WO2009110437A1 - 電動機 - Google Patents
電動機 Download PDFInfo
- Publication number
- WO2009110437A1 WO2009110437A1 PCT/JP2009/053894 JP2009053894W WO2009110437A1 WO 2009110437 A1 WO2009110437 A1 WO 2009110437A1 JP 2009053894 W JP2009053894 W JP 2009053894W WO 2009110437 A1 WO2009110437 A1 WO 2009110437A1
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- WO
- WIPO (PCT)
- Prior art keywords
- cooling medium
- rotor
- electric motor
- stator
- discharge port
- Prior art date
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Classifications
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K9/00—Arrangements for cooling or ventilating
- H02K9/19—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K1/00—Details of the magnetic circuit
- H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
- H02K1/22—Rotating parts of the magnetic circuit
- H02K1/32—Rotating parts of the magnetic circuit with channels or ducts for flow of cooling medium
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K21/00—Synchronous motors having permanent magnets; Synchronous generators having permanent magnets
- H02K21/12—Synchronous motors having permanent magnets; Synchronous generators having permanent magnets with stationary armatures and rotating magnets
- H02K21/24—Synchronous motors having permanent magnets; Synchronous generators having permanent magnets with stationary armatures and rotating magnets with magnets axially facing the armatures, e.g. hub-type cycle dynamos
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K5/00—Casings; Enclosures; Supports
- H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
- H02K5/12—Casings or enclosures characterised by the shape, form or construction thereof specially adapted for operating in liquid or gas
- H02K5/124—Sealing of shafts
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K5/00—Casings; Enclosures; Supports
- H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
- H02K5/18—Casings or enclosures characterised by the shape, form or construction thereof with ribs or fins for improving heat transfer
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K5/00—Casings; Enclosures; Supports
- H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
- H02K5/20—Casings or enclosures characterised by the shape, form or construction thereof with channels or ducts for flow of cooling medium
- H02K5/203—Casings or enclosures characterised by the shape, form or construction thereof with channels or ducts for flow of cooling medium specially adapted for liquids, e.g. cooling jackets
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K2205/00—Specific aspects not provided for in the other groups of this subclass relating to casings, enclosures, supports
- H02K2205/09—Machines characterised by drain passages or by venting, breathing or pressure compensating means
Definitions
- the present invention relates to an electric motor. More specifically, the present invention relates to an electric motor having a cooling structure for cooling a rotor during rotation.
- iron loss (vortex loss and hysteresis loss) is the main loss in the rotor of a permanent magnet type motor. Since the passing magnetic flux increases as the rotational speed of the rotor increases, this iron loss increases. As a result, the rotor generates heat. When the rotor generates heat and becomes high temperature, the magnetic properties of the magnet / magnetic material are deteriorated. Therefore, cooling of the rotor is required.
- Patent Document 1 Furthermore, there is a method in which an external oil pump is provided and the cooling medium is pumped by the external pump. JP 2001-37129 A
- the rotor can be efficiently cooled only by high-speed rotation, but it is expensive.
- the present invention has been made in view of the above problems.
- the objective of this invention is providing the electric motor which can cool a rotor with a cooling medium, without providing an external pump.
- a further object of the present invention is to provide an electric motor in which the cooling resistance of the rotor does not deteriorate due to an increase in the viscous resistance of the cooling medium when the rotor rotates at a low speed.
- An electric motor includes a stator, a rotor that is supported by a rotation shaft so as to rotate relative to the stator, and that is cooled by a cooling medium; A cooling medium storage section for storing a medium; and a cooling medium passage for guiding the cooling medium from the cooling medium storage section to the rotor; and a discharge port for discharging the cooling medium in the cooling medium passage,
- a cooling medium in the cooling medium storage unit is arranged by a negative pressure acting between the rotor and the discharge port, and the cooling medium storage unit is disposed below the discharge port while being disposed close to a rotating portion of the rotor. It is characterized by having a structure for sucking.
- an axial gap type electric motor includes a stator, a rotor that is supported by a rotating shaft so as to rotate relative to the stator, and that is cooled by a cooling medium, and on the stator side.
- a cooling medium storage section provided for storing the cooling medium; a cooling medium passage for guiding the cooling medium from the cooling medium storage section to the rotor; and approaching the stator or moving away from the stator.
- the rotor moves so that a gap between the rotor and the stator changes, and a discharge port for discharging the cooling medium in the cooling medium passage is provided on the rotor.
- FIG. 1 is a cross-sectional view showing the configuration of the motor according to the first embodiment of the present invention.
- FIG. 2 is a cross-sectional explanatory view of the lower half of the motor showing the flow of the cooling medium in the motor of FIG.
- FIG. 3 is an explanatory diagram showing the ATF (automatic transmission fluid) level due to negative pressure in a graph.
- FIG. 4 is an explanatory diagram showing the ATF discharge flow rate in a graph.
- 5A and 5B show a tip portion of a nozzle according to the second embodiment of the present invention.
- FIG. 5A is a cross-sectional explanatory diagram of a curved surface configuration
- FIG. 5B is a cross-sectional explanatory diagram of a multi-surface configuration.
- FIG. 6 is a cross-sectional explanatory view of the lower half of the motor showing the flow of the cooling medium according to the third embodiment of the present invention.
- FIG. 7 is a cross-sectional explanatory view of the lower half of the motor showing the flow of the cooling medium according to the fourth embodiment of the present invention.
- FIG. 8 is a cross-sectional explanatory view of the lower half of the motor showing the flow of the cooling medium according to the fifth embodiment of the present invention.
- FIG. 9 is an explanatory diagram on the rotor back side serving as a nozzle facing surface showing the tip of the nozzle according to the sixth embodiment of the present invention.
- 10 is an enlarged view of the tip of the nozzle of FIG. 9, FIG. 10A is a plan view of the nozzle, and FIG.
- FIG. 10B is a cross-sectional view of the nozzle.
- FIG. 11 is an explanatory cross-sectional view of the lower half of the motor according to the seventh embodiment of the present invention.
- FIG. 12 is a cross-sectional explanatory view of a motor according to the eighth embodiment of the present invention.
- FIG. 13 is a detailed explanatory view of the pressure regulating valve of FIG.
- FIG. 1 is a cross-sectional view showing a configuration of a motor 10 according to the first embodiment of the present invention.
- a motor 10 that is a permanent magnet type electric motor using a permanent magnet includes a stator (stator) 11 and a rotor (rotor) 12 that is rotatably supported.
- a facing surface of the stator 11 and a facing surface of the rotor 12 are arranged substantially parallel to a rotating shaft (rotor rotating shaft) 13 along the central axis direction of the cylindrical rotor 12.
- the motor 10 is a so-called radial gap motor having a gap AG between the rotor 12 and the stator 11.
- the stator 11 and the rotor 12 are housed inside the motor case 14.
- the motor 10 is installed and driven in a state where the rotating shaft 13 is laid down, that is, in a substantially horizontal state (the state shown in FIG. 1).
- the motor case 14 has a cylindrical case main body 14a and two disk-shaped case lids 14b and 14c that respectively close the openings on both sides of the case main body 14a.
- the case body 14a and the case lids 14b and 14c are fixed by, for example, bolts 15 so as to be in a liquid-tight state.
- the stator 11 around which the coil winding 16 is wound is attached to the inner wall surface of the case main body 14a.
- a rotating shaft 13 penetrating the center of the board surface of both case lid portions 14b and 14c is rotatably mounted on both case lid portions 14b and 14c via bearings 17a and 17b.
- a rotor reinforcing member 18 that reinforces the rotor 12 and is formed in a cup shape is attached to the rotating shaft 13.
- a bottom surface portion 18 a that is a rotating portion of the rotor 12 is fixed to the rotating shaft 13 with, for example, a bolt 19 with the rotating shaft 13 penetrating through the center portion thereof.
- An end ring 12 a is attached to the outer peripheral end surface of the outer peripheral surface portion 18 b of the rotor reinforcing member 18.
- a plurality of (for example, six) through-holes 20 located between the peripheral surface portion 18b and the bolt 19 and spaced apart at substantially equal intervals in the circumferential direction are opened in the bottom surface portion 18a of the rotor reinforcing member 18.
- the through hole 20 has a cross-sectional shape of a horizontally long hole (see FIG. 6) through which the cooling medium L (see FIG. 2) can pass, and the surface of the bottom surface portion 18a (ie, the surface on the case lid portion 14b side). To the back surface (that is, the surface on the case lid portion 14c side).
- a groove 21 formed in an annular shape that passes below the lower end of each through hole 20 and opens to the through hole 20 so as to communicate with each through hole 20 is a rotor reinforcing member 18. Is provided on the surface of the bottom surface portion 18a (that is, the surface on the case lid portion 14b side). The groove 21 functions as a receiving portion that receives the cooling medium L before entering the through hole 20.
- a cooling medium passage 22 serving as a flow path for the cooling medium L is formed along the radial direction of the case lid 14b inside the case lid 14b and below the rotary shaft 13.
- the upper end port 22 a is positioned near the upper portion of the groove 21 so as to face the through hole 20
- the lower end port 22 b is positioned on the extension of the inner peripheral surface of the case main body portion 14 a.
- the upper end port 22a and the lower end port 22b open to the back surface of the case lid portion 14b (that is, the surface on the rotor 12 side).
- a nozzle 23 is attached to the upper end opening 22a.
- the nozzle 23 has a tip end portion 23a that is a discharge port for discharging the cooling medium L (see FIG.
- a front end portion 23a (discharge port) is arranged close to the groove 21 above the surface of the bottom surface portion 18a (that is, the surface on the case lid portion 14b side), which is a rotating part when the motor 10 is driven.
- the upper end port 22 a and the lower end port 22 b are opened in a sealed space that houses the stator 11 and the rotor 12 inside the motor case 14.
- a cooling medium passage 22 is formed as a communication passage communicating with the sealed space.
- a tip portion 23 a that is a discharge port of the nozzle 23 communicates with the cooling medium passage 22.
- the tip portion 23 a is disposed close to the bottom surface portion 18 a that is the rotation portion of the rotor 12 so as to be affected by the airflow in the vicinity of the rotor 12 that rotates when the motor 10 rotates. That is, the front end portion 23a faces the surface of the bottom surface portion 18a of the rotating rotor reinforcing member 18.
- FIG. 2 is a cross-sectional explanatory view of the lower half of the motor 10 showing the flow of the cooling medium L in the motor 10 of FIG.
- the cooling medium is placed on the bottom of the sealed space (cooling medium reservoir 60) inside the motor case 14 so that the stator 11 positioned at the bottom of the sealed space (cooling medium reservoir 60) is substantially immersed. L is stored.
- the bottom of the sealed space (cooling medium storage unit 60) functions as a cooling medium storage unit 60 (reservoir) that is provided on the stator 11 side and stores the cooling medium L.
- the bottom part of the sealed space (cooling medium storage part 60) installed below the tip part 23 a of the nozzle 23 inside the motor case 14 and storing the cooling medium L is connected to the through hole 20 above the rotor 12.
- the cooling medium passage 22 of the motor 10 is arranged.
- the cooling medium passage 22 of the motor 10 guides the cooling medium L from the cooling medium reservoir 60 to the rotor 12.
- the cooling medium L discharged from the cooling medium passage 22 is, for example, a cooling liquid, but is not limited to this, and an automatic transmission fluid (ATF), cooling oil, or the like may be used.
- ATF automatic transmission fluid
- the cooling medium L is pumped up from the bottom of the sealed space (cooling medium reservoir 60) inside the motor case 14. It is done. From the nozzle 23 attached to the upper end port 22a of the cooling medium passage 22 toward the outer surface of the bottom surface portion 18a, which is the rotation part of the rotor 12, that is, the rear surface of the rotor 12 (the left surface of the rotor 12 in FIG. 2). The cooling medium L is discharged when the rotor 12 rotates at a high speed.
- the cooling medium L discharged from the nozzle 23 tends to flow in the outer diameter direction of the rotor 12 (direction of the stator 11) along the back surface of the rotor 12 by centrifugal force. However, the cooling medium L is received by the groove 21 that opens in the inner diameter direction (rotation shaft 13 direction) of the rotor 12 and is temporarily held in the groove 21.
- the cooling medium L temporarily held in the groove 21 passes through the through hole 20 communicating with the groove 21 and flows out to the inner peripheral portion of the rotor 12, that is, the inner surface of the peripheral surface portion 18 b of the rotor reinforcing member 18. Since the cooling medium L discharged to the back side of the rotor 12 can be guided to the surface side of the rotor 12 (the inner peripheral surface side of the rotor reinforcing member 18) through the through-hole 20, the surface of the rotor 12 The side can be cooled efficiently. Further, the groove 21 can prevent the cooling medium L flowing into the surface side of the rotor 12 (the inner peripheral surface side of the rotor reinforcing member 18) from being reduced.
- the cooling medium L flows out to the peripheral surface portion 18b. Since the outer diameter side (the front end of the peripheral surface portion 18b) is larger in diameter than the inner diameter side (the bottom surface portion 18a side), the cooling medium L is centrifugally applied to the front end of the peripheral surface portion 18b, that is, the opening of the rotor 12. It is washed away in the direction of the part.
- the cooling medium L flowing through the inner surface of the peripheral surface portion 18b of the rotor reinforcing member 18 is further pushed away from the tip of the peripheral surface portion 18b toward the outer diameter direction of the rotor 12 by centrifugal force.
- a plate 24 is attached to the tip of the peripheral surface portion 18b of the rotor reinforcing member 18.
- the cooling medium L flowing on the inner surface of the rotor 12 (the peripheral surface portion 18 b of the rotor reinforcing member 18) is detached from the end portion of the rotor 12.
- the front end portion (lower portion in FIG. 2) of the plate 24 enters the stator 11 side so as to close the gap AG.
- the plate 24 is installed at the end of the rotor 12 (end of the peripheral surface portion 18b).
- a plate 24 blocks the gap AG between the rotor 12 and the stator 11. Thereby, the plate 24 prevents the separation cooling medium L from entering the gap AG. Thereby, since the cooling medium L does not flow into the gap AG, the viscous resistance due to the separation cooling medium L does not occur.
- the cooling medium L discharged from the nozzle 23 flows along the inner surface of the peripheral surface portion 18b of the rotor reinforcing member 18 (see arrow C in FIG. 2).
- the inner peripheral part of the child 12 can be cooled.
- the rotor reinforcing member 18 of the rotor 12 has a downwardly inclined surface along the direction of the rotating shaft 13.
- the discharge cooling medium L is moved while absorbing the heat of the rotor 12 by the discharge cooling medium L, and the inclined surface of the rotor reinforcing member 18 rotates the discharge cooling medium L from the rotor 12 (rotor reinforcing member 18).
- the child 12 is separated by the centrifugal force when the child 12 rotates. Therefore, the cooling medium L absorbs the heat of the inner peripheral part of the rotor 12 by the rotor reinforcing member 18 that is formed in a cup shape and has an inner diameter that increases toward the opening. It is skipped to.
- the cooling efficiency can be improved and the discharge of the cooling medium L when the rotor 12 rotates at a low speed can be suppressed from the relationship between the negative pressure and the specific gravity of the cooling medium.
- a cooling device with good cooling efficiency and rotational efficiency can be configured.
- the cooling medium L is sucked up from the bottom of the sealed space (cooling medium storage unit 60) inside the motor case 14, that is, the cooling medium storage unit 60 storing the cooling medium L, and cooled to the rotor 12 from the tip 23a of the nozzle 23.
- the medium L can be sprayed.
- the cooling medium L is not discharged depending on the negative pressure during the low-speed rotation, so that viscous resistance due to the cooling medium L does not occur.
- the surface of the cooling medium L stored in the cooling medium storage unit 60 is located below the gap AG (outside in the radial direction of the rotor). By not including the medium L, the viscous resistance between the stator 11 and the rotor 12 can be reduced.
- the lower end port 22b of the cooling medium passage 22 opens toward the rotor 12 side of the case lid portion 14b, but opens toward the case main body portion 14a side of the case lid portion 14b (see FIG. 2). 1).
- a lower end port 22b is opened near the bottom of the sealed space bottom (cooling medium reservoir 60) so that the cooling medium L stored in the bottom of the sealed space (cooling medium reservoir 60) inside the motor case 14 can be sucked. It only has to be.
- FIG. 3 is an explanatory diagram showing the ATF level due to negative pressure in a graph.
- the cooling medium L (ATF) existing in the cooling medium passage 22 is sucked up by the negative pressure
- the suctioned height (ATF level) that is, in the cooling medium storing unit 60 that stores the ATF.
- the height (mm) from the ATF surface increases as the rotational speed (rpm) of the rotor 12 increases.
- the ATF starts to be discharged from the nozzle 23.
- the amount of ATF discharged from the nozzle 23 increases as the rotational speed increases at a rotational speed higher than the rotational speed of the rotor 12.
- the height of the ATF does not change and is the same as the height of the nozzle 23.
- FIG. 4 is an explanatory diagram showing the ATF discharge flow rate in a graph.
- the ATF when the ATF is discharged from the nozzle 23, the ATF is discharged from the nozzle 23 as the rotation speed increases at a rotation speed higher than the rotation speed (discharge rotation speed) of the rotor 12. The amount increases. That is, the discharge flow rate (m / s) increases. Further, at a rotational speed lower than the discharge rotational speed, only the height of the ATF in the cooling medium passage 22 changes, and ATF is not discharged.
- FIGS. 5A and 5B show a distal end portion 23a (discharge port) according to the second embodiment of the present invention.
- 5A is a cross-sectional explanatory diagram of a curved surface configuration
- FIG. 5B is a cross-sectional explanatory diagram of a multi-surface configuration.
- a dome-shaped curved surface in the nozzle 23 attached to the upper end port 22a of the cooling medium passage 22, a dome-shaped curved surface (see FIG. 5A) or a dome-shaped polyhedron protruding toward the bottom surface portion 18a (see FIG. 5A).
- a distal end portion 23a is formed in FIG. 5B).
- the front end portion 23 a that discharges the cooling medium L has a convex shape that faces the bottom surface portion 18 a of the rotor reinforcing member 18.
- Other configurations and operations are the same as those of the motor 10 (see FIG. 2) according to the first embodiment.
- FIG. 6 is a cross-sectional explanatory view of the lower half of the motor 30 showing the flow of the cooling medium L according to the third embodiment of the present invention.
- the motor 30 forms the cooling medium passage 22 formed inside the motor case lid portion 14b inside the case lid portion 14c, and the nozzle 23 attached to the upper end port 22a, It is directed to the opening side of the rotor reinforcing member 18, which is the opening side of the rotor 12.
- Other configurations and operations are the same as those of the motor 10 (see FIG. 2) according to the first embodiment.
- the cooling medium L discharged from the nozzle 23 toward the bottom surface portion 18a of the rotor reinforcing member 18 flows down along the inner surface of the peripheral surface portion 18b (see arrow C in FIG. 6). ), The inner periphery of the rotor 12 can be cooled.
- the through hole 20 is opened in the rotor 12 as compared with the case where the cooling medium L is discharged toward the back surface of the rotor 12 (the left surface of the rotor 12 in FIG. 6) (see FIG. 2). Since this is not necessary, the rotational strength of the rotor 12 can be set high.
- FIG. 7 is a cross-sectional explanatory view of the lower half of the motor 35 showing the flow of the cooling medium L according to the fourth embodiment of the present invention.
- the opposed surface of the stator 11 and the opposed surface of the rotor 36 are arranged perpendicular to the rotary shaft 13 along the central axis direction of the rotor 36.
- This is a so-called axial gap motor having a gap AG between the stators 11.
- Other configurations and operations are the same as those of the motor 10 (see FIG. 2) according to the first embodiment.
- the rotor 36 has a rotor reinforcing member 37 that reinforces the rotor 36 and is formed in a disk shape.
- the rotor reinforcing member 37 has a plurality of permanent magnets 38 arranged in an embedded state along the circumferential direction of the rotor reinforcing member 37 at a portion where the rotor reinforcing member 37 faces the stator 11. Further, the rotor reinforcing member 37 has a back yoke 38 a disposed on the back side of the permanent magnet 38.
- a cooling medium passage 39 penetrating the rotor reinforcing member 37 in the radial direction is formed on the back side of the back yoke 38a, which is the surface opposite to the surface on the air gap AG side of the rotor reinforcing member 37. .
- the upper end port 39 a opens below the nozzle 23 so as to face the tip end portion 23 a (discharge port) of the nozzle 23, and is stored in the bottom of the sealed space (cooling medium storage unit 60) inside the motor case 14.
- a lower end port 39 b is opened on the outer peripheral end surface of the rotor reinforcing member 37 so as to face the cooling medium L.
- the cooling medium L can be sucked or discharged from the nozzle 23 only when the rotor 36 rotates at high speed.
- the cooling medium L discharged from the nozzle 23 passes through the cooling medium passage 39. (Refer to arrow C in FIG. 7), it flows down and is stored in the bottom of the sealed space (cooling medium reservoir 60). Further, since the cooling medium passage 39 is provided inside the rotor 36, the vicinity of the back yoke 38a, that is, the vicinity of the heat generating portion can be cooled, and the cooling performance is improved.
- FIG. 8 is a cross-sectional explanatory view of the lower half of the motor 40 showing the flow of the cooling medium L according to the fifth embodiment of the present invention.
- the rotor 36 moves so as to approach or separate from the stator 11 (see the white arrow X indicating the variable gap structure in FIG. 8).
- This is a variable gap axial gap motor in which the gap AG between the rotor 36 and the stator 11 changes.
- the tip 23a which is a discharge port for discharging the cooling medium L, is positioned in the vicinity of the back surface, which is the side surface of the rotor reinforcing member 37 and is the side surface opposite to the surface on the air gap AG side. It faces the back surface of the reinforcing member 37. That is, the tip 23 a (discharge port) of the nozzle 23 is disposed in the vicinity of the rotating portion of the rotor 36.
- Other configurations and operations are the same as those of the motor 10 (see FIG. 2) according to the first embodiment.
- the gap AG when the gap AG is expanded, that is, when the induced voltage is reduced when the rotor 36 rotates at a high speed, the rotor 36 moves away from the stator 11, so The distance to the outlet is close, and the cooling medium L can be discharged from the tip 23a (discharge port).
- the cooling medium L discharged from the nozzle 23 flows along the back surface of the rotor reinforcing member 37 (see arrow C in FIG. 8), and is stored in the bottom of the sealed space (cooling medium storage unit 60).
- FIG. 9 is an explanatory diagram of the back side of the rotor 12 serving as a nozzle facing surface showing the tip 23a of the nozzle 23 according to the sixth embodiment of the present invention.
- 10A and 10B are enlarged views of the tip 23a of the nozzle 23 of FIG. 9,
- FIG. 10A is a plan view of the nozzle 23, and
- a tube-shaped tip flow passage forming portion (flow passage forming portion) 45 (see FIGS. 10A and 10B) is attached to the tip portion 23 a of the nozzle 23.
- the tip flow path forming portion 45 forms a flow path along the circumferential direction of the rotor 12, that is, the circumferential direction of the bottom surface portion 18a of the rotor reinforcing member 18, and has openings on both sides in the circumferential direction of the bottom surface portion 18a.
- the discharge ports (tip portions 23 a) of the nozzles 23 are opened by the tip flow passage forming portions 45 on both sides in the circumferential direction of the bottom portion 18 a along the bottom portion 18 a of the rotor reinforcing member 18.
- Other configurations and operations are the same as those of the motor 10 (see FIG. 2) according to the first embodiment.
- the front end flow path forming portion 45 is attached so that the substantially central portion in the longitudinal direction covers the front end portion 23 a of the nozzle 23.
- the outer surface of the tip flow passage forming portion 45 attached to the tip portion 23a of the nozzle 23 is in a state of being almost in contact with the bottom surface portion 18a of the rotor reinforcing member 18 (see FIG. 10A).
- the flow path width W1 of the connecting portion with the front end portion 23a of the nozzle 23 is the flow width W2 of at least one opening, that is, the radius of the bottom surface portion 18a of the rotor reinforcing member 18 in the front end flow path forming portion 45. It is formed shorter than the opening width in the direction (see FIG.
- the central portion (tip portion 23a of the nozzle 23) is made narrower than the vicinity of the entrance / exit, thereby generating a venturi effect and discharging more cooling medium L.
- the tip flow path forming portion 45 is located above the groove 21 provided in the bottom surface portion 18a of the rotor reinforcing member 18 and receiving the cooling medium L, the motor is assembled during the motor assembly operation. Assembly accuracy is improved.
- tip flow path forming portion 45 may be formed in a tube shape, or may be formed in a groove shape in which the bottom surface portion 18a side of the rotor reinforcing member 18 is opened.
- FIG. 11 is a cross-sectional explanatory view of the lower half of the motor 50 according to the seventh embodiment of the present invention.
- a pressure adjustment valve 51 and a filter 52 are provided above the upper end port 22a that is the cooling medium L discharge part of the case lid part 14b (that is, on the rotating shaft 13 side). Yes.
- a communication port communicating with the atmosphere opens on the outer surface of the case lid portion 14b.
- the pressure adjustment valve 51 controls the atmospheric pressure and the negative pressure inside the cooling medium passage 22.
- the filter 52 performs filtration of the atmosphere introduced from the outside into the sealed space inside the motor case 14 via the pressure adjustment valve 51.
- Other configurations and operations are the same as those of the motor 10 (see FIG. 2) according to the first embodiment.
- the pressure adjustment valve 51 has a function of sensing the temperature of the stator 11. That is, the pressure adjustment valve 51 senses the temperature of the coil winding (stator winding) 16 of the stator 11 and the temperature of the stator core. The pressure adjustment valve 51 opens and closes in accordance with these sensed temperatures, and adjusts the internal pressure of the cooling medium passage 22 to a state equivalent to the internal pressure of the motor 50 or a negative pressure state generated when the rotor 12 rotates. That is, when the temperature of the coil winding 16 or the temperature of the stator core is low, the pressure adjustment valve 51 makes the pressure inside the cooling medium passage 22 equal to the atmospheric pressure inside or outside the motor 50, and the temperature of the coil winding 16. Alternatively, when the temperature of the stator core is high, the pressure inside the cooling medium passage 22 is set to a negative pressure generated by the rotor 12.
- the pressure adjustment valve 51 is closed at a high load that requires cooling when the motor 50 is driven at a high speed.
- the pressure adjustment valve 51 is opened.
- the cooling medium L is prevented from being discharged from the nozzle 23.
- FIG. 12 is an explanatory cross-sectional view of a motor 55 according to the eighth embodiment of the present invention.
- the motor 55 is provided inside the motor case 14 with a pressure adjusting valve 51 that controls the atmospheric pressure and the negative pressure inside the cooling medium passage 22.
- an upper cooling medium passage 56 communicating with the cooling medium passage 22 is provided, and the nozzle 23 is mounted not on the cooling medium passage 22 but on the upper cooling medium passage 56.
- Other configurations and operations are the same as those of the motor 10 (see FIG. 2) according to the first embodiment.
- the upper cooling medium passage 56 is installed in the upper half of the case lid portion 14b. Instead of the upper end port 22 a (FIG. 2) formed in the cooling medium passage 22, an upper lower end port 56 a that opens near the lower portion of the groove 21 formed in the bottom surface portion 18 a of the rotor reinforcing member 18 is replaced with the upper cooling medium passage 56.
- the nozzle 23 is attached to the upper lower end port 56a. In the nozzle 23, the front end portion 23a (discharge port) is made to face and face the surface of the bottom surface portion 18a below the groove 21 (that is, the surface on the case lid portion 14b side).
- the upper cooling medium passage 56 has an upper upper end opening 56 b that opens at a position facing the coil winding 16 in the stator 11.
- the pressure adjustment valve 51 is attached to the upper upper end port 56b so as to be in contact with the coil winding 16.
- a temperature sensitive valve composed of a bimetal, a thermoelectric element or the like is used.
- FIG. 13 is a detailed explanatory view of the pressure adjustment valve 51 of FIG.
- the pressure is adjusted by a temperature-sensitive valve that controls the operation of a piston 51d that moves forward and backward with respect to the cylinder 51a by a biasing member (coil spring) 51b and temperature-sensitive metal 51c in the cylinder 51a.
- the valve 51 is configured.
- the upper upper end opening 56 b communicates with the internal space of the motor case 14 through an internal communication path 57 provided inside the case lid portion 14 b.
- the internal communication path 57 is opened and closed by the advancement / retraction operation of the piston 51d.
- the pressure regulating valve 51 composed of this temperature-sensitive valve
- the size of the temperature-sensitive metal 51c does not change as in the normal state.
- the negative pressure Pl state of the upper coolant passage 56 changes with the rotation of the rotor 12 facing the upper lower end port 56a.
- the biasing force of the biasing member 51b pushes up the piston 51d in accordance with the negative pressure Pl state.
- the internal communication path 57 is opened, and atmospheric pressure air in the internal space of the motor case 14 flows into the upper coolant passage 56 via the internal communication path 57 (see arrow Y in FIG. 13). Therefore, the negative pressure Pl state of the upper cooling medium passage 56 is eliminated.
- a metal / bimetal having a high coefficient of thermal expansion is used for the temperature-sensitive metal 51c.
- the pressure adjustment valve 51 formed of the temperature sensitive valve in a state where it is in contact with the coil winding 16 or located in the vicinity thereof, the pressure adjustment valve 51 is closed when the motor 55 is at a high load. In this state, the cooling medium L is discharged from the nozzle 23. When the load is low, the pressure adjusting valve 51 is opened and the cooling medium L is not discharged from the nozzle 23. Therefore, the output sensitivity of the motor 55 is high when the motor 55 is driven at high speed. Cooling control corresponding to can be performed.
- an electric motor that includes a stator and a rotor rotatably supported by a shaft and cools the rotor with a cooling medium is provided on the side of the stator, and stores the cooling medium.
- a medium storage section and a cooling medium passage for guiding the cooling medium from the cooling medium storage section to the rotor, and a discharge port for discharging the cooling medium in the cooling medium path is disposed close to the rotating portion of the rotor, The cooling medium is guided from the cooling medium storage section provided below to the rotor via the cooling medium passage and discharged from the discharge port.
- the rotor can be cooled by the cooling medium without providing an external pump, and the viscosity resistance of the cooling medium does not increase when the rotor rotates at a low speed, and the cooling efficiency of the rotor does not deteriorate.
Abstract
Description
図1は、本発明の第1実施形態に係るモータ10の構成を示す断面図である。図1に示すように、永久磁石を用いた永久磁石型電動機であるモータ10は、固定子(ステータ)11と、回転自在に軸支された回転子(ロータ)12とを備えている。円筒状の回転子12の中心軸方向に沿う回転軸(回転子回転軸)13に対して、固定子11の対向面と回転子12の対向面とが略平行に配置されている。モータ10は、回転子12と固定子11の間に空隙AGを有する、所謂ラジアルギャップモータである。固定子11と回転子12とは、モータケース14の内部に収納されている。このモータ10は、回転軸13を横倒し、即ち、略水平にした状態(図1に示す状態)で設置され、駆動される。
図5A,図5Bは、本発明の第2実施形態に係る先端部23a(吐出口)を示す。図5Aは曲面構成の断面説明図、図5Bは多面構成の断面説明図である。図5A、図5Bに示すように、冷却媒体通路22の上端口22aに装着されたノズル23では、底面部18a側に突出するドーム状の曲面(図5A参照)或るいはドーム状の多面体(図5B参照)に先端部23aを形成している。つまり、冷却媒体Lを吐出させる先端部23aを、回転子補強部材18の底面部18aに対向する凸形状になるようにしている。その他の構成及び作用は、第1実施形態に係るモータ10(図2参照)と同様である。
図6は、本発明の第3実施形態に係る冷却媒体Lの流れを示すモータ30下半部の断面説明図である。図6に示すように、モータ30は、モータケース蓋部14bの内部に形成されていた冷却媒体通路22を、ケース蓋部14cの内部に形成し、上端口22aに装着されたノズル23を、回転子12の開口部側である、回転子補強部材18の開口部側に向けている。その他の構成及び作用は、第1実施形態に係るモータ10(図2参照)と同様である。
図7は、本発明の第4実施形態に係る冷却媒体Lの流れを示すモータ35下半部の断面説明図である。図7に示すように、モータ35は、回転子36の中心軸方向に沿う回転軸13に対して固定子11の対向面と回転子36の対向面とが垂直に配置され、回転子36と固定子11の間に空隙AGを有する、所謂アキシャルギャップモータである。その他の構成及び作用は、第1実施形態に係るモータ10(図2参照)と同様である。
図8は、本発明の第5実施形態に係る冷却媒体Lの流れを示すモータ40下半部の断面説明図である。図8に示すように、モータ40では、固定子11に接近したり固定子11から離反するように回転子36が移動し(図8中、可変空隙構造を示す白抜き矢印Xを参照)、回転子36と固定子11の間の空隙AGが変化する可変空隙型アキシャルギャップモータである。
図9は、本発明の第6実施形態に係るノズル23の先端部23aを示すノズル対向面となる回転子12背面側の説明図である。図10A,図10Bは、図9のノズル23の先端部23aを拡大して示し、図10Aはノズル23の平面説明図、図10Bはノズル23の断面説明図である。
図11は、本発明の第7実施形態に係るモータ50の下半部の断面説明図である。図11に示すように、モータ50では、ケース蓋部14bの冷却媒体L吐出部である上端口22aよりも上部(即ち、回転軸13側)に、圧力調整バルブ51とフィルタ52とを設けている。
図12は、本発明の第8実施形態に係るモータ55の断面説明図である。図12に示すように、大気圧と、冷却媒体通路22内部の負圧との制御を行なう圧力調整バルブ51を、モータ55はモータケース14内部に設置している。それに対応して、冷却媒体通路22に連通する上部冷却媒体通路56を設け、ノズル23を冷却媒体通路22ではなく上部冷却媒体通路56に装着している。その他の構成及び作用は、第1実施形態に係るモータ10(図2参照)と同様である。
Claims (13)
- 固定子と、
前記固定子と相対的に回転するように回転軸に軸支され且つ冷却媒体により冷却される回転子と、
前記固定子の側に設けられ且つ前記冷却媒体を溜めておく冷却媒体貯留部と、
前記冷却媒体貯留部から前記回転子へ前記冷却媒体を案内する冷却媒体通路と、
を備える電動機において、
前記冷却媒体通路の前記冷却媒体を吐出する吐出口を、前記回転子の回転部位に近接配置すると共に、前記冷却媒体貯留部を前記吐出口よりも下方に設置し、前記回転子と吐出口との間に作用する負圧により前記冷却媒体貯留部内の冷却媒体を吸引する構造を持つことを特徴とする電動機。 - 横向き方向に位置する電動機の前記回転軸よりも下方のケース内の底部に、前記冷却媒体貯留部が設けられ、前記冷却媒体貯留部に溜められる前記冷却媒体の表面が、前記回転子と前記固定子との間の空隙よりも下方に位置することを特徴とする請求項1に記載の電動機。
- 前記吐出口を、前記回転子の回転部位に対向する凸形状に形成したことを特徴とする請求項1に記載の電動機。
- 前記回転子の周方向両側に開口し且つ前記回転子の周方向に沿う流路形成部を、前記吐出口に設けたことを特徴とする請求項1に記載の電動機。
- 前記流路形成部では、前記回転子の回転方向中央部が前記回転子の回転方向両端部の少なくとも一方よりも狭いことを特徴とする請求項4に記載の電動機。
- 前記回転子の周方向に沿って複数個配置され且つ前記回転子の表裏面を貫通し前記冷却媒体が通り抜ける貫通孔を、前記回転子が有することを特徴とする請求項1に記載の電動機。
- 前記吐出口から吐出された前記冷却媒体を受け止める受け口となり、且つ、受け止めた前記冷却媒体を前記貫通孔に送り込む受け部を、前記回転子が前記回転子の前記吐出口側の面に有することを特徴とする請求項6に記載の電動機。
- 前記流路形成部が前記受け部よりも上方に位置することを特徴とする請求項7に記載の電動機。
- 前記冷却媒体通路の内部圧力を調整する圧力調整バルブを設置したことを特徴とする請求項1に記載の電動機。
- 前記固定子の温度を感知する機能を前記圧力調整バルブが備え、感知した前記固定子の温度に応じて電動機の内部圧力と同等状態或いは前記回転子の回転時に発生する負圧状態に前記圧力調整バルブが調整することを特徴とする請求項9に記載の電動機。
- 前記回転軸方向に沿う下り傾斜面を前記回転子が有しており、前記回転子の熱を吸収しつつ前記冷却媒体を移動させて、前記傾斜面は、前記回転子から前記冷却媒体を前記回転子の回転時の遠心力により離脱させる、ことを特徴とする請求項1に記載の電動機。
- 前記回転子の端部から離脱する前記冷却媒体が前記空隙に入り込むのを、前記回転子と前記固定子との間の空隙を塞ぐことによって防止するプレートを、前記回転子が有することを特徴とする請求項11に記載の電動機。
- 固定子と、
前記固定子と相対的に回転するように回転軸に軸支され且つ冷却媒体により冷却される回転子と、
前記固定子の側に設けられかつ前記冷却媒体を溜めておく冷却媒体貯留部と、
前記冷却媒体貯留部から前記回転子へ前記冷却媒体を案内する冷却媒体通路と、
前記固定子に接近したり前記固定子から離反するように前記回転子が移動して、前記回転子と前記固定子との間の空隙が変化する可変空隙構造と、
を備えるアキシャルギャップ型電動機において、
前記冷却媒体通路の前記冷却媒体を吐出する吐出口を、前記回転子と前記固定子との間の前記空隙とは反対側の面に臨ませて前記回転子の回転部位に近接配置すると共に、前記冷却媒体貯留部を前記吐出口よりも下方に設置し、前記回転子と前記吐出口との間に作用する負圧により前記冷却媒体貯留部内の冷却媒体を吸引することを特徴とするアキシャルギャップ型電動機。
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US8203241B2 (en) | 2012-06-19 |
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