JP2011117369A - Electric pump - Google Patents

Electric pump Download PDF

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Publication number
JP2011117369A
JP2011117369A JP2009275569A JP2009275569A JP2011117369A JP 2011117369 A JP2011117369 A JP 2011117369A JP 2009275569 A JP2009275569 A JP 2009275569A JP 2009275569 A JP2009275569 A JP 2009275569A JP 2011117369 A JP2011117369 A JP 2011117369A
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Japan
Prior art keywords
bearing
shaft
rotor
axial
stator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP2009275569A
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Japanese (ja)
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JP4918936B2 (en
Inventor
Taku Ito
Tomonobu Kuroda
Kenichi Oishi
卓 伊東
健一 大石
朋伸 黒田
Original Assignee
Denso Corp
株式会社デンソー
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Priority to JP2009275569A priority Critical patent/JP4918936B2/en
Publication of JP2011117369A publication Critical patent/JP2011117369A/en
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    • HELECTRICITY
    • H02GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02KDYNAMO-ELECTRIC MACHINES
    • H02K7/00Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08Structural association with bearings
    • H02K7/085Structural association with bearings radially supporting the rotary shaft at only one end of the rotor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02Arrangements of bearings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10Outer members for co-operation with rotary pistons; Casings
    • F01C21/104Stators; Members defining the outer boundaries of the working chamber
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/008Enclosed motor pump units
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • HELECTRICITY
    • H02GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02KDYNAMO-ELECTRIC MACHINES
    • H02K7/00Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/14Structural association with mechanical loads, e.g. with hand-held machine tools or fans
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/40Electric motor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/50Bearings
    • F04C2240/51Bearings for cantilever assemblies
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/60Shafts
    • F04C2240/601Shaft flexion

Abstract

An electric pump capable of suppressing the inclination of the shaft and reducing the physique in the axial direction is provided.
A stator has a magnetic material part and forms a magnetic field by energizing a winding. The rotor 60 is rotatably arranged inside the stator 50 in the radial direction, and rotates by receiving a magnetic field formed in the stator 50 when the winding is energized. The shaft 70 rotates integrally with the rotor 60. The bearing portions 35 and 75 support the shaft 70 in a rotatable manner. The pump unit 12 sucks fluid from the suction port by the rotation of the shaft and discharges the fluid from the discharge port. Since the center of the first bearing portion 75 in the axial direction is located inside the inner region defined by both ends of the magnetic material portion 51 of the stator 50 in the axial direction, the tilt of the shaft 70 accompanying rotation can be suppressed. . Moreover, the physique of an axial direction can be made small compared with the case where it bears at the both ends of 60 of a rotor.
[Selection] Figure 3

Description

  The present invention relates to an electric pump.

  2. Description of the Related Art Conventionally, an electric motor that drives a shaft rotatably supported by a bearing portion by a magnetic field generated by energizing a winding is known. For example, in the electric oil pump of Patent Document 1, a motor bearing is provided on the housing side of the oil pump. Moreover, in patent document 2, the bearing part is provided in the both sides of the axial direction of the rotor.

JP 2003-269345 A JP 2005-160285 A

The shaft of the electric motor of Patent Document 1 is supported at one location. Further, since the position of the bearing portion in the axial direction deviates from the position of the rotor and the stator in the axial direction, there is a large runout in the radial direction of the rotor due to the inclination of the shaft, and the motor performance is not stable. Further, since the shaft has a large inclination, it is necessary to ensure a wide clearance between the stator and the rotor, and the motor output is reduced. In Patent Document 2, since bearings are provided on both sides in the axial direction of the rotor, the inclination of the shaft is suppressed, but the physique in the axial direction becomes large.
This invention is made | formed in view of the above-mentioned subject, The objective is to provide the electric pump which can suppress the inclination of a shaft and can make the physique of an axial direction small.

  The electric pump according to a first aspect includes a stator, a rotor, a shaft, at least one bearing portion, and a pump portion. The stator has a magnetic material portion and forms a rotating magnetic field by energizing the windings. The rotor is rotatably arranged inside the stator in the radial direction, and rotates by receiving a rotating magnetic field formed in the stator when the winding is energized. The shaft rotates integrally with the rotor. The bearing portion rotatably supports the shaft. The pump unit has a housing in which a suction port and a discharge port are formed. The pump unit sucks fluid from the suction port by the rotation of the shaft and discharges it from the discharge port.

  The present invention is characterized in that the axial center of at least one bearing portion is located inside an internal region defined by both ends of the magnetic material portion of the stator in the axial direction. Since the shaft is bearing inside the rotating magnetic field formed in the stator by energizing the windings, the inclination of the shaft can be suppressed. Since the inclination of the shaft is suppressed, the vibration in the radial direction of the rotor is reduced, and the motor performance is stabilized. In addition, since the vibration in the radial direction of the rotor is reduced, the clearance between the stator and the rotor can be reduced, and the output of the motor can be relatively increased. Furthermore, the physique in the axial direction can be reduced as compared with Patent Document 2 in which bearings are provided on both sides in the axial direction of the rotor.

  According to the second aspect of the present invention, the center of the at least one bearing portion in the axial direction coincides with the center of the magnetic material portion of the stator in the axial direction. Thereby, since it is bearing at the approximate center of the rotating magnetic field formed by the stator, the inclination of the shaft can be further suppressed.

  In the invention according to claim 3, the bearing portion has a first bearing portion and a second bearing portion. The center of the first bearing portion in the axial direction is located inside the inner region. The center of the second bearing portion in the axial direction is located outside the inner region. Since the bearing is carried out at two locations of the first bearing portion provided inside the inner region and the second bearing portion provided outside the inner region, that is, inside and outside the rotating magnetic field formed by the stator. The inclination of the shaft can be further suppressed.

According to the fourth aspect of the present invention, the center of the first bearing portion in the axial direction coincides with the center of the magnetic material portion of the stator in the axial direction. Thereby, the inclination of the shaft can be further suppressed at the approximate center of the rotating magnetic field formed by the stator.
In the invention according to claim 5, the radial clearance in the second bearing portion is a clearance that is smaller than the inclination amount of the radial shaft in the first bearing portion. Thereby, since the inclination of the shaft accompanying rotation is prescribed | regulated by the clearance of the 2nd bearing part provided in the exterior of an internal area | region, shaft inclination can be suppressed more. Moreover, the freedom degree of design of the radial clearance in the first bearing portion is increased.

The following configuration can be adopted as the pump unit.
The pump part of the invention described in claim 6 is a so-called internal gear pump, and has an inner rotor and an outer rotor. The inner rotor has outer teeth formed on the outer periphery and rotates integrally with the shaft. As for an outer rotor, the internal tooth meshed | engaged with the external tooth of an inner rotor is formed in an inner periphery. The housing rotatably accommodates the inner rotor and the outer rotor.

1 is a block diagram showing an overall configuration of an automatic transmission system using an electric pump according to an embodiment of the present invention. It is explanatory drawing explaining the hydraulic circuit of the automatic transmission which used the electric pump by one Embodiment of this invention. It is sectional drawing which shows the electric pump by one Embodiment of this invention. It is sectional drawing which shows the IV-IV sectional view of FIG. It is sectional drawing which shows the electric pump by the modification of this invention. It is sectional drawing which shows the electric pump by the modification of this invention.

Hereinafter, the electric pump by this invention is demonstrated based on drawing.
(One embodiment)
An electric pump according to an embodiment of the present invention is applied to an oil pump that supplies hydraulic oil to an automatic transmission.
FIG. 1 shows the overall configuration of a system according to this embodiment.
An internal combustion engine (hereinafter referred to as “engine”) 80 is a vehicle power generation device, and a crankshaft (not shown) is mechanically connected to a drive shaft 82 that connects left and right drive wheels 81. The automatic transmission 90 is provided in a power transmission system that transmits power from the crankshaft to the drive wheels 81. The automatic transmission 90 is provided with an electric pump 10 driven by electric power supplied from a battery 84.

  The battery 84 is connected to the electric pump 10, the starter 85, the alternator 86, the electrical component 87, and the like. The starter 85 applies initial rotation to the crankshaft of the engine 80. The alternator 86 is mechanically connected to the crankshaft of the engine 80, and converts the transmitted kinetic energy into electric energy. The converted electrical energy is charged in the battery 84. The electrical component 87 includes an air conditioner, a headlight, a fuel injection device, and the like. The ECU 89 is mainly composed of a known microcomputer. The ECU 89 performs so-called idle stop control for automatically stopping the engine 80 when the vehicle is stopped, and automatic start control for automatically starting the engine 80 from the idle stop state. Further, energization control for the electric pump 10 is performed. In FIG. 1, the control lines other than the control line to the electric pump 10 are omitted to avoid complication.

Here, the hydraulic circuit configuration of the automatic transmission 90 is shown in FIG. The automatic transmission 90 includes an electric pump 10, a mechanical hydraulic pump 91, a control valve 92, a plurality of friction engagement elements including a start clutch 93, a check valve 94, and the like.
The mechanical hydraulic pump 91 is driven by the engine 80, sucks oil stored in the oil pan 98 through the strainer 99, lubricates each part (not shown), and controls a plurality of frictional units through the control valve 92. Supply hydraulic pressure to the joint element.

The electric pump 10 is provided in parallel with the mechanical hydraulic pump 91. The electric pump 10 is provided in the bypass passage 96, and includes a pump unit 12, a motor unit 13, and the like. The pump unit 12 and the motor unit 13 are connected by a shaft 70. The motor unit 13 is connected to the driver 14. The electric pump 10 is driven during idle stop and supplies hydraulic pressure to the starting clutch 93.
The bypass passage 96 is connected to the hydraulic passage 97 on the downstream side of the mechanical hydraulic pump 91. A check valve 94 is provided between the connection portion of the bypass passage 96 and the hydraulic passage 97 and the electric pump 10. The check valve 94 opens when the hydraulic pressure in the bypass passage 96 overcomes the hydraulic pressure in the hydraulic passage 97.

  As described above, in this embodiment, idle stop control is performed to automatically stop the engine 80 when the vehicle is stopped. When the engine 80 stops, the mechanical hydraulic pump 91 driven by the engine 80 also stops. When the mechanical hydraulic pump 91 is stopped, if the electric pump 10 is not provided, oil cannot be supplied to the friction engagement element, and the hydraulic pressure decreases. When the engine 80 is restarted from a state in which the hydraulic pressure of the starting clutch 93 has decreased, the starting clutch slips, suddenly engages, etc., and a shift shock occurs. Thus, the gear shift shock can be reduced by driving the electric pump 10 during idle stop, supplying oil to the starting clutch 93 via the control valve 92, and maintaining the hydraulic pressure of the starting clutch 93.

Here, the detail of the electric pump 10 is demonstrated based on FIG.
The pump unit 12 of the electric pump 10 is an inscribed gear pump, and includes a housing 20, an inner rotor 40, an outer rotor 45, and the like.

The housing 20 has a first housing 21 and a second housing 31.
A suction port 23 and a discharge port 24 are formed in the first housing 21. The suction port 23 is formed on the front side of the sheet in FIG. 3, and the discharge port 24 is formed on the back side of the sheet in FIG. On the surface of the first housing 21 that contacts the second housing 31, a recess 26 is formed at a position corresponding to the shaft 70. One end of the shaft 70 is accommodated in the recess 26. The first housing 21 and the shaft 70 are not in contact with each other, and the rotation of the shaft 70 is not restricted by the first housing 21.

  The second housing 31 is formed in a substantially cylindrical shape. A cylindrical tube portion 32 is formed at the end of the second housing 31 on the motor portion 13 side in the axial direction. An accommodation chamber 34 for accommodating the inner rotor 40 and the outer rotor 45 is formed at the end of the second housing 31 opposite to the cylindrical portion 32. Further, the second housing 31 is formed with a bearing hole 35 as a second bearing portion that rotatably supports the shaft 70. The clearance formed between the bearing hole 35 and the shaft 70 is supplied with oil leaking from an oil chamber 49, which will be described later, thereby reducing the sliding resistance caused by the rotation of the shaft 70. Yes. An oil seal 33 is provided between the bottom portion of the cylindrical portion 32 and a first bearing portion 75 described later. This prevents oil from flowing into the motor unit 13 side.

  The first housing 21 and the second housing 31 are fixed with bolts 30. An O-ring groove 37 is formed on the contact surface of the second housing 31 with the first housing 21. An O-ring 371 is fitted in the O-ring groove 37 and seals between the first housing 21 and the second housing 31. Further, a cover 39 that houses the motor unit 13 is put on the opposite side of the second housing 31 from the first housing 21. An O-ring 381 is fitted into an O-ring groove 38 formed on the contact surface of the second housing 31 with the cover 39, thereby ensuring airtightness between the second housing 31 and the cover 39. The second housing 31 and the cover 39 constitute a housing for the pump portion 12 and constitute a housing for the motor portion 13.

The inner rotor 40 and the outer rotor 45 are formed of a material having excellent wear resistance, such as an iron-based sintered metal, and rotate into a space formed by the housing chamber 34 of the second housing 31 and the first housing 21. Accomodated as possible.
A shaft hole 41 having two flat portions 42 perpendicular to the axial direction is formed in the inner rotor 40 at the center. The two flat portions 42 are formed substantially in parallel. The two flat portions 42 are connected by a circular arc surface. The inner rotor 40 and the shaft 70 rotate together as a fitting portion 71 of the shaft 70 described later is fitted into the shaft hole 41. Further, seven external teeth 44 are formed on the outer periphery of the inner rotor 40.

  The outer rotor 45 is formed in a substantially cylindrical shape on the radially outer side of the inner rotor 40. Eight inner teeth 46 that mesh with the outer teeth 44 of the inner rotor 40 are formed on the inner periphery of the outer rotor 45. The rotation center of the inner rotor 40 and the rotation center of the outer rotor 45 are arranged so as to be eccentric, and a gap 48 is formed between the inner rotor 40 and the outer rotor 45. The gap 48 communicates with an oil chamber 49 formed across the first housing 21 and the second housing 31. The oil chamber 49 communicates with the suction port 23 and the discharge port 24. As a result, the suction port 23 and the discharge port 24 communicate with each other via the oil chamber 49 and the gap 48.

The motor unit 13 includes a stator 50, a rotor 60, and the like.
The stator 50 includes a magnetic material part 51 and an insulator 53. The magnetic material portion 51 is formed by laminating thin plates of magnetic material. The insulator 53 formed of a nonmagnetic material is provided outside the magnetic material portion 51 in the axial direction. A winding is wound around the insulator 53. A rotating magnetic field is formed in the magnetic material portion 51 of the stator 50 by energizing the winding.

The rotor 60 is formed in a bottomed cylindrical shape that opens to the pump unit 12 side, and is provided rotatably inside the stator 50 in the radial direction. The rotor 60 has a bottom portion 61 and a peripheral wall 64 provided on the outer periphery of the bottom portion 61. A hole 62 is formed at the center of the bottom 61. The end of the shaft 70 opposite to the fitting portion 71 is press-fitted and fixed in the hole 62. Thereby, the rotor 60 and the shaft 70 rotate integrally. A magnet 65 is affixed to the outer surface of the peripheral wall 64 in the radial direction. In this embodiment, the axial length of the magnet 65 of the rotor 60 is substantially the same as the axial length of the magnetic material portion 51 of the stator 50.
In addition, the distal end of the cylindrical portion 32 of the second housing 31 is accommodated in the accommodating space 68 formed by the inner wall 67 of the rotor 60. Note that a gap is formed between the inner wall 67 of the rotor 60 and the cylindrical portion 32 of the second housing 31, and the inner wall 67 and the cylindrical portion 32 are not in contact with each other.

  The shaft 70 is formed in a substantially cylindrical shape, one end in the axial direction is inserted into the shaft hole 41 of the inner rotor 40, and the other end is press-fitted into the rotor 60. At the end of the shaft 70 on the inner rotor 40 side, a fitting portion 71 having two cutout surfaces 72 cut out so as to be a plane substantially perpendicular to the axial direction is formed. The two notch surfaces 72 are formed substantially parallel by cutting or the like. The interval between the two notch surfaces 72 is substantially the same as the interval between the two flat portions 42 of the shaft hole 41 formed in the inner rotor 40. The relative rotation between the shaft 70 and the inner rotor 40 is restricted by fitting the fitting portion 71 into the shaft hole 41 with the cut-out surface 72 and the flat portion 42 corresponding to each other. Thereby, the shaft 70 and the inner rotor 40 rotate integrally.

The shaft 70 is supported at two locations of the first bearing portion 75 and the bearing hole 35 of the second housing 31.
The 1st bearing part 75 is provided in the accommodation space 68 formed in the radial inside of the rotor 60, and supports the shaft 70 rotatably. The first bearing portion 75 is a ball bearing including an inner ring 76, an outer ring 77, and a ball 78. A shaft 70 is press-fitted into the inner ring 76. In addition, the outer ring 77 constituting the outer shell of the first bearing portion 75 is press-fitted into the cylindrical portion 32 of the second housing 31 that is accommodated in the accommodation space 68. That is, the first bearing portion 75 is provided in a space formed on the radially inner side of the rotor 60. The ball 78 is held between the inner ring 76 and the outer ring 77 by a cage. The center O of the ball 78 is substantially coincident with the center of the first bearing portion 75 in the axial direction. That is, the center O of the ball 78 is located on a virtual line L3 (indicated by a two-dot chain line in FIG. 3) indicating the center of the first bearing portion 75 in the axial direction.
In this embodiment, the first bearing portion 75 and the bearing hole 35 of the second housing 31 constitute a “bearing portion”.

Here, in FIG. 3, the imaginary line L1 that is the position of the end 55 on the first housing 21 side of the magnetic material portion 51 of the stator 50 in the axial direction and the opposite side of the magnetic material portion 51 from the first housing 21. A virtual line L2 that is the position of the end portion 56 is indicated by a two-dot chain line. Further, the center position of the first bearing portion 75 in the axial direction is indicated by an imaginary line L3. As shown in FIG. 3, the virtual line L3 indicating the center position of the first bearing portion 75 in the axial direction is located inside the region defined by the virtual line L1 and the virtual line L2. In particular, in this embodiment, the virtual line L3 is located at the center of the virtual line L1 and the virtual line L2. Further, the bearing hole 35 is located outside the region defined by the virtual line L1 and the virtual line L2.
In this embodiment, a region between the virtual line L1 and the virtual line L2 corresponds to an “internal region”.

Furthermore, the axial inclination amount between the bearing hole 35 of the second housing 31 and the shaft 70 in the radial direction is set to a clearance smaller than the axial inclination amount between the inner ring 76 and the outer ring 77 and the ball 78 in the radial direction. ing.
In this embodiment, the internal clearance of the first bearing portion 75, that is, the radial clearance between the inner ring 76 and the outer ring 77 and the ball 78 corresponds to the “amount of inclination of the radial shaft in the first bearing portion”. The clearance in the radial direction between the hole 35 and the shaft 70 corresponds to “the amount of inclination of the shaft in the radial direction in the second bearing portion”.

Here, the operation of the electric pump 10 will be described.
When the winding wound around the insulator 53 of the stator 50 is energized, a rotating magnetic field is formed in the magnetic material portion 51 of the stator 50. Due to the formed rotating magnetic field, the rotor 60, the shaft 70, and the inner rotor 40 rotate together. Further, the outer rotor 45 rotates as the inner rotor 40 rotates. When the inner rotor 40 and the outer rotor 45 rotate, the meshing amount of the outer teeth 44 and the inner teeth 46 continuously changes, and the volume of the gap portion 48 formed between the inner rotor 40 and the outer rotor 45 is continuously increased. To change. As a result, oil is sucked into the region where the volume of the gap 48 increases via the suction port 23, and oil is discharged via the discharge port 24 from the region where the volume of the gap 48 decreases.

  In this embodiment, the shaft 70 is supported at two locations, the first bearing portion 75 and the bearing hole 35. The center in the axial direction of the first bearing portion 75 substantially coincides with the center in the axial direction of the magnetic material portion 51 of the stator 50. That is, since the center in the axial direction of the first bearing portion 75 is located at the approximate center of the rotating magnetic field formed by the stator 50, the tilt associated with the rotation of the shaft 70 can be suppressed.

  Further, the bearing hole 35 is located outside an internal region defined by both axial ends of the magnetic material portion 51 of the stator 50. Thus, since the bearing is provided inside and outside the rotating magnetic field formed by the stator 50, the tilt accompanying the rotation of the shaft 70 is further suppressed. Furthermore, the clearance in the radial direction between the bearing hole 35 and the shaft 70 of the second housing 31 is set so as to be smaller than the axial inclination amount of the inner ring 76 and the outer ring 77 and the ball 78 in the radial direction. Yes. Accordingly, the inclination of the shaft 70 can be further suppressed, and the degree of freedom in designing the internal clearance of the first bearing portion 75 that is a ball bearing is increased.

  As described above in detail, the center of the first bearing portion 75 in the axial direction is the inner side of the inner region defined by the ends 55 and 56 in the axial direction of the magnetic material portion 51 of the stator 50, that is, the virtual line L1 and the virtual line. It is located between the line L2. Thereby, since the shaft 70 is bearing at the center of the rotating magnetic field formed in the stator 50 by energizing the windings, the inclination of the shaft 70 accompanying the rotation can be suppressed. Since the inclination of the shaft 70 is suppressed, the vibration of the rotor 60 in the radial direction is reduced, and the motor performance is stabilized. Further, since the radial deflection of the rotor 60 is reduced, the clearance between the stator 50 and the rotor 60 can be reduced, and the output of the motor can be relatively increased. Furthermore, the physique in the axial direction can be reduced as compared with the case where the bearings are provided on both sides of the rotor 60 in the axial direction. In particular, in the present embodiment, since the first bearing portion 75 is provided using the accommodation space 68 formed on the radially inner side of the rotor 60, the space can be used effectively, contributing to downsizing. .

  The center of the first bearing portion 75 in the axial direction substantially coincides with the center of the magnetic material portion 51 of the stator 50. Thereby, since it is bearing at the approximate center of the magnetic field formed by the stator 50, the inclination of the shaft 70 can be further suppressed.

  Further, in this embodiment, the bearings are provided at two locations of the first bearing portion 75 and the bearing hole 35 of the second housing 31. The bearing hole 35 is located outside an internal region defined by both ends 55 and 56 in the axial direction of the magnetic material portion 51 of the stator 50. Thereby, since the shaft 70 is bearing by the inside and the outside of the rotating magnetic field formed by the stator 50, the inclination of the shaft 70 can be further suppressed.

  Furthermore, the radial clearance between the bearing hole 35 and the shaft 70 is a clearance that is smaller than the amount of inclination of the radial shaft between the inner ring 76 and the outer ring 77 and the ball 78 that extend to the internal clearance of the first bearing portion 75. It is set. Thereby, the inclination of the shaft 70 accompanying the rotation is defined by the clearance between the bearing hole 35 located outside the inner region and the shaft 70. Thereby, the inclination of a shaft can be suppressed more. Moreover, the design freedom of the radial clearance in the first bearing portion 75 is increased.

(Other embodiments)
In the above embodiment, the center of the first bearing portion in the axial direction substantially coincides with the center position of the magnetic material portion of the stator in the axial direction. In another embodiment, as shown in FIGS. 5 and 6, the center in the axial direction of the first bearing portion is located in an internal region defined by the end in the axial direction of the magnetic material portion of the stator. Good. In addition, the same code | symbol is attached | subjected to the structure substantially the same as 1st Embodiment, and description is abbreviate | omitted. In the example shown in FIG. 5, a virtual line L4 indicating the center of the first bearing portion 75 in the axial direction is a virtual line L1 indicating the position of the end portion 55 in the axial direction of the stator 50 and a virtual line indicating the position of the end portion 56. It is located between the line L2. In the example shown in FIG. 6, the imaginary line L5 indicating the center of the first bearing portion 75 in the axial direction indicates the position of the end portion 55 in the axial direction of the first bearing portion 75 with the imaginary line L1 and the end portion 56. It is located between the virtual line L2 indicating the position and substantially coincident with the virtual line L1. Even if comprised in this way, since it is bearing inside the rotating magnetic field formed by a stator, the inclination of a shaft can be suppressed.

  In the said embodiment, the 2nd bearing part was provided in the 2nd housing. That is, the 2nd bearing part was provided in the pump part side. In another embodiment, the second bearing portion may be provided on the side opposite to the pump portion. In addition, since the 2nd bearing part can suppress the inclination of a shaft, so that the distance with the 1st bearing part is separated, it is preferable. Moreover, in the said embodiment, although the bearing part was comprised by two, a 1st bearing part and a 2nd bearing part, only a 1st bearing part may be sufficient. Moreover, you may provide a bearing part in three or more places. When a plurality of bearing portions are provided, the other bearing portions are internal if the center in the axial direction of at least one bearing portion is located inside the inner region defined by the end in the axial direction of the magnetic material portion of the stator. It may be inside or outside the region.

  In the above embodiment, the inner rotor has seven teeth and the outer rotor has eight teeth. The number of teeth of the inner rotor and the outer rotor may be appropriately changed according to the required discharge amount. In that case, the number of inner teeth of the outer rotor may be one more than the number of outer teeth of the inner rotor. Further, the pump is not limited to the inscribed gear pump, and may be any pump as long as it is a rotary pump that sends fluid by rotating a shaft. Moreover, in the said embodiment, although the electric pump was an oil pump which sends oil, the fluid sent, such as a water pump, may not be oil.

The motor unit of the above embodiment is a so-called SPM motor in which a magnet is attached to the outer periphery of the rotor. However, the motor unit is not limited to the SPM motor, and may be another motor such as an IPM motor. Further, although a magnet is attached to the rotor, any number of magnetic poles may be used.
Furthermore, in the above embodiment, the length of the stator in the axial direction and the length of the rotor are substantially the same, but the length of the stator in the axial direction and the length of the rotor may be different.

Moreover, in the said embodiment, the electric pump was used for the automatic transmission device of the vehicle. In other embodiments, the pump for feeding fluid can of course be applied to other fields.
As mentioned above, this invention is not limited to the said embodiment at all, In the range which does not deviate from the meaning of invention, it can implement with a various form.

  10: Electric pump, 12: Pump part, 13: Motor part, 14: Driver, 20: Housing, 21: First housing, 23: Suction port, 24: Discharge port, 26: Recessed part, 30: Bolt, 31: First 2 housing, 32: cylindrical part, 33: oil seal, 34: accommodating chamber, 35: bearing hole (second bearing part), 37: O-ring groove, 38: O-ring groove, 39: cover, 40: inner rotor, 41: shaft hole, 42: flat portion, 44: external teeth, 45: outer rotor, 46: internal teeth, 48: gap portion, 49: oil chamber, 50: stator, 51: magnetic material portion, 53: insulator, 55 : End part, 56: End part, 60: Rotor, 61: Bottom part, 62: Hole, 64: Peripheral wall, 65: Magnet, 67: Inner wall, 68: Storage space, 70: Shaft, 71: Fitting part, 72: Notched surface, 80: Engine 81: Drive wheel, 82: Drive shaft, 84: Battery, 85: Starter, 86: Alternator, 87: Electrical component, 89: ECU, 90: Automatic transmission, 91: Mechanical hydraulic pump, 92: Control valve, 93 : Start clutch, 94: Check valve, 96: Bypass passage, 97: Hydraulic passage, 98: Oil pan, 99: Strainer

Claims (6)

  1. A stator having a magnetic material part and forming a rotating magnetic field by energizing the winding;
    A rotor that is rotatably arranged on the inner side in the radial direction of the stator and that rotates by receiving a rotating magnetic field formed by the stator;
    A shaft that rotates integrally with the rotor;
    At least one bearing portion rotatably supporting the shaft;
    A pump part having a housing in which an inlet and an outlet are formed; and a pump unit that sucks fluid from the inlet by the rotation of the shaft and discharges the fluid from the outlet;
    With
    An electric pump characterized in that the axial center of at least one of the bearing portions is located inside an internal region defined by both axial ends of the magnetic material portion of the stator.
  2.   2. The electric pump according to claim 1, wherein the center of at least one of the bearing portions in the axial direction coincides with the center of the stator in the axial direction.
  3. The bearing portion has a first bearing portion and a second bearing portion,
    The center of the first bearing portion in the axial direction is located inside the inner region,
    2. The electric pump according to claim 1, wherein a center of the second bearing portion in the axial direction is located outside the inner region.
  4.   The electric pump according to claim 3, wherein a center of the first bearing portion in the axial direction coincides with a center of the magnetic material portion of the stator in the axial direction.
  5.   5. The electric pump according to claim 3, wherein a radial clearance in the second bearing portion is set to be smaller than an inclination amount of a radial shaft in the first bearing portion.
  6. The pump portion has outer teeth with outer teeth formed on the outer periphery and rotating integrally with the shaft, and an outer rotor with inner teeth meshed with the outer teeth formed on the inner periphery.
    The electric pump according to claim 1, wherein the housing rotatably accommodates the inner rotor and the outer rotor.
JP2009275569A 2009-12-03 2009-12-03 Electric pump Active JP4918936B2 (en)

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JP2009275569A JP4918936B2 (en) 2009-12-03 2009-12-03 Electric pump
DE201010060735 DE102010060735A1 (en) 2009-12-03 2010-11-23 Electric pump
US12/957,650 US20110135516A1 (en) 2009-12-03 2010-12-01 Electric pump

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JP2011117369A true JP2011117369A (en) 2011-06-16
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JP4918936B2 (en) 2012-04-18
DE102010060735A1 (en) 2011-06-09
US20110135516A1 (en) 2011-06-09
DE102010060734A1 (en)

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