial position of the spool valve 82, the annular projecting portion 92 on the end portion side is in a state of abutting against the side annular wall portion 48c by the spring force of the coil spring 84 (see fig. 4).

For example, the working oil (lubricant oil, refrigerant) is fed to the rotating electric machine 10 via a pump (not shown). The hydraulic oil is supplied from the shaft 18 side into the cylinder chamber 46 through the hydraulic oil passage 68.

When the rotor 16 of the rotating electrical machine 10 rotates, the piston member 52 rotates together with the rotor core 32, and a centrifugal force is applied to the piston member 52. As shown in fig. 4, when the rotor 16 of the rotating electrical machine 10 rotates at a predetermined low speed (low-speed rotation), the hydraulic oil is introduced into only one of the cylinder chambers 46a through the hydraulic oil passage 68 and the supply port 69 a. The hydraulic oil introduced into one of the cylinder chambers 46a is accumulated only on the outer diameter side of one of the cylinder chambers 46a by the action of centrifugal force. The hydraulic oil accumulated on the outer diameter side of one cylinder chamber 46a presses the piston member 52 toward the other cylinder chamber 46 b. As a result, centrifugal pressure is generated only in one of the cylinder chambers 46 a. The piston member 52 is displaced in the arrow B direction by the low centrifugal pressure of the working oil.

When the rotor 16 of the rotating electrical machine 10 rotates at a low speed, the spool 82 is in the initial position (see fig. 4). In the initial position of the spool valve 82, the communication port 96a and the discharge port 94a on one side are in the blocked non-communication state by the second shoulder portion 86b, respectively. The other communication port 96b and the discharge port 94b are in a communication state via the second small diameter portion 88 b. Accordingly, the hydraulic oil supplied from the supply port 69a to the one cylinder chamber 46a is accumulated in the one cylinder chamber 46a, and a low centrifugal pressure is generated to press the piston member 52 in the arrow B direction. On the other hand, the hydraulic oil supplied from the supply port 69b into the other cylinder chamber 46b is discharged to the outside through the communication port 96b and the discharge port 94b in a communicating state.

As shown in fig. 5, when the rotor 16 of the rotating electrical machine 10 rotates at a predetermined high speed (high-speed rotation), the working oil is introduced only into the other cylinder chamber 46b through the supply port 69 b. A centrifugal force acts on the hydraulic oil (centrifugal hydraulic pressure) accumulated on the outer diameter side of the other cylinder chamber 46b, and the pressure of the hydraulic oil is increased. The piston member 52 is pressed in the direction of the small arrow shown in fig. 5 by the working oil of which pressure is increased (high centrifugal hydraulic pressure). That is, the inner wall of the piston member 52 facing the other cylinder chamber 46b functions as a pressure receiving surface to which a pressing force (centrifugal hydraulic pressure) of the hydraulic oil is applied, and the piston member 52 and the movable core 40 are integrally displaced in the arrow C direction by the pressing force (centrifugal hydraulic pressure).

In other words, when the rotor 16 of the rotating electrical machine 10 rotates at a predetermined high speed (rotates at a high speed), the centrifugal force is applied to the hydraulic oil accumulated on the outer diameter side of the other cylinder chamber 46b, and the hydraulic oil is pressurized. The pressurizing force applied to the hydraulic oil increases as the centrifugal force increases. The pressurized hydraulic oil generates a pressing force that presses the pressure receiving surface (inner wall 54a) of the piston member 52, and the piston member 52 is displaced in the direction of the arrow C (axial direction of the rotor shaft). The movable core 40 coupled to the piston member 52 is displaced integrally in the arrow C direction along with the piston member 52.

As a result, the movable core 40 is displaced in the arrow C direction integrally with the piston member 52 from the initial position disposed in the housing slot 42 of the rotor core 32. The predetermined high rotation (high-speed rotation) of the rotor 16 is set in advance based on, for example, performance required of the rotating electrical machine 10, the size of the rotating electrical machine 10, and the like.

When the rotor 16 of the rotating electrical machine 10 rotates at a high speed, the pressure receiving surface 90 of the spool 82 is pressed by the hydraulic oil introduced into the valve holding chamber 80 through the supply port 71. The spool valve 82 is displaced from the initial position in the arrow D direction against the spring force of the coil spring 84. Thereby, the one communication port 96a and the discharge port 94a are in a communication state via the first small diameter portion 88a, respectively. Further, the other side communication port 96b and the discharge port 94b are in the blocked non-communication state by the second shoulder portion 86b, respectively. As a result, the hydraulic oil supplied from the supply port 69b to the other cylinder chamber 46b accumulates in the other cylinder chamber 46b, and a high centrifugal pressure is generated to press and displace the piston member 52 in the arrow C direction. On the other hand, the hydraulic oil supplied from the supply port 69a into the one cylinder chamber 46a is discharged to the outside through the communication port 96a and the discharge port 94a which are in a communication state. When the rotor 16 of the rotating electric machine 10 rotates at a high speed, centrifugal pressure is generated only in the other cylinder chamber 46 b. The piston member 52 is displaced in the arrow C direction by the high centrifugal pressure of the working oil.

In this way, in the present embodiment, the hydraulic oil accumulated on the outer diameter side of the cylinder chamber 46 is pressurized by the centrifugal force, and the pressing force that presses the pressure receiving surface of the piston member 52 in the axial direction (the arrow B direction or the arrow C direction) can be generated. Thus, in the present embodiment, the piston member 52 and the movable core 40 can be displaced integrally in the axial direction of the rotor shaft (the direction of arrow B or the direction of arrow C).

In the present embodiment, the spool valve 82 can switch between discharging and accumulating the hydraulic oil supplied to the one cylinder chamber 46a and the other cylinder chamber 46 b. That is, at the time of low-speed rotation shown in fig. 4, the hydraulic oil can be accumulated in the one cylinder chamber 46a to generate centrifugal hydraulic pressure, and the hydraulic oil in the other cylinder chamber 46b can be discharged to the outside. On the other hand, at the time of high-speed rotation shown in fig. 5, the hydraulic oil can be accumulated in the other cylinder chamber 46b to generate centrifugal hydraulic pressure, and the hydraulic oil in the one cylinder chamber 46a can be discharged to the outside. As a result, in the present embodiment, by providing the valve mechanism 21 including the spool 82, for example, the timing of applying the centrifugal hydraulic pressure can be appropriately controlled.

That is, since the centrifugal hydraulic pressure is proportional to the square of the rotational speed of the rotor 16, the piston member 52 (movable core 40) may be displaced in a free state before a required centrifugal hydraulic pressure load is obtained, for example. In addition, there are situations where it takes time, or a higher rotational speed of the rotor 16 may be required, before the required centrifugal hydraulic load is achieved.

In the present embodiment, the piston member 52 can be further displaced step by the switching action of the spool valve 82. In other words, by switching between the discharge and the accumulation of the hydraulic oil by the spool 82, the centrifugal pressure generated in the cylinder chamber 46a on the one side can be gradually switched to the high centrifugal pressure generated in the cylinder chamber 46b on the other side. As a result, in the present embodiment, it is possible to appropriately avoid the piston member 52 (movable core 40) from being displaced before a required centrifugal hydraulic pressure load is obtained. Further, the piston member 52 is displaced by the switching action of the spool valve 82, so that a return spring or the like for biasing the piston member 52 is not required. Thus, in the present embodiment, the number of components can be reduced, and the manufacturing cost can be reduced.

In the present embodiment, for example, when oil having a high viscosity is used as the working oil, it is possible to appropriately suppress the centrifugal hydraulic pressure generated in a low-temperature environment from becoming excessively large.

As a result, in the present embodiment, by providing the valve mechanism 21 including the movable core displacement mechanism 20 and the spool 82, the rotating electrical machine 10 can be obtained which can be easily adjusted in magnetic field with a simple structure and can be reduced in size.

In the present embodiment, the cylinder portion 70 having the piston member 52 and the like is disposed on the inner diameter side of the coil end 28 of the coil 26. Thus, in the present embodiment, space can be effectively used and saved.

Fig. 6 is a partial cross-sectional view showing a modification of the hydraulic oil passage. The same reference numerals are given to the same components as those in fig. 4 and 5, and detailed description thereof will be omitted.

In the modification shown in fig. 6, a plurality of hydraulic oil discharge ports 98 are provided, and hydraulic oil is discharged to the outside from the hydraulic oil discharge ports 98. This can appropriately avoid the accumulation of the working oil in the cylinder chamber 46a on the one side and the cylinder chamber 46b on the other side. The hydraulic oil discharged from the plurality of hydraulic oil discharge ports 98 is used for lubricating and cooling, for example, windings, gears, and the like, not shown, disposed in the vicinity thereof.

By mounting such a rotating electric machine 10 on a vehicle not shown, it is possible to obtain a vehicle that can be easily adjusted in magnetic field with a simple structure and can be made compact.

In the present embodiment and the other embodiments, the movable core displacement mechanism 20 for displacing the movable core 40 in the axial direction of the rotor shaft is exemplified as the displacement mechanism, but the present invention is not limited to this. For example, as the displacement mechanism, a permanent magnet displacement mechanism may be employed, and the permanent magnet 34 may be displaced in the axial direction of the rotor shaft by using the permanent magnet displacement mechanism.

Claims

1. A variable magnetic field rotating electrical machine having a rotor provided so as to be integrally rotatable around an axis of a rotor shaft, and a movable core provided on the rotor,

the variable magnetic field rotating electrical machine includes a displacement mechanism for displacing the movable core in an axial direction of the rotor shaft,

the displacement mechanism includes:

a cylinder chamber for storing working oil in accordance with the rotational speed of the rotor;

a piston member coupled to one end portion of the movable core in the axial direction and provided to be displaceable along the cylinder chamber;

a sealing member provided to the piston member;

a cylinder portion including the piston member, the cylinder chamber, and the seal member; and

a valve mechanism capable of switching between discharge and accumulation of the hydraulic oil supplied into the cylinder chamber,

the valve mechanism has:

a valve body slidably housed in the valve holding chamber;

a valve biasing unit that is disposed at one end portion of the valve body in the axial direction and biases the valve body toward the other end side; and

a working oil pressure receiving surface provided at the other end portion of the valve element in the axial direction,

the movable core is displaced in the axial direction of the rotor shaft in accordance with the piston member by displacing the valve element and the piston member in the axial direction of the rotor shaft in accordance with an increase or decrease in the amount of accumulated hydraulic oil in the cylinder chamber and the valve holding chamber.

2. The variable magnetic field rotating electrical machine according to claim 1,

the variable magnetic field rotating electric machine is provided with a stator core and a coil end,

the cylinder portion is disposed on an inner diameter side of the coil end.

3. The variable magnetic field rotating electrical machine according to claim 1 or 2,

the valve core is composed of a slide valve,

the spool valve switches between discharge and accumulation of the hydraulic oil supplied to the cylinder chamber, and thereby the centrifugal pressure generated in one of the cylinder chambers divided by the piston member and the centrifugal pressure generated in the other of the cylinder chambers can be switched.

4. A vehicle, characterized in that,

the vehicle is provided with the variable magnetic field rotating electrical machine according to any one of claims 1 to 3.