JP2008151214A - Vane type hydraulic equipment, motor, and valve timing control device for internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide vane type hydraulic equipment improving energy utilization efficiency by preventing leakage of hydraulic fluid caused by the fluid flowing around an axial side portion of a partition wall, and a motor and a valve timing control device for an internal combustion engine, using the vane type hydraulic equipment. <P>SOLUTION: A seal groove 32 is formed in the side surface of the partition wall 21 of an annular housing 15, and a side wall seal member 33 brought in tight contact with a drive plate 16 is attached to the seal groove 32. The side wall seal member 33 prevents leakage of the hydraulic fluid between liquid chambers through a sliding clearance between the side surface of the partition wall 21 and the drive plate 16. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a vane hydraulic device such as a hydraulic actuator having a vane or a hydraulic motor, an electric motor using the vane hydraulic device, and a valve timing control device for an internal combustion engine.

  A valve timing control device is known as a device for arbitrarily changing the opening / closing timing of an intake valve or an exhaust valve (hereinafter referred to as “engine valve”) of an internal combustion engine. This valve timing control device is provided with phase changing means for changing the rotational phases of the output shaft of the internal combustion engine and the power transmission portion of the camshaft, and the phase changing means is controlled by the controller according to the driving situation of the vehicle. It is controlled (see, for example, Patent Document 1).

  As the phase changing means, for example, a vane type hydraulic actuator is used. This hydraulic actuator includes a substantially cylindrical housing closed on both sides in the axial direction by side wall members, and a vane rotor arranged coaxially and relatively rotatably on the inner peripheral side of the housing. A plurality of partition walls protrude from the inner peripheral surface in the circumferential direction, and a blade portion disposed between the partition walls on the housing side protrudes from the outer peripheral surface of the vane rotor. The vane section divides between adjacent partition walls in the housing into two liquid chambers, and hydraulic fluid is selectively supplied to and discharged from the two liquid chambers. When the housing and the vane rotor are rotated relative to one another, the working fluid is supplied to one liquid chamber before and after the blade portion, and the working fluid is discharged from the other liquid chamber.

In addition, a seal groove is formed on each of the front end surfaces of the partition wall and the blade portion so as to extend from one end to the other end in the axial direction, and in each seal groove, between the partition wall and the outer peripheral surface of the vane rotor, or A resin-made seal member that seals between the blade portion and the inner peripheral surface of the housing is accommodated, and a spring member that biases the seal member in the direction of the peripheral surface of the mating member is accommodated.
JP-A-9-303119

However, in this conventional vane type actuator, liquid leakage between the partition wall and the outer peripheral surface of the vane rotor and between the blade portion and the inner peripheral surface of the housing can be prevented by the seal member. In this case, hydraulic fluid may leak from the sliding gap between the axial side surface of the blade part functioning as the partition wall and the side wall of the housing. If the amount of hydraulic fluid leakage increases, unnecessary energy may be generated. Consumption will increase.
Such a problem is not limited to the vane actuator described above, and may occur in other hydraulic equipment such as a vane hydraulic pump when a similar seal structure is used.

  Therefore, the present invention uses a vane type hydraulic device capable of preventing the leakage of hydraulic fluid around the axial side portion of the partition wall and improving the energy utilization efficiency, and the vane type hydraulic device. An object of the present invention is to provide a valve timing control device for an electric motor and an internal combustion engine.

The invention according to claim 1, which solves the above-described problem, is a cylindrical member (for example, an annular housing 15 in an embodiment described later), and coaxially and relatively rotatable on the inner peripheral side of the cylindrical member. Arranged shaft members (for example, vane rotor 14 in the embodiment described later), the cylindrical member and axial members on both sides in the axial direction, together with the outer peripheral surface of the shaft member and the inner peripheral surface of the cylindrical member A side wall member (for example, a drive plate 16 in an embodiment described later) that forms a space portion, and a plurality of portions in the space portion are protruded from at least one of the outer peripheral surface of the shaft member and the inner peripheral surface of the cylindrical member. A blade-like partition wall (for example, a partition wall 21 in the later-described embodiment) and a partition wall partitioned into a liquid chamber (for example, an advance-side working chamber 24 and a retard-side working chamber 25 in the later-described embodiment) Axial direction at the wall tip A peripheral wall seal member (for example, a peripheral wall seal member 22 in an embodiment described later) disposed so as to extend from one end to the other end and in close contact with the peripheral wall of the mating member facing the front end surface of the partition wall; Side wall seal members disposed on both side surfaces so as to extend from the base end to the front end of the partition wall and in close contact with the side wall member facing the side wall of the partition wall (for example, the side wall seal member 33 in the embodiments described later) It is characterized by comprising.
Thereby, the space between the front end of the partition wall and the peripheral wall facing it is sealed by the peripheral wall seal member, and the space between both side surfaces of the partition wall and the side wall member facing it is sealed by the side wall seal member.

According to a second aspect of the present invention, in the vane hydraulic device according to the first aspect, an urging member (for example, a leaf spring 34 in an embodiment described later) is interposed between the partition member and the side wall seal member. It is characterized by being.
Thereby, the side wall seal members on both sides of the partition wall are pressed against the side wall member by the biasing member.

According to a third aspect of the present invention, in the vane hydraulic device according to the first aspect, the sidewall seal member is an elastic member.
As a result, the side wall seal members on both sides of the partition wall are pressed against the side wall member by its own elasticity.

According to a fourth aspect of the present invention, in the vane hydraulic device according to the first aspect, the side wall seal member is a corrugated plate member having at least one curved shape in a direction facing the side wall member. Features.
As a result, the seal members on both sides of the partition wall are pressed against the side wall member by the reaction force generated when the curved shape is deformed.

  The invention according to claim 5 is an inner circumferential rotor (for example, an inner circumferential side in an embodiment described later) in which a permanent magnet (for example, a permanent magnet 9 in an embodiment described later) is arranged along the circumferential direction. A rotor 6) and an outer peripheral rotor (for example, a permanent magnet is disposed along the circumferential direction, coaxially and relatively rotatably disposed on the outer peripheral side of the inner peripheral rotor. An outer periphery side rotor 5 in an embodiment described later, and phase changing means for changing the rotational phase of the inner periphery rotor and the outer periphery rotor relative to each other (for example, phase change in the embodiment described later) Means 12), for example, an electric motor 1 in an embodiment to be described later, wherein the phase changing means uses the vane hydraulic device according to any one of claims 1 to 4. The vane hydraulic device is separated by the partition wall. Is the by supplying and discharging hydraulic fluid in the circumferential direction around the liquid chamber, and wherein the obtaining a driving force for changing the rotational phase of the inner periphery side rotor and the outer periphery side rotor.

  According to a sixth aspect of the present invention, there is provided an output shaft from which the power of the internal combustion engine is output, a camshaft that rotates in conjunction with the output shaft and drives an engine valve of the internal combustion engine to open and close, 5. A valve timing control device for an internal combustion engine, comprising: a phase changing unit that relatively rotates the phase of the two to change the rotational phase of the two, and the phase changing unit includes the phase changing unit according to claim 1. The hydraulic fluid is supplied to and discharged from the fluid chambers in the circumferential direction separated by the partition wall of the vane hydraulic device to change the rotational phase of the camshaft and the output shaft. It is characterized by obtaining a driving force.

  According to the first aspect of the present invention, the gap between the tip of the partition member and the peripheral wall of the mating member is sealed by the peripheral wall seal member, and the gap between the side walls and the side wall member of the partition member is sealed by the side wall seal member. The leakage of the hydraulic fluid around the partition wall can be effectively prevented. Therefore, according to the present invention, it is possible to reduce the leakage of the working fluid when the device is operated, and to improve the energy utilization efficiency.

  According to the second aspect of the present invention, since the side wall seal members on both sides of the partition wall are pressed against the side wall member by the biasing member, liquid leakage between the both side surfaces of the partition wall and the side wall member is prevented by the side wall seal member. Since both sides of the partitioning member can be reliably pressed from both sides in the axial direction by the urging members, the partitioning member is centered in the axial direction by the urging members on both sides in the axial direction. Contact between the partition member and the side wall member can be avoided.

  According to the third aspect of the invention, since the side wall seal member is pressed against the side wall member by its own elasticity, liquid leakage between the both side surfaces of the partition wall and the side wall member is reliably prevented by the side wall seal member. Moreover, since both side surfaces of the partition member are similarly pressed from both sides in the axial direction by the side wall seal members, the partition member is centered in the axial direction by the side wall seal members on both sides in the axial direction, and the partition member and the side walls are Contact of members can be avoided.

  According to the fourth aspect of the present invention, the side wall member is pressed against the side wall member by the reaction force accompanying the deformation of the curved portion of the seal member, so that the side wall seal member ensures liquid leakage between the both side surfaces of the partition wall. In addition, since both side surfaces of the partition member are similarly pressed from both sides in the axial direction by the side wall seal members, the partition member is centered in the axial direction by the side wall seal members on both sides in the axial direction to Contact between the member and the side wall member can be avoided.

  According to the invention described in claim 5, since the phase changing means for changing the relative phase between the inner rotor and the outer rotor of the electric motor is constituted by a vane hydraulic device with less leakage of hydraulic fluid, A reliable phase change can be performed without increasing the size of the hydraulic fluid supply source for operating the phase change means.

  According to the sixth aspect of the present invention, the phase changing means for changing the rotational phases of the output shaft and the camshaft is constituted by a vane hydraulic device with little hydraulic fluid leakage, so that the phase changing means is operated. Thus, it is possible to perform a reliable phase change without increasing the size of the hydraulic fluid supply source.

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

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

  The rotor unit 3 includes an annular outer circumferential rotor 5 and an annular inner circumferential rotor 6 disposed coaxially inside the outer circumferential rotor 5, and includes the outer circumferential rotor 5 and the inner circumferential surface. The side rotor 6 is rotatable within a set angle range.

  The outer rotor 5 and the inner rotor 6 are formed by, for example, sintered rotor cores 7 and 8 made of sintered metal, and are biased toward the outer periphery of the rotor cores 7 and 8. A plurality of magnet mounting slots 7a, 8a are formed at equal intervals in the circumferential direction. In each of the magnet mounting slots 7a and 8a, two flat plate-like permanent magnets 9 and 9 magnetized in the thickness direction are mounted in parallel. Two permanent magnets 9, 9 mounted in the same magnet mounting slot 7a, 8a are magnetized in the same direction, and a pair of permanent magnets 9 mounted in each adjacent magnet mounting slot 7a, 7a and 8a, 8a. The magnetic poles are set so that the directions of the magnetic poles are opposite to each other. That is, in each of the rotors 5 and 6, a pair of permanent magnets 9 whose outer peripheral side is an N pole and a pair of permanent magnets 9 that are an S pole are alternately arranged in the circumferential direction. A notch 10 for controlling the flow of magnetic flux of the permanent magnet 9 is rotated between the adjacent magnet mounting slots 7a, 7a and 8a, 8a on the outer peripheral surfaces of the rotors 5, 6. It is formed along the axial direction of the children 5 and 6.

  The same number of magnet mounting slots 7a, 8a of the outer rotor 5 and inner rotor 6 are provided, and the permanent magnets 9 of the rotors 5, 6 correspond to each other on a one-to-one basis. Therefore, by making the pair of permanent magnets 9 in each of the magnet mounting slots 7a and 8a of the outer peripheral rotor 5 and the inner peripheral rotor 6 face each other with the same polarity (with different polar arrangement), the rotor unit 3 is able to obtain a field weakening state (see FIGS. 4 and 5B) in which the field of the entire field is most weakened, and the magnet mounting slots 7a of the outer peripheral rotor 5 and the inner peripheral rotor 6. , 8a, the pair of permanent magnets 9 are opposed to each other with different polarities (with the same polarity arrangement), so that the field of the entire rotor unit 3 is most strongly strengthened (see FIGS. 2 and 5). (See (a)) can be obtained.

  The rotor unit 3 includes a rotation mechanism 11 for relatively rotating the outer peripheral rotor 5 and the inner peripheral rotor 6. The rotating mechanism 11 constitutes a part of phase changing means 12 for arbitrarily changing the relative phase of the two rotors 5 and 6, and is based on the pressure of the working fluid that is an incompressible working fluid. It is designed to be operated. The phase changing means 12 is composed mainly of the turning mechanism 11 and a hydraulic control device (not shown) that controls the pressure of the hydraulic fluid supplied to the turning mechanism 11.

  1 to 4, the rotating mechanism 11 is disposed on the outer periphery of the vane rotor 14 so as to be relatively rotatable, and the vane rotor 14 (shaft member) that is spline-fitted to the outer periphery of the rotating shaft 4 so as to rotate integrally therewith. And the annular housing 15 is integrally fitted and fixed to the inner peripheral surface of the inner peripheral rotor 6, and the vane rotor 14 is connected to the annular housing 15 and the inner peripheral side. The rotor 6 is integrally coupled to the outer peripheral rotor 5 via a pair of disk-shaped drive plates 16 and 16 (side wall members) straddling the side end portions on both sides of the rotor 6. Therefore, the vane rotor 14 is integrated with the rotary shaft 4 and the outer peripheral rotor 5, and the annular housing 15 is integrated with the inner peripheral rotor 6.

  In the vane rotor 14, a plurality of vanes 18 (partition walls) protruding radially outward are provided at equal intervals in the circumferential direction on the outer periphery of a cylindrical boss portion 17 that is spline-fitted to the rotary shaft 4. On the other hand, the annular housing 15 is provided with a plurality of concave portions 19 on the inner peripheral surface at equal intervals in the circumferential direction, and the corresponding vanes 18 of the vane rotor 14 are accommodated in the concave portions 19. Each recess 19 is constituted by a bottom wall 20 having an arc surface that substantially matches the rotational trajectory of the tip of the vane 18 and a substantially triangular partition wall 21 that separates the adjacent recesses 19, 19. The vane 18 can be displaced between the one partition wall 21 and the other partition wall 21 during relative rotation of the annular housing 15. In the case of this embodiment, the partition wall 21 also functions as a stopper that restricts the relative rotation of the vane rotor 14 and the annular housing 15 by contacting the vane 18.

  Further, the base 15a portion of the annular housing 15 fixed to the inner peripheral rotor 6 is formed in a cylindrical shape having a constant thickness, and as shown in FIG. 1, with respect to the inner peripheral rotor 6 and the partition wall 21. Projects outward in the axial direction. Each end projecting outward of the base portion 15a is slidably held in an annular guide groove 16a formed in the drive plate 16, and the annular housing 15 and the inner peripheral rotor 6 are connected to the outer peripheral rotor. 5 and the rotating shaft 4 are supported in a floating state.

  The drive plates 16 and 16 on both sides connecting the outer rotor 5 and the vane rotor 14 are slidably in contact with both side surfaces (both end surfaces in the axial direction) of the annular housing 15, and are on the side of each recess 19 of the annular housing 15. Respectively. Therefore, each recessed part 19 forms the independent space part by the boss | hub part 17 of the vane rotor 14, and the drive plates 16 and 16 of both sides, and this space part is the introduction space 23 into which a hydraulic fluid is introduce | transduced. Each introduction space 23 is divided into two chambers by the corresponding vanes 18 of the vane rotor 14, and one room is an advance side working chamber 24 and the other room is a retard side working chamber 25. The advance side working chamber 24 rotates the inner circumferential side rotor 6 relative to the outer circumferential side rotor 5 in the advance direction by the pressure of the working fluid introduced inside, and the retard side working chamber 25 is The inner rotor 6 is rotated relative to the outer rotor 5 in the retard direction by the pressure of the working fluid introduced therein. In this case, “advance angle” means that the inner circumferential rotor 6 is advanced relative to the outer circumferential rotor 5 in the rotational direction of the electric motor 1 indicated by an arrow R in FIGS. 2 and 4. “Angle” means that the inner rotor 6 is advanced to the opposite side of the rotation direction R of the electric motor 1 with respect to the outer rotor 5.

  Further, the supply and discharge of the hydraulic fluid to and from each of the advance side working chambers 24 and the retard side working chambers 25 is performed through the rotating shaft 4. Specifically, the advance side working chamber 24 is connected to the advance side supply / discharge passage 26 of the hydraulic control device, and the retard side operation chamber 25 is connected to the retard side supply / discharge passage 27 of the hydraulic control device. However, as shown in FIG. 1, a part of the advance side supply / discharge passage 26 and the retard side supply / discharge passage 27 are formed by passage holes 26a, 27a formed along the axial direction of the rotary shaft 4, respectively. It is configured. The end portions of the passage holes 26a and 27a are connected to annular grooves 26b and 27b formed at positions offset in the axial direction of the outer peripheral surface of the rotating shaft 4, and the annular grooves 26b and 27b are connected to the vane rotor 14. Are connected to a plurality of conduction holes 26c,..., 27c. Each conduction hole 26c of the advance side supply / discharge passage 26 connects the annular groove 26b and each advance side working chamber 24, and each conduction hole 27c of the retard side supply / exhaust passage 27 connects to the annular groove 27b and each retard side. The working chamber 25 is connected.

In the case of the electric motor 1, when the inner circumferential rotor 6 is at the most retarded position with respect to the outer circumferential rotor 5, the permanent magnets 9 of the outer circumferential rotor 5 and the inner circumferential rotor 6 have different polarities. When the inner rotor 6 is in the most advanced position with respect to the outer rotor 5, the outer rotor rotates. The permanent magnets 9 of the child 5 and the inner rotor 6 are set so as to face each other with the same poles and to have a field weakening state (see FIGS. 4 and 5B).
The electric motor 1 can arbitrarily change the state of the strong field and the state of the weak field by controlling the supply and discharge of the hydraulic fluid to and from the advance side working chamber 24 and the retard side working chamber 25. Thus, when the strength of the magnetic field is changed, the induced voltage constant is changed accordingly, and as a result, the characteristics of the electric motor 1 are changed. That is, if the induced voltage constant increases due to the strong field, the allowable rotational speed at which the motor 1 can be operated decreases, but the maximum torque that can be output increases. Conversely, if the induced voltage constant decreases due to the weak field, Although the maximum torque that can be output from the electric motor 1 decreases, the allowable rotational speed at which the motor 1 can operate increases.

  By the way, in the vane rotor 14 and the annular housing 15 that constitute the rotation mechanism 11, a seal groove 30 having a substantially U-shaped cross section extending from one end to the other end in the axial direction is formed on each end face of the vane 18 and the partition wall 21. In each seal groove 30, an inner surface of the bottom wall 19 of the annular housing 15 (a peripheral wall of the mating member), a peripheral wall seal member 22 that is in close contact with an outer peripheral surface of the boss portion 17 of the vane rotor 14 (a peripheral wall of the mating member), A leaf spring 31 (biasing member) that urges the circumferential wall seal member 22 in the direction of the circumferential wall of the mating member is accommodated.

  Each partition wall 21 of the annular housing 15 is linearly formed with a substantially U-shaped seal groove 32 extending from the proximal end to the distal end of the partition wall 21 on both side surfaces in the axial direction. A side wall seal member 33 that is in close contact with the inner side surfaces of the drive plates 16 on both sides and a leaf spring 34 (biasing means) that urges the side wall seal member 33 toward the dry plate 16 are accommodated. In the case of this embodiment, the side wall seal member 33 is formed in a substantially rectangular shape with a highly liquid-tight resin material, and the end surface on the side in sliding contact with the drive plate 16 is formed flat.

  As described above, in the phase changing means 12 of the electric motor 1, between the tip of each vane 18 of the vane rotor 14 and the inner peripheral surface of the annular housing 15, the tip of the partition wall 21, and the outer peripheral surface of the boss portion 17 of the vane rotor 14. Are sealed by the peripheral wall sealing member 22, and the side surfaces of the partition wall 21 and the inner side surface of the drive plate 16 are sealed by the side wall sealing members 33, so that the operation of the adjacent working chambers 24, 25 is performed. The peripheral wall seal member 22 can prevent the liquid from passing around the vane 18 and the sliding portion on the tip side of the partition wall 21, and the adjacent operation through the sliding gap between the side surface of the partition wall 21 and the drive plate 16. The side wall seal member 33 can prevent the working fluid from flowing between the chambers 24 and 25. Therefore, in this phase change means 12, the leakage of the hydraulic fluid between the working chambers 24 and 25 at the time of phase change or phase holding can be efficiently suppressed, and the energy use efficiency can be increased.

  In the case of this embodiment, the side wall seal members 33 arranged on both sides in the axial direction of each partition wall 21 are pressed against the drive plates 16 and 16 on both sides by the leaf springs 31. It is possible to improve the sealing performance by being brought into close contact with the inner surface of the ring 16, and the annular housing 15 itself is centered between the drive plates 16 and 16 by the reaction force of the leaf springs 31 arranged on both sides of each partition wall 21. Thus, direct contact between the annular housing 15 and the drive plate 16 can be prevented, and the operational stability of the phase changing means 12 can be enhanced.

  Since the electric motor 1 has the structure in which the phase changing unit 12 has less leakage of the hydraulic fluid as described above, the hydraulic fluid supply source such as an oil pump that supplies the hydraulic fluid to the phase changing unit 12 is reduced in size. This is advantageous for mounting on a vehicle.

  In the above embodiment, the leaf spring is used as the biasing member for biasing the peripheral wall seal member and the side wall seal member. However, the biasing member is not limited to the plate spring, and other spring members such as a coil spring. It may be.

  9 to 11 show a second embodiment of the present invention, and FIGS. 12 to 14 show a third embodiment of the present invention. These embodiments are different from the first embodiment in the structure of the partition walls 121, 221 of the annular housing 15 and the side wall seal members 133, 233, and the other parts have the same configuration. Therefore, only the parts different from the first embodiment will be described below, and the description of the common parts will be omitted.

  In the second embodiment shown in FIGS. 9 to 11, the side wall seal members 133 attached to the side surfaces on both sides in the axial direction of the partition wall 121 are formed of an elastic member such as rubber. The side wall seal member 133 is formed in a columnar shape having a substantially elliptical cross section, and a seal groove 132 that matches the cross sectional shape of the side wall seal member 133 is formed on the side surface of the partition wall 121.

  In this embodiment, the side wall seal member 133 is formed of an elastic member, and is in close contact with the inner surface of the drive plate by its own elasticity. For this reason, it is possible to prevent the hydraulic fluid from leaking between the adjacent working chambers by going around the side of the partition wall 121 in the axial direction as in the first embodiment.

  In this embodiment, substantially the same functions and effects as in the first embodiment can be obtained, but a separate biasing member is not required to press the side wall seal member 133 against the drive plate. This is advantageous in reducing the number of parts and assembly man-hours.

  In the third embodiment shown in FIGS. 12 to 14, the side wall seal members 233 attached to the side surfaces on both sides in the axial direction of the partition wall 221 are formed of corrugated resin members having a plurality of curved shapes. A seal groove 232 having a substantially U-shaped cross section is formed on both side surfaces of the partition wall 221 in the axial direction, and a side wall seal member 233 is disposed in the seal groove 232 so that a part of the waveform protrudes upward. ing.

In this embodiment, the corrugated top of the side wall seal member 233 abuts on the inner surface of the drive plate, and the side wall seal member 233 is pressed against the drive plate by a wave-shaped deformation reaction force.
In the case of this embodiment as well, the same functions and effects as those of the first embodiment can be obtained, and a separate biasing member is not required as in the second embodiment. Assembly time can be reduced.

  The present invention is not limited to the above embodiments, and various design changes can be made without departing from the scope of the invention. For example, in the above description, the vane type hydraulic device is applied to the phase changing means of the electric motor. However, the valve timing for changing the relative rotation phase of the output shaft and the camshaft of the internal combustion engine using the same vane type hydraulic device. It can be applied to the phase changing means of the control device. Further, the vane hydraulic device according to the present invention is not limited to the above-described phase changing means, and may be a vane pump, a vane motor, or the like.

1 is a cross-sectional view of a main part of an electric motor according to a first embodiment of the present invention. The side view which abbreviate | omitted some components of the rotor unit controlled to the most retarded angle position of the electric motor of the embodiment. The disassembled perspective view of the rotor unit of the electric motor of the embodiment. The side view which abbreviate | omitted some components of the rotor unit controlled to the most advanced angle position of the electric motor of the embodiment. The figure (a) which shows typically the strong field state where the permanent magnet of the inner circumference side rotor and the permanent magnet of the outer circumference side rotor are arranged in the same polarity, and the permanent magnet and outer circumference side rotation of the inner circumference side rotor The figure which also described the figure (b) which shows typically the field-weakening state by which the permanent magnet of a child was arrange | positioned differently. The perspective view of the side wall seal member and urging | biasing member used with the electric motor of the embodiment. Sectional drawing corresponding to the AA cross section of FIG. 8 which shows the same embodiment. The perspective view of the partition wall part of the annular housing of the embodiment. The perspective view of the side wall seal member which shows 2nd Embodiment of this invention. Sectional drawing corresponding to the BB cross section of FIG. 11 which shows the same embodiment. The perspective view of the partition wall part of the annular housing of the embodiment. The perspective view of the sealing member which shows 3rd Embodiment of this invention. Sectional drawing corresponding to CC cross section of FIG. 14 which shows the same embodiment. The perspective view of the partition wall part of the annular housing of the embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Electric motor 5 ... Outer peripheral side rotor 6 ... Inner peripheral side rotor 9 ... Permanent magnet 12 ... Phase change means (vane type hydraulic equipment)
14 ... Vane rotor (shaft member)
15 ... Annular housing (tubular member)
16 ... Drive plate (side wall member)
21, 121 ... partition wall 22 ... peripheral wall seal member 24 ... advance side working chamber (liquid chamber)
25 ... retarded-side working chamber (liquid chamber)
33, 133 ... side wall seal member 34 ... leaf spring (biasing means)

Claims (6)

A tubular member;
A shaft member arranged coaxially on the inner peripheral side of the cylindrical member and capable of relative rotation; and
Side wall members disposed on both axial sides of the cylindrical member and the shaft member, and forming a space portion together with the outer peripheral surface of the shaft member and the inner peripheral surface of the cylindrical member;
A blade-like partition wall that protrudes from at least one of the outer peripheral surface of the shaft member and the inner peripheral surface of the tubular member, and that divides the space portion into a plurality of liquid chambers;
A peripheral wall sealing member disposed at the tip of the partition wall so as to extend from one end to the other end in the axial direction and in close contact with the peripheral wall of the mating member facing the tip surface of the partition wall;
Side wall seal members disposed on both side surfaces of the partition wall so as to extend from the base end to the tip end of the partition wall and in close contact with the side wall member facing the side surface of the partition wall. And vane type hydraulic equipment.   The vane hydraulic device according to claim 1, wherein a biasing member is interposed between the partition member and the side wall seal member.   The vane type hydraulic device according to claim 1, wherein the side wall seal member is an elastic member.   The vane type hydraulic device according to claim 1, wherein the side wall seal member is a corrugated plate member having at least one curved shape in a direction facing the side wall member. An inner rotor on which permanent magnets are arranged along the circumferential direction;
An outer peripheral rotor on which the permanent magnet is disposed along the circumferential direction, coaxially and relatively rotatably arranged on the outer peripheral side of the inner peripheral rotor,
Phase changing means for changing the rotational phase of both of the inner and outer rotors by relatively rotating the inner and outer rotors;
An electric motor with
The vane type hydraulic device according to any one of claims 1 to 4 is used for the phase changing unit.
A driving force that changes the rotational phases of the inner and outer rotors by supplying and discharging hydraulic fluid to and from the circumferential fluid chambers separated by the partition wall of the vane hydraulic device. An electric motor characterized by obtaining. An output shaft from which the power of the internal combustion engine is output;
A camshaft that rotates in conjunction with the output shaft to open and close the engine valve of the internal combustion engine;
Phase changing means for rotating the output shaft and the camshaft relative to each other to change the rotational phase of both;
An internal combustion engine valve timing control apparatus comprising:
The vane type hydraulic device according to any one of claims 1 to 4 is used for the phase changing unit.
The hydraulic fluid is supplied to and discharged from the fluid chambers in the circumferential direction separated by the partition wall of the vane hydraulic device to obtain a driving force for changing the rotational phase of the camshaft and the output shaft. A valve timing control device for an internal combustion engine.

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