JP2014173444A - Electric pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an electric pump capable of suppressing partial wear of inner and outer rotor parts while adopting a consequent-type motor rotor.SOLUTION: A motor rotor 22 is a consequent pole-type rotor which has a plurality of magnets 28 with one magnetic pole embedded in a circumferential direction of a rotor core 26 so that a magnet pole part 27 can be formed and which is configured so that an iron core part of the rotor core 26 between the respective magnet pole parts 27 can function as the other magnetic pole. Inner and outer rotor parts 36b and 36a are made of a resin material.

Description

  The present invention relates to an electric pump.

  2. Description of the Related Art Conventionally, for example, the electric pump shown in Patent Document 1 includes a motor unit as a drive source having a motor stator around which a coil is wound and a motor rotor that rotates by excitation of the motor stator, and a metal pump rotor (pump action unit) And. The pump rotor is composed of an inner rotor portion having external teeth and an outer rotor portion having internal teeth meshing with the external teeth, and fluid is supplied by the rotation of the inner rotor portion and the outer rotor portion based on the rotation of the motor rotor. Yes.

  As a rotor of a motor, for example, as shown in Patent Document 2, a plurality of magnets having one magnetic pole are embedded in the circumferential direction of the rotor core to form a magnet magnetic pole part, and the rotor core between each magnet magnetic pole part is formed. There is a continuous pole type rotor configured such that the iron core functions as the other magnetic pole. Such a rotor is advantageous in terms of cost reduction, for example, because the amount of magnet used can be reduced.

JP 2012-97582 A JP 2009-273214 A

  In the above-described continuous pole type rotor, the magnetic pole is composed of a magnetic magnetic pole portion having a magnetic flux forcing force (induction) and an iron core portion having no magnetic force forcing force, and therefore magnetic imbalance is likely to occur. Therefore, when the continuous rotor is employed in the motor rotor of the electric pump as described in Patent Document 1, the surface pressure in the engagement between the outer teeth and the inner teeth of the inner rotor portion and the outer rotor portion is locally increased. As a result, local wear (uneven wear) occurs in the inner teeth, which may affect the pump action.

  The present invention has been made to solve the above-described problem, and an object of the present invention is to provide an electric pump that can suppress uneven wear of the inner rotor portion and the outer rotor portion while adopting a continuous motor rotor. There is.

  An electric pump that solves the above problems is a pump action comprising a motor rotor that rotates by excitation of a motor stator around which a coil is wound, an inner rotor portion that has external teeth, and an outer rotor portion that has internal teeth that mesh with the external teeth. An electric pump that feeds fluid by rotation of the inner rotor portion and the outer rotor portion based on rotation of the motor rotor, wherein the motor rotor has a plurality of magnets with one magnetic pole embedded in the circumferential direction of the rotor core. A magnetic pole portion is formed, and the iron core portion of the rotor core between the magnet magnetic pole portions is a continuous pole type rotor configured to function as the other magnetic pole, and the inner rotor portion and the outer rotor portion At least one is made of a resin material.

  According to this configuration, at least one of the inner rotor portion and the outer rotor portion is made of a resin material that is less likely to be worn than metal, so that the deviation between the inner rotor portion and the outer rotor portion is adopted while adopting a continuous rotor for the motor rotor. Wear can be suppressed.

In the electric pump, it is preferable that the magnets of the motor rotor are embedded in the rotor core.
According to this configuration, it is possible to improve the amount of magnetic flux in the iron core portion, so that magnetic imbalance between the magnet magnetic pole portion and the iron core portion can be suppressed. Thereby, the partial wear of an inner rotor part and an outer rotor part can be suppressed more. Moreover, since the magnet is embedded in the rotor core, damage to the magnet can be suppressed.

In the electric pump, it is preferable that the number of slots of the motor stator is set to an integral multiple of the number of the magnet magnetic pole portions.
According to this configuration, when a certain magnet magnetic pole portion faces one teeth portion of the stator, the magnet magnetic pole portion and teeth portion face each other at other locations, so that the radial direction applied to the motor rotor can be reduced. Uneven load can be reduced. Thereby, it becomes possible to suppress the vibration of the motor rotor.

  In the electric pump, the inner rotor portion is fixed to a rotating shaft that rotates integrally with the motor rotor so as to be integrally rotatable, and a first shaft supporting portion that supports the rotating shaft between the inner rotor portion and the motor rotor; It is preferable to include a second shaft support portion that supports the rotating shaft at a position on the side opposite to the motor rotor from the inner rotor portion.

  According to this configuration, since the first and second shaft support portions are provided on both sides in the axial direction of the inner rotor portion to which a load is applied (so-called both-side support), it is possible to suppress the shaft shake of the motor rotor (rotary shaft). As a result, damage to the magnet of the motor rotor can be further suppressed.

  In the electric pump, it is preferable that the outer rotor portion of the pump action portion is provided on an inner peripheral side of the rotor core and is configured to rotate integrally with the rotor core.

According to this configuration, since the outer rotor portion of the pump action portion is integrally formed on the inner peripheral side of the rotor core of the motor rotor, it can contribute to downsizing of the electric pump in the axial direction.
In the electric pump, the inner rotor portion and the outer rotor portion are preferably configured by including a carbon fiber or a glass fiber in a resin material.

According to this structure, the intensity | strength of the inner rotor part and outer rotor part which consist of resin materials can be improved.
In the electric pump, it is preferable that the resin material forming the inner rotor portion and the outer rotor portion is made of engineering plastic.

  According to this configuration, by adopting an engineering plastic excellent in heat resistance, durability and mechanical properties (abrasion resistance and impact strength) to the resin material constituting the inner rotor portion and the outer rotor portion of the pump action portion, Contributes to improving the quality of electric pumps.

  In the electric pump, the inner rotor portion is fixed to a rotating shaft that rotates integrally with the motor rotor so that the inner rotor portion can rotate integrally, and the outer teeth of the inner rotor portion are set to a number of teeth different from an integer multiple of the number of the iron core portions. Preferably it is.

  According to this configuration, it is possible to suppress resonance between the motor rotor and the inner rotor portion, and as a result, it is possible to contribute to low vibration of the electric pump.

  According to the electric pump of the present invention, uneven wear of the inner rotor portion and the outer rotor portion can be suppressed while adopting a continuous type motor rotor.

It is sectional drawing which shows the state which assembled | attached the electric oil pump of 1st Embodiment to the transmission. It is a top view of the motor rotor of the same form. It is a schematic diagram for demonstrating the pump rotor of the same form. It is an axial sectional view of the electric oil pump of the second embodiment. It is an axial orthogonal direction sectional view of the electric oil pump of the same form. It is a schematic diagram for demonstrating the pump rotor of another example.

(First embodiment)
Hereinafter, a first embodiment of an electric pump (electric oil pump) will be described.
As shown in FIG. 1, the electric oil pump 10 of this embodiment is used for a transmission 11 (driving force transmission device) mounted on a vehicle, and a pump mounting recess 12 recessed in the transmission 11. The electric oil pump 10 is partly embedded in an embedded manner.

  The housing 13 of the electric oil pump 10 includes a substantially cylindrical motor case 14, a pump case 15 provided at one end of the motor case 14 in the axial direction (hereinafter referred to as the first end 14 a), and the axial direction of the motor case 14. It is comprised from the circuit case 16 provided in the other end part (henceforth the 2nd end part 14b).

  The motor case 14 is made of a metal material (preferably iron) and is provided so that the central axis L1 thereof is parallel to the horizontal direction. Inside the motor case 14 is housed a motor portion 17 as a drive source for the electric oil pump 10. The motor unit 17 includes an annular motor stator 21 fixed to the inner peripheral surface of the motor case 14, and a motor rotor 22 disposed inside the motor stator 21.

  The motor stator 21 has a stator core 23 made of a plurality of electromagnetic steel plates laminated in the axial direction. The stator core 23 is formed with a plurality of tooth portions 23a extending radially inward, and a coil 24 is wound around each tooth portion 23a. The outer peripheral surface of the stator core 23 is in metal contact with the inner peripheral surface of the motor case 14. Further, the central axis of the motor stator 21 is configured to coincide with the central axis L <b> 1 of the motor case 14. Further, the coil 24 is inserted into a space (slot) formed between the circumferential directions of the tooth portions 23a.

  The motor rotor 22 has a rotating shaft 25 and a substantially cylindrical rotor core 26 that is fitted and fixed (press-fit) to the rotating shaft 25. The rotor core 26 is configured by laminating a plurality of electromagnetic steel plates in the axial direction. The rotating shaft 25 is made of stainless steel, which is a nonmagnetic metal, and the axis of the rotating shaft 25 is configured to coincide with the central axis L <b> 1 of the motor case 14.

  As shown in FIG. 2, a plurality of (four in the present embodiment) magnet magnetic pole portions 27 that are radially opposed to the teeth portion 23 a are formed on the outer peripheral portion of the rotor core 26 at equal intervals in the circumferential direction. Each magnet magnetic pole portion 27 is formed by embedding a plate-like magnet 28 in the peripheral portion of the rotor core 26. That is, the motor rotor 22 of the present embodiment is configured as an embedded magnet type (IPM type) motor rotor.

  Specifically, magnet housing holes 26a drilled in the axial direction are provided in the circumferential portion of the rotor core 26 at equal intervals (90-degree intervals) in the circumferential direction, and the radial direction of the rotor core 26 is provided in each magnet housing hole 26a. Each magnet magnetic pole portion 27 is formed by accommodating and fixing each magnet 28 in an orthogonal manner. Each magnet 28 is disposed so that the magnetic pole surface on the radially outer side of the rotor core 26 has the same polarity (for example, S pole). As a result, four magnet magnetic pole portions 27 having the same polarity (S pole) are formed in the motor rotor 22 at substantially equal intervals (approximately 90 ° intervals) along the circumferential direction. Between the circumferential directions of the magnet magnetic pole portions 27, an iron core portion 26b of the rotor core 26 is formed to project outward in the radial direction. A pseudo magnetic pole having a polarity different from that of the adjacent magnet magnetic pole portion 27 is formed in each iron core portion 26 b by the magnetic action of the magnet 28. That is, the motor rotor 22 is configured as a so-called continuous pole type rotor.

  Here, the number of slots of the motor stator 21 (the number of teeth portions 23a) is set to an integral multiple of the number of magnet magnetic pole portions 27. That is, in this embodiment, since the number of the magnet magnetic pole portions 27 is 4, the number of slots of the teeth portion 23a is set to an integral multiple of 4. As a result, when one magnet magnetic pole portion 27 faces one tooth portion 23a, the magnet magnetic pole portion 27 and the tooth portion 23a also face each other at other locations, so that the radial direction applied to the motor rotor 22 can be reduced. Uneven load can be reduced.

  The pump case 15 includes a main body portion 31 assembled to the first end portion 14 a of the motor case 14 and a lid portion 32 assembled to the main body portion 31. Both the main body 31 and the lid 32 are made of an aluminum material that is a nonmagnetic metal. The main body 31 is press-fitted and fixed to the opening of the first end 14 a of the motor case 14. The pump chamber 33 formed inside the main body 31 is liquid-tightly closed by a lid portion 32 assembled from the motor portion 17 side in the direction of the axis L1.

  Further, the pump case 15 has a rotary shaft 25 by a shaft support recess 34 (second shaft support portion) provided in the pump chamber 33 and a shaft support hole 35 (first shaft support portion) formed through the lid portion 32. Is supported. The shaft support hole 35 (lid portion 32) is provided on the motor portion 17 side of the pump chamber 33, and the shaft support recess 34 is provided on the non-motor portion side (discharge port 37 side) of the pump chamber 33. In the pump chamber 33, a pump rotor 36 (pump action part) connected to the rotary shaft 25 is disposed.

  As shown in FIG. 3, the pump rotor 36 is of an inscribed gear type, and is of an inscribed gear type, and has an outer rotor portion 36a having n teeth (n is a natural number of 3 or more) teeth, The inner rotor portion 36b includes n-1 pieces, and one end side of the rotary shaft 25 is fixed to the inner rotor portion 36b.

  Specifically, the inner rotor portion 36b has four external teeth Tb, and the outer rotor portion 36a has five internal teeth (grooves) Ta that mesh with the external teeth Tb. The outer rotor portion 36a rotates by sliding on the inner peripheral surface of the pump chamber 33 around the shaft center Xa deviating from the shaft center Xb of the inner rotor portion 36b (the rotation shaft 25) based on the rotation of the inner rotor portion 36b. It is supposed to be configured.

  In the present embodiment, the inner rotor portion 36b and the outer rotor portion 36a are formed of an engineering plastic that is a resin material having excellent heat resistance, durability, and mechanical properties (wear resistance and impact strength). Further, in order to improve the strength, carbon fiber (or glass fiber) is mixed in the engineering plastic constituting the inner rotor portion 36b and the outer rotor portion 36a. Examples of engineering plastics include polyimide materials and polyamide materials.

  As shown in FIG. 1, the bottom 31 a of the main body 31 of the pump case 15 is exposed to the outside of the motor case 14, and the bottom 31 a has a cylindrical shape protruding along the axial direction of the motor case 14. A discharge port 37 is formed. The inside of the discharge port 37 is in communication with the pump chamber 33. Further, the central axis L2 of the discharge port 37 is shifted from the central axis L1 of the motor case 14. In addition, a check valve 38 is provided inside the discharge port 37 to prevent the flow of oil from an oil outlet passage 41 (described later) to the pump chamber 33.

  The check valve 38 includes a ball 38a and a compression coil spring 38b. The ball 38a is provided so as to be able to close the narrowed portion 37a in the discharge port 37, and the compression coil spring 38b biases the ball 38a toward the narrowed portion 37a. The ball 38a closes the constriction 37a when the pump rotor 36 is not driven, and is separated from the constriction 37a against the spring pressure by the oil pressure when the pump rotor 36 is driven. Allow distribution.

  In addition, a suction port 31 b that connects the space between the pump case 15 and the pump mounting recess 12 (oil inflow space S) and the pump chamber 33 is formed on the outer peripheral portion of the main body 31 of the pump case 15. . The suction port 31b extends vertically downward from the position of the pump chamber 33 (perpendicular to the central axis L1), and is formed to open vertically downward from the outer peripheral surface (lower surface) of the main body 31.

  The second end portion 14b of the motor case 14 is formed with a flange portion 14c extending outward in the radial direction over the entire circumference of the second end portion 14b. The flange portion 14c is in contact with the end surface (fixed surface 11a) where the pump mounting recess 12 is provided in the assembly direction of the electric oil pump 10 (the direction along the central axis L1 of the motor case 14). . The second end portion 14b of the motor case 14 is closed by a circuit case 16 that houses a circuit board 39 on which the circuit element 39a is mounted. The circuit case 16 and the flange portion 14c of the motor case 14 are fastened and fixed to the fixing surface 11a of the transmission 11 by screws (not shown).

  The pump mounting recess 12 of the transmission 11 has a circular shape when viewed in the assembly direction, and has a stepped shape with a larger inner diameter on the opening side (the fixed surface 11a side). A circular oil outlet passage 41 is formed in the bottom surface 12 a of the pump mounting recess 12, and a discharge port 37 of the pump case 15 is fitted into the oil outlet passage 41. As a result, the discharge port 37 b at the tip of the discharge port 37 is disposed in the oil outlet passage 41. Further, the inner peripheral surface of the oil outlet passage 41 and the outer peripheral surface of the discharge port 37 are sealed in a liquid-tight manner by a seal member 42.

  Also, oil from the oil pan is introduced into the pump mounting recess 12 at a position on the lower side in the vertical direction on the inner peripheral surface 12b of the pump mounting recess 12 (the inner peripheral surface on the bottom surface 12a side than the fitting recess 43). For this purpose, an oil introduction path 12c is formed.

  A circular fitting recess 43 is formed near the opening of the pump mounting recess 12, and a shaft fitting portion 44 formed in the motor case 14 is fitted into the fitting recess 43. The outer peripheral surface of the centering fitting portion 44 is formed in a circular shape centered on the central axis L1 of the motor case 14, and the centering fitting portion 44 is fitted into the fitting recess 43, so that the pump is mounted. The motor case 14 is aligned with respect to the recess 12.

  Further, a taper portion 46 whose diameter increases toward the fixed surface 11a is formed at the opening end portion (end portion on the fixed surface 11a side) of the pump mounting recess 12 over the entire circumference of the opening end portion. . A sealing portion 47 provided between the flange portion 14c of the motor case 14 and the shaft fitting portion 44 is pressed against the taper portion 46 in the direction of the axis L1. The part is sealed in a liquid-tight manner.

  In the motor case 14, the outer diameter of the portion on the first end portion 14 a side from the tip end portion 44 a (insertion tip) in the assembly direction of the shaft fitting portion 44 is smaller than the outer diameter of the shaft fitting portion 44. A gap is set between the small diameter portion 45 and the inner peripheral surface 12 b of the pump mounting recess 12.

  In addition, the oil inflow space S in the pump mounting recess 12 is between the radial direction of the outer diameter surface of the motor case 14 and the outer peripheral surface of the main body 31 (pump case 15) and the inner peripheral surface 12b of the pump mounting recess 12; It is formed over the axial direction between the bottom 31 a of the main body 31 and the bottom surface 12 a of the pump mounting recess 12. In the oil inflow space S, oil inflow from the oil introduction path 12c is allowed.

Next, the operation of this embodiment will be described.
In the electric oil pump 10 having the above-described configuration, the motor rotor 22, the rotary shaft 25, and the inner rotor portion 36b are rotated by the excitation of the coil 24 of the motor stator 21, and the outer rotor portion 36a is rotated by the engagement of the internal teeth Ta and the external teeth Tb. Then, the oil in the oil inflow space S is sucked into the pump chamber 33 from the suction port 31b and discharged from the discharge port 37b of the discharge port 37 to the oil outlet passage 41 by the pump action by the rotation of the inner rotor portion 36b and the outer rotor portion 36a. Is done.

  Here, since the inner rotor portion 36b and the outer rotor portion 36a of the present embodiment are made of a resin material (engineering plastic), for example, the weight can be reduced and the buffering property (elasticity) is excellent as compared with a metal material. Therefore, the collision noise between the inner rotor portion 36 b and the outer rotor portion 36 a and between the outer rotor portion 36 a and the inner peripheral surface of the pump chamber 33 is suppressed. Furthermore, it is excellent in corrosion resistance and ease of molding compared to metal materials.

  Since the resin material has elasticity compared to metal, in this embodiment, the impact due to the engagement between the inner rotor portion 36b and the outer rotor portion 36a is more elastic than in the case where the inner rotor portion 36b and the outer rotor portion 36a are made of metal. Thus, the wear resistance is improved. For this reason, even if the motor rotor 22 is configured as a continuous pole type as in the present embodiment, uneven wear of the inner rotor portion 36b and the outer rotor portion 36a can be suppressed.

  On the other hand, the resin material is inferior in heat resistance, durability and impact strength as compared with the metal material. Therefore, in this embodiment, engineering plastics excellent in heat resistance, durability, and impact strength are adopted as the resin material constituting the inner rotor portion 36b and the outer rotor portion 36a in order to compensate for the disadvantages. Furthermore, in this embodiment, the strength of the inner rotor part 36b and the outer rotor part 36a is improved by mixing carbon fiber (or glass fiber) with the engineering plastic.

  In addition, since the inner rotor portion 36b and the outer rotor portion 36a are made of a resin material, the variation in the tip clearance (gap in the radial direction) between the external teeth Tb and the internal teeth Ta due to thermal expansion and contraction becomes significant. . That is, the tip clearance increases at a low temperature, and the tip clearance decreases at a high temperature. In the low temperature state, the viscosity of the oil increases and it becomes difficult to flow, but the chip clearance increases due to the low temperature, so that the surface pressure between the outer teeth Tb and the inner teeth Ta decreases, and as a result, power saving of the motor unit 17 (Ie, downsizing of the motor unit 17). On the other hand, when the tip clearance is large due to the low viscosity of the oil at high temperatures, the pump efficiency (volumetric efficiency) is significantly reduced. However, the tip clearance is reduced at high temperatures, so the reduction in pump efficiency is suppressed. ing.

  Further, when the variation in the tip clearance between the inner rotor portion 36b and the outer rotor portion 36a becomes significant, the inner rotor portion 36b, the outer rotor portion 36a, and the motor rotor 22 are likely to be shaken. Therefore, in the present embodiment, the motor rotor 22 is made of the embedded magnet type, so that even if the rotor core 26 interferes with the motor stator 21 due to shaft shake, the magnet 28 is prevented from directly contacting the motor stator 21. Has been. Moreover, since the motor rotor 22 is of the embedded magnet type, the amount of magnetic flux in the iron core portion 26b can be improved, so that magnetic imbalance between the magnet magnetic pole portion 27 and the iron core portion 26b can be suppressed. Thereby, the partial wear of the inner rotor part 36b and the outer rotor part 36a is suppressed more.

  The continuous pole type motor rotor 22 employed in the present embodiment is a pseudo magnetic pole different from an actual magnet although the iron core portion 26b functions as a magnetic pole, and there is no magnet having a different magnetic pole in the vicinity of the magnet 28. The magnetic flux of the magnet 28 is likely to flow to parts other than the iron core part 26b. However, in this embodiment, since the pump rotor 36 (inner rotor portion 36b and outer rotor portion 36a) is made of resin, magnetization of the pump rotor 36 due to leakage magnetic flux is suppressed, and iron powder or the like is applied to the pump rotor 36 by magnetic force. Adsorption is prevented. Thereby, for example, it is prevented that good operation is hindered by iron powder or the like entering between the inner rotor portion 36b and the outer rotor portion 36a or between the outer rotor portion 36a and the inner peripheral surface of the pump chamber 33. ing.

  Further, when the motor unit 17 is driven, the oil in the oil pan flows into the oil inflow space S through the oil introduction path 12 c by the rotation (pump action) of the pump rotor 36, and the oil accumulated in the oil inflow space S In the state where the oil level (water level) reaches at least the inlet of the suction port 31b (in this embodiment, the lower end in the vertical direction), oil flows into the pump chamber 33 from the suction port 31b and oil from the discharge port 37b. It is discharged to the outlet path 41. In other words, the oil is supplied from the oil introduction path 12c to the oil outlet path 41 while maintaining the state where the oil is accumulated in the oil inflow space S.

  On the other hand, when the motor unit 17 is not driven, the oil in the oil pan does not flow into the oil inflow space S, but the check valve 38 in the discharge port 37 leads from the oil inflow space S to the oil introduction path 12c (oil pan side). The oil spill is suppressed. Specifically, when the motor unit 17 is not driven, the check valve 38 closes the flow path (constriction 37a) in the discharge port 37, so that air enters the pump chamber 33 from the oil outlet path 41. Accordingly, the outflow of oil from the oil inflow space S, that is, the lowering of the oil level in the oil inflow space S is suppressed. That is, even when the motor unit 17 is not driven, the state where oil is accumulated in the oil inflow space S is maintained.

  As described above, oil is stored in the oil inflow space S regardless of whether the motor unit 17 is driven or not. A part of the pump case 15 and the motor case 14 is immersed in the oil stored in the oil inflow space S. Thereby, the heat of the electric oil pump 10 (especially the heat generated in the motor stator 21) is preferably radiated to the transmission 11 side through oil that generally has better thermal conductivity than air.

  In addition, when the electric oil pump 10 is driven in a state where no oil is stored in the oil inflow space S, such as during an initial operation after the electric oil pump 10 is assembled in the pump mounting recess 12, the oil flows into the oil inflow space S from the oil introduction path 12c. The pump rotor 36 rotates with no oil in the pump chamber 33 until the oil level of the oil to reach reaches the suction port and the oil flows into the pump chamber 33. Here, in the present embodiment, the suction port 31b is provided on the lower side in the vertical direction than the pump rotor 36, and opens downward in the vertical direction, so that the oil level of the oil in the oil inflow space S is the suction port 31b. It is possible to shorten the time to reach the entrance. As a result, it is possible to shorten the time for which the pump rotor 36 rotates in the absence of oil. As a result, the generation of friction between the pump rotor 36 and the pump case 15 is suppressed, and the wear of the pump rotor 36 is reduced. Is to be suppressed.

  In the present embodiment, a check valve 38 is provided in the pump case 15 on the discharge port 37b side (downstream side of the flow path) with respect to the pump rotor 36 (pump chamber 33). This prevents air from entering the pump chamber 33 from the oil outlet passage 41 through the discharge port 37b, and as a result, corrosion of internal components (for example, the rotary shaft 25) due to water vapor in the air is suppressed. Yes.

Next, characteristic effects of the present embodiment will be described.
(1) Since the inner rotor portion 36b and the outer rotor portion 36a are made of a resin material that is less likely to be worn than metal, the motor rotor 22 may be a concentric rotor, and the inner rotor portion 36b and the outer rotor portion 36a may be offset. Wear can be suppressed.

  Moreover, the inner rotor part 36b and the outer rotor part 36a are made of resin, so that corrosion of the inner rotor part 36b and the outer rotor part 36a can be suppressed, and further, the electric oil pump 10 can be reduced in weight.

  (2) Since each magnet 28 is embedded in the rotor core 26, the amount of magnetic flux in the iron core portion 26b can be improved, and as a result, magnetic imbalance between the magnet magnetic pole portion 27 and the iron core portion 26b can be suppressed. it can. Thereby, the partial wear of the inner rotor part 36b and the outer rotor part 36a can be suppressed more. Further, even if the rotor core 26 interferes with the motor stator 21 due to the shaft runout, the magnet 28 is prevented from coming into direct contact with the motor stator 21, thereby suppressing damage and dropout of the magnet 28. .

  (3) The number of slots of the motor stator 21 (the number of teeth portions 23a) is set to an integral multiple of the number of magnet magnetic pole portions 27. As a result, when one magnet magnetic pole portion 27 faces one tooth portion 23a, the magnet magnetic pole portion 27 and the tooth portion 23a also face each other at other locations, so that the radial direction applied to the motor rotor 22 can be reduced. Uneven load can be reduced. Thereby, the vibration of the motor rotor 22 can be suppressed.

  (4) A shaft support hole 35 for supporting the rotary shaft 25 between the inner rotor portion 36b fixed to the rotary shaft 25 so as to be integrally rotatable and the motor rotor 22, and a motor rotor side (discharge port 37 side) from the inner rotor portion 36b. ), And a shaft support recess 34 that supports the rotary shaft 25 at the position. According to this configuration, the shaft support recess 34 and the shaft support hole 35 are provided on both sides in the axial direction of the inner rotor portion 36b to which a load is applied (so-called “both ends”), so As a result, interference between the rotor core 26 and the motor stator 21 can be suppressed, and damage to the magnet 28 of the motor rotor 22 can be further suppressed.

  (5) Since the resin material constituting the inner rotor portion 36b and the outer rotor portion 36a employs an engineering plastic excellent in heat resistance, durability, and mechanical properties (abrasion resistance and impact strength), the electric oil pump 10 Can contribute to the improvement of quality.

  (6) Since the inner rotor portion 36b and the outer rotor portion 36a are configured by including a carbon fiber (or glass fiber) in a resin material (engineering plastic), the strength of the inner rotor portion 36b and the outer rotor portion 36a can be improved.

  (7) Oil inflow between the inner surface of the pump mounting recess 12 and the outer surface of the housing 13 (the motor case 14 and the pump case 15) from which oil flows from the oil introduction path 12c based on the operation of the pump rotor 36. A space S is formed, and a part of the housing 13 is immersed in oil accumulated in the oil inflow space S. The pump case 15 is provided with a check valve 38 for suppressing the backflow of oil from the oil inflow space S to the oil introduction path 12c. According to this configuration, since a part of the housing 13 is immersed in the oil in the oil inflow space S, the heat of the housing 13 (especially the heat of the motor unit 17) is generally made of oil having a higher thermal conductivity than air. It is possible to suitably dissipate heat. In addition, since the backflow of oil from the oil inflow space S to the oil introduction path 12c is suppressed by the check valve 38 when the operation of the pump rotor 36 is stopped, heat dissipation due to a decrease in the oil in the oil inflow space S. Can be prevented from worsening.

  (8) Since the check valve 38 is provided on the discharge port 37 b side with respect to the pump rotor 36, it is possible to prevent air from flowing into the pump chamber 33 from the oil outlet passage 41 through the discharge port 37 b. it can. Thereby, it can suppress that internal components, such as the rotating shaft 25, corrode by the water vapor | steam in air.

  (9) The opening end (inlet end) of the suction port 31b is provided below the pump rotor 36 (pump chamber 33) in the vertical direction. For this reason, it is possible to shorten the time until the oil level (water level) of the oil in the oil inflow space S reaches the suction port 31b during operation in a state where no oil is accumulated in the oil inflow space S. As a result, it is possible to shorten the time for which the pump rotor 36 rotates in the absence of oil, and as a result, the wear of the pump rotor 36 can be suppressed and the reduction of the service life can be suppressed.

  (10) The housing 13 includes a discharge port 37 that protrudes in the axial direction and has a discharge port 37 b at the tip, and is fitted into the oil outlet passage 41. According to this configuration, alignment between the discharge port 37b of the electric oil pump 10 and the oil outlet passage 41 on the transmission 11 side is facilitated, and the assemblability can be improved.

  (11) Since the check valve 38 is provided in the discharge port 37, the space of the check valve 38 on the discharge port 37b side of the pump rotor 36 is secured, and the shaft of the housing 13 in the pump mounting recess 12 is secured. It can suppress that direction length (length which does not include the insertion insertion part to the oil extraction path 41) becomes long.

(Second Embodiment)
Hereinafter, a second embodiment of the electric pump (electric oil pump) will be described. Note that the electric pump of the present embodiment is also used for a transmission mounted on a vehicle, as in the first embodiment.

  As shown in FIG. 4, the electric oil pump 50 according to the present embodiment includes an electric motor 51 configured by a brushless motor as a drive source and an internal gear type pump mechanism 81 (pump action unit) integrally formed. It is assembled and configured.

  The electric motor 51 includes a bottomed cylindrical front housing 52 and an end cover 53 that closes the opening. The front housing 52 has a bottom concave portion 52a in which the center portion of the bottom outer surface of the bottomed cylindrical shape is folded inward in a bottomed cylindrical shape. Annulus is formed around the bottom recess 52a in the front housing 52, specifically, an outer cylindrical portion 52b, an inner cylindrical portion 52c that is a cylindrical portion of the bottom recess 52a, and an annular bottom portion 52d that connects the bottom side of the housing 52. A stator accommodating portion 54 is formed. An annular stator 55 (motor stator) is accommodated in the annular stator accommodating portion 54.

  As shown in FIGS. 4 and 5, the stator 55 includes a magnetic metal stator core 56 having an outer ring portion 56a and ten teeth portions 56b extending inward in the radial direction from the outer ring portion 56a. And a coil 57 is wound around each tooth portion 56b. The coil 57 is connected for each of the three phases, and a drive current corresponding to each phase is supplied. In the stator 55, the outer ring portion 56a of the stator core 56 is fixed to the inner peripheral surface of the outer cylindrical portion 52b of the front housing 52 by press-fitting or the like, and the tip end portion (the radially inner end portion) of the teeth portion 56b is the inner side. It faces the cylindrical portion 52c. The stator 55 is configured such that a rotating magnetic field is generated at the tip end portion of the tooth portion 56 b based on power feeding to the coil 57. Incidentally, since the front housing 52 including the inner cylindrical portion 52c facing the tip of the tooth portion 56b is made of a non-magnetic iron-based metal material, a magnetic field generated at the tip of the tooth portion 56b causes the inner cylindrical portion 52c. It also occurs in the inner space of the bottom recess 52a.

  A circuit board 61 that supplies a drive current to the coil 57 of the stator 55 is held by a circuit holder 62 in the vicinity of the opening of the front housing 52. The circuit holder 62 is entirely made of resin or has a surface coated with resin, and is fixed to the inner peripheral surface of the opening of the front housing 52 or the stator 55. The circuit board 61 is held such that its plane is orthogonal to the central axis L <b> 1 of the motor 51. Various electronic components including a semiconductor switching element 63 and a temperature sensor 64 for generating a three-phase drive current are mounted on the circuit board 61, and a drive control circuit 65 for controlling the drive current supplied to the stator 55 is configured. ing. An end cover 53 is attached to the opening of the front housing 52 with a mounting bolt 58 or the like so as to cover the circuit board 61. The end cover 53 is provided with a connector portion 66 for feeding power from the outside to the built-in circuit board 61, sending / receiving signals to / from the outside, and the like.

  A drive rotor 71 (motor rotor), which is a rotor of the motor 51, is inserted from the outside into the bottom recess 52a of the front housing 52, and the center axis (rotation center) of the drive rotor 71 is the center axis L3 of the motor 51 (bottom recess 52a). And is rotatably accommodated so as to match. The drive rotor 71 is partitioned from the stator 55, the circuit board 61, and the like by the wall surface of the bottom recess 52a, and operates in oil when in use.

  The drive rotor 71 includes a rotor core 72 made of a substantially cylindrical metal material and a magnet 73, and is configured in an annular shape so as to form a pump chamber 74 at the center (the center of the rotor core 72).

  On the outer periphery of the rotor core 72, a plurality (four in this embodiment) of magnet magnetic poles 72a that are radially opposed to the teeth 56b are formed at equal intervals in the circumferential direction. Each magnet magnetic pole portion 72 a is formed by embedding a plate-like magnet 73 in the peripheral portion of the rotor core 72. That is, the drive rotor 71 is configured as an embedded magnet type (IPM type) rotor.

  In addition, each magnet 73 is arranged such that the magnetic pole surface on the radially outer side of the rotor core 72 has the same polarity (for example, S pole). As a result, four magnet magnetic pole portions 72a having the same polarity (S pole) are formed in the drive rotor 71 at substantially equal intervals (approximately 90 ° intervals) along the circumferential direction. Between the circumferential directions of the magnet magnetic pole portions 72a, an iron core portion 72b of the rotor core 72 is formed to protrude radially outward. A pseudo magnetic pole having a polarity different from that of the adjacent magnet magnetic pole part 72a is formed in each iron core part 72b by the magnetic action of the magnet 73. That is, the drive rotor 71 is configured as a so-called continuous pole type rotor.

  Further, in the present embodiment, eight slits 75 penetrate in the axial direction at equal intervals in the circumferential direction between the outer peripheral magnet 73 portion and the central pump chamber 74 in the drive rotor 71 (rotor core 72). Is formed. Each slit 75 is formed in an arc shape extending between the magnetic pole centers of adjacent magnets 73.

  On the inner peripheral side (center portion) of the rotor core 72, an outer rotor portion 82 constituting the pump mechanism 81 is formed integrally with the rotor core 72. That is, the outer rotor portion 82 is made of a metal material. The outer rotor portion 82 is formed in an annular shape having a plurality (five in this embodiment) of concave portions 82a (inner teeth) at equal intervals in the circumferential direction, and constitutes a pump chamber 74. The shape of each concave part 82a is formed along the trochoid curve.

  Inside the outer rotor portion 82 (pump chamber 74), an inner rotor portion 83 (driven rotor) that performs pumping operation of the pump mechanism 81 is rotatably accommodated. The inner rotor portion 83 has the same axial length as that of the drive rotor 71 and is configured so as to substantially overlap the whole in the same direction (see FIG. 4), thereby shortening the electric oil pump 50.

  The inner rotor portion 83 has a plurality (four in this embodiment) of convex portions 83a (external teeth) at equal intervals in the circumferential direction, and the shape of each convex portion 83a is formed along a trochoidal curve. A rotation shaft 84 is fitted and fixed at the center of the inner rotor portion 83.

  As in the first embodiment, the inner rotor portion 83 is formed of an engineering plastic that is a resin material having excellent heat resistance, durability, and mechanical properties (wear resistance and impact strength). Further, in order to improve the strength, carbon fiber (or glass fiber) is mixed in the engineering plastic constituting the inner rotor portion 83 and the outer rotor portion 82.

  Here, the bottom recess 52a is folded back as an inner cylindrical portion 52c from the bottom side of the front housing 52, and has a back bottom portion 52e extending in the direction orthogonal to the axis on the back side. A support recess 52f that rotatably supports the proximal end portion of the rotation shaft 84 of the inner rotor portion 83 is formed in the inner bottom portion 52e. The support recess 52f is set so that the center axis L4 of the inner rotor portion 83 (rotary shaft 84) is offset from the center axis L3 of the motor 51 (drive rotor 71). In other words, the inner rotor portion 83 rotates at a position deviated from the rotation center of the drive rotor 71.

  Therefore, the inner rotor portion 83 has a drive rotor so that its convex portion 83a meshes with the concave portion 82a of the pump chamber 74 of the drive rotor 71 on the side where the rotation center is deviated, and disengagement on the opposite side of the deviated portion. 71 rotates in an eccentric state. Therefore, as an operation of the pump mechanism 81, the volume of each space in the pump chamber 74 surrounded by the adjacent convex portion 83a and the concave portion 82a is expanded on the side where the meshing is disengaged, thereby generating a negative pressure. Then, oil is sucked into the space. On the other hand, the volume of the space surrounded by the adjacent convex portion 83a and the concave portion 82a is reduced on the meshing side, whereby the pressure in the space causes the oil in the space to be discharged.

  Further, an annular recess 52g that is further recessed is formed on the outer peripheral edge of the bottom portion 52e. The annular recess 52g functions as an oil reservoir between the drive rotor 71 and a part of the sucked oil flows, thereby improving pump efficiency. The annular recess 52g is a bulging portion 52h inside the front housing 52, and a temperature sensor 64 such as a thermistor mounted on the circuit board 61 is in surface contact with the bulging portion 52h. . The temperature sensor 64 is in surface contact with the bulging portion 52h, for example, by a portion having a large area. The temperature sensor 64 mainly detects the temperature of oil in the pump chamber 74 (annular recess 52g), and is used for control of the motor 51 (control of drive current) by the drive control circuit 65 including the detected oil temperature.

  A port block 91 is attached to the bottom of the front housing 52 with mounting bolts 92 and the like. The port block 91 includes a protruding portion 91a that fits into a bottom recess 52a in which the drive rotor 71 and the inner rotor portion 83 are accommodated, and an annular seal member 93 is provided on the outer peripheral side of the protruding portion 91a with the port block 91 and the front housing 52. And is sandwiched between. That is, the bottom recess 52a (pump chamber 74) is sealed.

  The protrusion 91a is formed with a support recess 91b for inserting and supporting the tip of the rotating shaft 84. The port block 91 in the vicinity of the support recess 91b is provided with a suction port 94 and a discharge port 95 that communicate with the pump chamber 74 at predetermined positions, respectively. Connected to the oil circulation path.

Next, the operation (action) of the electric oil pump 50 of this embodiment will be described.
The drive control circuit 65 performs drive control of the electric motor 51 by pulse width modulation control (PWM control), and adjusts the drive current amount supplied to the coil 57 of the stator 55 by the PWM control (PWM duty). Yes. When a rotating magnetic field is generated in the stator 55 based on such current supply to the coil 57, the drive rotor 71 in the bottom recess 52a of the housing 52 rotates, and the inner rotor portion 83 of the pump mechanism 81 is rotated accordingly. The pump is operated and oil flows. The amount of oil flow is adjusted by PWM control for the motor 51.

  The drive control circuit 65 also performs output control of the motor 51 in accordance with the oil temperature. That is, when the oil temperature is low, the oil viscosity is high, and when the oil temperature is high, the oil viscosity is low. Therefore, the drive control circuit 65 needs the output of the motor 51 according to the oil temperature (viscosity) sufficiently and sufficiently. Adjustment is performed so that the motor 51 can achieve power saving and other effects.

  In the present embodiment, the temperature sensor 64 for detecting the temperature of the oil used for controlling the motor 51 is provided on the other side surface (bulging portion 52h) of the bottom recess 52a of the housing 52 where one side surface is exposed to the oil. The temperature of the contact portion of the housing 52 is detected, that is, the temperature of the oil is indirectly detected through the housing 52. At this time, since the temperature sensor 64 is brought into contact with the portion of the housing 52 that is exposed to oil and highly dependent on the temperature change of the oil, the temperature sensor 64 detects the temperature of the oil more accurately, and the drive control circuit 65 An effect such as higher power saving by the control can be obtained.

Next, characteristic effects of the present embodiment will be described.
(12) The inner rotor portion 36b that constitutes the pump mechanism 81 is made of a resin material that is less likely to be worn compared to metal, so that the inner rotor portion 36b is adopted while adopting a continuous rotor for the drive rotor 71 (motor rotor). And the partial wear of the outer rotor part 36a can be suppressed. Moreover, since the inner rotor part 83 consists of resin materials, the corrosion can be suppressed and also the electric oil pump 50 can be reduced in weight.

  Further, since the inner rotor portion 83 is made of a resin material, the variation in the tip clearance between the concave portion 82a and the convex portion 83a due to the thermal expansion and contraction becomes remarkable, and the inner rotor portion 83 and the outer rotor portion 82 ( Although the drive rotor 71) is likely to run out of shaft, the drive rotor 71 of the present embodiment has the magnet 73 embedded in the rotor core 72, so that even if the rotor core 72 interferes with the stator 55 due to shaft runout, The magnet 73 is prevented from coming into direct contact with the stator 55, thereby preventing damage to the magnet 73.

  (13) Since the outer rotor portion 82 is integrally formed on the inner peripheral side of the rotor core 72 of the drive rotor 71 (motor rotor) and is configured to rotate integrally with the rotor core 72, the electric oil pump 50 can be reduced in the axial direction. Can contribute.

In addition, you may change the said embodiment as follows.
The configuration such as the shape of the pump case 15 is not limited to the first embodiment, and may be changed as appropriate.

  For example, in the first embodiment, the inlet end of the suction port 31b is formed on the lower surface of the main body 31 of the pump case 15. However, for example, the suction port 31b is the same as the pump chamber 33 in the vertical direction. You may comprise so that it may be located above a position or the pump chamber 33. FIG.

  Further, in the first embodiment, the check valve 38 is provided in the discharge port 37 on the downstream side (discharge port 37b side) from the pump chamber 33, but other than this, for example, the upstream side from the pump chamber 33. For example, it may be provided in the suction port 31b.

  Moreover, in the said 1st Embodiment, although the discharge port 37 which has the discharge port 37b at the front-end | tip protruded from the pump case 15, for example, the discharge port 37 is abbreviate | omitted and the discharge port 37b (outlet) is pump case. You may form in the bottom face of 15.

  In the first embodiment, the rotary shaft 25 is supported on both sides of the pump rotor 36 in the axial direction. However, for example, the rotary shaft 25 is supported on both sides of the motor rotor 22 in the axial direction. Also good.

  The number of slots (number of teeth 23a) is set to an integer multiple of the number of magnet magnetic poles 27, but is not particularly limited to this, and the number of slots and the number of magnet magnetic poles 27 depends on the configuration. May be changed as appropriate.

  In the first embodiment, the number of teeth of the inner rotor portion 36b (external teeth Tb) is four, and the number of teeth of the outer rotor portion 36a (internal teeth Ta) is five. However, the number of teeth of the inner rotor portion 36b is The number may be any number obtained by subtracting 1 from the number of teeth of the outer rotor portion 36a.

  For example, as shown in FIG. 6, the number of teeth of the inner rotor portion 36b may be six, and the number of teeth of the outer rotor portion 36a may be seven. In such a configuration, since the number of teeth of the inner rotor portion 36b is set to a number of teeth different from an integer multiple of the number of iron core portions 26b of the motor rotor 22 (four in the first embodiment), the motor rotor 22 and the inner rotor portion Resonance with 36b can be suppressed, and as a result, the vibration of the electric pump can be reduced.

  In the first embodiment, both the outer rotor portion 36a and the inner rotor portion 36b are made of resin. However, the present invention is not particularly limited to this, and either the outer rotor portion 36a or the inner rotor portion 36b is made of resin. Either one may be made of metal.

  In the second embodiment, the integrally formed product of the rotor core 72 and the outer rotor portion 82 is made of metal and the inner rotor portion 83 is made of resin. However, for example, a resin is provided on the inner peripheral side of the metal rotor core 72. It is good also as a structure which provided the manufactured outer rotor part so that integral rotation was possible. In this case, the inner rotor portion 83 may be made of resin or metal.

  -In each above-mentioned embodiment, although inner rotor part 36b, 83 and outer rotor part 36a, 82 were comprised with the engineering plastic containing carbon fiber (or glass fiber), it is not specifically limited to this, Carbon fiber It is good also as a structure which does not contain glass fiber. Further, as the engineering plastic constituting the inner rotor portions 36b and 83 and the outer rotor portions 36a and 82, polycarbonate materials, polyacetal materials, etc. may be used in addition to the polyimide materials and polyamide materials described above.

  In each of the above embodiments, the outer rotor portions 36a and 82 and the inner rotor portions 36b and 83 of the pump rotor 36 (pump mechanism 81) are substantially spiral with the internal teeth Ta (concave portion 82a) and the external teeth Tb (convex portion 83a). You may comprise by the helical gear formed in the shape. According to this configuration, the internal teeth Ta (concave portion 82a) and the external teeth Tb (convex portion 83a) are engaged not only in the rotation direction but also in the axial direction, and therefore the shaft of the pump rotor 36 (pump mechanism 81). It is possible to suppress the deviation and to prevent the generation of abnormal noise due to the meshing.

  In each of the above embodiments, the teeth 23a and 56b (slots) of the stator cores 23 and 56 may have a so-called skew structure that is inclined with respect to the axial direction. According to this structure, it can contribute to suppression of cogging torque.

  The electric oil pumps 10 and 50 may be applied to an electric pump for circulating oil such as an engine other than the vehicle transmission, or may be applied to an electric pump for circulating a fluid other than oil.

  DESCRIPTION OF SYMBOLS 10,50 ... Electric oil pump (electric pump), 21 ... Motor stator, 22 ... Motor rotor, 24, 57 ... Coil, 25, 84 ... Rotary shaft, 26, 72 ... Rotor core, 26b, 72b ... Iron core part, 27, 72a ... Magnet pole part, 28, 73 ... Magnet, 34 ... Shaft support recess (second shaft support part), 35 ... Shaft support hole (first shaft support part), 36 ... Pump rotor (pump action part), 36a, 82 ... Outer rotor , 36b, 83 ... Inner rotor part, 55 ... Stator (motor stator), 71 ... Drive rotor (motor rotor), 81 ... Pump mechanism (pump action part), 82a ... Concave part (internal teeth), 83a ... Convex part ( External teeth), Ta ... internal teeth, Tb ... external teeth.

Claims (8)

A motor rotor rotating by excitation of a motor stator around which a coil is wound;
An inner rotor portion having external teeth and an outer rotor portion having inner teeth meshing with the external teeth;
An electric pump that feeds fluid by rotation of the inner rotor portion and the outer rotor portion based on rotation of the motor rotor,
The motor rotor is configured such that a plurality of magnets of one magnetic pole are embedded in the circumferential direction of the rotor core to form a magnet magnetic pole part, and the iron core part of the rotor core between the magnet magnetic pole parts functions as the other magnetic pole. Consequent pole type rotor,
At least one of the inner rotor part and the outer rotor part is made of a resin material. The electric pump according to claim 1,
Each of the magnets of the motor rotor is embedded in the rotor core. The electric pump according to claim 1 or 2,
The number of slots of the motor stator is set to an integral multiple of the number of the magnet magnetic pole portions. The electric pump according to any one of claims 1 to 3,
The inner rotor portion is fixed to a rotating shaft that rotates integrally with the motor rotor so as to be integrally rotatable,
A first shaft support portion that supports the rotation shaft between the inner rotor portion and the motor rotor; and a second shaft support portion that supports the rotation shaft at a position on the opposite side of the motor rotor from the inner rotor portion. An electric pump characterized by that. The electric pump according to any one of claims 1 to 3,
The electric pump according to claim 1, wherein the outer rotor portion of the pump action portion is provided on an inner peripheral side of the rotor core and is configured to rotate integrally with the rotor core. In the electric pump according to any one of claims 1 to 5,
The electric pump according to claim 1, wherein the inner rotor portion and the outer rotor portion are configured by including carbon fiber or glass fiber in a resin material. The electric pump according to any one of claims 1 to 6,
The electric pump, wherein the resin material constituting the inner rotor portion and the outer rotor portion is made of engineering plastic. The electric pump according to any one of claims 1 to 7,
The inner rotor portion is fixed to a rotating shaft that rotates integrally with the motor rotor so as to be integrally rotatable,
The external pump of the inner rotor part is set to a number of teeth different from an integer multiple of the number of the iron core parts.