阅读说明：本技术 支承系统 (Bearing system ) 是由 S·达舍尔 于 2018-09-28 设计创作，主要内容包括：本发明涉及一种用于电动机转子的支承系统。该支承系统包括定子和至少一个径向轴承。该定子在此形成该径向轴承的一部分。本发明还涉及一种具有这种支承系统的增压装置。所述增压装置和支承系统尤其也可以与燃料电池一起使用。(The present invention relates to a bearing system for a rotor of an electric motor. The support system includes a stator and at least one radial bearing. The stator here forms part of the radial bearing. The invention also relates to a charging device having such a bearing system. The pressure intensifier and support system may also be used with fuel cells, among other things.)

1. A support system (10) for a rotor (400) of an electric motor (2), comprising:

a stator (100);

at least one radial bearing (200);

it is characterized in that the preparation method is characterized in that,

the stator (100) forms part of the radial bearing (200).

2. The support system (10) of claim 1, wherein the radial bearing (200) is an air bearing.

3. Support system (10) according to any one of the preceding claims, wherein the radial bearing (200) is formed radially (24) between said stator (100) of the electric motor (2) and a rotor (400) which is fitted into the stator (100) in the operating state.

4. The support system (10) of any one of the preceding claims, wherein the stator (100) is configured such that a bearing membrane (210, 220) can be fixed on the stator (100).

5. Support system (10) according to any of the preceding claims, wherein the stator (100) comprises at least one groove (120) for fixing a bearing membrane (210, 220), said groove extending radially (24) into the stator (100).

6. The support system (10) of claim 5, wherein the groove (120) is disposed on a can inner surface (150) of the stator (100).

7. The support system (10) according to any one of claims 5 or 6, wherein the stator (100) comprises a plurality of winding ribs (110) extending in a radial direction (24), and wherein the groove (120) is provided in one of said winding ribs (110).

8. The support system (10) of any of claims 4 to 7, wherein the groove (120) extends in an axial direction (22) from a first axial end (142) of the stator (100), and optionally wherein the groove (120) extends in the axial direction (22) from a second axial end (144) of the stator (100).

9. The support system (10) according to any one of claims 4 or 8, wherein the groove (120) does not extend to an axial center (152) of the stator (100).

10. The support system (10) of any of the preceding claims, comprising a first radial bearing (200a) and a second radial bearing (200b), wherein the first radial bearing (200a) is seated on the first axial end (142) of the stator (100), and wherein the second radial bearing (200b) is seated on the second axial end (144) of the stator (100).

11. The support system (10) of claim 10, further comprising at least one spacer (300) disposed on the can inner surface (150) of the stator (100) and through which the first radial bearing (200a) and the second radial bearing (200b) are spaced from each other in the axial direction (22).

12. Support system (10) according to any of the previous claims, wherein the radial bearing (200) comprises at least one wave shaped membrane (210) and/or at least one smooth membrane (220) arranged along the inner circumferential surface (170) of the stator (100).

13. The support system (10) of claim 12, wherein the smoothing membrane (220) is disposed against the undulating membrane radially (24) inwardly proximate to the undulating membrane (210), and optionally wherein the undulating membrane (210) is disposed against the stator radially (24) proximate to the stator (100).

14. Support system (10) according to any one of claims 12 or 13 when dependent on claim 5, wherein the wave shaped membrane (210) and/or the smooth membrane (220) respectively comprise at least one locking element (250) designed to be inserted in a groove (120) of the stator (100) in order to lock the wave shaped membrane (210) and/or the smooth membrane (220) in a position-proof manner in the circumferential direction (26) and/or in the radial direction (24).

15. A supercharging device (1) comprising:

a shaft (500);

an electric motor (2) comprising a rotor (400), wherein the rotor (400) is arranged on the shaft (500); and

at least one compressor wheel (600);

characterized in that the charging device (1) comprises a support system (10) according to any one of the preceding claims, wherein the stator (100) is part of an electric motor (2), and optionally wherein the charging device (1) is designed for use with a fuel cell (3).

Technical Field

The present invention relates to a support system for a rotor of an electric motor. The invention also relates to a charging device having such a bearing system.

Background

More and more new generation vehicles are equipped with a supercharging device to achieve the required purpose and legal requirements. The development of supercharging devices requires optimization of the individual components not only with respect to their reliability and efficiency, but also of the overall optimization system with respect to their reliability and efficiency.

The known supercharging devices usually have at least one compressor with a compressor wheel which is connected to a drive unit via a common shaft. The compressor compresses fresh air drawn in for the internal combustion engine or the fuel cell. Thereby, the amount of air or oxygen supplied to the engine for combustion or to the fuel cell for reaction is increased. This in turn leads to a power boost of the internal combustion engine or the fuel cell.

The charging device may be equipped with different drive units. In particular, electric superchargers in which the compressor is driven by an electric motor and exhaust gas turbochargers in which the compressor is driven by an exhaust gas turbine are known from the prior art. A combination of both drive units is also used. Systems whose drive units comprise electric motors generally comprise a stator disposed within a bearing housing, which surrounds a rotor disposed on or integrated into a shaft. In the prior art, the system of compressor wheel, shaft and rotor and, if appropriate, exhaust gas turbine is usually mounted in a bearing housing by means of a radial and axial air bearing via the shaft. The known systems generally lead to higher installation space requirements and design constraints.

Disclosure of Invention

It is an object of the present invention to provide a support system or charging device having a compact structure.

The invention relates to a bearing system for a rotor of an electric motor according to claim 1 and a charging device having such a bearing system according to claim 15.

A support system for a rotor of an electric motor includes a stator and at least one radial bearing. The stator here forms part of the radial bearing. That is, the stator assumes part of the function of a radial bearing. In other words, this means that a part of the function of the radial bearing is integrated into the stator. Thus, the additional components that are usually required in addition, such as an additional bearing sleeve that is arranged in the bearing housing and surrounds the motor shaft, can be dispensed with. The result is fewer parts and less space requirement for the radial mechanism. In particular, however, this also results in a smaller axial installation space requirement, since the bearing system according to the invention does not require the axial space normally occupied by the bearing bush axially next to the stator. This ultimately results in a more compact support system or, when employed within a supercharging device, a more compact supercharging device.

In the design of the support system, the radial bearing may be an air bearing. In contrast to, for example, oil lubricated bearings, air bearings do not require oil supply and also do not have to be completely sealed. The air bearing, i.e. also the radial bearing, can thus be arranged flexibly in different regions of the bearing system or, when the bearing system is used in a charging device, in different regions of the charging device. The air bearing is advantageous, in particular for use in fuel cells, since the fuel cell should not be contaminated by foreign substances, so that there is no risk of damage or functional failure. In the case of oil-lubricated bearings, this is ensured only by a complete oil seal, which cannot be achieved or can only be achieved at high cost. Thus, the air bearing also results in a more reliable drive system, especially when used with a fuel cell.

In the case of a bearing system design which can be combined with the previous design, the radial bearing can be formed radially between the stator of the electric motor and the rotor which is inserted into the stator in the operating state. In this way, the additional components that are usually required in addition, such as an additional bearing sleeve that is arranged on the motor shaft, can be dispensed with. That is, the radial bearing may be partly constituted by components already present in the motor. The result is fewer parts and less space requirement for the radial mechanism. In particular, however, this also results in a smaller axial installation space requirement, since the bearing system according to the invention does not require the axial space normally occupied by the bearing bush axially next to the stator. This ultimately results in a more compact support system or, when employed within a supercharging device, a more compact supercharging device.

In a support system design that may be combined with any of the previous designs, the stator may be designed such that the bearing membrane may be secured to the stator. In particular, the stator may be designed such that the bearing membrane may be fixed within the stator.

In a support system design that may be combined with the previous design, the stator may comprise at least one groove for fixing a bearing membrane, which extends radially into the stator.

In a support system design that can be combined with the previous design, the groove can be designed to fix the bearing membrane in a position that is secured against displacement in the radial and/or circumferential direction. Further, the groove may have an L-shaped cross section. Alternatively, the groove may have a T-shaped cross-section.

In a support system design in which the stator includes at least one groove, the groove may be positioned on the inner surface of the stator can.

Alternatively or additionally, the stator may comprise a plurality of radially extending winding ribs. The groove may then be provided in one of said winding ribs. Alternatively or additionally, the stator may include a plurality of axially extending packing ribs. The groove can then be provided in one of the packing ribs.

In a support system design in which the stator includes at least one groove, the groove may extend axially through the entire length of the stator. Alternatively or additionally, the groove may extend in an axial direction from the first axial end of the stator. Alternatively or additionally, the groove may extend in the axial direction from the second axial end of the stator. Alternatively or additionally, the groove does not extend to the axial center of the stator.

In a support system design that may be combined with any of the previous designs, the support system may include a first radial bearing and a second radial bearing. The first radial bearing may be arranged here at a first axial end of the stator. The second radial bearing may be arranged here at the second axial end of the stator. Alternatively or additionally, the support system may comprise at least one spacer. The spacer may be disposed on an inner surface of the housing of the stator. The first radial bearing and the second radial bearing may be axially spaced apart from each other by the spacer. By using two radial bearings in comparison to one radial bearing, the potential contact or friction surfaces between the bearing membrane and the motor rotor or motor shaft supported therein in the operating state can be reduced. The efficiency of the support system can be improved. This can be achieved, for example, by using, instead of one radial bearing, two radial bearings spaced apart from one another in the axial direction, each having a small axial extent, so that the sum of the axial extents of the two radial bearings is smaller than the axial extent of the individual radial bearing. The further the two radial bearings are spaced apart from one another, the greater the bearing stability of the motor rotor or motor shaft which is inserted into the stator in the operating state can be. A more efficient support system can thus be provided by the advantageous design. Vibrations and vibrations of the support system can also be reduced by the design.

In a support system design where the support system comprises a recess and which may be combined with the previous design, the spacer may comprise a fixing. The fixing portion may be designed to be insertable into the recess. Alternatively or additionally, the fastening part can be designed so as to be axially displaceable into the recess.

In a design of the support system in which the support system comprises at least one spacer, the spacer can be designed substantially in the shape of a rib in the axial direction. Alternatively, the spacer can be designed in the shape of a substantially cylindrical segment in the circumferential direction around the stator axis.

In a support system design that may be combined with any of the previous designs, the radial bearing may include at least one wave film and/or at least one smooth film. The wave film and/or the smoothing film may be disposed along an inner circumferential surface of the stator. Furthermore, the corrugated and/or smooth film can be designed in the shape of a ring segment around the stator axis. Alternatively or additionally, the smoothing membrane may be arranged radially inwardly against the corrugated membrane, immediately adjacent to the corrugated membrane. Alternatively or additionally, the corrugated membrane can be arranged radially next to the stator against the stator. Alternatively or additionally, the wave shaped membrane may be designed to bias the smooth membrane in a radial direction towards the motor rotor which is enclosed in the stator in the working state. By means of the described advantageous embodiment, a very narrow air gap can be produced between the rotor of the electric motor, which is inserted into the stator in the operating state of the bearing system, and the smoothing membrane, as a result of which a bearing action can be produced between the rotor and the stator or between the rotor and the smoothing membrane.

In the design of the support system comprising at least one wave-shaped membrane and/or at least one smoothing membrane, the wave-shaped membrane may be designed to be elastically compressible between the smoothing membrane and the stator by means of a radial movement of the smoothing membrane, so that an air gap may be formed in the radial direction between the rotor and the smoothing membrane which are incorporated in the stator in the operating state. In other words, this means that the smoothing film can be arranged directly against the motor rotor inserted into the stator when the bearing system or the electric motor or the pressure boosting device is not operating. In operation, an air gap may be formed radially between the smooth membrane and the rotor by radial movement of the smooth membrane towards the corrugated membrane and the stator radially adjacent the corrugated membrane, permitted by the elastic compressibility of the corrugated membrane. This air gap produces a bearing action and results in little friction compared to a smooth membrane or rolling bearing which bears against the rotor.

In designs of the support system in which the support system comprises at least one wave shaped membrane and/or at least one smoothing membrane and the stator comprises at least one groove, the wave shaped membrane and/or the smoothing membrane may each comprise at least one locking element. The locking element can be designed to be inserted into a groove of the stator in order to fix the corrugated and/or smooth membrane in the circumferential and/or radial direction in a position-proof manner. Additionally, the respective locking member may project in the radial direction from the corrugated membrane and/or the respective smooth membrane in the mounted state. In addition, the locking element can be designed as a rib-like projection extending in the radial direction and in the axial direction. Alternatively or additionally, the locking element may have an L-shaped cross-section. Alternatively, the locking element may have a T-shaped cross-section.

In designs where the support system comprises at least one corrugated membrane and/or at least one smooth membrane, the support system may comprise at least one axial locking element. The axial lock may be designed to fix the corrugated membrane and/or the smooth membrane and/or the spacer against axial displacement.

In a support system design that may be combined with the previous design, the support system may include a first axial lock. The first axial lock may be disposed at a first axial end of the stator. Alternatively or additionally, the support system may comprise a second axial lock disposed at the second axial end of the stator.

In a support system design that may be combined with any of the previous designs, the support system may further comprise at least one thrust bearing.

The invention also relates to a supercharging device. The supercharging arrangement comprises a shaft, an electric motor and at least one compressor wheel. The motor has a rotor. The rotor is mounted on the shaft. The supercharging arrangement further comprises a bearing system according to any of the preceding designs. The stator is here part of an electric motor. The pressure boosting device may be particularly designed for use with fuel cells. The air bearing is particularly advantageous here because the fuel cell should not be contaminated by foreign matter, so that there is no risk of damage or functional failure. In the case of oil-lubricated bearings, this is ensured only by a complete oil seal, which cannot be achieved or can only be achieved at high cost. Thus, the air bearing also results in a more reliable drive system, especially when used with a fuel cell.

Drawings

FIG. 1 shows a side cross-sectional view of a supercharging assembly with a known support system for an electric motor;

FIG. 2A shows a side cross-sectional view of the support system of the present invention with a radial bearing in a supercharging device;

FIG. 2B shows a side cross-sectional view of the inventive support system of FIG. 2A with an alternative radial bearing installed in place;

3A-3D show a plurality of cross-sectional views of different mounting states of the support system of the invention including a stator, a bearing membrane and a rotor;

FIGS. 4A-4B show a cross-sectional view (B-B) and a corresponding detail view in a side sectional view along section line A-A of the support system of the present invention, here showing two radial bearings with spacers;

5A-5B illustrate different cross-sectional side views of different in-place support systems including exemplary designs of spacers and radial bearings;

fig. 6 shows a schematic view of a pressure intensifying apparatus of the present invention comprising a fuel cell.

Detailed Description

In the context of the present application, the expressions "shaft" and "axial" relate to the axis of the stator or of the rotor. Referring to the drawings (see, e.g., fig. 1 or 2A), the axial direction is indicated by reference numeral 22. The radial direction 24 here relates to the axis of the stator or of the rotor. Likewise, the circumference or circumference 26 relates to the axis of the stator or of the rotor.

Fig. 1 shows a known support system 1010 for an electric motor 3000 in a supercharging arrangement 1000. The support system 1010 includes a thrust bearing 800 and a radial bearing 2000, thereby supporting the rotor 400 of the motor 3000 mounted on the shaft 500. The thrust bearing 800 and the radial bearing 2000 are thin film bearings including the wavy film 210 and the smooth film 220. Thrust bearing 800 is formed between a bearing disk 850 seated on shaft 500 and housing 1900. In the illustrated example, the motor 3000 is installed in the booster device 1000, and thus the housing 1900 belongs to the booster device 1000. Specifically, the thrust bearing 800 is thus formed between the compressor back wall 1962 of the compressor housing 1960 and the bearing housing 1910. As an alternative to this, it is also known that the thrust bearing 800 is formed between a turbine rear wall 1972 of a turbine housing 1970 and a bearing housing 1910. Referring to the view of fig. 1, this means that the shaft 500 is axially mounted to the compressor back wall 1962 and the bearing housing 1910 between the compressor back wall 1962 and the bearing housing by way of the bearing disk 850. The radial bearing 2000 is formed between the shaft 500 and the bearing housing 2100. The bearing sleeve 2100 is seated in corresponding grooves in the bearing housing 1910 on the right and left sides of the stator 1100 of the motor 3000 in the axial direction 22. That is, the shaft 500 is radially mounted within the bearing housing 1910 by the bearing sleeve 2100.

In contrast, FIG. 2A illustrates the support system 10 of the present invention. Similar to the support system of fig. 1, the embodiment of the support system 10 of the present invention according to fig. 2A has similar components and elements, most of which have different reference numerals for clarity, although some may be designed to be identical. In fig. 2B to 5B, which also show the inventive design of the bearing system 10 as in fig. 2A, like features are provided with the same reference numerals as in fig. 2A.

Fig. 2A shows the support system 10 of the present invention for a rotor 400 of an electric motor 2. The support system 10 includes a stator 100 and two radial bearings 200. In alternative designs, the support system 10 may include only one radial bearing 200 or more than two radial bearings 200. The stator 100 here forms part of a radial bearing 200. That is, the stator 100 serves a partial function of the radial bearing 200. In other words, this means that the functional parts of the radial bearing 200 are integrated into the stator 100. Thus, the usually additionally required parts of the known support system 1010 of fig. 1, such as for example an additional bearing sleeve 2100, which is located in the bearing housing 1900 and surrounds the shaft 500 of the electric motor 3000, can be dispensed with. The result is fewer parts and less space requirement for the radial direction 24. However, in particular, this also results in a smaller installation space requirement in the axial direction 22, since the bearing system 10 according to the invention does not require the axial space which is usually taken up by the bearing sleeve 2100 (compare fig. 1 and 2A) of the known bearing system 1010 in the axial direction 22 next to the stator. This ultimately leads to a compact support system 10 or, if the support system 10 is used in an electric motor 2 or a charging device 1, to a compact electric motor 2 and/or a compact charging device 1.

The radial bearing 200 is designed as an air bearing. In contrast to, for example, oil lubricated bearings, air bearings do not require oil supply and also do not have to be completely sealed. The air bearings, i.e. also the radial bearings 200, can thus be flexibly arranged in different regions of the bearing system 10 or, in the case of a bearing system 10 in the electric motor 2 or in the charging device 1, in different regions of the electric motor 2 and/or of the charging device 1. The air bearing is advantageous, in particular for use in the fuel cell 3, because the fuel cell 3 should not be contaminated by foreign matter, so that there is no risk of damage or functional failure. In the case of oil-lubricated bearings, this is ensured only by a complete oil seal, which cannot be achieved or can only be achieved at high cost. The air bearing thus also results in a more reliable drive system, especially when used with the fuel cell 3.

Fig. 2A and 2B show the support system 10 mounted within the electric motor 2, which is integrated into the supercharging assembly 1. The support system 10 or the motor 2 may be used in other devices than a supercharging device. Here it can be seen that the radial bearing 200 is formed in the radial direction 24 between the stator 100 and the rotor 400 of the electric motor 2 which is inserted into the stator 100. That is, the support system 10 further includes a shaft 500 along with the rotor 400 mounted on the shaft. The rotor 400 and the shaft 500 are made in one piece in the example shown in the drawings, but may also be made separately from each other in alternative designs. The rotor 400 is here part of a shaft 500, which is situated in the stator 100 for the most part in the axial direction 22. It can also be seen that the radial bearing 200 is not arranged here on the right or left side of the stator 100 in the axial direction 22. In other words, the radial bearing 200 does not protrude beyond the length of the stator 100 in the axial direction 22. That is, the radial bearing 200 is disposed in the stator 100 in the axial direction 22. This saves installation space and weight. Finally, this may result in a more compact device.

Similar to the radial bearing 2000 of the known support system 1010 of fig. 1, the radial bearing 200 of the support system 10 according to the present invention includes at least one corrugated membrane 210 and at least one smooth membrane 220 (see fig. 2A and 2B). Thus, the radial bearing 200 may also be referred to as a film bearing or (as described above) an air bearing. The corrugated film 210 and the smooth film 220 may also be collectively referred to as bearing films 210, 220. The wavy film 210 and the smooth film 220 are arranged along the inner circumferential surface 170 of the stator 100 (see fig. 3B, in particular). In other words, the wavy film 210 and the smooth film 220 are disposed radially inwardly of the inner circumferential surface 170 on the can inner surface 150 of the stator 100. Here, the smoothing film 220 is arranged in the radial direction 24 inwardly against the corrugated film next to the corrugated film 210 (see fig. 3C in particular). The smooth membrane 220 is disposed immediately radially 24 outwardly of the rotor 400 or shaft 500. Furthermore, the corrugated membrane 210 is arranged in the radial direction 24 next to the stator 100 and in the radial direction 24 next to the stator. The corrugated membrane 210 is here designed to bias the smooth membrane 220 in the radial direction 24 towards the rotor 400 of the motor 2 mounted in the stator 100. By means of this advantageous design, a very narrow air gap can be produced between the rotor 400 of the electric motor 2 inserted into the stator 100 and the smoothing membrane 220 during operation of the bearing system 10, as a result of which a bearing action can be produced between the rotor 400 and the stator 100 or between the rotor 400 and the smoothing membrane 220. Therefore, the rotor 400, the smooth film 220, the wavy film 210, and the stator 100 are respectively adjacently disposed directly side by side in the radial direction 24. The rotor 400, smooth film 220, corrugated film 210, and stator 100 thus collectively form the radial bearing 200 (see, in particular, fig. 2A, 2B, and 3D). The wave film 210 is designed to be elastically compressible between the smooth film 220 and the stator 100 by the radial 24 movement of the smooth film 220, so that a narrow air gap may be formed in the radial direction 24 between the rotor 400 mounted in the stator 100 and the smooth film 220 in operation.

Thus, the rotor 400 or the shaft 500 forms a first bearing surface of the radial bearing 200, which is oriented in the direction of the smoothing film 220, and the smoothing film 220 forms a second bearing surface of the radial bearing 200, which is oriented in the direction of the rotor 400. When the support system 10 or the motor 2 or the supercharging device 1 is not operating, i.e. when the rotor 400 or the shaft 500 is not rotating, the smoothing membrane 220 abuts the rotor 400 (see for example fig. 2A and 2B). In other words, the first bearing surface of the radial bearing 200 abuts the second bearing surface of the radial bearing 200. When the electric motor 2 or the supercharging device 1 is switched into operation, the rotor 400 or the shaft 500 itself rotates and a relative movement in the circumferential direction 26 occurs between the rotor 400 and the smoothing membrane 220. Thereby, the air flows between the smooth film 220 and the rotor 400 in the radial direction and applies a radial force to the rotor 400 and the smooth film 220. An air gap is thus present between the rotor 400 and the smooth membrane 220, whereby a bearing effect is obtained. This air gap is schematically shown in fig. 3D. That is, an air gap occurs in the radial direction 24 between the first bearing surface of the radial bearing 200 and the second bearing surface of the radial bearing 200. By the compressibility of the corrugated membrane 210, the smooth membrane 220 may move in the radial direction 24 relative to the corrugated membrane 210 and will press it against the stator 100. The stator 100 thus serves in particular as a fixed bearing. Thus, the wave film 210 (elastic) is compressed between the smooth film 220 and the stator 100. For this reason in particular, the corrugated membrane 210 may also be referred to as an elastic member 210 or an elastic membrane 210, while the smooth membrane 220 may also be referred to as a support membrane 220. In other words, this means that the smoothing membrane 220 can be arranged directly against the rotor 400 when the support system 10 or the electric motor 2 or the supercharging device 1 is not in operation (see, for example, fig. 2A and 2B). That is, in operation, an air gap may be formed in the radial direction 24 between the smooth film 220 and the rotor 400 by movement of the smooth film 220 in the radial direction 24 relative to the corrugated film 210 until the stator 100 abuts the corrugated film 210 outward in the radial direction 24. This air gap produces a bearing action and results in less friction than a smooth membrane 220 or rolling bearing against the rotor 400.

It is to be noted here that the figures present only a schematic representation of the support system 10 of the invention. For example, the wave-shaped course of the wave-shaped film 210 of the radial bearing 200 is preferably designed in the circumferential direction 26 in fig. 2A, rather than in the axial direction 22 as shown.

Fig. 3A to 3D show various installation states of the support system 10 of the present invention. As is clear from all four views, the stator 100 is designed such that the bearing membranes 210, 220 can be fixed on or in the stator. Fig. 3A shows a stator 100 having a plurality of winding ribs 110 around which a plurality of windings 140 are wound in fig. 3B. Also visible in fig. 3B are the fillers 130, which are arranged between the winding ribs 110 in the circumferential direction 26 and form filler ribs 132 there in each case. As shown in fig. 2A and 2B, the filler material may also surround the winding ribs 110 in the axial direction 22. That is, the first axial end 142 of the stator 100 and the second axial end 144 of the stator 100 may be formed of the filler 130. Fig. 3C shows the bearing films 210, 220 incorporated into the stator 100 in addition to the stator 100 of fig. 3C. Here, the support system 10 comprises, for example, three corrugated membranes 210 and three smooth membranes 220 each. In other embodiments, the number of the wave films 210 and the smooth films 220 may be more or less than three. The number of the wave films 210 and the number of the smoothing films 220 may also be different from each other. The wave shaped film 210 and the smooth film 220 are now designed in the shape of ring segments around the axis of the stator 100. Advantages are gained in thermal expansion due to the support system 10 including the plurality of smooth membranes 220 and the plurality of corrugated membranes 210. Due to the disconnection between the individual bearing membranes 210, 220, a space exists into which the material of the bearing membranes 210, 220 can expand upon heating, depending on the temperature. In fig. 3D, the rotor 400 is loaded into the stator 100, compared to fig. 3C. Here, the support system 10 is in operation. As can be appreciated, a radial air gap, i.e., air gap, has been formed in the radial direction 24 between the rotor 400 and the smooth membrane 220 and the undulating membrane 210 is compressed between the smooth membrane 220 and the can inner surface 150 of the stator 100.

Fig. 3A to 3D also show that the stator comprises three grooves 120, which extend into the stator 100 in the radial direction 24. The groove 120 is designed for fixing the bearing membranes 210, 220. In alternative designs, the stator 100 may include more or less than three grooves 120. The number of grooves 120 may be correlated to the number of bearing membranes 210, 220. For each pair of bearing membranes 210, 220, in which at least one groove 120 may advantageously be provided, the pair may consist of one corrugated membrane 210 and one smooth membrane 220. The recess 120 can now be integrated into the "original" stator 100 as shown in fig. 3A and be left free during casting, so that it is not filled with filler 130. Alternatively or additionally, the recesses 120 can be left free or formed during casting by corresponding stops which are inserted into the region of the filler ribs 132, or can be machined into the stator 100 after casting. The grooves 100 can be arranged in the winding rib 110 and/or the filler rib 132 and/or the filler 130 arranged next to the winding rib 110 in the axial direction 22. The groove 120 is now arranged on the housing inner surface 150 of the stator 100.

The grooves 120 may be formed in one of the winding ribs 110 as shown in fig. 3A to 3D, respectively. In this embodiment, three grooves 120 for respective three smooth films 220 and three wavy films 210 are formed in the respective winding ribs 110 spaced from each other in the circumferential direction 26. The grooves 120 are spaced apart from one another at equal intervals in the circumferential direction 26, but may also be arranged at different intervals in the circumferential direction in the housing inner surface 150 of the stator 100 in alternative embodiments. Alternatively or additionally, one, more or all of the grooves 120 can also be arranged in the filler rib 132.

Here, the groove 120 may extend in the axial direction 22 over the entire length of the stator 100. Alternatively, the groove 120 may extend in the axial direction 22 from the first axial end 142 of the stator 100. Alternatively, the groove 120 may extend in the axial direction 22 from the second axial end 144 of the stator 100. In the latter two cases, the groove 120 does not extend to the axial center 152 of the stator 100. If the stator 100 comprises a plurality of grooves 120, these grooves 120 can also be designed differently. In particular, the grooves 120 can have different axial runs. In this regard, fig. 2A, for example, shows the support system 10 where the radial bearing 200 is disposed closer to the axial center 152 of the stator in the axial direction 22 than the radial bearing 200 of the support system 10 of fig. 2B. This has the advantage that, for example, the one or more grooves 120 do not have to extend over the entire length of the stator 100 in the axial direction 22 (see fig. 2A), but can alternatively extend over the entire length thereof. For example, the groove 120 may extend in such an example only in an axially central region of the stator 100, and need not be present in the region of one or both axial ends 142, 144 of the stator 100.

The groove 120 is designed to fix the bearing membranes 210, 220 at least in the circumferential direction 26 in a position-proof manner. This can already be done with a simple I-shaped cross-section of the groove 120 (not shown). Such a groove 120 also has the advantage that the respective bearing membrane 210, 220 does not have to be moved in the axial direction 22 from one axial end 142, 144 of the stator 100, but can simply be fitted in the respective groove 120 radially 24 outwards. In addition, the groove 120 can be designed to fix the bearing membranes 210, 220 in the radial direction 24 in a position-proof manner. Such a groove 120 is shown in fig. 3A to 3D, wherein the groove 120 is designed, for example, in a T-shape. By means of the additional assembly in the circumferential direction 26, the respective bearing membrane 210, 220 is prevented from slipping out radially. Other cross-sectional shapes of the groove 120 besides a T-shape or an I-shape are also contemplated. The cross-sectional shape of the groove 120 may also be designed as S-shaped, L-shaped or,/"(slash-shaped) just to mention a few possibilities.

In the example of fig. 3C and 3D, each of the wave membranes 210 and each of the smooth membranes 220 includes a locking member 250. In an alternative design, it is also possible that only some of the bearing membranes 210, 220 comprise locking members 250. Some of the bearing membranes 210, 220 or their locking members 250 may also simultaneously secure other bearing membranes 210, 220 by corresponding designs known to those skilled in the art. The locking elements 250 are here designed to be inserted into the corresponding recesses 120 of the stator 100. Thus, the corrugated membrane 210 and/or the smooth membrane 220 (similar to the explanations above with respect to the grooves 120) may be secured against misalignment in the circumferential direction 26 and/or the radial direction 24. The respective locking elements 250 project in the radial direction 24 beyond the respective corrugated membrane 210 and the respective smooth membrane 220. The locking element 250 can be designed in particular as a rib-shaped projection, but can also be designed as a pin-shaped or other suitable projection which can engage in a groove, preferably extending substantially in the radial direction 24 and in the axial direction 22. In addition, the locking member 250 may have an assembly in the circumferential direction 26 (similar to the groove 120) to prevent radial sliding out of the respective bearing membrane 210, 220. Accordingly, the locking element 250 is designed in fig. 3C and 3D with an L-shaped cross section. However, the cross-sectional shape of the locking element 250 may alternatively be T-shaped, I-shaped, S-shaped, or "/" shaped, to name a few possibilities.

Alternatively, instead of the groove 120 in the stator 100, a projection may be formed in the stator 100, which may engage with a correspondingly shaped element (groove and/or projection) of the bearing membrane 210, 220 to fix the bearing membrane 210, 220 in the circumferential direction 26 and/or the radial direction 24 against misalignment. The locking member 250 may also, for example, extend substantially in the axial direction 22 and/or the circumferential direction 26 (deep-cut and/or protrude from the respective bearing membrane 210, 220) and may engage with correspondingly shaped elements (grooves and/or protrusions) of the stator 100.

The number of grooves 120 and the number of locking members 250 may be different. In particular, each bearing membrane pair (210+220) may have more grooves 120 than locking members 250.

Fig. 4B shows a side cross-sectional view of the support system 10 along section line a-a of fig. 4A, where section line a-a extends vertically through the support system 10 and its groove 120 and the locking element 250 of the smooth membrane 220 in the cross-sectional view of fig. 4A. As already noted, the exemplary support system 10 includes two radial bearings 200. One of the two radial bearings 200 is a first radial bearing 200a, and the other is a second radial bearing 200 b. As has been described further above, the radial bearings 200a, 200b can be arranged at different axial positions on the housing inner surface 150 of the stator 100. In this connection, fig. 5A and 5B show, in particular, a sectional side view similar to fig. 4B with two different positioning of the radial bearings 200a, 200B. By using two radial bearings 200a, 200b in comparison to a single radial bearing 200 extending over the entire axial width of the stator 100, the potential contact or friction surfaces between the bearing membranes 210, 220 and the rotor 400 or the shaft 500 of the electric motor 2 mounted therein in the operating state can be reduced. The efficiency of the support system 10 may be improved. This can be achieved, for example, by using, instead of the single radial bearing 200, two radial bearings 200a, 200b spaced apart from one another in the axial direction 22, each having a small extent in the axial direction 22, so that the sum of the axial extents of the two radial bearings 200a, 200b is smaller than the axial extent of the single radial bearing 200. The further apart the two radial bearings 200a, 200b are from each other, the greater the stability of the support of the rotor 400 or the shaft 500 of the electric motor 2 which is inserted into the stator 100 in the operating state. Thus, a more efficient support system 10 may be provided by the advantageous design. Vibration and chatter of support system 10 may also be reduced by the described design.

In connection therewith, fig. 5B shows the support system 10, wherein a first radial bearing 200a is arranged at the first axial end 142 of the stator 100 and a second radial bearing 200B is arranged at the second axial end 144 of the stator 100.

The support system 10 of fig. 5B also includes a spacer 300. The spacer 300 is seated on the can inner surface 150 of the stator 100. In alternative embodiments, the spacer 300 can also be embodied in other forms, in particular in the form of a sleeve. The first radial bearing 200a and the second radial bearing 200b are spaced apart from each other in the axial direction 22 by a spacer 300. Alternatively, the two radial bearings 200a, 200b can also be held at an axial distance such that the recess 120 is not completed in the axial center region of the stator 100, so that the radial bearings 200a, 200b are prevented by their locking elements 250 from sliding into the axial center region of the stator 100.

In the example shown, the spacer 300 is formed in the axial direction 22 in a rib-like manner. Particularly when the spacer 300 is configured in a rib shape, the spacer 300 includes a fixing portion (not shown). The fastening part is designed in such a way that it can be inserted radially 24 into the recess 120 and/or can be moved axially 22 into the recess. Alternatively, the spacer 300 may be designed in a substantially cylindrical segment shape in the circumferential direction 26 around the axis of the stator 100.

Additionally, the support system 10 may also include a plurality of spacers 300 distributed along the circumferential direction 26. Alternatively or additionally, the support system 10 may include a plurality of spacers 300 spaced from one another along the axial direction 22. In particular, as shown in fig. 5A, a radial bearing 200 can be arranged between two spacers 300. The respective radial bearing 200a, 200b is now held in place, in particular in its axial position, by the spacer 300.

Further, the support system 10 may include at least one axial lock 270 (see fig. 2A and 2B). The axial lock 270 is designed to secure the undulating membrane 210 and/or the smooth membrane 220 and/or the spacer 300 against axial 22 displacement. In particular, the support system 10 may include a first axial lock 270a and a second axial lock 270 b. In the example of fig. 2A and 2B, the axial locking members 207a, 270B are each formed as part of the compressor rear wall 962 or of the turbine rear wall 972. Alternatively, the first axial lock 270a and the second axial lock 270b may also be constructed as separate pieces. The first axial lock 270a may be disposed on the first axial end 142 of the stator 100 and the second axial lock 270b may be disposed on the second axial end 144 of the stator 100.

The support system 10 may also include at least one thrust bearing 800 (see fig. 2A and 2B).

The invention also relates to a supercharging device 1 (see fig. 2A and 2B). The supercharging apparatus 1 includes a shaft 500, a motor 2, a compressor wheel 600 and a turbine wheel 700. The motor 2 has a rotor 400. The rotor 400 is seated on the shaft 500. The supercharging apparatus 1 further comprises a support system 10 according to any of the preceding embodiments. Here, the stator 100 is a part of the motor 2.

The pressure boosting device 1 may be designed in particular for use with a fuel cell 3. In connection with this, fig. 6 shows a very simplified schematic view of a charging device 1 according to the invention (such as the one described in connection with the previous figures) with a compressor 6, a turbine 7 and an electric motor 2. Air flows into the compressor 6 through the compressor inlet 6a and is compressed there. The compressed air flows into the fuel cell 3 through the compressor outlet 6b communicating with the air inlet 3a of the fuel cell 3 to react with hydrogen gas. The fuel cell 3 may be supplied with hydrogen gas by a hydrogen gas supply device 3 c. The reaction product (water vapor) can be sent out of the fuel cell 3 through the air outlet 3 b. As shown in fig. 6, the reaction products can be used here to drive a turbine 7. For this purpose, the air outlet 3b is connected to a turbine inlet 7a of the turbine 7, whereby the turbine 7 or the turbine wheel can be driven by the reaction products before they leave the turbine 7 and the charging device 1 via the turbine outlet 7 b. The turbine 7 now drives the compressor 6 via the common shaft 500. Here, the motor 2 can alternatively or additionally drive the compressor 6 via the shaft 500. The air bearing is particularly advantageous here because the fuel cell 3 should not be contaminated by foreign matter in order not to risk damage or functional failure. In the case of oil-lubricated bearings, this is ensured only by a complete oil seal, which cannot be achieved or can only be achieved at high cost. The air bearing thus also results in a more reliable drive system, especially when used with the fuel cell 3.

While the invention has been described above and defined in the appended claims, it should be understood that the invention may alternatively be defined according to the following embodiments:

1. a support system (10) for a rotor (400) of an electric motor (2), comprising:

a stator (100);

at least one radial bearing (200);

it is characterized in that the preparation method is characterized in that,

the stator (100) forms part of the radial bearing (200).

2. The support system (10) of embodiment 1, wherein the radial bearing (200) is an air bearing.

3. The bearing system (10) according to one of embodiments 1 or 2, wherein the radial bearing (200) is formed in the radial direction (24) between the stator (100) and a rotor (400) of the electric motor (2) which is inserted into the stator (100) in the operating state.

4. The support system (10) according to any one of the preceding embodiments, wherein the stator (100) is designed such that several bearing membranes (210, 220) can be fixed on the stator (100).

5. The support system (10) according to any one of the preceding embodiments, wherein the stator (100) comprises at least one groove (120) for fixing the bearing membrane (210, 220), said groove extending radially (24) into the stator (100).

6. The bearing system (10) according to embodiment 5, wherein the groove (120) is designed to fix the bearing membrane (210, 220) in a position in the radial direction (24) and/or in the circumferential direction (26) in a position-proof manner, in particular wherein the groove (120) has an L-shaped cross section, particularly preferably wherein the groove (120) has a T-shaped cross section.

7. The support system (10) of any of embodiments 5 or 6, wherein the groove (120) is disposed on a can inner surface (150) of the stator (100).

8. The support system (10) of any of embodiments 5-7, wherein the stator (100) includes a plurality of winding ribs (110) extending in a radial direction (24), and wherein the groove (120) is disposed in one of the winding ribs (110).

9. The support system (10) of any of embodiments 5-8, wherein the stator (100) includes a plurality of packing ribs (132) extending in an axial direction (22), and wherein the groove (120) is disposed in one of the packing ribs (132).

10. The support system (10) of any of embodiments 5-9, wherein the groove (120) extends the entire length of the stator (100) in the axial direction (22).

11. The support system (10) of any of embodiments 5-10, wherein the groove (120) extends in an axial direction (22) from the first axial end (142) of the stator (100).

12. The support system (10) of any of embodiments 5-11, wherein the groove (120) extends in an axial direction (22) from the second axial end (144) of the stator (100).

13. The support system (10) of any of embodiments 5-12, wherein the groove (120) does not extend to an axial center (152) of the stator (100).

14. The support system (10) of any one of the previous embodiments, comprising a first radial bearing (200a) and a second radial bearing (200b), wherein the first radial bearing (200a) is disposed at a first axial end (142) of the stator (100), and wherein the second radial bearing (200b) is disposed at a second axial end (144) of the stator (100).

15. The support system (10) of embodiment 14, further comprising at least one spacer (300) seated on a can inner surface (150) of the stator (100) and by means of which the first radial bearing (200a) and the second radial bearing (200b) are spaced apart from each other in the axial direction (22).

16. The bearing system (10) according to embodiment 15 as dependent on embodiment 5, wherein the spacer (300) comprises a fixing portion which is designed to be able to be fitted into the recess (120), in particular to be able to be moved in the axial direction (22) into the recess (120).

17. The bearing system (10) according to any one of embodiments 15 or 16, wherein the spacer (300) is designed in the axial direction (22) in a substantially rib shape.

18. The bearing system (10) according to any one of embodiments 15 to 17, wherein the spacer (300) is designed in a substantially cylindrical segment shape in a circumferential direction (26) around the axis of the stator (100).

19. The support system (10) according to any one of the previous embodiments, wherein the radial bearing (200) comprises at least one wave film (210) and/or at least one smooth film (220) arranged along the inner circumferential surface (170) of the stator (100).

20. The bearing system (10) according to embodiment 19, wherein the wave shaped membrane (210) and/or the smooth membrane (220) are designed as ring segments around the axis of the stator (100).

21. The support system (10) of any of embodiments 19 or 20, wherein the smoothing membrane (220) is disposed against the undulating membrane (210) radially inward of and immediately adjacent to the undulating membrane (24).

22. The support system (10) of any one of embodiments 19 to 21, wherein the corrugated membrane (210) is arranged adjacent to the stator (100) in a radial direction (24) against the stator.

23. The support system (10) of any of embodiments 19-22, wherein the wave shaped membrane (210) is designed to bias the smooth membrane (220) in a radial direction (24) towards a rotor (400) of the electric motor (2) that is encased in the stator (100) in an operational state.

24. The support system (10) of any of embodiments 19 to 23, wherein the undulating membrane (210) is designed to be elastically compressible between the smoothing membrane (220) and the stator (100) by movement of the smoothing membrane (220) in the radial direction (22), so that an air gap can be formed in the radial direction (24) between the smoothing membrane (220) and the rotor (400) which is incorporated into the stator (100) in the operating state.

25. Support system (10) according to any one of embodiments 19 to 24, as far as dependent on embodiment 3, wherein the wave-shaped membrane (210) and/or the smooth membrane (220) respectively comprise at least one locking element (250) designed to be inserted into a groove (120) of the stator (100) in order to fix said wave-shaped membrane (210) and/or said smooth membrane (220) in a manner preventing misalignment in the circumferential direction (26) and/or in the radial direction (24).

26. The bearing system (10) according to embodiment 25, wherein the respective locking element (250) projects in the installed state in the radial direction (24) from the corrugated membrane (210) and/or the respective smooth membrane (220), in particular wherein the locking element (250) is designed as a rib-like projection which extends in the radial direction (24) and in the axial direction (22).

27. The support system (10) of any of embodiments 25 or 26, wherein the locking element (250) has an L-shaped, preferably T-shaped cross-section.

28. The support system (10) of any of embodiments 19-27, further comprising at least one axial lock (270) designed to fix the corrugated membrane (210) and/or the smooth membrane (220) and/or the spacer (300) against axial (22) movement.

29. The support system (10) of embodiment 28, comprising a first axial lock (270a) disposed on the first axial end (142) of the stator (100).

30. The support system (10) of any of embodiments 28 or 29, comprising a second axial lock (270b) disposed on the second axial end (144) of the stator (100).

31. The support system (10) of any of the preceding embodiments, further comprising a thrust bearing (800).

32. A supercharging device (1) comprising:

a shaft (500);

an electric motor (2) comprising a rotor (400), wherein the rotor (400) is arranged on the shaft (500); and

at least one compressor wheel (600);

it is characterized in that the preparation method is characterized in that,

characterized in that the supercharging device (1) comprises a support system (10) according to any of the preceding embodiments, wherein the stator (100) is part of an electric motor (2), and optionally wherein the supercharging device (1) is designed for use with a fuel cell (3).