Rotor assembly with motor

Abstract

The invention relates to a rotor assembly (1) comprising a rotor body (2) which forms a plurality of slots (3) in axial direction for accommodating windings (4), rotor poles (5) which are formed in radial direction between each two slots (3), windings (4) which are arranged in the slots (3) and which surround the rotor poles (5), slot closure elements (6) which close the slots (3) in radial direction, at least one spacer (7) which is arranged in circumferential direction between two windings (4) in a slot (3), wherein the spacer (7) comprises at least one continuous cooling channel (8) which extends in axial direction and which can be flowed through by a cooling medium, wherein a filling body (11) made of a non-ferromagnetic material is provided in the cooling channel (8) and the filling body (11) has cooling fins (12) which protrude from its surface towards an inner wall (19) of the spacer (7).

Description

[0001] This invention relates to a rotor assembly comprising a rotor body having a plurality of slots formed axially to accommodate windings, rotor poles formed radially between each pair of slots, windings arranged in the slots and surrounding the rotor poles, slot closure elements closing the slots radially, and at least one isolator arranged circumferentially between two windings in the slots, wherein the isolator includes at least one axially extending continuous cooling channel through which a cooling medium may flow. The invention also relates to an electric motor.

[0002] In motor vehicles, electric motors are increasingly being used as drive systems to replace internal combustion engines that require fossil fuels. Significant efforts have been made to improve the everyday usability of electric drives and provide users with a familiar driving experience.

[0003] When developing motors for applications such as E-axis or hybrid modules, there is a persistent need to increase power density and efficiency while reducing manufacturing costs. Against this backdrop, it is also known to design motors as externally excited synchronous motors (FSMs). An externally excited synchronous motor is a special type of synchronous motor in which the magnetic field in the rotor is not generated by permanent magnets, but by energized coils. These coils are often referred to as field coils or excitation coils. To power the coils in the rotating rotor, current must be supplied through a suitable transmission device.

[0004] Due to manufacturing processes, gaps may occur between every two sets of excitation windings in the rotor. In particular, supports or isolators are inserted, which completely or largely fill these gaps. Especially in high-speed applications, the isolators prevent accidental movement of the excitation coil windings in a centrifugal force field. EP 1 494 335 B1 discloses a corresponding isolator disposed between adjacent excitation coils.

[0005] Especially in terms of improving power density and efficiency, it is particularly necessary to cool the rotor and dissipate heat when the externally excited synchronous motor is running. For example, air-cooled rotors or fluid-cooled hollow shafts are known in the prior art. DE102018220810A1 discloses a fluid-cooled rotor for an electric motor, as well as an externally excited synchronous motor with directly or near-loss-cooled rotor windings. EP3618241A1 discloses a fluid-cooled hollow shaft with tapered walls.

[0006] The objective of this invention is to provide a device suitable for discharging heat energy from the rotor of an externally excited synchronous motor, which has a compact structure and high operational safety.

[0007] This task is achieved by a rotor assembly comprising a rotor body having a plurality of slots formed axially to accommodate windings, rotor poles formed radially between each pair of slots, windings arranged in the slots and surrounding the rotor poles, slot closure elements closing the slots radially, and at least one isolator arranged circumferentially between two windings in the slot, wherein the isolator includes at least one axially extending continuous cooling channel through which a cooling medium flows, wherein a filler made of a non-ferromagnetic material is disposed in the cooling channel, and the filler has cooling fins protruding from its surface toward the inner wall of the isolator.

[0008] The advantage of this solution lies in its ability to dissipate heat losses caused by heat conduction elements as close as possible to their point of origin. This significantly improves the rotor's speed stability, thermal performance, efficiency, and available torque density, representing an improvement over existing technologies.

[0009] The insulator and the filler with cooling fins provide a particularly large surface area relative to the cooling medium within the cooling channel, enabling excellent heat transfer to the cooling medium. Furthermore, the cooling medium is preferably guided near the outer contour of the insulator, which also helps to enhance heat transfer to the cooling medium.

[0010] According to a preferred embodiment of the present invention, the cooling fins and the filler can be integrally formed, preferably as a single-piece structure. The advantage of this embodiment is that it enables particularly good heat transfer and allows the cooling fins to be formed in a particularly advantageous manufacturing manner.

[0011] Cooling fins can optimize heat transfer from the filler and insulator to the cooling medium by increasing the surface area. Cooling fins can be embedded in the filler, for example, through extrusion or pressing processes.

[0012] Preferably, the cooling fins have a constant cross-section in the axial direction. Furthermore, the cooling fins preferably maintain a substantially constant radial distance from the axis of rotation in the axial direction.

[0013] The advantage of this embodiment is that the structure of the cooling fins avoids the pumping effect caused by the rotational speed and direction of rotation when the cooling fins extend into the cooling channels. Furthermore, this structure allows for the manufacture of the filler via extrusion and / or injection molding processes. More preferably, the cooling fins have substantially the same geometry, which is particularly advantageous in manufacturing and simplifies the modeling of heat transfer.

[0014] In principle, it can also be envisioned that the insulator also has cooling fins that extend from the inner wall of the insulator toward the filler.

[0015] According to one embodiment, a cavity is formed within the slot, defined by the winding and the isolator, and the cavity is filled with a potting material. An advantage of this embodiment is that the potting material within the cavity improves the thermal connection between the winding and the isolator. The cavity is formed due to manufacturing tolerances of the winding and the isolator.

[0016] According to one embodiment, the cooling medium is a coolant. The advantage of this embodiment is that, compared to gas, the coolant has a higher heat capacity and higher thermal conductivity, thus enabling better cooling or removal of heat losses. In particular, the coolant may contain oil and / or water.

[0017] According to one embodiment, the rotor body has a laminated structure. The advantage of this embodiment is that it can minimize eddy current losses in the rotor body.

[0018] The isolator is preferably made of a non-ferromagnetic material to avoid affecting the electromagnetic function of the rotor or motor. The isolator is preferably at least partially made of a material with good thermal conductivity to achieve a good thermal connection between the rotor windings and the cooling medium. Here, the isolator can be manufactured using aluminum extrusion, plastic extrusion, or plastic injection molding processes. This allows for a hollow interior but sealed exterior structure, enabling the cooling medium to be guided and maintaining a seal even under high pressure.

[0019] Therefore, the isolator essentially provides two functions. On the one hand, the isolator helps to fix the winding within the slot under centrifugal force; on the other hand, it enables fluid-based cooling within the slot through cooling channels. Thus, the rotor winding achieves stable speed support and simultaneous cooling through this isolator.

[0020] Preferred embodiments of the present invention According to a preferred embodiment of the invention, the filler may be provided with a fastener on at least one front end face, by which the filler is connected to an axially adjacent component. The advantage of this embodiment is that the filler can be securely fixed in a predetermined position relative to the isolator. The fastener also allows for modular assembly of the rotor assembly, resulting in a compact axial structure. Furthermore, the fastener helps the filler, and indirectly the isolator, withstand the high centrifugal forces exerted by the windings at rotational speeds and maintain shape stability under these external forces.

[0021] Fasteners can be selected from form-fit fasteners, force-fit fasteners and / or material-fit fasteners.

[0022] In one possible implementation, the fastener is a threaded structure, integrally formed with the filler, preferably an integral structure. Preferably, the thread protrudes from one front end face of the filler. It is also preferable to have a first thread protruding from a first front end face of the filler, and a second thread protruding from a second front end face of the filler. Preferably, the fastener is a threaded profile. Here, it is particularly preferred that the profile at least partially passes through the filler and protrudes from one front end face of the filler. It is particularly preferred that the profile completely passes through the filler and protrudes from both front end faces of the filler respectively. The profile can be rotatably or fixedly disposed within the filler. Further preferably, only the portion of the profile protruding from one front end face of the filler is threaded. It is also preferable that the profile has a substantially circular cross-sectional profile.

[0023] The fastener may also be an internal thread formed within the filler, integrally molded with the filler, preferably an integral structure. Preferably, the internal thread extends into a front end face of the filler. It is also preferable to provide a first internal thread extending to a first front end face of the filler, and a second internal thread extending to a second front end face of the filler.

[0024] According to another preferred embodiment of the present invention, the fastener may also be a sleeve with internal threads, which is rotatably and fixedly inserted into the filler body. Preferably, a first sleeve is inserted into a first front end face of the filler body, and a second sleeve is inserted into a second front end face of the filler body.

[0025] In principle, fasteners can also be designed to connect to axially adjacent components through deformation. For example, a riveting boss can be used.

[0026] According to another preferred improvement of the invention, a fluid inlet element can be connected to the first axial end of the cooling channel, and a fluid outlet element can be connected to the second axial end, allowing the cooling medium to flow into the cooling channel through the fluid inlet element and out of the cooling channel through the fluid outlet element. This enables a particularly advantageous connection between the isolation element and the cooling circuit. Preferably, the fluid inlet element and the fluid outlet element are substantially identical in structure.

[0027] The isolator has an inner wall region at at least one axial end designed to form a smooth inner profile along its axial length (preferably up to 15 mm). This region can also be post-processed by machining. An inlet or outlet element for the cooling medium is then inserted into this region. The inlet and / or outlet elements can be connected to the isolator by bonding, welding, press fitting, and / or form fitting. In a preferred embodiment, the inlet or outlet element is sealed to the isolator by a seal (such as an O-ring). This creates a sealed assembly for the cooling medium, each assembly inserted between two rotor coils but substantially not exceeding the axial length of the rotor coils, thus these assemblies do not significantly increase the axial length of the rotor.

[0028] Preferably, the inlet element and / or outlet element are provided with openings and / or channels for guiding the cooling medium to flow axially and / or radially, thereby transforming the shape of the openings inside the isolator into a shape suitable for guiding the cooling medium to adjacent components.

[0029] Furthermore, according to another preferred embodiment of the invention, adjacent components can be configured as fluid inlet elements or fluid outlet elements, thereby enabling a particularly compact rotor assembly structure in the axial direction.

[0030] According to another particularly preferred embodiment of the invention, the inner wall of the isolator can be configured as a planar structure in the region of the protruding cooling fins of the filler, which is particularly advantageous in manufacturing. In this context, it is conceivable that the isolator be manufactured using a forming process (e.g., forming from sheet metal). When the isolator is manufactured using an extrusion process, the simplified geometry also particularly advantageously reduces manufacturing costs.

[0031] Furthermore, the invention can be further improved such that the fluid inlet element and / or fluid outlet element are at least partially inserted into the isolator and conform to the inner wall of the isolator. This achieves a high degree of sealing between the fluid inlet element and / or fluid outlet element and the isolator. This structure has also proven particularly advantageous in absorbing and supporting centrifugal forces during rotor assembly operation.

[0032] In another preferred embodiment of the invention, the fluid inlet element and / or fluid outlet element may each have a hydraulic channel for guiding the cooling medium to flow radially. It can also be advantageously further modified so that the fluid inlet element and / or fluid outlet element each have a hydraulic channel for guiding the cooling medium to flow axially. This forms a channel system through which the cooling medium can be selectively guided into and / or drawn out of the isolator. The hydraulic channel may include open or closed channels, inlet surfaces, centrifugal sections, and / or free-fall sections.

[0033] In a further preferred embodiment, the inlet element and / or outlet element each have an axial opening. This allows the cooling medium to be guided through the respective axial openings to components axially adjacent to the inlet element and / or outlet element. In yet another preferred embodiment, the outlet element may have an axial opening through which the cooling medium is thrown out of the rotor during operation and directed radially outwards towards the stator components, thereby achieving additional cooling of the stator components.

[0034] According to one embodiment, the rotor assembly includes a rotor shaft that is hollow and has radial openings for guiding cooling medium.

[0035] According to another preferred embodiment of the present invention, a fluid inlet element and / or a fluid outlet element may be respectively connected to a rotor shaft configured as a hollow shaft, so that the cooling medium can flow from the rotor shaft into the fluid inlet element and / or from the fluid outlet element into the rotor shaft.

[0036] Preferably, the fluid inlet element and / or fluid outlet element each have radial openings that connect to corresponding radial openings in the rotor shaft. Most preferably, the radial openings of the fluid inlet element and / or fluid outlet element are sealed to the radial openings of the rotor shaft by seals. This allows the cooling medium to be guided from the rotor shaft to the isolator, or from the isolator to the rotor shaft, without integrating the guidance of the cooling medium into the axial rotor housing components, thus saving axial space. The radial openings of the rotor shaft are connected to the cooling channels of the isolator via the fluid inlet element and / or fluid outlet element, thereby forming a channel system, such as... Figure 4 As shown.

[0037] Therefore, in a preferred embodiment of the invention, the cooling channels can be connected to the cooling system via a channel system. Particularly advantageously, the cooling channels are connected to the cooling system at both front ends via corresponding components, preferably fluid inlet elements and / or fluid outlet elements, thereby forming a closed cooling loop. Finally, the invention can also advantageously be implemented such that the filler has fasteners on its first front end face to connect the filler to an axially adjacent component, and that the filler has fasteners on its second front end face to connect the filler to an axially adjacent component.

[0038] In another preferred embodiment of the invention, the isolator may be provided with an electrically insulating layer at least partially on its outer wall. This electrically insulating layer may be, for example, an electrically insulating coating. It is also conceivable that the electrically insulating layer is a separate component, detachably or fixedly connected to the isolator. In this way, the isolator can achieve electrical insulation from live parts, particularly preventing electrical contact between excitation coils or between the excitation coils and the vehicle, thereby meeting high-voltage safety requirements. The coating can be achieved by painting, covering, or adhesive application. For less stringent electrical insulation requirements, the aluminum isolator can be anodized. For higher requirements, it can be covered with plastic, coated with an alternative material, or a thin film can be applied to the contact surface with the rotor coils. This ensures that no electrical short circuits are formed between the excitation coils or between the excitation coils and the vehicle.

[0039] According to another preferred embodiment of the invention, the spacer may be provided with a length greater than that of the filler. Particularly preferred is that the filler is completely contained within the spacer and does not protrude axially from the spacer. Most preferred is that the filler is recessed at one front end face of the spacer. Most preferably, the filler is recessed relative to the spacer at both front end faces.

[0040] The isolator is preferably connected to a slot closure element, which radially closes the slot and provides stable rotational support for the support body. The slot closure element is preferably made of a non-ferromagnetic and non-conductive material (such as plastic), thus not affecting the electromagnetic performance of the motor or generating additional eddy current losses in this component. The slot closure element can be manufactured using plastic injection molding or extrusion processes and connected to the isolator by form-fitting or adhesive bonding. Alternatively, the slot closure element can be directly injection molded onto the isolator. In this case, the slot closure element can be integrally molded with the plastic overlay of the isolator.

[0041] The present invention can also be advantageously implemented as an integral connection between the slot closure element and the isolator.

[0042] The advantage of this structure is that, through integral connection, the slot closure element and the isolator can be manufactured as a single component, thereby reducing the complexity of the rotor assembly. Another advantage is that the integral connection provides more stable components. Particularly preferred is that the slot closure element and the isolator are of a monolithic structure, for example, made of aluminum or plastic.

[0043] In another preferred embodiment of the invention, the isolator may also be made of aluminum. The isolator is preferably manufactured using an aluminum extrusion process. The material properties of aluminum allow for good mechanical properties and good thermal conductivity within the isolator. Since aluminum is non-ferromagnetic, it does not affect the electromagnetic function of the motor. Alternatively, the isolator can be manufactured using a plastic extrusion process, but its thermal conductivity is typically lower.

[0044] Furthermore, the invention can be further improved such that at least two cooling channels are separated from each other by ribs extending tangentially along the cross-section of the isolator. Inside the isolator, such ribs help maintain shape stability under high external centrifugal forces. Therefore, the isolator can also withstand the centrifugal forces of surrounding components without undergoing critical deformation.

[0045] The external cross-sectional profile of the isolator can also be non-rectangular. Preferably, the cross-sectional profile of the isolator is designed to minimize the distance between the winding and the isolator. For example, it can be envisioned that the isolator has a trapezoidal segment at its radially outer end, with a rectangular segment connecting radially inward at its short side. This further optimizes heat transfer from the winding to the isolator, since the thermal conductivity of the potting material that typically fills the cavity between the winding and the isolator is lower than that of the isolator.

[0046] According to another preferred improvement of the invention, the isolation body may include multiple cooling channels spaced apart from each other in the radial and / or circumferential directions. This structure is advantageous in that it enables better cooling or heat dissipation. Another advantage is that the multiple spaced cooling channels allow for more uniform cooling or heat dissipation.

[0047] The object of the invention is also achieved by an electric motor, particularly suitable for motor vehicle powertrain systems, including a rotor assembly according to any one of claims 1-12. The invention will now be described in more detail with reference to the accompanying drawings, but this is not intended to limit the general concept of the invention. Attached Figure Description Attached image description: Figure 1 : Segmented cross-sectional view of the rotor assembly Figure 2 : A detailed cross-sectional view of the rotor assembly implementation. Figure 3 Exploded view of the rotor assembly's isolator and its adjacent components. Figure 4 : Axial cross-sectional view of the rotor assembly Figure 5 : A schematic diagram of a motor vehicle equipped with an electric drive system.

[0049] Figure 1 A rotor assembly 1 is shown, comprising a rotor body 2 having a plurality of slots 3 formed axially to accommodate windings 4, and rotor poles 5 formed radially between each pair of slots 3. The rotor assembly 1 also includes windings 4 arranged in the slots 3 and surrounding the rotor poles 5. The slots 3 are radially closed by slot closure elements 6. The slot closure elements 6 may, in particular, be integrally formed with an isolator 7.

[0050] The rotor assembly 1 also includes isolators 7, each isolator 7 arranged circumferentially between two windings 4 in the slot 3. Each isolator 7 includes at least one axially extending continuous cooling channel 8 through which a cooling medium can flow. A filler 11 made of a non-ferromagnetic material is disposed within the cooling channel 8. The filler 11 has cooling fins 12 protruding from its surface toward the inner wall 19 of the isolator 7, these cooling fins 12 being integrally formed with the filler 11. The inner wall 19 of the isolator 7 has a planar structure in the region where the cooling fins 12 protrude from the filler 11, such as... Figure 2 As shown in the embodiment, the insulator 7 and the filler 11 with cooling fins 12 can thus provide a larger surface area for the cooling medium within the cooling channel 8 to achieve efficient heat transfer. Furthermore, the cooling medium can be guided along the optimal path of the outer contour of the insulator 7, which helps to improve the efficiency of heat transfer to the cooling medium. In the illustrated embodiment, the filler 11 has a two-part structure, including a filler portion with a rectangular cross-section and a body portion with a trapezoidal cross-section.

[0051] The isolator 7 essentially serves two functions. On one hand, it helps maintain the stability of the winding 4 in the slot 3 under centrifugal force; on the other hand, it enables liquid-based cooling within the slot through the cooling channel 8. Therefore, the rotor winding 4 is safely and firmly supported by the isolator 7, while simultaneously achieving efficient cooling.

[0052] exist Figure 2 In this embodiment, a connecting member 38 extends radially outward into the isolator 7 at the bottom of the groove 3 and forms a shape-fitting connection with it, thereby better supporting the centrifugal force generated during the operation of the rotor assembly.

[0053] Both the isolator 7 and the filler 11 have a trapezoidal cross-sectional section on the radially outer side, with a rectangular section connected to the radially inner side of the shorter side, facing the rotor shaft 46. In this embodiment, the cross-sectional profile of the isolator 7 or the filler 11 resembles a key. The filler 11 is therefore a two-part structure, with the trapezoidal section as the first part and the rectangular section as the second part, as shown below. Figure 1 and Figure 3 As shown. The isolator 7 forms radially outer and radially inner cooling channels 8 through ribs extending in the circumferential direction.

[0054] At least a portion of the outer wall 36 of the isolator 7 is provided with an electrical insulating layer 37, such as Figure 2 As shown. Insulating layer 37 can be as follows: Figure 2 The part shown is a single component, but it can also be a coating on the outer wall 36.

[0055] from Figure 3 It can be seen that the filler 11 has a fastener 31 on at least one front end face 30, through which the filler 11 is connected to the axially adjacent component 32.

[0056] exist Figure 3 In this embodiment, the fastener 31 is designed as a threaded structure and is integrally formed with the filler 11, preferably as a single piece. The thread protrudes from one front end face 30 of the filler 11. Figure 3 In the embodiment shown, the second thread, which serves as a fastener 34, protrudes from the opposite front end face 33 of the filler 11.

[0057] Fastener 31 is a threaded profile that completely passes through the filler 11 and protrudes from its front end face. The profile is rotated and fixed within the filler. As... Figure 3 As shown, only the protruding portions from the front faces 30 and 33 of the filler 11 are threaded. The profile has a basically circular cross-section. In the assembled state of the rotor assembly 1, the fastener 34 passes through the socket 48 of the fluid outlet element 43 and is locked by a nut. Similarly, the fastener 31 passes through the socket 47 of the fluid inlet element 41 and is also locked by a nut.

[0058] The adjacent component 32 serves as a fluid inlet element 41 on one side and a fluid outlet element 43 on the other. A fluid inlet element 41 is connected to the first axial end 40 of the cooling channel 8, and a fluid outlet element 43 is connected to the second axial end 42, so that the cooling medium can flow into the cooling channel 8 through the fluid inlet element 41 and flow out of the cooling channel 8 through the fluid outlet element 43.

[0059] The length of the separator 7 is greater than the length of the filler 11. The filler 11 is completely contained within the separator 7 and does not protrude axially from the separator, but rather recedes relative to the separator 7 at both front end faces. Figure 3-4 As can be seen from the combination, the fluid inlet element 41 and the fluid outlet element 43 are at least partially inserted into the isolator 7 and conform to the inner wall 19 of the isolator 7. The fluid inlet element 41 and the fluid outlet element 43 have profiles corresponding to the profile 49 of the inner wall 19 of the isolator 7.

[0060] The isolator 7 is designed with a uniform inner profile (preferably up to 15 mm) along its axial length in the inner wall region 19 at its axial ends 40, 42. These regions can be formed by machining processes. Within these regions, fluid inlet and outlet elements 41, 43 for the cooling medium are inserted during the assembly of the rotor assembly 1 and fixed within the isolator 7 by bonding, welding, press fitting, or form fitting. The fluid inlet and outlet elements 41, 43 can be sealed to the isolator 7 by seals (such as O-rings). This creates a sealed assembly for the cooling medium, which is inserted between every two windings 4 but does not significantly exceed the axial length of the windings 4 of the rotor assembly 1, thus not significantly increasing the axial length of the rotor assembly 1.

[0061] The fluid inlet and outlet elements 41 and 43 are internally provided with openings and / or channels to guide the cooling medium to flow axially and / or radially, thereby making the shape of the openings inside the isolator 7 suitable for guiding the cooling medium to adjacent components. The fluid inlet element 41 and the fluid outlet element 43 respectively have a hydraulic channel 44 for guiding the cooling medium to flow radially and a hydraulic channel 45 for guiding the cooling medium to flow axially, as shown below. Figure 4 As shown by the arrow in the image.

[0062] Fluid inlet element 41 and fluid outlet element 43 are respectively connected to the rotor shaft 46, which is configured as a hollow shaft, so that the cooling medium can flow from the rotor shaft 46 into the fluid inlet element 41 and from the fluid outlet element 43 into the rotor shaft 46. The fluid inlet element 41 and fluid outlet element 43 each have radial openings that connect to corresponding radial openings in the rotor shaft 46. In this way, the cooling medium can be guided from the rotor shaft 46 to the isolator 7, or from the isolator 7 to the rotor shaft 46, without integrating the guidance of the cooling medium into the axial rotor housing components, thus saving axial space. The radial openings of the rotor shaft 46 are connected to the cooling channels 8 of the isolator 7 via the fluid inlet element 41 and fluid outlet element 43, thereby forming a channel system, such as... Figure 4 As shown.

[0063] The filler 11 has a fastener 31 on its first front end face 30, through which the filler 11 is connected to the axially adjacent component 32; and the filler 11 has a fastener 34 on its second front end face 33, through which the filler 11 is connected to the axially adjacent component 35.

[0064] from Figure 1-4 The rotor assembly 1 shown can be used in particular for the motor 50, which is used in the power transmission system 51 of the motor vehicle 52, such as... Figure 5 As shown.

[0065] This invention is not limited to the embodiments shown in the accompanying drawings. The above description should not be considered restrictive but rather illustrative. The following patent claims should be understood as indicating that the described features are present in at least one embodiment of the invention. This does not exclude the presence of other features. If the patent claims and the above description define "first" and "second" features, such designations are used only to distinguish two features of the same type and do not indicate order or priority.

[0066] Explanation of reference numerals in the attached figures 1 Rotor assembly 2 Rotor body 3 slots 4 windings 5 rotor poles 6-slot closure element 7. Insulator 8 Cooling Channels 11. Filler 12 Cooling fins 19 Inner Wall 30 Front end 31 Fasteners 32 parts 33 Front end 34 Fasteners 35 parts 36 outer wall 37 Insulation layer 38 Connecting parts 40 end 41 Fluid inlet element 42 end 43 Fluid outlet element 44 Hydraulic Channel 45 Hydraulic Channel 46 Rotor shaft 47 sockets 48 sockets 49. Outline 50 motors 51 Powertrain System 52 Motor vehicles

Claims

1. A rotor assembly (1), comprising: - A rotor body (2) having multiple slots (3) formed in the axial direction to accommodate windings (4). - Rotor poles (5), which are formed radially between each pair of slots (3), - Winding (4), which is arranged in slot (3) and surrounds rotor pole (5). - A slot closing element (6) that closes the slot (3) in the radial direction. - At least one isolator (7) is arranged circumferentially between two windings (4) in a slot (3). - Wherein, the isolation body (7) includes at least one axially extending continuous cooling channel (8) through which a cooling medium can flow. Its features are, A filler (11) made of non-ferromagnetic material is provided in the cooling channel (8), and the filler (11) has cooling fins (12) protruding from its surface toward the inner wall (19) of the insulator (7).

2. The rotor assembly (1) according to claim 1, characterized in that, The filler (11) has a fastener (31) on at least one front end face (30) to connect the filler (11) to an axially adjacent component (32).

3. The rotor assembly (1) according to claim 1 or 2, characterized in that, A fluid inlet element (41) is connected to the first axial end (40) of the cooling channel (8), and a fluid outlet element (43) is connected to the second axial end (42) of the cooling channel (8), so that the cooling medium can flow into the cooling channel (8) through the fluid inlet element (41) and flow out of the cooling channel (8) through the fluid outlet element (43).

4. The rotor assembly (1) according to claim 3, characterized in that, The adjacent component (32) is a fluid inlet element (41) or a fluid outlet element (43).

5. The rotor assembly (1) according to any one of the preceding claims, characterized in that, The inner wall (19) of the isolator (7) is planar in the area of ​​the cooling fins (12) protruding from the filler (11).

6. The rotor assembly (1) according to any one of claims 3-5, characterized in that, The fluid inlet element (41) and / or fluid outlet element (43) are at least partially inserted into the isolator (7) and abut against the inner wall (19) of the isolator (7).

7. The rotor assembly (1) according to any one of claims 3-6, characterized in that, The fluid inlet element (41) and / or fluid outlet element (43) each have a hydraulic passage (44) for guiding the cooling medium to flow radially.

8. The rotor assembly (1) according to any one of claims 3-7, characterized in that, The fluid inlet element (41) and / or fluid outlet element (43) each have a hydraulic passage (45) for guiding the cooling medium to flow axially.

9. The rotor assembly (1) according to any one of claims 3-8, characterized in that, The fluid inlet element (41) and / or the fluid outlet element (43) are respectively connected to the rotor shaft (46) which is configured as a hollow shaft, so that the cooling medium can flow from the rotor shaft (46) into the fluid inlet element (41) and / or from the fluid outlet element (43) into the rotor shaft (46).

10. The rotor assembly (1) according to any one of claims 2-9, characterized in that, The filler (11) has a fastener (31) on its first front end face (30) to connect the filler (11) to an axially adjacent component (32); and the filler (11) has a fastener (34) on its second front end face (33) to connect the filler (11) to an axially adjacent component (35).

11. The rotor assembly (1) according to any one of claims 2-9, characterized in that, The insulator (7) has at least a partial electrical insulating layer (37) on its outer wall (36).

12. An electric motor (50), particularly for a power transmission system (51) of a motor vehicle (52), comprising a rotor assembly (1) according to any of the preceding claims.

Images