阅读说明：本技术 具有用于转子的多功能盘状元件的电机 (Electrical machine with a multifunctional disk element for the rotor ) 是由 T·克莱因 S·莱曼 A·特林肯舒 于 2019-12-04 设计创作，主要内容包括：本发明涉及一种用于机动车辆传动系的电机(1),该电机具有定子(2)、安装成相对于定子(3)旋转的转子(3)和接纳转子(3)以用于共同旋转的驱动轴(4),其中,除了转子(3),沿驱动轴(4)的轴向方向还布置有盘状元件(5),该盘状元件也连接至驱动轴(4)以用于共同旋转,并且该盘状元件由金属片材制成,盘状元件(5)具有可以由涡流传感器检测的发送器轮廓(6)和用于使冷却剂流朝向定子(2)偏转的冷却剂导引轮廓(7),并且盘状元件利用轴向预应力被按压抵靠在转子(3)的端面(8)上。(The invention relates to an electric machine (1) for a motor vehicle drive train, having a stator (2), a rotor (3) mounted for rotation relative to the stator (3) and a drive shaft (4) receiving the rotor (3) for co-rotation, wherein, in addition to the rotor (3), a disc element (5) is arranged in the axial direction of the drive shaft (4), which is also connected to the drive shaft (4) for co-rotation and is made of sheet metal, the disc element (5) has a transmitter contour (6) which can be detected by an eddy current sensor and a coolant guide contour (7) for deflecting the coolant flow towards the stator (2), and the disc element is pressed with an axial prestress against an end face (8) of the rotor (3).)

1. An electric machine (1) for a motor vehicle drive train, having a stator (2), a rotor (3) mounted for rotation relative to the stator, and a drive shaft (4) receiving the rotor (3) for co-rotation, a disc element (5) being arranged in the axial direction of the drive shaft (4) next to the rotor (3), the disc element being made of sheet metal and also connected to the drive shaft (4) for co-rotation, the disc element (5) having a transmitter contour (6) detectable by an eddy current sensor and a coolant guiding contour (7) for deflecting a coolant flow towards the stator (2), and being pressed with an axial prestress against an end face (8) of the rotor (3).

2. The electrical machine (1) according to claim 1, characterized in that the transmitter profile (6) has at least one window (9).

3. The electrical machine (1) according to claim 1 or 2, characterized in that the coolant guiding profile (7) is formed in a first section (10a) by a recess (11) on the side of the disc element (5) facing the rotor (3).

4. The electrical machine (1) according to any of claims 1 to 3, characterized in that the coolant guiding profile (7) is formed in the second section (10b) by at least one axial through hole (12).

5. The electrical machine (1) according to any of claims 1 to 4, characterized in that the stator (2) is arranged with at least one winding (13) radially outside the outlet (14) of the coolant guiding profile (7).

6. The electrical machine (1) according to any of claims 1 to 5, characterized in that at least one contact surface (15, 16) of the disc-shaped element (5) that axially rests on the rotor (3) is formed by a deformation (17) realized by a projection or deep drawing.

7. An electric machine (1) as claimed in claim 6, characterized in that the first contact surface (15) delimits the coolant guide contour (7) radially from the outside.

8. The electrical machine (1) according to claim 6 or 7, characterized in that the second contact surface (16) has a conical extension, when viewed in the disassembled initial state of the disc element (5).

9. The electrical machine (1) according to any of claims 1 to 8, characterized in that the disc-shaped element (5) is pressed against the rotor (3) under elastic prestress by means of a fastening device (18) supported on the drive shaft (4).

10. The electrical machine (1) according to any of claims 1 to 9, characterized in that a fluid guiding element (19) is arranged on a side of the rotor (3) axially remote from the disc element (5).

Technical Field

The present invention relates to an electric machine for a drive train of a motor vehicle, in particular a hybrid drive (hybrid drive) of a motor vehicle, such as a car, truck, bus or other commercial vehicle.

Background

Known hybrid drives have a relatively powerful electric machine, the efficiency of which still needs to be further improved. In particular, it is necessary to reliably detect the position or speed of the rotor. Furthermore, the rotor should be fixed in the rotor assembly as stably as possible. In any operating state, reliable cooling of the individual components of the electric machine should also be ensured.

Disclosure of Invention

It is therefore an object of the present invention to provide an electrical machine for high performance applications that operates efficiently and reliably.

According to the invention, this is achieved by the subject matter of claim 1. Thus, an electric machine for a motor vehicle drive train is achieved, which electric machine is provided with a stator, a rotor mounted for rotation relative to the stator, and a drive shaft receiving the rotor for co-rotation. In the axial direction of the drive shaft, a disk-shaped element is arranged next to the rotor, which is made of sheet metal and is also connected to the drive shaft for joint rotation, wherein the disk-shaped element has a transmitter contour detectable by the eddy current sensor and a coolant guide contour for deflecting the coolant to the stator, and the disk-shaped element is pressed with an axial prestress against an end face of the rotor.

By providing such a disc-like element several functions can be simultaneously realized with a single component. The result is a particularly powerful motor.

Further advantageous embodiments are claimed by the dependent claims and are explained in more detail below.

The transmitter contour is provided with a geometry which is particularly easy to manufacture and to detect if the transmitter contour has at least one window, preferably several windows arranged in a distributed manner in the circumferential direction. Furthermore, the eddy-current sensor is preferably arranged offset by a certain gap in the axial direction with respect to the transmitter contour.

With regard to the coolant guiding contour, it is also advantageous if it is formed in the first section by a recess/empty space on the side of the disk element facing the rotor (axial side). This significantly reduces the cost of manufacturing the coolant guiding profile.

If the coolant guiding contour is formed in the second section by at least one axial through hole, preferably by a plurality of through holes distributed in the circumferential direction, the coolant is reliably guided away from the rotor on the radial outside of the coolant guiding contour. The result is as low a fluid resistance of the rotor as possible.

As already mentioned, it is particularly advantageous if the second section is arranged adjacent to the first section in the radial direction immediately outside the first section.

The stator is suitably arranged with at least one winding which is located radially outside the outlet of the coolant guiding profile and/or is arranged at the same height as the outlet of the coolant guiding profile in the axial direction.

Furthermore, it is advantageous if at least one contact surface of the disc element, which axially rests on the rotor, is formed by a deformation/elevation realized by a projection or deep drawing. The contour of the disc element is thus produced in a particularly simple manner.

The first contact surface serves to guide the coolant away from the rotor if the first contact surface radially delimits the coolant guiding profile from the outside.

The second contact surface is also realized with a conical extension/shape when viewed in the disassembled initial state (unassembled state) of the disc element. The first contact surface is also preferably realized with such a conical extension/shape and is arranged radially outside the second contact surface.

It is therefore particularly advantageous if the disk element is pressed against the rotor under elastic prestress by means of a fastening device, preferably a nut, which is supported on the drive shaft. The elastic properties are achieved in particular by a conical extension of the second contact surface. Since the disc-shaped element is made of sheet metal, the disc-shaped element is also used as a pre-stressed spring.

Furthermore, it is advantageous to use a further disc-shaped element forming a fluid guide element on the side of the rotor axially remote from the disc-shaped element. The fluid guide element is realized in a similar way as the disc-shaped element, preferably in the same way as the disc-shaped element, except for the transmitter contour. The fluid guide element preferably has two contact surfaces (a first contact surface and a second contact surface) realized by a deep drawing technique. The first contact surface and/or the second contact surface preferably also have a conical shape. The fluid guide element also has a coolant guide profile consisting of a second section and a first section.

The respective first section of the coolant guiding profile is then preferably connected to a coolant inlet/coolant supply on the radially inner side of the rotor. The coolant supply is preferably at least partially introduced into the drive shaft.

Furthermore, it is advantageous if the rotor consists of or has a laminated rotor core, since the disc element according to the invention is used particularly effectively for pressing several sheet metal sections forming the laminated rotor core against each other.

In other words, a multifunctional sheet metal for a rotor of an electric machine (motor) is realized according to the present invention. The multifunctional sheet of the rotor of the electric machine has a structure for integrating three different functions, namely, a function of a signal transmitter (transmitter profile) of the eddy current sensor, a function of preventing outer diameter delamination during operation, and a function of supplying fluid to the stator of the electric machine to achieve cooling.

Drawings

Hereinafter, the present invention will now be described in detail with reference to the accompanying drawings.

In the drawings:

fig. 1 shows a longitudinal sectional view of a partly illustrated electric machine according to a preferred exemplary embodiment of the present invention, wherein the disc elements contacting the rotor of the electric machine are clearly visible,

figure 2 shows the side of the disc-shaped element according to figure 1 resting against the rotor during operation,

figure 3 shows the side of the disc element facing away from the rotor,

figure 4 shows a longitudinal section of the disc-shaped element,

figure 5 shows a longitudinal cross-section of a fluid guide element also used in figure 1,

fig. 6 shows the side of the flow guiding element according to fig. 5 facing away from the rotor during operation, an

Fig. 7 shows the side of the fluid guide element according to fig. 5 resting against the rotor during operation.

The drawings are merely schematic in nature and are used for understanding the present invention. Like elements are provided with like reference numerals.

Detailed Description

The basic structure of the electrical machine 1 according to the invention can be seen particularly clearly in fig. 1. The electric machine 1 is used in its preferred operating state in a hybrid transmission of a motor vehicle drive train, which is not shown here for the sake of clarity. The electric machine 1 is used in a typical manner for supporting the driving of a hybrid vehicle. According to other embodiments, the electric machine 1 can also be used in a motor vehicle that is purely electrically driven.

The motor 1 has a stator 2 fixed to a housing. A rotor 3 designed as an inner rotor is rotatably mounted radially inside the stator 2. The rotor 3 is attached to the drive shaft 4 for co-rotation. The rotor 3 is mounted axially on the drive shaft 4 from the outside and is connected by means of teeth 20 (saw teeth), which are indicated in fig. 1 only in terms of their position. During operation, the drive shaft 4 is also coupled or can be coupled to a transmission shaft of the hybrid transmission.

For axially fixing the rotor 3 relative to the drive shaft 4, a disk element 5 designed according to the invention is arranged on a first axial side of the rotor 3. The disc element 5 fulfils several functions. The disc element 5 is manufactured as a stamped part. On the one hand, the disc element 5 is designed as a transmitter wheel for the sensor device 21. The disc element 5 thus has a transmitter contour 6, which transmitter contour 6 is operatively connected to a sensor device 21, which sensor device also has an eddy current sensor, which is not shown here for the sake of clarity. As can be easily observed in fig. 2 and 3, the transmitter profile 6 is realized by several windows 9 (the windows in fig. 1 are only indicated with respect to their radial position) evenly distributed in the circumferential direction. The transmitter profile 6 is designed and interacts with the sensor device 21 during operation such that the angular/rotational position of the rotor 3 and more preferably the speed of the rotor can be detected.

As a further function, the disk element 5 is in principle designed such that it is pressed against the rotor 3 with an axial prestress. The disc element 5 is realized completely as a spring element/spring washer. For this purpose, the disc element 5 has a conical shape. On the disc element 5 there are two contact surfaces 15, 16 which bear against the rotor 3 on its end face 8 (first axial side) in the axial direction of the drive shaft 4. The first contact surface 15 is annular in shape and extends continuously in the circumferential direction around the drive shaft 4. The second contact surface 16 is formed radially inside the first contact surface 15 and is subdivided into a plurality of surface sections 25 distributed in the circumferential direction.

Due to the conical extension of the disc element 5, the second contact surface 16 is conically inclined in the uninstalled state with respect to a comparative plane oriented perpendicularly to the drive shaft 4. The first contact surface 15 formed radially outside the second contact surface 16 is also conically inclined. These conical contact surfaces 15, 16 can also be clearly seen in fig. 4. During assembly, according to fig. 1, the second contact surface 16 is moved towards the rotor 3 via another path than the path for the first contact surface 15. This produces an elastic prestress of the disc element 5 and an application of prestress directly acting on the rotor 3. The fastening means 18, which are realized as nuts, press the disc element 5 such that the second contact surface 16 is at the same axial level as the axial level of the first contact surface 15, so that the rotor 3 is prestressed in the axial direction. The fastening device 18 is fastened directly to the drive shaft 4, i.e. screwed to the drive shaft 4, on the side of the disk element 5 facing away from the rotor 3. For planar contact of the fastening device 18 on the disc element 5, the disc element is provided with a flat contact surface, i.e. arranged to extend perpendicularly to the drive shaft 4 (by means of turning).

Furthermore, the disc element 5 fulfils the function of a coolant line. For this purpose, the disc element 5 has a coolant guiding contour 7 for deflecting/diverting the coolant flow during operation. The first section 10a of the coolant guiding contour 7 extends in the radial direction and is formed by an axial recess 11 (also referred to as empty space) between the rotor 3 and the disk element 5. As can be observed in fig. 2, between the two convex deformations 17 representing the surface sections 25 there is a passage of the coolant guiding profile 7 in the circumferential direction, which allows coolant to flow through the passage in the radial direction. The first section 10a is connected to the supply 22. The first section 10a is coupled to the supply 22, in particular via an axially extending groove/recess 23 formed between the rotor 3 and the drive shaft 4. On the radial outside of the first section 10a, the coolant guide profile 7 merges directly into the second section 10 b. The second section 10b is realized by a plurality of through holes 12 distributed in the circumferential direction. The second section 10b is directly delimited by the first contact surface 15 from the outside in the radial direction. Thus, during operation the coolant flows axially away from the rotor 3 through the respective through hole 12. The coolant exits at an outlet 14 of the coolant guiding contour 7 in the axial direction towards the environment, so that during operation the coolant is conveyed in the radial direction to the individual windings 13 of the stator 2 under the influence of centrifugal forces.

On the second axial side of the rotor 3, i.e. on the axial side facing away from the disk element 5, a flow guide element 19 is arranged. The flow guiding element 19 can be seen in detail in connection with fig. 5 to 7 and forms a further (second) disc-shaped element. The fluid guide element 19 is clamped in the axial direction between a radial shoulder 24 of the drive shaft 4 and the rotor 3. The clamping is carried out in a typical manner by means of a fastening device 18 which presses the assembly of the disc element 5, the rotor 3 and the fluid guide element 19 against a shoulder 24. The structure of the fluid guide member 19 is the same as that of the disc member 5, unless otherwise described below.

The flow guiding element 19 therefore also has a coolant guiding contour 27, as can be observed in fig. 6 and 7. The coolant guiding contour 27 of the fluid guiding element 19 is provided with a first section 10a which is in turn connected to the supply 22. A second section 10b in the form of a through hole 12 is connected to the first section 10a for transferring coolant to the windings 13 of the stator 2.

In the present embodiment, the two contact surfaces 26a, 26b formed similarly to the contact surfaces 15, 16 of the disc element 5 are realized by means of drawing and punching. The first contact surface 26a formed by the deformation 17 is realized by drawing, and the second contact surface 26b formed by the deformation 17 is realized by punching. The width of the fluid guide member 19 is smaller than the width of the disc member 5. Furthermore, as can be observed from fig. 5, the fluid guide element 19 has a conical extension. Thus, in the unassembled state, the second contact surface 26b of the fluid guide element 19 is also positioned in a conical manner with respect to a comparison plane extending perpendicularly to the drive shaft 4. When the contact surfaces 26a, 26b of the fluid guide element 19 are pressed against the rotor 3, the fluid guide element 19 acts as a prestressing element and accordingly applies a further prestressing force to the rotor 3. However, the transmitter profile 6 is preferably omitted in comparison to the disc element 5.

In other words, the solution according to the invention comprises a special design of the single circular sheet metal part (disc element 5). The sheet 5 essentially contains the stamped window 9 for the signal transmitter 6, the boss 17 and the opening 12 for the oil line, and it acts as an axial spring for axially holding the rotor sheets together. Looking in more detail, the sheet metal part 5 is located on the same shaft 4 as the rotor 3 of the motor 1. The torque is transmitted by means of a form fit through a groove in the shaft 4 and a corresponding lug in the sheet metal part 5. The nut 18 clamps the sheet metal member 5 and the rotor 3. Thus, the metal sheet 5 rotates at the same speed as the rotor 3. The signaling function is realized by several stamped windows 9 in the sheet metal part 5. A certain distance between the signal generator 6 and the rotor 3 is required in order not to negatively affect the signal quality. In order to be able to maintain the distance, the sheet 5 is convex on the inside and outside. The projections 17 also assist in the distribution of oil. The oil flows through the shaft 4 and reaches the rotor 3 through four holes evenly distributed around the circumference. The oil is led to the sheet metal parts 5, 19 to the right and to the left through the grooves in the rotor 23. The raised portions 17 in the sheet 5 form cavities locally between the rotor 3 and the sheet 5. Centrifugal forces direct the oil radially outward through the cavity. The oil collects at the outer diameter and flows out of the metal sheet 5 through several punched holes 12. The centrifugal force ensures that the oil splashes onto the windings 13 of the stator 2. The outflow from the holes 12 ensures that the oil hits the winding 13 at a distance of at least one sheet metal thickness from the air gap of the electrical machine 1. This prevents excessive oil from entering the air gap between the stator 2 and the rotor 3. A metal sheet 19 is also required on the right hand side of the rotor 3. This has the same oil guiding function as described above. The difference is that in the case of this sheet 19, the distance to the air gap is smaller due to the thinner sheet thickness. Thus, the sheet 19 is drawn in an outer diameter. The oil flows out of the opening 12 for the balancing hole. No additional holes for oil flow are required here, since no sensor blocks the oil flow. The signal transmitter function is not applicable to this sheet 19, since the rotor position has already been determined by another sheet 5. The third function is to hold the rotor laminations axially together at the outer diameter. After stamping and embossing both sheets 5, 19 are easily set/shaped in a conical manner. The upright metal sheet 5 is pressed flat against the rotor 3 by means of a nut 18. The sheet 5 behaves like a spring. This ensures that forces are always acting on the rotor 3 at the outer diameter. Delamination is no longer possible. The additional turning operation on the metal sheets 5, 19 ensures a flat contact surface of the nut.

List of reference numerals

1 electric machine 2 stator 3 rotor 4 drive shaft 5 disc element 6 transmitter profile 7 coolant guide profile 8 end face 9 window 10a first section 10b second section 11 recess 12 through hole 13 outlet 15 first contact surface 16 second contact surface 17 deformation 18 fastening device 19 fluid guide element 20 tooth 21 sensor device 22 supply 23 recess 24 shoulder 25 surface section 26a first contact surface 26b fluid guide element second contact surface 27 fluid guide element coolant guide profile.