WO2020094514A1 - Moteur électrique équipé d'un dispositif de refroidissement par fluide - Google Patents

Moteur électrique équipé d'un dispositif de refroidissement par fluide Download PDF

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Publication number
WO2020094514A1
WO2020094514A1 PCT/EP2019/079926 EP2019079926W WO2020094514A1 WO 2020094514 A1 WO2020094514 A1 WO 2020094514A1 EP 2019079926 W EP2019079926 W EP 2019079926W WO 2020094514 A1 WO2020094514 A1 WO 2020094514A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid
fluid outlet
outlet openings
cooling tube
rotor shaft
Prior art date
Application number
PCT/EP2019/079926
Other languages
German (de)
English (en)
Inventor
Michael Hacklberger
Mario Springer
Original Assignee
Zf Friedrichshafen Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2020094514A1 publication Critical patent/WO2020094514A1/fr

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Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/003—Couplings; Details of shafts
    • 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
    • H02K9/20—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil wherein the cooling medium vaporises within the machine casing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • 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
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans
    • 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
    • H02K9/197—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil in which the rotor or stator space is fluid-tight, e.g. to provide for different cooling media for rotor and stator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K2001/003—Arrangement or mounting of electrical propulsion units with means for cooling the electrical propulsion units
    • B60K2001/006—Arrangement or mounting of electrical propulsion units with means for cooling the electrical propulsion units the electric motors
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K2213/00—Specific aspects, not otherwise provided for and not covered by codes H02K2201/00 - H02K2211/00
    • H02K2213/03—Machines characterised by numerical values, ranges, mathematical expressions or similar information

Definitions

  • the invention relates to an electrical machine with a fluid cooling device according to the preamble of claim 1, as already with the
  • WO 2016/050534 A1 has become known.
  • a lance-shaped cooling pipe is axially inserted into a section of a rotor shaft designed as a hollow shaft, through which a cooling fluid can flow into an annular space between the latter and the rotor shaft and absorb heat loss from the rotor .
  • the cooling tube is fixed axially on one side with a first section to a fixed support element and projects into the rotor shaft with a second, free section.
  • the coolant can flow in and out on the same end face of the electrical machine, as a result of which only a sealing element between the rotating rotor and the fixed elements of the machine is required.
  • the free-standing section of the cooling tube is excited to vibrate during operation of the electrical machine and is subjected to excessive mechanical stress due to bending. Such an action can lead to an undesired permanent deformation of the cooling tube.
  • the object of the invention is to further improve such a generic electrical machine with a fluid cooling device.
  • a cooling tube arranged inside the rotor shaft is to be better protected from acting forces.
  • an electrical machine with a fluid cooling device which comprises a stator and a rotor, and the rotor being rotatable about an axis relative to the stator by means of a rotor shaft is stored.
  • the fluid cooling device has a cooling tube which is fixed by means of a first section to a support element fixed to the stator and which is connected to a fluid inlet.
  • the cooling tube extends with a second self-supporting section axially within a central recess of the rotor shaft and forms an annular space with the rotor shaft, so that the cooling tube r is in fluid connection with the annular space and with a fluid outlet.
  • the rotor shaft can be closed in a fluid-tight manner on the axial side facing away from the fluid inlet.
  • the fluid inlet and the fluid outlet can be formed jointly on one and the same end face of the electrical machine and, in a still further respect, in particular on a bearing plate functioning as a carrier element.
  • the free-carrying portion of the cooling tube has first radial fluid outlet openings.
  • the provision of radial fluid outlet openings allows the cooling tube to experience a force directed against the respective outflow direction, in particular a recoil force, when the cooling fluid flows out of these fluid outlet openings.
  • These first radial fluid outlet openings can advantageously be designed and arranged relative to one another such that a superimposition of the recoil forces leads to a centering of the cooling tube in the region of the first radial fi u id outlet openings. Active centering of the cooling tube against external forces can be achieved. The desired effect already occurs in one spatial direction when there are two radial fluid outlet openings, which are preferably designed in opposite directions.
  • two further radial fluid outlet openings can be provided or at least three radial fluid outlet openings with a number n that are equally distributed around the circumference by an angle of 3607h
  • At least two or all of the first radial fluid outlet openings on the cooling tube preferably have the same axial position.
  • the first radial fluid outlet openings can also be arranged at different axial positions.
  • An oscillation amplitude of the cooling tube increases with the axial distance from the first section fixed on the carrier element.
  • a particularly effective centering of the cooling tube can be made possible by forming the first radial fluid outlet openings at an end region of the second section.
  • the cross section of an axial fluid outlet opening on the cooling tube can at least be reduced compared to the cross section of an axial fluid inlet opening. Another advantage is that the cooling tube can be axially closed at its free end region.
  • the cooling tube can have a constant inner diameter over its axial extent.
  • the cantilevered section of the cooling tube can have second radial fluid outlet openings axially spaced from the first radial fluid outlet openings, the second radial fluid outlet openings being designed with a larger cross section than the first radial fluid outlet openings are.
  • the second radial fluid outlet openings as well as the first radial fluid outlet openings can be arranged.
  • the provision of the first radial fluid outlet openings alone provides a fluid backflow in the annular space present between the cooling tube and the rotor shaft.
  • the additional provision of second radial fluid outlet openings divides the fluid flow guided by the cooling tube into two partial fluid streams which exit through the first and the second radial fluid outlet openings.
  • the first and the second radial fluid outlet openings can be designed and dimensioned such that a first partial fluid flow through the first radial fluid exit openings essentially stabilizes the position of the cooling tube and that a second partial fluid flow through the second radial fluid Outlet openings essentially for cooling the rotor shaft and the rotor. wearing.
  • the first partial fluid flow can be set lower than the second partial fluid flow by suitable dimensioning of the first and second fluid outlet openings.
  • the recess of the rotor shaft in the area of the first radial fluid outlet openings can in principle have at least approximately the same inner diameter compared to an area of the second radial fluid outlet openings.
  • the recess of the rotor shaft in the region of the first radial fluid outlet openings can also have an inner diameter that is reduced compared to a region of the second radial fluid outlet openings. In this way, the recoil forces can be increased and centering of the cooling tube can be further improved.
  • a gap can be formed in the area of the first radial fluid outlet openings between an outer circumferential surface of the cooling tube and an inner circumferential surface of the recess of the rotor shaft, which gap is filled by a cooling fluid present and the gap is dimensioned in this way is that a plain bearing is formed between the cooling tube and the rotor shaft.
  • the gap can in particular be designed as a capillary gap.
  • FIG. 1 shows an electrical machine designed as a vehicle axle drive with a fluid cooling device with a cooling tube in an axial sectional view
  • FIG. 2 shows an enlarged section of the fluid cooling device from FIG. 1 in the region of a bearing plate of the electrical machine
  • FIG. 3 shows a perspective illustration of the electrical machine in the region of the end shield from FIG. 3; 4 is a perspective view of a coolant flange formed on a housing of the electrical machine;
  • FIG. 5 shows a detail of a fluid cooling device modified in the area of the cooling tube compared to the arrangement of FIG. 1.
  • the figures show an electrical machine 1, which is provided and designed in particular for driving an electric or hybrid vehicle.
  • the electric machine 1 is provided for installation in or on a vehicle axle and thus represents an electric axle drive 2 in connection with further components.
  • the electric machine 1 thus delivers its power to vehicle wheels for moving the vehicle.
  • an electric vehicle drive and a vehicle with such an electric machine 1 are also described, going beyond the electric machine 1 explained in detail below.
  • the electrical machine 1 comprises a stator 4 fixed in a housing 3 with a stator lamination stack 5 and with a stator winding 6 and a rotor 7 with a rotor lamination stack 8 and with a short-circuit cage 9.
  • the electrical machine 1 is thus designed as an asynchronous machine.
  • the rotor 7 is rotatably mounted about an axis A to the stator 4 by means of a rotor shaft 10, a first bearing 13 arranged on a first bearing plate 11 and a second bearing 14 arranged on a second bearing plate 12.
  • the rotor shaft 10 is operatively connected to a gear 36 shown on the left in FIG. 1, which can transmit the engine torque to vehicle wheels via further transmission elements, not shown here in the drawing.
  • the electrical machine 1 has a fluid cooling device 15 through which a cooling fluid can flow and which can dissipate heat loss to a heat exchanger located outside the electrical machine 1.
  • the fluid cooling device 15 comprises a metallic cooling tube 16 which is attached to a support element 17 which is fixed to the stator 4, in particular to the first bearing plate 11 and which is connected via an axial fluid inlet opening 16f to a fluid inlet 18 provided on the bearing plate 11.
  • the cooling tube r has a lance-shaped shape, the axial extent of which, therefore, its length L is many times greater than its diameter D. In the exemplary embodiment, this ratio L / D> 10, in particular greater than 15, and here in particular is approximately 17.
  • the cooling tube 16 is axially fixed and supported on one side only by means of a first section 16a through the bearing plate 11 and extends with it Larger second free-standing section 16b in the axial direction within a central recess 10a of the rotor shaft 10 and forms an annular space 10b with the rotor shaft 10.
  • a length ratio of a length of the first section 16a to a length of the second section 16b, that is to say the ratio of the length of the fastened section 16a to the length of the unsecured, free section 16b is greater than 10 and is specifically approximately 14.
  • the cooling tube 16 is axially open on both sides and is thus in the installed state shown in FIG. 1 via an axial fi u-outlet opening 16e with the annular space 10b and with a fluid outlet 19 also provided on the first bearing plate 11 Fluid connection.
  • the first bearing plate 11 has a central first through opening 11a for forming the fluid inlet 18 and a second through opening 11b arranged radially to the first through opening for forming the fluid outlet 19. Both through openings 11a, b thus emerge from the bearing plate 11 on an end mounting surface 11c facing away from the rotor 7.
  • a sealing area 20 with a sealing element 21 is provided between the rotor shaft 10 and the bearing plate 11 functioning as a carrier element 17.
  • the sealing element 21 has the task of at least essentially preventing fluid from flowing into a space 22 of the electrical machine 1 lying outside the sealing area 20 when the cooling fluid flows from the fluid inlet 18 to the fluid outlet 19.
  • the sealing element 21 is designed as an axial mechanical seal 23.
  • the mechanical seal 23 comprises a first section 23a which is fixed on the carrier element 17 and further comprises a second section 23b which is fixed on the rotor shaft 10 and which is in sealing connection with the first section 23a.
  • the second section 23b of the mechanical seal 23 is at least partially axially overlapping to the first bearing 13.
  • the first bearing 13 has both on the axial side facing the mechanical seal 23 and on the axial side facing the rotor laminated core 8 a sealing arrangement 13c acting between a radially inner bearing ring 13a and a radially outer bearing ring 13b with two sealing disks 13d, e .
  • the bearing interior 13f is further sealed against the ingress of cooling fluid by means of a high-speed grease. On the one hand, this lubricates the bearing 13 and, on the other hand, the penetration of fluid into the inner space 22 of the electrical machine 1 is prevented by the created grease barrier.
  • an inner diameter 10c of the rotor shaft 10 or the central recess 10a present there can be made larger than in the area of an axial extension of the rotor laminated core 8 in the area of the first bearing 13.
  • the rotor shaft 10 is designed as a hollow shaft and is closed in a fluid-tight manner by a closure 24 on the axial side facing away from the fluid inlet 18.
  • the closure 24 can be designed as a separate closure plug or as a bottom region of the rotor shaft 10. Due to the coaxial arrangement of the rotor shaft 10 and the cooling tube 16, the fluid flow undergoes a reversal of direction against the inflow direction and can flow out again on the axial side of the fluid inlet 18, for which purpose a sealing arrangement in the form of the sealing element 21 is only required on this side.
  • the cooling tube 16, the first bearing 13 and the stator-fixed section 23a of the sealing element 23 are thus received by the first bearing plate 11.
  • the first bearing plate 11 also receives an electrical potential equalization element 25 which interacts with the rotor shaft 10.
  • an electrical potential equalization element 25 which interacts with the rotor shaft 10.
  • a slip ring arrangement 26 is provided as the potential equalization element 25, which reduces potential differences that occur as shaft voltages between the stator 4 and the rotor 7 by means of an electrical short circuit.
  • the potential equalization element 25 is arranged axially adjacent to the first bearing 13, in particular axially between the bearing 13 and the rotor laminated core 8.
  • the cooling tube 16 is fixed to a fastening area 11f provided on the end shield 11 or generally on the carrier element 17.
  • the cooling tube 16 is arranged by means of an interference fit in an axial extension 11e protruding from a base body 11d of the bearing plate 11 and which forms the fastening region 11f. It can be seen in the figures that the fastening area 11f partially overlaps axially with the stator-fixed section 23a of the sealing element 21 or the mechanical seal 23.
  • a cover element 27 made of a plastic with a web arrangement 27 a is arranged there in a fluid-tight manner.
  • a fluid inlet channel 28 and a fluid outlet channel 29 are formed by the web arrangement 27a between the bearing plate 11 and the cover element 27 and / or in the cover element 27.
  • the housing 3 of the electrical machine 1 is formed as a casting from a light metal material, in the present case from an aluminum material.
  • the housing 3 simultaneously forms a fluid cooling jacket 30 surrounding the stator 4 with a fluid channel arrangement 31.
  • the housing 3 On the side facing the first bearing plate 11, the housing 3 has a coolant flange 32 integrally formed therewith with two fluid channel sections 32a, b, which are in fluid communication with the fluid inlet channel 28 and the fluid outlet channel 29 of the cover element 27.
  • the fluid channel section 32a forms an external coolant connection 40.
  • the external coolant connection can be arranged, for example, at another position of the stator cooling jacket or at power electronics for controlling the electrical machine 1, which with its housing and with its cooling circuit with the electrical machine 1 and with there trained fluid cooling device 15 is connected.
  • the further fluid channel section 32b forms a connecting channel to the fluid cooling jacket 30 of the stator 4.
  • the fluid cooling device 15 can thus have a cooling section 15a for cooling the rotor 7 and a cooling section 15b for cooling the stator 4, through which the cooling fluid flows in succession, and a fluid connection provided between them is designed as a fixed, tubeless connection channel 32b is.
  • a leakage space 33 is provided with a fluid collecting area 34, into which a portion of the cooling fluid passing through the sealing area 20 can enter and be collected.
  • the leakage space 33 also has a gas collecting area 35, which is arranged geodetically higher than the fluid collecting area 34 in an operating position of the electrical machine 1. When using a cooling fluid with materially at least one volatile component, this can escape via the mechanical seal 23 and collect in the gas collection area 35.
  • a closable engagement opening 34a with a removable closure cover 34b is provided on the fluid collecting area 34 in order to remove the solid-shaped component.
  • a closable fluid drain opening 34c is provided there with a drain element 34d, in particular a drain screw or a drain plug.
  • the fluid drain opening 34c is substantially aligned geodetically downward and arranged geodetically lower in relation to a gas discharge opening 35a of the gas collecting area 35.
  • the engagement opening of the closure cover 34b is designed with a larger cross section than the fluid discharge opening 35a.
  • the fluid drain opening 34c is provided at least approximately at a 6 o'clock position, that is to say between a 5 o'clock and a 7 o'clock position.
  • the gas discharge opening 35a is at least approximately provided at a 12 o'clock position, that is to say between an 11 o'clock and a 01 o'clock position.
  • the fluid collecting area 34 and the gas collecting area 35 are provided at least approximately in the same axial position.
  • the mechanical seal 23 can also be located at this axial position or at least axially overlap with the fluid collection area 34 and / or the gas collection area 35.
  • the gas discharge opening 35a of the gas collecting area 35 furthermore has a pressure compensation element 41, as a result of which gases can escape from the gas collecting area 35.
  • the pressure compensation element 41 comprises a semipermeable membrane, which is permeable to air to enable pressure compensation, but is not permeable to fluid.
  • the second bearing 14 is provided axially spaced apart from the first bearing 13 for mounting the rotor 7, and if necessary it can also be designed axially on one or both sides with sealing rings and with a lubricant filling.
  • the bearing 14 is provided radially between the rotor shaft 10 and the second bearing plate 12, the rotor laminated core 8 extending in an axial space between the first and the second bearings 11, 12.
  • the central recess 10a extends axially through the second bearing 14 within the rotor shaft 10.
  • the cooling tube 16 also extends axially beyond the second bearing 12 within the rotor shaft 10.
  • the inside diameter of the rotor shaft 10 in the area of the axial extent of the rotor laminated core 8 and in the area of the second bearing 12 is larger than in the area of the first bearing 11.
  • the rotor shaft 10 has a shaft section which projects axially beyond the second bearing 12 and leads into the gear 36 with an output element 38 designed as a gearwheel 37.
  • the central recess 10a of the rotor shaft 10 extends axially into the area of the output element 38 and can therefore also be flowed through by the cooling fluid.
  • the cooling tube 16 can also extend axially into the area mentioned.
  • the output element 38 and thus further elements in heat exchange and / or a lubricant or coolant located outside of the rotor shaft 10 can thus also reach the area of action of the fluid cooling device 15 and be cooled.
  • the output element 38 is arranged on the rotor shaft 10 axially between the second bearing 14 and a third bearing 39.
  • the central recess 10a of the rotor shaft 10 extends axially into the region of the third bearing 39 and is therefore flowed through by the cooling fluid up to this position.
  • the third bearing 39 is therefore also in the range of action of the fluid cooling device 15 described above.
  • FIG. 5 shows a detail of a fluid cooling device modified in the area of the cooling tube compared to the arrangement of FIG. 1, which is described in detail below.
  • This exemplary embodiment is based on the same structure explained above with reference to FIGS. 1-4. The features and design variants described for this purpose should also apply or be present except for the differences described below.
  • the cooling tube 16 in turn extends axially within a central recess 10a of the rotor shaft 10 with a second self-supporting section 16b and forms an annular space 10b with the rotor shaft 10, so that the cooling tube 16 is in fluid connection with the annular space 10b and with a fluid outlet 19 stands.
  • the Ro The gate shaft 10 is closed in a fluid-tight manner on the axial side facing away from the fluid inlet 18, for which purpose the recess 10a is only axially open on one side.
  • the fluid inlet 18 and the fluid outlet 19 are in turn formed jointly on one and the same end face of the electrical machine 1 and in particular on the bearing plate 11 functioning as a carrier element 17, as can be seen in FIGS. 1 and 2.
  • the cooling tube 16 extends axially into the region of the driven element 38, which is not, however, inevitable. This means that the cooling tube 16 can also end within the axial extent of the rotor laminated core 8 or between the second bearing 14 and the third bearing 39 or after the third bearing 39.
  • the self-supporting section 16b of the cooling tube 16 has first radial fluid outlet openings 16c.
  • first radial fluid outlet openings 16c In the present case, four first, circular, radial flow openings 16c are provided, all of which have the same axial position on the cooling tube 16 and which are formed on an end region 16d of the second section 16b.
  • the cooling tube 16 has a constant inner diameter over its entire axial extent and is axially closed at its free end region 16d, so that no fluid can escape there in the axial direction.
  • the first radial fluid outlet openings 16c are designed and arranged with respect to one another such that a superimposition of the recoil forces leads to a centering of the cooling tube 16 in the region of the first radial fluid outlet openings 16c.
  • the self-supporting section 16b of the cooling tube 16 has second radial fluid outlet openings 16g axially spaced from the first radial fluid outlet openings 16c.
  • the second radial fi uid outlet openings 16g are formed with a recognizably larger cross section than the first radial fluid outlet openings 16c.
  • a fluid stream V guided by the cooling pipe 16 is thereby initially divided into two fluid sub-streams V1, V2 and, according to the number of fluid outlet openings 16c, 16g, into still further fluid sub-streams VT, V2 ', which are divided by the first and the first second radial fluid outlet openings 16c, 16g out to step.
  • the first and the second radial fluid outlet openings 16c, 16g are designed and dimensioned such that a first partial fluid flow through the first radial fluid outlet openings 16c essentially stabilizes the position of the cooling tube and that a second fluid Partial flow through the second radial fluid outlet openings 16g essentially contributes to cooling the rotor shaft and the rotor.
  • the first fluid partial flow V1 is set lower than the second fluid partial flow V2 due to the dimensioning of the first and second fluid outlet openings shown.
  • the recess 10a of the rotor shaft 10 has in the area of the first radial fluid outlet openings 16c an inner diameter 10c that is reduced compared to an area of the second radial fluid outlet openings 16g. Furthermore, a gap 42 is formed in the region of the first radial fluid outlet openings 16c between an outer peripheral surface of the cooling tube 16 and an inner peripheral surface of the recess 10a of the rotor shaft 10. This gap 42 can be filled by a cooling fluid present when the electrical machine is in operation.
  • the gap 42 is dimensioned such that a plain bearing 43 is formed between the cooling tube 16 and the rotor shaft 10).
  • the gap 42 can in particular be designed as a capillary gap. In this way, the self-supporting section of the cooling tube can be stabilized particularly effectively by creating a fluid bearing point.
  • Stator core 16c first radial fluid outlet opening stator winding 16d end region
  • Rotor 16e axial fluid outlet opening rotor core 16f axial fluid inlet opening

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Motor Or Generator Cooling System (AREA)

Abstract

L'invention concerne un moteur électrique (1) comprenant un stator (4), un rotor (7) et un dispositif de refroidissement par fluide (15), le rotor (7) étant monté rotatif autour d'un axe (A) par rapport au stator (4) au moyen d'un arbre de rotor (10). Le dispositif de refroidissement par fluide (15) comprend un tuyau de refroidissement (16) qui est fixé, au moyen d'une première partie (16a), à un élément de support (17) fixé au stator (4), et qui est relié à une admission de fluide (18). Le tuyau de refroidissement (16) s'étend avec une deuxième partie (16b) en porte-à-faux axialement dans un évidement (10a) central de l'arbre de rotor (10) et forme avec cet arbre de rotor (10) un espace annulaire (10b), de sorte que ledit tuyau de refroidissement (16) soit en liaison fluidique avec cet espace annulaire (10b) et avec une sortie de fluide (19). Dans le moteur électrique selon l'invention, ladite partie (16b) en porte-à-faux du tuyau de refroidissement (16) comporte de premières ouvertures de sortie de fluide radiales (16c).
PCT/EP2019/079926 2018-11-05 2019-10-31 Moteur électrique équipé d'un dispositif de refroidissement par fluide WO2020094514A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018218813.0A DE102018218813A1 (de) 2018-11-05 2018-11-05 Elektrische Maschine mit einer Fluid-Kühleinrichtung
DE102018218813.0 2018-11-05

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Publication Number Publication Date
WO2020094514A1 true WO2020094514A1 (fr) 2020-05-14

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Publication number Priority date Publication date Assignee Title
DE102020206743A1 (de) 2020-05-29 2021-12-02 Zf Friedrichshafen Ag Antriebseinheit für ein elektrisch angetriebenes Fahrzeug

Citations (5)

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Publication number Priority date Publication date Assignee Title
EP1892512A2 (fr) * 2006-08-24 2008-02-27 AVL List GmbH Machine électrique d'entraînement ou de charge pour bancs d'essai haute puissance
US20130002064A1 (en) * 2011-06-29 2013-01-03 General Electric Company Electrical machine
DE102012203691A1 (de) * 2012-03-08 2013-09-12 Siemens Aktiengesellschaft Kühleinrichtung für einen Rotor einer elektrischen Maschine
WO2016050534A1 (fr) 2014-09-30 2016-04-07 Siemens Aktiengesellschaft Machine electrique à refroidissement par liquide
DE102016004931A1 (de) * 2016-04-23 2017-10-26 Audi Ag Elektrische Maschine sowie Verfahren zum Betreiben einer elektrischen Maschine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1892512A2 (fr) * 2006-08-24 2008-02-27 AVL List GmbH Machine électrique d'entraînement ou de charge pour bancs d'essai haute puissance
US20130002064A1 (en) * 2011-06-29 2013-01-03 General Electric Company Electrical machine
DE102012203691A1 (de) * 2012-03-08 2013-09-12 Siemens Aktiengesellschaft Kühleinrichtung für einen Rotor einer elektrischen Maschine
WO2016050534A1 (fr) 2014-09-30 2016-04-07 Siemens Aktiengesellschaft Machine electrique à refroidissement par liquide
DE102016004931A1 (de) * 2016-04-23 2017-10-26 Audi Ag Elektrische Maschine sowie Verfahren zum Betreiben einer elektrischen Maschine

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