Classifications

• • 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
  • H02K5/128—Casings or enclosures characterised by the shape, form or construction thereof specially adapted for operating in liquid or gas using air-gap sleeves or air-gap discs
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
  • B60L50/00—Electric propulsion with power supplied within the vehicle
  • B60L50/50—Electric propulsion with power supplied within the vehicle using propulsion power supplied by batteries or fuel cells
  • B60L50/51—Electric propulsion with power supplied within the vehicle using propulsion power supplied by batteries or fuel cells characterised by AC-motors
• • 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
  • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
  • H02K5/173—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings
  • H02K5/1732—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings radially supporting the rotary shaft at both ends of the rotor
• • 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
• • H—ELECTRICITY
  • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
  • H02K—DYNAMO-ELECTRIC MACHINES
  • H02K9/00—Arrangements for cooling or ventilating
  • H02K9/22—Arrangements for cooling or ventilating by solid heat conducting material embedded in, or arranged in contact with, the stator or rotor, e.g. heat bridges
• • H—ELECTRICITY
  • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
  • H02K—DYNAMO-ELECTRIC MACHINES
  • H02K9/00—Arrangements for cooling or ventilating
  • H02K9/22—Arrangements for cooling or ventilating by solid heat conducting material embedded in, or arranged in contact with, the stator or rotor, e.g. heat bridges
  • H02K9/223—Heat bridges
• • H—ELECTRICITY
  • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
  • H02K—DYNAMO-ELECTRIC MACHINES
  • H02K9/00—Arrangements for cooling or ventilating
  • H02K9/22—Arrangements for cooling or ventilating by solid heat conducting material embedded in, or arranged in contact with, the stator or rotor, e.g. heat bridges
  • H02K9/227—Heat sinks
• • 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
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
  • Y02T10/00—Road transport of goods or passengers
  • Y02T10/60—Other road transportation technologies with climate change mitigation effect
  • Y02T10/70—Energy storage systems for electromobility, e.g. batteries

Definitions

• the invention relates to an electrical machine, in particular for a vehicle, and a vehicle with such a machine.
• Such an electrical machine can generally be an electric motor or a generator.
• the electrical machine can be designed as an external rotor or as an internal rotor.
• a generic machine for example from US 5,214,325. It comprises a housing which surrounds a housing interior and which has a circumferential jacket which radially delimits the housing interior, axially on the one hand a rear wall axially delimiting the housing interior and axially on the other hand a front wall axially delimiting the housing interior.
• a stator of the machine is firmly connected to the jacket.
• a rotor of the machine is arranged in the stator, a rotor shaft of the rotor being rotatably mounted on the front side wall via a front shaft bearing.
• the stator of a conventional electrical machine comprises stator windings which are supplied with electrical current during operation of the machine. This also generates heat in the rotor, which must be dissipated to prevent overheating and the associated damage or even destruction of the rotor. It is also necessary to dissipate the heat in order not to demagnetize the windings or permanent magnets of the rotor due to excessive temperature. It is known from the prior art to provide a cooling channel in the housing of an electrical machine, through which a coolant can flow, which in turn can absorb the waste heat generated in the machine and transport it out of the housing.
• an object of the present invention to provide an improved embodiment for an electrical machine in which the aforementioned disadvantages are largely or even completely eliminated.
• an improved embodiment for an electrical machine is to be created, which is characterized by improved cooling of the rotor and at the same time low manufacturing costs.
• the housing parts are formed separately from the heat transfer body.
• each of the two housing parts and the heat transfer body are formed in two parts. This makes it possible to select a material with a lower thermal conductivity for the housing parts than for the heat transfer body. Since materials with a high thermal conductivity are more expensive to procure than materials with a low thermal conductivity, considerable cost savings can be achieved in the manufacture of the electrical machine.
• An electrical machine in particular for a vehicle, comprises a stator and a rotor which can be rotated about an axis of rotation relative to the stator.
• An axial direction of the machine is defined by the axis of rotation.
• the machine comprises a housing which surrounds an interior of the housing.
• the housing comprises a first and a second housing part, which delimit the interior of the housing, preferably along the axial direction, and on which the rotor is rotatably mounted by means of a bearing device.
• the two housing parts can in particular be the axial “end shields” mentioned at the beginning.
• the bearing device can have two bearing elements, in particular in the form of shaft bearings, a first shaft bearing on the first housing part and a second bearing element on the second housing part, that is to say preferably on a second bearing plate, which the first th bearing plate is axially opposite, is arranged.
• a heat transfer body is arranged axially between at least one housing part - ie the first or second housing part - and the rotor. This heat transfer body, together with said housing part, delimits a coolant chamber, which is preferably designed as a cooling channel, coolant collector chamber or / and coolant distributor chamber, in each case for a coolant to flow therethrough.
• the heat transfer body is formed separately from the two housing parts. This makes it possible to choose a different material for the housing parts than for the heat transfer body. Thus, a material with a particularly high rigidity can be used for the housing parts and a material with a high thermal conductivity for the heat transfer body.
• the heat transfer body and the two housing parts are made of different materials. This makes possible it is to use a material with lower thermal conductivity for the housing parts than for the heat transfer structure. This leads to cost advantages in the manufacture of the machine.
• the material of the first and / or second housing part can have a higher upper yield strength and / or yield strength than the material of the heat transfer body.
• the material of the heat transfer body has a higher thermal conductivity than the material of the first and / or second housing part.
• a relatively inexpensive material with low thermal conductivity can be used in the housing parts that do not have to transfer heat from the rotor to the coolant chamber.
• a heat transfer structure for transferring waste heat from the rotor to the heat transfer body is provided on the relevant heat transfer body and on the rotor.
• the heat transfer structure and the two housing parts are expediently made of non-uniform material. This makes it possible to use a material with lower thermal conductivity for the housing parts than for the heat transmission structure. This leads to cost advantages in the manufacture of the machine.
• the material of the heat transfer structure particularly preferably has a higher thermal conductivity than the material of the first and / or second housing part.
• the heat transfer structure which is particularly critical for effective cooling of the rotor, can thus be selectively equipped with particularly good heat transport properties.
• the heat transfer body and the heat transfer structure are made of the same material. In this way, effective heat transfer is ensured both by the heat transfer structure and by the heat transfer body.
• the rotor can expediently be mounted directly on the housing parts. This allows the heat transfer structure to be made particularly thin-walled, since no bearing forces are introduced from the rotor into the heat transfer structure.
• the rotor is particularly preferably not mounted on the housing parts via the heat transfer structure and preferably also not via the heat transfer body.
• This variant also makes it possible to design the heat transfer structure to be particularly thin-walled, since no bearing forces are introduced from the rotor into the heat transfer structure.
• a wall thickness of the first or / and second housing part measured in the axial direction is expediently at least twice, preferably at least five times, a wall thickness of the heat transfer body.
• the heat transfer body can thus be made particularly thin-walled.
• At least two heat transfer bodies are provided to limit the coolant space, both of which are formed separately from the two housing parts.
• a first heat transfer body is arranged axially between the first housing part and the rotor and a second heat transfer body is arranged axially between the rotor and the second housing part.
• the bearing device comprises a first bearing element and a second bearing element, which are arranged axially at a distance from one another, so that the rotor is arranged axially between the two bearing elements.
• the axial position of the bearing elements is determined such that less than 35%, preferably less than 10%, of the radial forces absorbed by the bearing elements are passed on to the respective heat transfer element. In this way, overloading of the heat transfer body is avoided.
• the bearing device comprises a first bearing element, by means of which the rotor is mounted on the first housing part, and a second bearing element, by means of which the rotor is mounted on the second housing part.
• the two bearing elements are axially spaced apart.
• a distance measured along the axial direction between the first heat transfer body and the first housing part is larger - and is preferably at least twice - as a distance between the first bearing element and the first housing part.
• a distance measured along the axial direction between the second heat transfer body and the second housing part is larger - and is preferably at least twice - as a distance between the second bearing element and the second housing part.
• the stator is attached to at least one of the two housing parts.
• the stator is attached to the heat transfer body, in this embodiment it is possible to make the heat transfer body particularly thin-walled and to be particularly close to the rotor. onieren.
• this embodiment is accompanied by further material savings and thus cost advantages.
• the stator is arranged at a distance from the heat transfer body or only lies loosely on it. In this way it can be avoided that excessive forces are introduced into the heat transfer body, which could lead to damage to the heat transfer body, in particular if it is thin-walled, as proposed here.
• the heat transfer body is clamped between the stator and the housing part with a pretensioning force which is sufficient to ensure a fluid-tight surface pressure for sealing elements located therebetween, in particular in the form of elastomer seals.
• the heat transfer body and the at least one housing part are preferably formed in two parts. This makes it easier to choose a different material for the housing part, in particular with low thermal conductivity, than for the heat transfer body. This measure is also accompanied by considerable cost advantages in the manufacture of the electrical machine.
• the heat transfer body is attached to the at least one housing part.
• a detachable or non-detachable fastening is conceivable.
• the latter can in particular be a material connection.
• the heat transfer structure comprises a plurality of projections which project axially from the rotor to the heat transfer body and which engage in complementary recesses provided on the heat transfer body.
• the heat transfer structure comprises a plurality of projections projecting axially from the heat transfer body to the rotor, which engage in recesses provided on the rotor and complementary thereto. In both alternatives, a large interaction surface for heat transfer from the rotor to the heat transfer body is ensured.
• the projections can particularly preferably be designed like a comb. Since the complementary recesses in this variant also have a comb-like geometry, a particularly large interaction surface for the heat transfer from the rotor to the heat transfer body is ensured in this way.
• the heat transfer body and the rotor for realizing the heat transfer structure are particularly preferably arranged relative to one another in such a way that in the area of the heat transfer structure there is an axial distance between the heat transfer body and the rotor - this is measured along the axial direction - at most 1 mm, preferably at most 0. Is 5 mm.
• the annular or air gap formed between the heat transfer body and the rotor has a small gap width, so that effective heat transfer from the rotor to the heat transfer body is ensured.
• the heat transfer body can be designed as a cooling plate which extends at least in sections transversely to the axial direction and whose wall thickness measured along the axial direction is at most 3 mm.
• the projections or recesses resulting in the heat transfer structure are formed or formed on or in this cooling plate along the axial direction.
• a recess depth or projection height of the recesses or projections forming the heat transfer structure on the heat transfer body is particularly preferably at least three times, preferably at least five times, the wall thickness of the cooling plate.
• the heat transfer structure has a large interaction area, so that a particularly large amount of heat can be transferred from the rotor to the heat transfer body per unit of time. At the same time, the cooling plate remains particularly thin-walled.
• the heat transfer body with the heat transfer structure can be a deep-drawn component, in particular a shaped sheet metal part, with a rib structure, the rib structure being produced by a deep-drawing or forming process.
• At least one housing part has a fastening section to which the heat transfer body is fastened, the bearing device for the rotatable mounting of the rotor also being attached to the fastening section.
• Both housing parts that is to say both the first and the second housing part, particularly preferably have a fastening section configured in this way.
• the bearing device is not attached to the housing via the heat transfer body as in many conventional electrical machines.
• the heat transfer body can therefore be made particularly thin-walled.
• the fastening section can particularly preferably be designed as a sleeve projecting axially from the housing part inwards into the housing interior, on the inside of which a bearing element of the bearing device is arranged.
• a sleeve-like design ensures a particularly stable attachment of the bearing device to the housing part.
• the heat transfer body is made of a different material than at least one of the two housing parts.
• both housing parts are made of a different material than the heat transfer body. This variant allows a relatively expensive material with high thermal conductivity to be used only for the heat transfer body - as part of the heat transfer structure, whereas a cheaper material with lower thermal conductivity can be used for the housing part (s).
• the material of at least one housing part preferably both housing parts, has a thermal conductivity that is less than the thermal conductivity of the heat transfer body.
• a relatively inexpensive material with low thermal conductivity can be used in the housing parts that do not have to transfer heat from the rotor to the coolant chamber.
• the material of the heat transfer body particularly preferably has a thermal conductivity of at least 100 W / (m * k), preferably of at least 150 W / (m * k). In this way, an effective heat transfer from the rotor via the cooling channel to the coolant present in the coolant chamber is ensured.
• An annular gap which is part of the coolant chamber, can expediently be formed between winding end sections of the stator coils, which protrude into the coolant chamber, and the heat transfer body.
• the invention further relates to a vehicle, in particular a motor vehicle with an electrical machine presented above.
• a vehicle in particular a motor vehicle with an electrical machine presented above.
• the advantages of the electrical machine explained above are therefore also transferred to the vehicle according to the invention. Further important features and advantages of the invention emerge from the subclaims, from the drawings and from the associated description of the figures on the basis of the drawings.
• FIG. 1 shows an example of an electrical machine according to the invention in a longitudinal section along the axis of rotation of the rotor
• FIG. 2 shows a detailed view of FIG. 1 in the area of the heat transfer body.
• FIG. 1 illustrates an example of an electrical machine 1 according to the invention.
• the machine 1 comprises a housing 2 which surrounds a housing interior 3.
• a stator 4 and a rotor 5 are arranged in the housing interior 3.
• the stator 4 can have a stator body 12 and a plurality of stator coils 13, not shown in FIG. 1, which are embedded in the stator body 12 and for driving the rotor 5 are electrically energized.
• the stator 4 is fixedly attached to a peripheral wall 14 of the housing 2.
• the rotor 5 comprises a rotor shaft 6 and a plurality of permanent magnets 7, not shown in FIG. 1, which are arranged on the rotor shaft 6 in a rotationally fixed manner.
• the rotor 5 can be rotated relative to the stator 3 about an axis of rotation D, which is defined by the central longitudinal axis M of the rotor shaft 6.
• An axial direction A of the electrical machine 1 is also defined by the axis of rotation D.
• a radial direction R extends perpendicularly from the axis of rotation D.
• a circumferential direction U runs around the axis of rotation D.
• the permanent magnets 7 of the rotor 5 can be arranged along the circumferential direction U of the rotor shaft 6 with alternating magnetic polarization. In other words, magnetic north poles N and magnetic south poles S alternate along the circumferential direction U.
• the housing 2 comprises a first and a second housing part 8a, 8b.
• These two housing parts 8a, 8b are also known to the person skilled in the art as so-called “end shields” and delimit the housing interior 3 along the axial direction A.
• Another, third housing part 8c, which delimits the machine radially, is made by overmolding the stator 5 from plastic. fabric formed.
• the first and the second housing part 8a, 8b can also be formed separately from the third housing part 8c.
• the rotor 5 with the rotor shaft 6 is rotatably mounted on the housing 2 via a bearing device 9.
• the bearing device 9 comprises a first bearing element 10a, via which the rotor shaft 6 is rotatably mounted on the first housing part 7a.
• the bearing device 9 comprises a second bearing element 10b, which is arranged axially at a distance from the first bearing element 10a, so that the rotor is arranged axially between the two bearing elements 10a, 10b, and via which the rotor shaft 6 is rotatably mounted on the second housing part 8b is.
• the two bearing elements 10a, 10b - also known to the person skilled in the art under the name “shaft bearing” - are firmly connected to the first and second housing parts 8a, 8b.
• the stator 4 with the stator body 12 and the stator coils 13 is also fastened to the housing parts 8a, 8b, 8c.
• a first and a second heat transfer body 11 a, 11 b are also provided for dissipating waste heat generated by the rotor 5 including its permanent magnets 7 during operation.
• the two heat transfer bodies 11a, 11b are formed separately from the two housing parts 8a, 8b and, together with the two housing parts 8a, 8b, delimit a coolant chamber 15 which is designed as a cooling channel and through which a coolant K can flow.
• the first and the second heat transfer bodies 11a, 11b and the housing parts 8a, 8b respectively assigned to the heat transfer bodies 11a, 11b are each formed in two parts.
• the first heat transfer body 11 a can be attached to the first housing part 8 a, for example by means of a material connection.
• the second heat transfer body 11b can be fastened to the second housing part 8b, preferably also by means of a material connection.
• a suitable detachable connection can also be considered.
• the two heat transfer bodies 11 a, 11 b of the heat transfer structure 18 are preferably locked exclusively by axial pressure.
• the rotor 5 is expediently mounted directly on the housing parts 8a, 8b. In particular, as can be seen in FIG. 1, the rotor 5 is not mounted on the housing parts 8a, 8b via the heat transfer structure 18 and also not via the heat transfer bodies 11a, 11b.
• the first heat transfer body 11 a is arranged along the axial direction A between the first housing part 8 a and the rotor 5.
• the second warm The transmission body 11b is arranged along the axial direction A between the rotor 5 and the second housing part 8b.
• the coolant K can absorb heat generated by the rotor 5 during operation of the machine 1 via the two heat transfer bodies 11 a, 11 b, so that overheating and — associated with this — damage or even destruction of the machine 1 can be avoided .
• a coolant inlet 16 for introducing the coolant K into the coolant chamber 15 and in the second housing part 8b a coolant outlet 17 for discharging the coolant K from the coolant chamber 15. Heat is passed on to the coolant K flowing through the coolant space 15 via the two heat transfer bodies 11 a, 11 b, which in each case partially delimit the coolant space 15, and is removed therefrom from the machine 1.
• the two heat transfer bodies 11a, 11b can both be designed as cooling plates 22a, 22b which extend at least in sections transversely to the axial direction A, that is to say along the radial direction R, and whose wall thickness W measured along the axial direction A in the region of the heat transfer structure 18 is at most 3 mm.
• the cooling plates 22a, 22b can be realized by deep-drawn sheet metal parts.
• the two heat transfer bodies 11 a and 11 b are arranged at a distance from the stator 4 with the stator body 12 and only lie loosely on the latter with contact sections 19.
• a wall thickness of the first and second housing parts 8a, 8b measured in the axial direction A is at least twice, preferably at least five times, a wall thickness of the first and second heat transfer bodies 11a, 11b.
• the heat transfer structure 18 and the two housing parts 8a, 8b are designed to be non-uniform in material.
• the two heat transfer bodies 11a, 11b are non-material compared to the two housing parts 8a, 8b educated.
• the two heat transfer bodies 11 a, 11 b and the heat transfer structure 18 are made of the same material.
• the material of the heat transfer structure 18 expediently has a higher thermal conductivity than the material of the first and the second housing part 8a, 8b.
• the material of the heat transfer body has a higher thermal conductivity than the material of the two housing parts 8a, 8b.
• the material of the two housing parts 8a, 8b has a thermal conductivity that is less than the thermal conductivity of the heat transfer body 8a, 8b.
• the material of the heat transfer body 11 a, 11 b has a thermal conductivity of at least 100 W / (m * k) , preferably from at least 150 W / (m * k).
• the axial position of the bearing elements 10a, 10b along the axial direction A is expediently determined such that less than 35%, preferably less than 10%, of the radial forces absorbed by the bearing elements 10a, 10b are passed on to the heat transfer bodies 8a, 8b become. In this way, an overload of the respective heat transfer body 8a, 8b is avoided.
• the material of the first and second housing parts 8a, 8b can also have a higher upper yield strength and a higher proof stress than the material of the heat transfer body 11a, 11b.
• FIG. 2 is a detailed illustration of FIG. 1 in the region of the first heat transfer body 11 a.
• the heat transfer structure 18 for transferring waste heat from the rotor 5 to the heat transfer body 11 a formed.
• the heat transfer structure 18 comprises a plurality of projections 21, which protrude from the rotor 5 to the first heat transfer body 11 a along the axial direction A and which engage in complementary recesses 20 provided on the heat transfer body 11 a.
• the first heat transfer body 11 a comprises a plurality of projections 21 projecting axially from the heat transfer body to the rotor 5, which projections 21 complementary to the projections 21 , Engage recesses 20 provided on the rotor 5.
• the projections 21 can preferably be formed like a comb.
• a distance X measured in the area of the heat transfer structure 18 between the heat transfer body 11 a and the rotor 5 along the axial direction is expediently at most 1 mm, preferably at most 0.5 mm.
• a recess depth T1 of the recesses T1 forming the heat transfer structure 18 on the first heat transfer body 11a and a projection flute H 1 of the projections 21 forming the heat transfer structure 18 on the first heat transfer body 11a is at least three times, preferably at least three is five times the aforementioned wall thickness W of the cooling plate.
• the illustration in FIG. 2 also shows that the first housing part 8a has a (first) fastening section 23a, to which the first heat transfer body 11a is fastened.
• the bearing device 9 for rotatably mounting the rotor 5 is attached to the (first) fastening section 23a.
• the (first) fastening section 23a is expediently designed as a sleeve 24 projecting axially inward from the first housing part 11a into the housing interior 3, on the inside 25 of which the first bearing element 10a of the bearing device 9 is arranged.
• the second housing part 8b also has such a (second) fastening section (23b) on which the second heat transmission body 11 b and the rotor 5 are attached.
• the second bearing element 10b of the bearing device 9 can be attached to the second fastening section 23b.
• first heat transfer body 11 a and for the first housing part 8 a associated with this first heat transfer body 11 a also apply mutatis mutandis to the second heat transfer body 11 b and the second housing part 8 b assigned to the second heat transfer body 11 b .
• An annular gap 27, which is part of the coolant chamber 15, can expediently be formed between the winding end sections 26 of the stator coils 13, which protrude into the coolant chamber 15, and the heat transfer bodies 11 a, 11 b.

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• Engineering & Computer Science (AREA)
• Power Engineering (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Life Sciences & Earth Sciences (AREA)
• Sustainable Development (AREA)
• Sustainable Energy (AREA)
• Transportation (AREA)
• Mechanical Engineering (AREA)
• Motor Or Generator Cooling System (AREA)
• Motor Or Generator Frames (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=67439225

Family Applications (1)

Country Status (6)

Family Cites Families (23)

• 2018
  • 2018-09-13 DE DE102018215608.5A patent/DE102018215608A1/de active Pending
• 2019
  • 2019-07-24 US US17/276,118 patent/US12009722B2/en active Active
  • 2019-07-24 JP JP2021513215A patent/JP7344958B2/ja active Active
  • 2019-07-24 EP EP19744690.9A patent/EP3850733A1/de active Pending
  • 2019-07-24 CN CN201980060221.9A patent/CN112703664A/zh active Pending
  • 2019-07-24 WO PCT/EP2019/069903 patent/WO2020052846A1/de unknown

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