EP3895288A1 - Rotor device for an electric machine and electric machine - Google Patents
Rotor device for an electric machine and electric machineInfo
- Publication number
- EP3895288A1 EP3895288A1 EP19828234.5A EP19828234A EP3895288A1 EP 3895288 A1 EP3895288 A1 EP 3895288A1 EP 19828234 A EP19828234 A EP 19828234A EP 3895288 A1 EP3895288 A1 EP 3895288A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rotor
- impact
- fluid
- hill
- shaft
- 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 137
- 238000001816 cooling Methods 0.000 claims abstract description 15
- 230000000630 rising effect Effects 0.000 claims description 10
- 230000002093 peripheral effect Effects 0.000 claims description 9
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 claims description 3
- 229910052782 aluminium Inorganic materials 0.000 claims description 3
- 239000004020 conductor Substances 0.000 claims description 3
- 229910052802 copper Inorganic materials 0.000 claims description 3
- 239000010949 copper Substances 0.000 claims description 3
- 238000005488 sandblasting Methods 0.000 claims description 3
- 239000012809 cooling fluid Substances 0.000 description 60
- 238000004519 manufacturing process Methods 0.000 description 9
- 230000008901 benefit Effects 0.000 description 7
- 230000000694 effects Effects 0.000 description 6
- 238000009826 distribution Methods 0.000 description 5
- 238000005516 engineering process Methods 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 239000007921 spray Substances 0.000 description 5
- 230000015572 biosynthetic process Effects 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 230000001174 ascending effect Effects 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000003595 mist Substances 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000007493 shaping process Methods 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 238000004804 winding Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000004049 embossing Methods 0.000 description 1
- 238000005242 forging Methods 0.000 description 1
- 230000003116 impacting effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000005304 joining Methods 0.000 description 1
- 230000014759 maintenance of location Effects 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
- 238000003892 spreading Methods 0.000 description 1
- 230000007480 spreading Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
Classifications
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K1/00—Details of the magnetic circuit
- H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
- H02K1/22—Rotating parts of the magnetic circuit
- H02K1/32—Rotating parts of the magnetic circuit with channels or ducts for flow of cooling medium
-
- 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
Definitions
- the present invention relates to a rotor device for an electrical machine, in particular for an electric motor, according to the preamble of claim 1, and to an electrical machine, in particular an electric motor, according to claim 15.
- An electrical machine usually has a rotor (rotor) and a stator (stator), the rotor being rotatably mounted about a common longitudinal axis with respect to the stator.
- the rotor can be designed as a hollow cylindrical body (hollow shaft).
- Fluid lances rotating with the hollow shaft and not rotating relative to the hollow shaft are known in the prior art.
- Fluid lances are hollow bodies positioned in hollow shafts, which protrude into the hollow shaft from an axial end of the hollow shaft and are designed to transport a fluid from an axial end of the fluid lance to an outlet opening at the opposite end of the fluid lance, at which the fluid is directed or leaves the fluid lance in an undirected manner and meets an inner wall of the hollow shaft.
- a rotating fluid lance shows e.g. the W02017214232A1 or DE102013020324A1.
- a standing fluid lance shows e.g. DE102016004931A1.
- Such a rotor device comprising a rotor and a fluid lance, is in need of improvement, particularly if the rotor is installed in an electric motor of a vehicle.
- dynamic loads such as cornering the vehicle, have an influence on the exit of the cooling fluid from the fluid lance. If this cooling fluid flow is unfavorably deflected, this can result in a reduction in the cooling effect.
- a rotor device with the characterizing features of claim 1. Because an inner wall of the hollow shaft is equipped with an impact hill, a cooling fluid stream of a cooling lance directed at the impact hill can be divided in a predetermined manner and, in this respect, can be guided in predetermined ways within the hollow shaft.
- An impact hill is to be understood as an inward geometrical elevation with respect to the inner wall of the hollow shaft, in particular at the axial level of an outlet opening of a cooling fluid lance.
- the fluid lance is equipped with a radial fluid outlet opening, preferably a conical bore, the fluid outlet opening being directed towards the impact hill.
- a radial fluid outlet opening preferably a conical bore
- the radial fluid outlet opening ensures that the exiting cooling fluid jet is always directed onto the impact hill, and the conical bore can ensure that the cooling fluid jet is fanned out somewhat. This can further ensure that the cooling fluid jet hits the impact hill, even if, for example, the cooling fluid jet should be deflected in space by movements of the rotor shaft device.
- an almost center-symmetrical division of the cooling fluid flow on both sides of the hollow shaft can be achieved, the difference in the cooling fluid flow volume on both sides being less than 10%.
- the fluid lance is a standing fluid lance.
- a disadvantage of rotating lances is that the cooling fluid experiences a rotating component of motion even before impacting the inner circumferential surface, so that the relative speed between the fluid and the fluid impact point is low.
- the point of impact of the fluid on the inner peripheral surface is static; he is not moving.
- Standing fluid lances are advantageous because the speed difference between oil and oil impact point is higher.
- the point of impact is dynamic and covers the entire inner circumference of the rotor shaft. This can improve the cooling performance.
- the impact hill transforms the inner wall into a first inner wall section and a second Interior wall section divides.
- the cooling fluid which has been divided accordingly by the impact hill, flows over the resulting inner wall sections.
- a first fluid drain opening is arranged in the first inner wall section and a second fluid drain opening is arranged in the second inner wall section.
- the cooling fluid flows out through the fluid drain openings.
- the fluid drainage openings are preferably as far as possible from the impact hill, so that the cooling fluid can travel a correspondingly long distance and the most extensive possible heat exchange can take place.
- the fluid outlet openings can be designed to direct and / or spray the cooling fluid in the direction of a rotor end face or a winding head of a stator.
- the rotor shaft is configured as an assembled and / or rotationally welded rotor shaft composed of at least two parts, in particular a first rotor half-shaft and a second rotor half-shaft. This can facilitate, for example, the introduction or also the shaping of the impact hill into the center of the rotor shaft, for example if the impact hill is introduced before the rotor half-waves are connected.
- the inner wall of the rotor shaft is equipped with shaft shoulders, in particular with a first shaft shoulder between the impact hill and the first fluid drain opening, preferably immediately before the first fluid drain opening, and a second wave shoulder between the impact hill and the second fluid drain opening, preferably immediately before the second fluid drain opening.
- the hollow shaft forms a bath between the impact hill and the respective fluid drain opening.
- the shaft shoulders act as a retention dam for the cooling fluid.
- the cooling fluid can be stowed, as it were, through the shaft shoulders.
- the thickness of the fluid film can be adjusted by the height of the shaft shoulders above the inner wall. Furthermore, it is possible to delay the throughput time of the cooling fluid, so that the cooling fluid flows away too quickly and the heat absorption capacity of the cooling fluid can be better utilized.
- the bath tub then extends between a first and a second wave shoulder.
- a further shaft shoulder advantageously follows behind the first outlet opening, preferably behind the first and the second outlet opening.
- the first inner wall section and / or the second inner wall section is structured, in particular with axially extending straight or spiral ribs, microstructuring by sandblasting and / or small craters.
- the structuring basically has a surface-enlarging effect, so that an improved heat exchange is made possible.
- the channels defined by the ribs are, in particular, technically advantageous, spiral-shaped or, in terms of production technology, straight. Spiral channels have the advantage that the cooling fluid film is accelerated by the rotation axially outwards in the direction of the fluid outlet openings and this results in a defined fluid delivery, so that standing oil is effectively avoided.
- the displacement takes place primarily through the centrifugal-related endeavor to form a fluid film that is as thin-walled and uniform as possible.
- the ribs can be uniformly high or can be designed to rise axially outward, that is to say in the direction of the respective rotor shaft end, ie the groove depth increases. Evenly rising ribs can begin axially closer to the impact hill, where there is still a greater difference between the shaft peripheral speed and the fluid film peripheral speed. The fluid film then spills - because of the longer path - thermally advantageous from one groove to the next until the relative speed has largely adapted.
- the channels defined by the ribs are, in particular, technically advantageous, spiral-shaped or, in terms of production technology, straight. Spiral channels have the advantage that the cooling fluid film is accelerated by the rotation and this creates a defined fluid delivery, so that standing cooling fluid is effectively avoided. In the case of straight-line channels or smooth inner walls, the displacement takes place primarily through the endeavor to form a fluid film that is as thin-walled and uniform as possible.
- a fluidic bypass is provided between the first inner wall section and the second inner wall section, in particular the resulting trough-shaped structure consisting of a wave shoulder, inner wall and impact hill on the one hand and impact hill inner wall and wave shoulder on the other.
- the fluidic bypass is formed by grooves in the rotor shaft or an annular impact hill designed as a separate part, in particular a part provided with axial external grooves.
- a fluidic bypass configured in this way is easy to produce in terms of production technology.
- the impact hill is provided with radially extending channels, the channels ending in particular in the fluidic bypass.
- the channels ending in particular in the fluidic bypass.
- a portion of the cooling fluid sprayed onto the impact hill can enter directly into the radially extending channels and thereby reach the respective inner wall sections via the fluidic bypass.
- the radially extending channels can in particular also be designed in the form of a continuous radial gap.
- the impact hill is designed in one piece with the rotor shaft or as a separate part, in particular as a ring made of a good heat-conducting material, preferably aluminum or copper.
- a one-piece design with the rotor shaft is particularly useful in connection with a two-part rotor shaft, since a central impact hill can be shaped well in terms of production technology.
- a separate configuration opens up, in particular, a selection of materials for the impact hill, which can differ from the material of the rotor shaft - generally steel - in particular with regard to their thermal conductivity.
- the impact hill has an ascending flank, a summit and a descending in the axial direction Has flank.
- the impact hill has a rising flank, a first peak, a depression, a second peak and a descending flank.
- the second variant in particular is able to “catch” the fluid jet even better if there are deviations due to dynamic effects.
- This shape of the impact hill also means that the cooling fluid that is incident is distributed approximately evenly to both sides even when it does not hit the center.
- Another object of the present invention is to provide an improved electrical machine, in particular to propose an electrical machine whose internal rotor cooling is less sensitive to the position of the electrical machine in space.
- the electrical machine is installed in a motor vehicle.
- the aim is to ensure that the cooling fluid distribution is as uniform as possible in all driving situations, in particular in the event of an imbalance, centrifugal forces when cornering, etc.
- this object is achieved by an electrical machine with the characterizing features of claim 15. Because the electrical machine has a rotor device according to at least one of the preceding claims, the advantages of the rotor device outlined above can be used for the electric motor.
- Fig. 1 shows an electrical machine according to the invention with an inventive
- Fig. La is an enlarged section of Fig. 1;
- FIG. 3 shows a rotor shaft with a fluid lance of a rotor device according to the invention with an indicated flow course of the cooling fluid
- Fig. 4 shows a variant of a rotor shaft with a fluid lance of an inventive
- Fig. 5 shows a variant of a rotor shaft with a fluid lance of an inventive
- Rotor device with indicated flow of the cooling fluid; 6a) -d) cross-sectional representations through the rotor shaft according to sections A to D from FIG. 5;
- Fig. 7 shows a variant of a rotor shaft with a fluid lance of an inventive
- Fig. 9 shows a variant of a rotor shaft with a fluid lance of an inventive
- FIG. 9a shows a cross-sectional view through the rotor shaft according to section A from FIG. 9;
- FIG. 10 shows the rotor shaft with a fluid lance of a rotor device according to the invention
- FIG. 11 shows a variant of a rotor shaft with a fluid lance according to the invention
- FIG. 11a shows an enlarged detail from FIG. 11
- Fig. 14 is an annular impact hill as a single part in a perspective view.
- Fig. 15 an annular impact hill as used from two mirror-symmetrical
- a rotor device essentially comprises a rotor R with a rotor shaft 1 and a rotor pack 2.
- the rotor pack 2 generally consists of a number of rotor plates which are connected to the rotor shaft 1 in a twisted test.
- the rotor shaft 1 is an at least partially hollow shaft, preferably a hollow shaft.
- the rotor device according to the invention comprises a fluid lance 3 for internal rotor cooling.
- An electrical machine according to the invention in particular an electric motor, essentially comprises a stator S and the rotor device according to the invention.
- the electrical machine can also be an electrical generator.
- the rotor shaft 1 is an at least partially hollow shaft, preferably a hollow shaft.
- the rotor shaft has an axis of rotation or longitudinal axis 11.
- the rotor shaft 1 also has an inner wall 12.
- the fluid lance 3 is essentially an elongated tube which is inserted laterally into the rotor shaft 1. In the ideal case, the longitudinal axis 31 of the fluid lance 3 runs in the longitudinal axis 11 of the hollow shaft 1.
- the fluid lance 3 is closed on one end, but is provided in the region of this end with a radial fluid outlet opening 32, preferably a conical bore.
- the fluid outlet opening 32 is preferably designed with a throttling effect and / or has an additional throttling element. The exit speed of the cooling fluid can thereby be increased.
- the fluid lance 3 used here is preferably a standing fluid lance.
- the speed difference between impact hill 4 and fluid is higher than when a co-rotating fluid lance is used.
- the use of a rotating fluid lance is also conceivable.
- the inner wall 12 of the rotor shaft 1 is equipped with an impact hill 4.
- the impact hill 4 is basically designed as an elevation with respect to the inner wall 12.
- the impact hill 4 usually extends over the circumference of the inner wall.
- the impact hill 4 is preferably designed as an annular elevation.
- the impact hill 4 is arranged approximately in the middle, preferably in the middle, of the rotor shaft 1.
- the impact hill divides the inner wall 12 into a first inner wall section 12a and a second inner wall section 12b.
- the impact hill 4 is preferably designed as a separate part, in particular as a press-in part.
- the impact hill 4 can thus be placed independently of other tolerance chains (e.g. in the case of a rotor shaft assembled / rotationally welded from two half shafts; positioning tolerance of the fluid lance, etc.).
- the impact hill 4 can also be manufactured independently.
- the impact hill 4 is preferably made of a good heat-conducting material such as copper or aluminum. It is preferably inserted into the hollow shaft by thermal joining.
- An impact hill as a separate insert or press-in part is shown by way of example in FIGS. 13, 14 and 15.
- the impact hill is made as a one-piece ring, the ring being cut for illustration in order to illustrate the cross section.
- the impact hill is designed as two identical, but mirror-replaceable and axially spaced-apart ring parts, the spacing forming a continuous radial gap.
- Fluid drain openings 13 are preferably provided in the rotor shaft 1, in particular at the end, but at least axially spaced from the impact hill 4.
- a first fluid drain opening 13a is provided in the region of the first axial end and a second fluid drain opening 13b in the region of the other axial end of the rotor shaft 1, or a first fluid drain opening 13a is in the first inner wall section 12a and a second fluid drain opening 13b in the second inner wall section 12b arranged.
- the fluid drain openings 13 are preferably radial bores in the rotor shaft 1.
- the impact hill 4 has an ascending flank 41, a summit 42 and a descending flank 43 in the axial direction.
- Cooling fluid flows into the fluid lance 3 and is directed out of the fluid outlet opening 32 in the direction of the impact hill 4.
- the cooling fluid is preferably discharged from the fluid lance as a compact fluid jet.
- the fluid outlet opening 32 of the fluid lance 3 is ideally positioned in such a way that cooling fluid emerging here meets the summit 42 of the impact hill 4.
- the impact hill prevents or reduces a standing boundary layer: the fluid jet preferably hits the impact hill directly; it is not distracted by a boundary layer above it.
- the cooling jet preferably strikes the surface of the impact hill perpendicularly.
- the fluid jet is divided to a certain extent by the impact hill 4 and part of the fluid flows out via the first inner wall section 12a in the direction of the first fluid drain opening 13a, while the other part of the fluid flows out via the second inner wall section 12b in the direction of the second fluid drain opening 13b.
- the rotor shaft of the rotor device is configured as an assembled and / or rotationally welded rotor shaft. It is essential here that the rotor shaft is composed of two parts, in particular a first rotor half-wave la and a second rotor half-wave lb. This can facilitate, for example, the introduction or also shaping of the impact hill 4 into the center of the rotor shaft, for example if the impact hill 4 is introduced before the rotor half-waves 1 a, 1 b are connected.
- FIG. 3 An example of such an embodiment is shown in FIG. 3.
- the rotor device in particular the rotor shaft R, is equipped with shaft shoulders 14.
- a shaft shoulder is a shoulder between a larger inner rotor shaft diameter and a smaller inner rotor shaft diameter. The transition is not abrupt, but is designed over a transition region in which the diameter decreases.
- a first wave shoulder 14a is preferably arranged between the impact hill 4 and the first fluid drain opening 13a, in particular immediately in front of the first fluid drain opening 13a, and a second wave shoulder 14b between the impact hill 4 and the second fluid drain opening 13b, in particular immediately in front of the second fluid drain opening 13b.
- the hollow shaft forms a bath between the impact hill 4 and the respective fluid drain opening.
- the wave shoulders 14 act as a retaining dam.
- the thickness of the fluid film can be adjusted by the height of the shaft shoulders 14 above the inner wall 12. Furthermore, it is possible to delay the throughput time of the cooling fluid, so that the cooling fluid flows away too quickly and the heat absorption capacity of the cooling fluid can be better utilized.
- the fluid outflow openings 13, in particular their diameter or possible variances in different fluid outflow openings, are eliminated as an influencing factor for the outflow speed of the cooling fluid from the hollow shaft. The flow rate of the cooling fluid is not changed by the shape of the fluid drain openings.
- shaft shoulders 14 are advantageous in the case of asymmetrically acting force components, in particular when cornering or when the rotor axis is tilted, since the fluid cannot flow freely to one side, but is applied to a shaft shoulder 14a or 14b and an obliquely positioned fluid film is formed, which is formed on both sides 12a, 12b of the rotor inner wall extends.
- This effect is especially at low rotational speeds, in particular ⁇ 500 / min, of importance, at which the centripetal forces are not yet dominant and cannot force a uniform fluid film thickness.
- An example of such an embodiment is shown in FIG. 4.
- the inner wall 12a or 12b is not smooth, but is structured.
- Axial ribs 121 are suitable as structures.
- the ribs can have a rectangular cross section.
- the grooves formed between two ribs can be rectangular.
- the inner profile of the hollow shaft thus represents a continuous rectangular function.
- the ribs can also have a wave-shaped cross section.
- the grooves can be correspondingly wave-shaped.
- the contour of the inner profile of the hollow shaft then represents an approximately sinusoidal course.
- FIGS. 12a and 12e can be used to illustrate rectangular or wavy ribs or grooves.
- the ribs 121 have a surface-enlarging effect.
- the channels defined by the ribs 121 are, in particular, technically advantageous, spiral-shaped or, in terms of production technology, straight. Spiral channels have the advantage that the cooling fluid film is accelerated by the rotation and a defined fluid delivery is created, so that standing oil is effectively avoided. In the case of straight-line channels or smooth inner walls, the displacement takes place primarily through the endeavor to form a fluid film that is as thin-walled and uniform as possible.
- the ribs 121 can be uniformly high or can rise axially outwards, i.e. in the direction of the respective rotor shaft end, i.e. the groove depth increases.
- the inner wall of the shaft can also have a microstructuring, e.g. by sandblasting or the introduction of small craters (dimples).
- the microstructuring can also be introduced, for example, in the form of an embossing process, in particular when manufacturing the hollow shaft by means of an internal mandrel.
- FIGS. 5 to 8 Examples of such embodiments are shown in FIGS. 5 to 8, in particular constantly high ribs, without rising, starting at a distance from the impact hill in FIG. 5 or Fig. 6. Rising ribs with twist are shown for example in Fig. 7 or 8. Here, too, the ribs begin at an axial distance from the impact hill 4.
- a fluidic bypass 44 is provided between the first inner wall section 12a and the second inner wall section 12b or the resulting trough-shaped structure consisting of shaft shoulder 14a, inner wall 12a and impact hill 4 on the one hand, and impact hill 4 inner wall 12b and shaft shoulder 14b on the other hand is.
- fluidic bypass 44 is meant a fluidic connection that is not formed by the interior of the ring-shaped impact hill 4. Rather, this means a fluidic connection which is formed by separate passage openings which are formed, for example, by grooves in the rotor shaft or the annular impact hill designed as a press-in part.
- an initial unequal distribution of cooling fluid can be compensated for, since the cooling fluid tends to form a uniformly thick fluid film due to the rotation-related circumferential forces.
- An unequal distribution can e.g. Be the result of a non-central impact hill 4 or a deflection of the exit jet due to centrifugal force when cornering.
- FIGS. 9 and 10 An example of such an embodiment is shown in FIGS. 9 and 10, in FIG. 10 with the inclined position indicated.
- the impact hill 4 is provided with radially extending channels 45.
- This embodiment is generally only used if the above-mentioned fluid bypass 44 is provided.
- the radially extending channels 45 then open into the axially extending bypass channels 44.
- a corresponding exemplary embodiment is shown in FIG. 14 in the form of a separate impact hill 4.
- the radially extending channels 45 can also be designed as a continuous radial gap.
- the impact hill can be designed as a separate insert in the form of two identical ring parts which are to be inserted in the hollow shaft in a mirror-inverted manner.
- the rings can be symmetrical or asymmetrical, but the former simplifies assembly without misunderstanding, since the latter must be installed in a direction-dependent / mirrored manner.
- the axial distance between the ring parts determines the width of the ring gap.
- the gap between the rings positioned next to each other in a mirrored manner depends on the configuration of the oil jet from the lance and must be set accordingly with a spacer ring / washer.
- An embodiment with two axially asymmetrical rings is shown in FIG. 15.
- two identical rings spaced apart from one another could also be used, with a fluidic bypass (compensation channel) as Outer circumferential groove in the rings itself analogous to FIG. 14 or as an inner circumferential groove of the hollow rotor shaft analogous to FIG. 12a,
- the diameter of the radial channels 45 is smaller than the fluid jet emerging from the fluid lance 3 or its fluid outlet opening 31 or impinging on the impact hill 4, so that the majority of the cooling fluid is deflected to both sides via the impact hill 4.
- the radial channels 45 are so deep that spray formation is prevented.
- the fluid jet impinging in the axial bypass channels 44 is forced directly to the full circumferential speed by the side walls of the bypass channels 44, as a result of which it is shredded. Since the spray mist has no space for spreading, but instead settles immediately on the walls of the bypass channels 44 or is carried away by the subsequent fluid flow, spray mist formation is effectively prevented.
- the impact hill 4 can also be advantageously designed with a depression 46 on the impact hill.
- the impact hill thus has a cross section which is characterized by the following sequence along the longitudinal axis: a rising flank 41, a first summit 42a, a trough 46, a second summit 42b and a descending flank 43.
- This shape of the impact hill the impinging cooling fluid is distributed approximately evenly on both sides even when it is not centered. This can in particular also reduce the influence of positioning errors between the fluid lance and the impact hill caused by production.
- Embodiments according to the invention are shown, for example, in FIGS. 11 or 14.
- the bump may be integral with the shaft, e.g. hammered.
- the impact hill can be designed as a separate press-in part.
- the inner profile of the shaft or parts of the inner profile can be hammered.
- the macro-structuring in the form of the inner wall, the impact hill, the ribs or grooves and shaft shoulders can be included in the inner profile.
- the microstructuring (surface design or enlargement, for example by craters) can also be carried out by stamping or hammering.
- the rotor shaft can be assembled, in particular from two half-waves welded together (rotationally).
- the half-waves can in particular be made unequal, so that the impact hill is completely formed in a half-wave.
- the impact hill 4 divides the fluid flow symmetrically on the left and right sides.
- the center-symmetrical cooling distribution is largely insensitive to positional tolerances. Mounting the fluid lance slightly eccentrically, i.e. axially displaced relative to the center of the impact hill, is largely without consequences.
- the cooling functions perfectly even when the vehicle is in an inclined position in which the rotor device or electrical machine according to the invention is mounted, in particular when the vehicle is rotated about the longitudinal axis or cornering.
- the cooling works well even at low fluid pressure, since no high exit speeds at the fluid lance are necessary to penetrate a fluid film or boundary layer of the cooling fluid present at the point of impact. In particular, no standing fluid film can form due to the impact hill, so that a boundary layer of the cooling fluid is not present or is greatly reduced. This allows the pressure of the cooling system to be reduced compared to the standard.
- a typical field of application of the invention is the implementation in vehicles with at least one electrical machine as the drive.
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 |
---|---|---|---|
DE102018221569.3A DE102018221569A1 (en) | 2018-12-12 | 2018-12-12 | Rotor device for an electrical machine and electrical machine |
PCT/EP2019/084708 WO2020120603A1 (en) | 2018-12-12 | 2019-12-11 | Rotor device for an electric machine and electric machine |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3895288A1 true EP3895288A1 (en) | 2021-10-20 |
Family
ID=69024248
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19828234.5A Pending EP3895288A1 (en) | 2018-12-12 | 2019-12-11 | Rotor device for an electric machine and electric machine |
Country Status (5)
Country | Link |
---|---|
US (1) | US20220060072A1 (en) |
EP (1) | EP3895288A1 (en) |
CN (1) | CN113597731B (en) |
DE (1) | DE102018221569A1 (en) |
WO (1) | WO2020120603A1 (en) |
Families Citing this family (21)
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---|---|---|---|---|
DE102020210222A1 (en) | 2020-08-12 | 2022-02-17 | Volkswagen Aktiengesellschaft | Rotor shaft for a rotor of an electrical machine with a fluid conducting part and fluid conducting part for a rotor shaft |
CN111969791B (en) * | 2020-08-18 | 2021-12-03 | 中国第一汽车股份有限公司 | Oil-water mixed cooling motor system and vehicle |
DE102020121663A1 (en) * | 2020-08-18 | 2022-02-24 | Nidec Motors & Actuators (Germany) Gmbh | Motor shaft arrangement with motor shaft and inlet pipe |
CN111917210B (en) * | 2020-08-24 | 2021-07-27 | 浙江向阳齿轮机电有限公司 | Motor rotor and motor |
DE102021200118A1 (en) | 2020-12-10 | 2022-06-15 | Robert Bosch Gesellschaft mit beschränkter Haftung | Electrical machine and transmission |
DE102021200121A1 (en) | 2020-12-10 | 2022-06-15 | Robert Bosch Gesellschaft mit beschränkter Haftung | Electrical machine and transmission |
DE102021200117A1 (en) | 2020-12-10 | 2022-06-15 | Robert Bosch Gesellschaft mit beschränkter Haftung | Electrical machine and transmission |
DE102021200120A1 (en) | 2020-12-10 | 2022-06-15 | Robert Bosch Gesellschaft mit beschränkter Haftung | Electrical machine and transmission |
DE102020007864A1 (en) * | 2020-12-21 | 2021-03-04 | Daimler Ag | Hollow shaft for a rotor of a machine of a motor vehicle, and method |
GB202103793D0 (en) * | 2021-03-18 | 2021-05-05 | Cummins Inc | Cooling a rotating electrical machine |
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2018
- 2018-12-12 DE DE102018221569.3A patent/DE102018221569A1/en active Pending
-
2019
- 2019-12-11 WO PCT/EP2019/084708 patent/WO2020120603A1/en unknown
- 2019-12-11 EP EP19828234.5A patent/EP3895288A1/en active Pending
- 2019-12-11 US US17/312,815 patent/US20220060072A1/en active Pending
- 2019-12-11 CN CN201980083106.3A patent/CN113597731B/en active Active
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WO2020120603A1 (en) | 2020-06-18 |
CN113597731B (en) | 2024-06-14 |
DE102018221569A1 (en) | 2020-06-18 |
US20220060072A1 (en) | 2022-02-24 |
CN113597731A (en) | 2021-11-02 |
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