EP4022748A1 - Electrical machine - Google Patents
Electrical machineInfo
- Publication number
- EP4022748A1 EP4022748A1 EP20761830.7A EP20761830A EP4022748A1 EP 4022748 A1 EP4022748 A1 EP 4022748A1 EP 20761830 A EP20761830 A EP 20761830A EP 4022748 A1 EP4022748 A1 EP 4022748A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fluid
- electrical machine
- rotor
- machine according
- end plate
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000012530 fluid Substances 0.000 claims abstract description 99
- 125000006850 spacer group Chemical group 0.000 claims description 21
- 239000000112 cooling gas Substances 0.000 claims description 3
- 239000000110 cooling liquid Substances 0.000 claims description 2
- 238000001816 cooling Methods 0.000 description 36
- 239000012809 cooling fluid Substances 0.000 description 26
- 239000000463 material Substances 0.000 description 5
- 239000002826 coolant Substances 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Classifications
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K9/00—Arrangements for cooling or ventilating
- H02K9/10—Arrangements for cooling or ventilating by gaseous cooling medium flowing in closed circuit, a part of which is external to the machine casing
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K9/00—Arrangements for cooling or ventilating
- H02K9/10—Arrangements for cooling or ventilating by gaseous cooling medium flowing in closed circuit, a part of which is external to the machine casing
- H02K9/12—Arrangements for cooling or ventilating by gaseous cooling medium flowing in closed circuit, a part of which is external to the machine casing wherein the cooling medium circulates freely within the casing
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K17/00—Asynchronous induction motors; Asynchronous induction generators
- H02K17/02—Asynchronous induction motors
- H02K17/16—Asynchronous induction motors having rotors with internally short-circuited windings, e.g. cage rotors
- H02K17/20—Asynchronous induction motors having rotors with internally short-circuited windings, e.g. cage rotors having deep-bar rotors
-
- 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
- H02K5/15—Mounting arrangements for bearing-shields or end plates
-
- 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
- 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
- H02K7/04—Balancing means
-
- 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
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K15/00—Methods or apparatus specially adapted for manufacturing, assembling, maintaining or repairing of dynamo-electric machines
- H02K15/16—Centering rotors within the stator; Balancing rotors
- H02K15/165—Balancing the rotor
Definitions
- the invention relates to an electrical machine according to the features of the preamble of claim 1.
- DE 11 2012 004 272 T5 discloses an electrical machine with a rotor designed as a drum rotor, which is arranged on a shaft and around which a stator is arranged concentrically.
- blades are arranged on one end face of the rotor. The blades generate a stream of cooling air, which flows through gaps in the coil ends of the stator.
- a disadvantage of the electrical machine described is that, due to the blades, drag losses that are too high occur at high speeds.
- JP 200927328845 A Another electrical machine is known from JP 200927328845 A.
- an end plate is arranged on a shaft on an end face of the rotor.
- the end disk comprises sections which each have an inlet for a cooling fluid radially on the inside. Furthermore, outlet openings are arranged in the sections. Coolant can be introduced into the sections, which flows through the outlet openings onto the stator coils. This variant can only be implemented with great effort. Furthermore, the above-mentioned electrical machine is costly to implement.
- the invention is therefore based on the object of specifying an electrical machine in which the cooling is improved so that drag losses are reduced and thus applications with high speeds are possible.
- this object is achieved with a view to the electrical machine by the subject matter of claim 1.
- the object is achieved by an electrical machine that is cooled or can be cooled by a fluid.
- the electrical machine comprises a rotor, a stator and at least one end plate, which are arranged in a housing, the end plate and the rotor being arranged on a shaft, in particular a hollow shaft, and the end plate being arranged on is arranged at least one axial end of the rotor.
- At least one first fluid area is formed between a first end face of the end disk and an axial end of the rotor and a second fluid area is formed between a second end face of the end disk and the housing, the two fluid areas having at least one outer fluid connection and at least one inner fluid connection that the connect the two fluid areas to one another in such a way that the fluid can circulate at least in sections between the first and the second fluid area.
- Balancing disks, short-circuit rings and / or cover disks are possible as end disks. Balancing disks are to be understood as meaning disk-shaped means for balancing the rotor. Mass-neutral, positive (add material) or negative (remove material) balancing can be used for balancing.
- Short-circuit rings are the connecting elements on the front of the rotor for short-circuit rods located in axial grooves to form a short-circuit cage of a squirrel-cage rotor (asynchronous machine / ASM). Several short-circuit rings spaced apart from one another can be provided.
- Cover disks are disks attached to the end of a laminated rotor core for axially holding magnets inserted in rotor slots (for permanent magnet machines / PSM).
- the first end disk is preferably designed as a balancing disk.
- the second end disk preferably comprises short-circuit rings and / or cover disks. It is conceivable that the electrical machine has a plurality of second end plates, which are arranged between a first end plate and the rotor.
- the invention has the following advantages.
- the internal and external fluid connection enables the cooling fluid to circulate.
- the internal fluid connection rotates with the shaft and rotor.
- the flow is generated by the centripetal force of the rotating electrical machine.
- the cooling fluid is at least partially ring-shaped in a longitudinal section of the housing. In other words, an annular vortex flow is created.
- the first and second end faces of the end disk, in particular the balancing disk have a contact surface with the eddy flow.
- it is advantageous if the distance between the inner and the outer fluid connection is as large as possible.
- the circulating flow on both sides of the end plate improves convection.
- the use of additional air conveying means such as, for example, blades, can thereby be dispensed with. In this way, drag losses are avoided or reduced during operation.
- the outer fluid connection has an annular gap which is delimited by the end plate and an inner surface of the housing.
- the annular gap is advantageous because it enables good circulation without disturbing edges.
- the external fluid connection is arranged in the end plate. This is advantageous if a mixing of cooling fluids is to be possible.
- the circulating fluid has an axial and / or radial direction at least in sections. This results in an annular flow which is in contact with both sides of the end disk, in particular the balancing disk, and cools it.
- the inner fluid connection extends at least partially between the end faces of the end plate.
- the two fluid areas are connected to one another by the shortest route.
- the shaft has a hollow shaft and the inner fluid connection extends at least partially in the hollow shaft.
- the hollow shaft has a cylindrical shape.
- the hollow shaft has, for example, a first bore in the first fluid area and a second bore in the second fluid area.
- the hollow shaft therefore includes the internal fluid connection.
- the first and second fluid areas are fluidly connected to one another due to the cylindrical shape of the hollow shaft.
- the hollow shaft has recesses, in particular grooves, on the surface.
- the recesses are spaced from one another and are arranged in the region of the end disk in such a way that the cooling fluid can flow through the recess between the end disk and the hollow shaft.
- the electrical machine also particularly preferably has a first end disk and at least one second end disk, the first end disk being designed as a balancing disk and the second end disk as at least one short-circuit ring, in particular several stacked short-circuit rings. It is thus possible to further enlarge the cooling surface and to cool the end face of the rotor more effectively.
- the first end plate is preferably spaced from the at least one short-circuit ring. It is possible for the short-circuit rings to be spaced apart from one another. This allows the cooling fluid to circulate between the second end disks.
- the radii of the short-circuit rings are preferably increasing from the axially inside to the axially outside.
- spacers are arranged between the end disk and the rotor.
- the spacers allow that in operation, if the temperature of the Rotor increases, the distance between the end disk and the rotor remains constant.
- several end plates which are spaced apart from one another by spacers. These can for example be manufactured integrally from the same material as the end disks or integrally from a different material than the end disks, for example plastic molded onto the end disks. This ensures a constant spacing, ergo gap, even when the thermal expansion of various rotor components differs greatly, for example when a short-circuit cage expands axially in relation to a balancing disk.
- the inner fluid connection have different cross-sections and / or cross-sectional shapes. This is advantageous because the flow rate of the cooling fluid can be regulated or set through the cross section and the cooling fluid impinges on the cooling surface at a greater speed.
- the inner fluid connection can thus be implemented as a nozzle or diffuser. In other words, the inner fluid connection can have a nozzle or diffuser. Furthermore, by adapting the cross-sectional shape of the inner fluid connection, noises, in particular whistling, can be reduced.
- a fluid flows through the hollow shaft and has an outlet opening in the area of the end plate.
- the hollow shaft can be used as a feed line for the cooling fluid.
- the rotor cooling can be combined with the cooling of the hollow shaft through the outlet opening.
- the cooling fluid comprises a cooling gas, in particular air and / or a cooling liquid, in particular dielectric oil. This can improve the cooling performance. It is advantageous that the cooling media remain separate from one another or can be mixed, depending on the application.
- the first end plate and / or the second end plate have a slope, the slope of the slope of the first end plate in the direction of the rotor being positive and the slope of the slope of the second end plate in the direction of the rotor being negative.
- the bevel of the first end plate makes it possible to increase the circulation of the cooling fluid.
- the bevel of the second end plate enables a self-evacuating air gap.
- the air gap corresponds to the axial gap between the stator and the rotor.
- FIG. 1 is a section through an electrical machine according to the invention
- Fig. 2 is a section through an electrical machine according to the invention
- FIG. 4 shows a section through an electrical machine according to FIG. 1 with hollow shaft cooling
- FIG. 5 shows a section through an electrical machine according to FIG. 1 with spaced apart
- FIG. 6 shows a section through an electrical machine according to FIG. 4 with two cooling media
- Embodiment with parallel air and oil cooling Embodiment with parallel air and oil cooling
- Embodiment with an axial cooling channel Embodiment with an axial cooling channel
- FIG. 10 shows a section through an electrical machine according to FIG. 8 with a spacer
- FIG. 11 shows a section through an electrical machine according to FIG. 10 with an additional one
- FIG. 12 shows a section through an electrical machine according to FIG. 10 with an additional one
- Fig. 13 is a perspective view of a rotor according to the invention
- 14A shows a perspective view of an end plate according to an exemplary embodiment according to the invention
- 14B shows a further perspective view of the end plate according to FIGS. 14A and
- Embodiment with a fluid lance Embodiment with a fluid lance.
- FIGS. 1 to 12 each show an exemplary embodiment of an electrical machine 10.
- FIGS. 1 to 12 have the following features in common.
- the electrical machine 10 comprises a housing 14.
- a rotor 11, a stator 12, a first end disk 13 ', in particular a balancing disk, several second end disks 13' ', in particular short-circuit rings, and a hollow shaft are arranged coaxially in the housing 14.
- a cooling medium can flow through the housing 14.
- the rotor 11 and the end disks 13 ‘, 13 ′′ are fixedly arranged on the hollow shaft.
- the hollow shaft 15 ’ is rotatably mounted.
- the first end disk 13 ‘ is arranged between an end face of the rotor 11 and the housing 14.
- the second end disks 13 ′′ are arranged between the rotor face and the first end disk 13 ‘.
- the radius of the first end disk 13 is smaller than the radius of the rotor 11.
- a first fluid region 16 is formed between the end face of the rotor 11 and the first end disk 13 '.
- a second fluid area 17 is formed between the first end disk 13 'and the housing 14.
- the first end disk 13 ‘has a bevel 22 radially on the outside.
- the slope 22 is positive in the direction of the rotor 11.
- the radius of the first end disk 13 ‘on the side facing the rotor 11 is greater than the radius on the side facing away from the rotor 11. The radius increases in the direction of the rotor 11.
- the second end disk 13 ′′ also has a bevel 22 radially on the outside.
- the bevel 22 of the second end disk 13 ′′ is negative in the direction of the rotor 11.
- the radius of the second end disk 13 ′′ on the side facing the rotor 11 is smaller than the radius on the side facing away from the rotor 11. The radius decreases in the direction of the rotor 11.
- the stator 12 encloses the rotor 11. An axially extending gap is formed between the rotor 11 and the stator 12.
- the first end plate 13 ' has a plurality of through openings in the first end plate 13 '.
- the through openings are arranged in the circumferential direction on the first end disk 13 '.
- the Through openings form an inner fluid connection 19. More precisely, the inner fluid connection 19 is arranged radially inward with a view of the outer fluid connection 18.
- annular gap is formed between the first end disk 13 'and the inner circumferential surface of the housing 14.
- the annular gap forms an outer fluid connection 18 between the first and second fluid areas 16, 17. More precisely, the annular gap forms a radially outer fluid connection 18.
- the rotation of the rotor 11 and the resulting centripetal force creates a radial air flow.
- the air flows radially outward in the first fluid region 16.
- the air flows along a first end face of the first end disk 13 and along one end face of the second end disk 13 ′′.
- the air flows through the annular gap, that is to say the outer fluid connection 18, into the second fluid area 17.
- the air flows radially inward.
- the air flows along a second end face of the first end disk 13 '.
- the air flows back into the first fluid region 16 through the inner fluid connection 19.
- the air circulates around the first end disk 13 ‘.
- the flow is ring-shaped in longitudinal section.
- the effective cooling surface of the rotor 11 is increased in this way. Furthermore, the convection is improved by the circulation of the air.
- FIG. 2 shows an embodiment which essentially corresponds to that shown in FIG.
- the inner fluid connection 19 in FIG. 2 is not arranged in the first end disk 13 '.
- the hollow shaft 15 ' has an outlet opening 21 between the first end plate 13' and the rotor 11 and an inlet opening 23 between the first end plate 13 'and the housing 14.
- the inner fluid connection 19 is part of the hollow shaft 15 '.
- the inner fluid connection 19 extends from the inlet opening 23 in the second fluid area 17 through the hollow shaft 15 'to the outlet opening 21 in the first fluid area 16. In contrast to FIG. 1, the circulation takes place through the openings in the hollow shaft 15'.
- FIG. 3 shows an embodiment which differs from the previously described embodiments only in the form of the internal fluid connection.
- Grooves distributed over the circumference are arranged on the contact surface between the first end plate 13 'and the hollow shaft 15'.
- the axial width of the grooves is greater than the axial width of the first end plate 13 '.
- the grooves can be traversed by the cooling fluid. The grooves thus form the inner fluid connection 19 between the first and second fluid areas.
- FIG. 4 shows an exemplary embodiment which has an internal fluid connection 19 according to FIG. 1.
- the hollow shaft 15 ' has its own cooling.
- the cooling of the hollow shaft 15 ' is connected to the cooling of the rotor 11 by an outlet 22 which is arranged between the first end disk 13 ′ and the rotor 11.
- the cooling fluid flows through the outlet 22 from the hollow shaft 15 'into the first fluid area 16.
- the cooling fluid of the hollow shaft cooling flows at least in sections parallel to the cooling fluid of the rotor cooling. It is possible for the two cooling fluids to mix with one another.
- the two cooling fluids can be the same or different cooling fluids.
- FIG. 5 an electrical machine 10 with an internal fluid connection according to FIG. 1 is shown. 5 differs from one another by the second end disks 13 ′′, which are spaced apart from one another and are designed as short-circuit rings as described above.
- the short-circuit rings 13 ‘are arranged in the first fluid region 16. It is possible for the cooling fluid to circulate between the short-circuit rings, the first end disk 13 'and the rotor 11. In other words, it is possible that several annular flows arise. The annular flows are parallel at least in sections. It is thus possible to realize a larger effective cooling surface for the second end disks 13 ′′.
- FIG. 6 essentially corresponds to FIG. 4.
- the hollow shaft cooling according to FIG. 6 comprises an oil, in particular a dielectric oil
- the rotor cooling comprises a cooling gas, in particular air.
- other cooling fluids are possible.
- FIG. 7 essentially corresponds to FIG. 6.
- FIG. 7 comprises an enlarged outlet 22. This makes it possible to guide the oil of the hollow shaft cooling and the air of the rotor cooling essentially in parallel without mixing. In the event that mixing of the cooling fluids is desired, a nozzle shape is alternatively possible.
- FIG. 8 shows a combination of the exemplary embodiments according to FIGS. 5 and 6.
- FIG. 8 comprises the second end disks 13 ′′ in the form of the spaced-apart short-circuit rings according to FIG. 5 and an outlet 22 for the cooling fluid of the hollow shaft cooling according to FIG. 6.
- the outlet 22 and the short-circuit rings are arranged in the first fluid area 16.
- the spaces between the short-circuit rings and the end face of the rotor 11 are therefore flowed through with oil.
- the first end disk 13 ' is surrounded by air.
- the oil flow essentially influences the circulating air flow or the annular flow around the first end disk 13 'only slightly or not at all.
- FIG. 9 shows an exemplary embodiment which essentially corresponds to FIG. 6 in structure.
- a channel 24 is arranged between the rotor 11 and the hollow shaft 15 ′, in particular in the laminated core of the rotor 11.
- the channel 24 extends in the axial direction.
- the channel 24 forms a fluid connection between the two axial ends of the rotor 11.
- the cooling fluid can circulate between the two axial ends of the rotor 11 through the channel 24 and the gap between the rotor 11 and the stator 12. Air flows through the channel 24 and the gap. The air flows through the channel 24 to the left side of the rotor 11 and through the gap to the right side of the rotor 11. The direction of flow can be reversed.
- the bevel 22 of the second end disk 13 ′′ is arranged at one end of the gap.
- the air flows along the slope 22 and is deflected radially outward. This creates a further circulating flow around the first end disk 13 ', which runs parallel to the already existing circulating flow. More precisely, the further circulating flow encloses the already existing circulating flow.
- the inner fluid connection 19 is wider than in FIG. 6. Mixing of the cooling fluids is at least reduced in this way.
- FIG. 10 essentially corresponds to FIG. 8.
- the second end disks 13 ′′ have spacers 20.
- the spacers 20 are ring-shaped and are arranged between the second end disks 13 ′′. More precisely, the spacers 20 are arranged radially on the outside between the second end disks 13 ′′.
- the spacers 20 comprise hard plastic. Other materials are conceivable.
- the second end disks 13 ′′ have through openings which are each formed on the radially inner side of the spacer 20.
- the spacers can be formed integrally with the end plates 13 ‘, 13 ′′ or separately.
- the spacers 20 enable a constant flow between the second end disks 13 ′′ and seal the gap between the rotor 11 and the stator 12 against the oil of the hollow shaft cooling.
- the 11 comprises an additional spacer which is arranged between the first end plate 13 'and the opposite second end plate 13' '.
- the first end plate 13 ' comprises the outer and the inner fluid connection 18, 19.
- the additional spacer is arranged after the outer fluid connection 18 in the radial direction.
- the additional spacer creates a bottleneck.
- the additional spacer enables the oil from the hollow shaft cooling and the air from the rotor cooling to be mixed in a targeted manner.
- the inner and / or the outer fluid connection 18, 19 are then preferably designed as nozzles.
- FIG. 12 shows an exemplary embodiment similar to FIG. 11.
- 12 comprises a spacer 20 which is arranged radially inwardly in front of the inner fluid connection 19.
- the oil thus only flows between the rotor 11 and the second end disks 13 ′′.
- the oil and air are only brought together in the second fluid area.
- the oil can be transported away with the air vortex.
- first end disks 13 show a rotor 11 which is arranged on a hollow shaft. On the end faces of the rotor 11, first end disks 13 ‘are arranged, which are designed as balancing disks.
- the balancing disk 13 is shown in detail in FIGS. 14A and 14B.
- the balancing disk 13 comprises a slope 22 which rises in the direction of the rotor 11.
- the balancing disk 13 also has bores which are arranged distributed over the circumference. The bores form the inner fluid connection 19.
- a crown-shaped spacer formed integrally with the balancing disk 13 is arranged on the side facing the rotor 11.
- the spacer 20 is arranged radially in front of the bores, starting from the central longitudinal axis.
- the hollow shaft 15 ’ includes a supply line for a cooling fluid, in particular for a dielectric oil.
- the electrical machine 10 comprises the stator 12, the rotor 11, the first end plate 13 ', several second end plates 13 ", a hollow shaft 15' and a fluid lance which is inserted in the hollow shaft 15 ' is arranged.
- the structure of the electrical machine essentially corresponds to that of FIG. 4.
- the cooling lance protrudes as far as the center of the electrical machine 10.
- the cooling lance is arranged on the central longitudinal axis of the electrical machine 10. Furthermore, the cooling lance has a supply opening for a cooling fluid in the area of the center of the electrical machine 10.
Landscapes
- Engineering & Computer Science (AREA)
- Power Engineering (AREA)
- Motor Or Generator Cooling System (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102019122944.8A DE102019122944A1 (en) | 2019-08-27 | 2019-08-27 | Electric machine |
PCT/EP2020/073843 WO2021037906A1 (en) | 2019-08-27 | 2020-08-26 | Electrical machine |
Publications (1)
Publication Number | Publication Date |
---|---|
EP4022748A1 true EP4022748A1 (en) | 2022-07-06 |
Family
ID=72243142
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20761830.7A Pending EP4022748A1 (en) | 2019-08-27 | 2020-08-26 | Electrical machine |
Country Status (5)
Country | Link |
---|---|
US (1) | US20220294304A1 (en) |
EP (1) | EP4022748A1 (en) |
CN (1) | CN114175470A (en) |
DE (1) | DE102019122944A1 (en) |
WO (1) | WO2021037906A1 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3890163A1 (en) * | 2020-04-01 | 2021-10-06 | GE Energy Power Conversion Technology Ltd. | Method for sizing of a rotor with non-through shaft, associated rotor and motorcompressor |
US20230127634A1 (en) * | 2021-10-22 | 2023-04-27 | Dana Belgium N.V. | Vehicle propulsion unit with electric machine that includes a balancing plate assembly and method for assembling said electric machine |
DE102021133860A1 (en) | 2021-12-20 | 2023-06-22 | Bayerische Motoren Werke Aktiengesellschaft | Flow element and electrical machine with flow element |
US20240055951A1 (en) * | 2022-08-09 | 2024-02-15 | Borgwarner Inc. | Induction rotor with end ring cooling features |
DE102022211820A1 (en) * | 2022-11-09 | 2024-05-16 | Robert Bosch Gesellschaft mit beschränkter Haftung | Rotor of an electrical machine |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB255981A (en) * | 1925-05-14 | 1926-08-05 | British Thomson Houston Co Ltd | Improvements in and relating to dynamo electric machines |
US2413525A (en) * | 1944-02-10 | 1946-12-31 | Allis Louis Co | Totally enclosed dynamoelectric machine |
US2618756A (en) * | 1949-06-06 | 1952-11-18 | Carl J Fechheimer | Liquid cooled electrical machine |
DE1099064B (en) * | 1957-01-28 | 1961-02-09 | Vickers Electrical Co Ltd | Cooling gas supply in a completely encapsulated, explosion-proof electric motor |
JPS5789370U (en) * | 1980-11-19 | 1982-06-02 | ||
JPS62122456U (en) * | 1985-09-13 | 1987-08-04 | ||
JP2009273288A (en) | 2008-05-09 | 2009-11-19 | Kura Gijutsu Kenkyusho:Kk | Flux shunt control rotary electric machine system |
DE102009001838A1 (en) * | 2009-03-25 | 2010-09-30 | Robert Bosch Gmbh | driving means |
US9742242B2 (en) | 2011-10-13 | 2017-08-22 | Mitsubishi Electric Corporation | Rotary electric machine including a stator coil end cooling construction and rotor with dual fan blades |
US8896167B2 (en) * | 2012-05-25 | 2014-11-25 | Deere & Company | Electric machine rotor cooling method |
DE102012218696B4 (en) * | 2012-10-15 | 2015-02-12 | Continental Automotive Gmbh | Rotating electric machine and motor vehicle with a rotating electric machine |
DE102013020332A1 (en) * | 2013-12-04 | 2014-07-31 | Daimler Ag | Electric machine i.e. asynchronous machine, for use in drive train of e.g. hybrid vehicle, has shaft comprising outlet opening for guiding coolant from channel of shaft to surrounding of shaft, and duct element comprising flow opening |
US9762106B2 (en) * | 2014-12-04 | 2017-09-12 | Atieva, Inc. | Motor cooling system |
DE102016200423A1 (en) * | 2016-01-15 | 2017-07-20 | Continental Automotive Gmbh | Electric machine |
DE102016209173A1 (en) * | 2016-05-25 | 2017-11-30 | Volkswagen Aktiengesellschaft | Rotor for an electric machine |
DE102016222846A1 (en) * | 2016-11-21 | 2018-05-24 | Audi Ag | Electric machine |
-
2019
- 2019-08-27 DE DE102019122944.8A patent/DE102019122944A1/en active Pending
-
2020
- 2020-08-26 WO PCT/EP2020/073843 patent/WO2021037906A1/en unknown
- 2020-08-26 CN CN202080053545.2A patent/CN114175470A/en active Pending
- 2020-08-26 EP EP20761830.7A patent/EP4022748A1/en active Pending
- 2020-08-26 US US17/637,043 patent/US20220294304A1/en active Pending
Also Published As
Publication number | Publication date |
---|---|
CN114175470A (en) | 2022-03-11 |
US20220294304A1 (en) | 2022-09-15 |
WO2021037906A1 (en) | 2021-03-04 |
DE102019122944A1 (en) | 2021-03-04 |
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