EP4073395A1

EP4073395A1 - Bearing holder for receiving a bearing

Info

Publication number: EP4073395A1
Application number: EP20820401.6A
Authority: EP
Inventors: Johannes Lang; Adrian Zajac
Original assignee: Efficient Energy GmbH
Current assignee: Efficient Energy GmbH
Priority date: 2019-12-11
Filing date: 2020-12-07
Publication date: 2022-10-19
Also published as: CN115087806A; DE102020210331A1; US20220307550A1; JP2023505901A; WO2021116016A1

Abstract

A bearing holder (10) comprises an inner portion (30) and an outer portion (20), wherein the inner portion (30) has a receiving contour for receiving a bearing, and the outer portion (20) is designed to be attached to a housing. A transition region (25) between the inner portion (30) and the outer portion (20) has a spring (55). The transition region (25) lies at least partially in a plane perpendicular to an axial axis (70) of the receiving contour and lies at least partially in one plane with at least one part of the inner and of the outer portion (20, 30). The transition region (25) has a damper (80) and the damper (80) is designed to dampen a vibration of the inner portion (30) in order to reduce a transmission of the vibration from the inner portion (30) to the outer portion (20). Furthermore, an electric motor, a method for producing a bearing holder (10) and methods for operating a bearing holder (10) are described.

Description

Bearing holder for receiving a bearing

description

The present invention relates to a bearing holder for receiving a bearing which can accommodate a rotor of an electric motor, such an electric motor being used as a compressor motor in heat pumps which is operated with water as the working fluid.

Fig. 1 shows a bearing holder known from DE 102016 203411 A1. The bearing holder is held on a motor housing by means of a spring arrangement (not shown). The spring arrangement is designed to allow a tilting deflection of the bearing holder with respect to the motor housing at least around one, preferably two tilting axes, which are perpendicular to an axis of the motor shaft, while preferably a translational deflection in the direction of the motor shaft is difficult or avoided is. The bearing section can thus give way to the tilting of the motor shaft due to the spring arrangement so that it can rotate on its axis of inertia. As a result, no permanent additional force is exerted on the bearings, since the entire bearing holder can be deflected

Furthermore, the bearing holder is not only coupled to the motor housing with a spring arrangement, but also with an additional damping arrangement. This ensures that vibrations of the bearing holder with respect to the motor housing, which are undesirable, that is to say which would, for example, result in a resonance increase, are suppressed or resonances are damped. The damping system is particularly useful in the event of a shock to the motor in order to bring the motor shaft back to its axis of inertia relatively quickly. The damping system has also proven particularly useful when starting up the engine when the engine shaft is driven through the rigid body resonances.

The bearing holder 10 of DE 102016203411 A1 has an outer section 20 and an inner section 30 as well as a spring arrangement 40. The spring arrangement 40 also has two or more spring legs 50 evenly distributed over the circumference of a circle. The damping system (not shown) is implemented by one or more elastic damping elements, such as for example O-rings, which, due to the Tilting deflection of the bearing holder with respect to a motor housing are continuously “rolled” so that the bearing holder can, as it were, emit energy due to a vibration via the work performed on the damping belt.

1 shows that the spring arrangement 40 of the bearing holder 10 has two or more elongated springs 50, the spring struts each having a spring section which extends parallel to the axis of a motor shaft (not shown).

US Pat. No. 8,282,285 B2 discloses a bearing holder which has a structure extending in the circumferential direction in order to essentially transfer a radial bearing load to a housing when a radial deflection or deformation of the structure extending in the circumferential direction caused by the radial bearing load is within a predetermined limit lies. For this purpose, the bearing holder comprises an inner section and an outer section. A wave-shaped structure is arranged between the inner section and the outer section and transfers the bearing load to the housing.

The US 6,224,533 B1 discloses a support device for a centrifuge rotor which is provided between a frame element and a bearing holder and is arranged so that it absorbs relative movements between the centrifuge rotor and the frame element.

EP 2 800913 B1 discloses a turbo machine which, among other things, includes a bearing holder. The bearing holder is secured to a housing at a first section, while a second section is radially movable with respect to the first section. The second section is connected to a radial bearing and is configured to move axially to eliminate thrust loads on the radial bearing.

EP 1 890 041 B1 discloses an arrangement for mounting a shaft of a vacuum pump with a housing with a first bearing and a second bearing. The first bearing generates forces in the direction of the shaft axis and has an axial rigidity. The second bearing is designed as a roller bearing and is arranged in a bearing holder with axial and radial rigidity. The bearing holder is designed such that a rigidity in the axial direction is greater than a rigidity in the radial direction, the axial rigidity of the bearing holder being greater than that of the first bearing. DE 102016 212552 A1 discloses an electric compressor designed as an electric motor-operated impeller compressor for arrangement in a charging system of an internal combustion engine. A compressor impeller and a rotor are arranged on a common rotor shaft and connected to the rotor shaft in a rotationally fixed manner. The rotor shaft is only rotatably supported in an area between the compressor impeller and the rotor by means of a bearing arrangement around the rotor axis of rotation, the bearing arrangement being received in a bearing seat of a one-piece bearing seat housing part and at least one vibration-damping component being arranged between the bearing arrangement and the bearing seat.

WO 2018 181 186 A1 discloses a bearing assembly with a rotating shaft, a bearing which is mounted in a housing in such a way that it supports the rotating shaft with respect to a housing. Further, the bearing structure includes an inner race through which the rotary shaft is inserted and an outer race having an annular groove portion formed on an outer peripheral surface facing an inner wall surface of the housing. In addition, the bearing assembly includes an O-ring that is disposed on the groove portion of the outer race of the bearing, protrudes outward in a radial direction with respect to the outer peripheral surface, and comes into contact with the inner wall surface of the housing. A clearance is formed between the inner wall surface of the housing and the outer peripheral surface of the bearing. The clearance is larger than a radial displacement amount of the O-ring.

JP 2017 166553 A discloses a bearing device with a bearing, a bearing holder and an elastic element, the bearing having a horizontal axis and being provided for mounting a shaft extending in the horizontal direction.

Generally problematic with bearing holders for electric motors and especially with electric motors that are operated at high speeds are the heating and the oscillations or vibrations that occur in the bearing area. Typically, contact bearings are used, such as ball bearings or roller bearings. With such contact bearings, friction occurs, which leads to a power loss. On the one hand, this power loss is problematic in that it has to be dissipated and, on the other hand, it is problematic in that, if it is not dissipated or not dissipated sufficiently, it increases bearing wear and thus reduces the service life of the bearing and the entire electric motor. At the same time, the problems with imbalances become greater, the greater the speeds of the electric motors, since the bearing holder as such increases begins to swing. This means that with such contact bearings vibrations occur at high speeds that have to be damped so that the bearing holder is exposed to less mechanical stress. Otherwise the service life of the bearing and the entire electric motor is also reduced. In general, the power loss increases the higher the speeds and the higher the imbalances.

However, high speeds are required in order, for example, to operate a heat pump with a reasonably acceptable volume that uses water as the working medium. Water has the property that water generates a great deal of water vapor in relation to a certain volume of liquid water. In principle, this is advantageous for the overall efficiency of the heat pump. However, this large amount of steam must be conveyed away and, in particular, compressed. Compressor motors are therefore required which, if they are not to be too large, have to run at very high speeds, for example at speeds greater than 50,000 rpm. However, the problem with such high-speed motors is the bearing power loss and ultimately the bearing life. The faster the motor is operated, the more power it generates and the shorter its service life. All of these points are disadvantageous because a high power loss means that the efficiency of the electric motor is reduced. In addition, a reduced service life leads to higher costs or, on the other hand, in order to still achieve a sufficient service life, to extreme demands on the components, to the extent that the components and in particular the bearings have to withstand the high power losses with little wear.

The object of the present invention is to provide an improved bearing holder for an electric motor, an electric motor with such an improved bearing holder and an improved method for producing and operating a bearing holder.

This object is achieved by a bearing holder according to claim 1, an electric motor according to claim 26, a method for producing the bearing holder according to claim 28 or a method for operating the bearing holder according to claim 31.

The bearing holder according to the present teaching includes an inner portion and an outer portion; wherein the inner section has a receiving contour for receiving a bearing and the outer section is designed to to be attached to a housing. A transition area between the inner section and the outer section has a spring. The transition area lies at least partially in a plane perpendicular to an axial axis of the receiving contour and at least partially in a plane with at least part of the inner and outer sections. Furthermore, the transition area has a damper and the damper is designed to dampen an oscillation of the inner section in order to reduce and, ideally, completely eliminate a transmission of the oscillation from the inner section to the outer section.

The spring provided in the transition area can comprise several spring elements, each spring element being to be regarded as a spring. The springs are preferably arranged along a circumference in the transition area between the inner and the outer section. The springs are preferably formed along a transition surface. The springs are preferably flat. In particular, flat is to be understood here as meaning that the springs extend in a plane perpendicular to the axial axis of an inserted rotor. When the springs are vibrated, for example by moving the rotor, the springs vibrate in the plane perpendicular to the axial axis.

The transition area comprises a transition volume, and thus a plurality of transition planes, which extends from a lower surface of a cover plate to an upper surface of a cover plate between the inner section and the outer section. The transition volume includes the spring or springs. The transition area or the transition volume thus comprises a plurality of transition planes which are perpendicular to the axial axis. In other words, the transition volume forms a gap between the inner section and the outer section. The springs can consequently oscillate in the transition area and thus in the transition planes lying parallel to one another. The transition volume or the transition area is consequently defined by an outer circumference of the inner section, by an inner circumference of the outer section and by an upper and a lower surface of two opposing cover plates. In other words, the transition region lies at least partially in a plane perpendicular to an axial axis of the receiving contour and lies at least partially in a plane with at least part of the inner and outer sections. The transition planes of the transition area are thus horizontally extending planes in which the spring or springs vibrate. Even if the spring is in the transition levels of the transition area swing, extends the spring or the springs parallel to the axial axis, in particular between the opposite cover plates. Each individual spring is a three-dimensional structure, the oscillation of a spring taking place in a plane parallel to the axial axis.

The transition volume or the transition area are flooded with a coolant, such as, for example, water or a refrigerant. As a result, each spring can be damped on the one hand and, on the other hand, heat can be dissipated from the spring via the coolant at the same time. The transition volume forms a gap between the inner and outer sections. During operation, the coolant is continuously introduced into the transition area and discharged again from the transition area. In other words, the transition area has a damper, namely, for example, the coolant in the transition area, and the damper is designed to dampen a vibration of the inner section in order to reduce a transmission of the vibration from the inner section to the outer section . The vibrations of the individual springs are assigned to the inner section, since a vibration from a moving rotor is first transmitted to the inner section, so that the springs begin to vibrate.

The receiving contour for receiving a bearing into which a rotor can be inserted preferably has a hollow cylindrical shape. Due to the hollow-cylindrical shape, a bearing can be introduced into the bearing holder. The receiving contour can, however, also have a geometry that deviates from the cylindrical shape. It is important that the hollow area of the receiving contour can accommodate a bearing. Accordingly, the hollow area of the receiving contour is designed to be complementary to an outer circumference of the bearing.

The proposed bearing holder enables the vibrations that occur to be decoupled by means of a spring arrangement or a contour arrangement which can be implemented in a small installation space.

The proposed bearing holder can be mounted on a housing of a turbo compressor or a refrigeration device. In general, the proposed bearing holder can be attached to devices which comprise rotating shafts, spindles or a rotor in order to hold the same. In other words, the proposed bearing holder can be used wherever vibrations arise which are caused by another egg. ment, often the device itself, must be decoupled or attenuated. With the proposed bearing holder, the service life of the bearing holder can be improved. This is because, on the one hand, the proposed bearing holder can dampen a vibration and, at the same time, heat that arises or occurs in the area of the bearing holder can be dissipated. Damping and heat dissipation can be done in a compact manner in a narrow space with the proposed bearing holder. In the present case, the means for damping (coolant, springs and / or elastomer in the transition area) of a vibration and the means for heat dissipation (coolant and / or elastomer in the transition area) are used in a synergetic manner, whereby the bearing holder as such has a compared to Bearing holders known from the prior art have smaller dimensions, that is to say extension. In particular, an extension along the axial axis of the rotor is smaller, as a result of which a transmission surface between the rotor and the bearing holder is also smaller. By decoupling the rapidly rotating system, for example a rotor of a radial turbo compressor, from the housing, noise development and stress on the bearing can be reduced, which increases the service life of the bearing holder or the rotating system as such.

With the bearing holder proposed herein, predetermined degrees of damping can be achieved or implemented so that, among other things, critical bending frequencies of the system in which the bearing holder is installed can be placed in certain areas depending on the planned working area of the system or the electric motor.

Another aspect of the present technical teaching relates to an electric motor in which a rotor is in operative connection with the proposed bearing holder. An electric motor, which is designed with the proposed bearing holder, can be operated at high speeds, for example, since the bearing holder is designed to reduce vibrations and, in the best case, to eliminate them. As a result, the service life of an electric motor or the period in which maintenance would have to be carried out can be extended.

Another aspect of the present technical teaching relates to a method for the manufacture of the bearing holder, in which a bearing holder can be modeled and manufactured in accordance with the performance that an electric motor should or must provide, in which the bearing holder is installed. The proposed warehouse keeper can be inexpensive gen processes such as 3D laser cutting or water jet cutting. However, it would also be conceivable to manufacture the proposed bearing holder by means of wire EDM or milling. When producing the bearing holder, for example, the radial and axial rigidity can be easily adjusted via the material thickness and / or the cutting pattern with which the springs are formed. Another aspect of the present technical teaching relates to a method for operating the Lagerhal age, in particular after its manufacture.

Preferred exemplary embodiments of the present invention are explained in detail below with reference to the accompanying drawings. Show it:

1 shows a bearing holder known from the prior art,

2a shows a bearing holder with an indicated outer section

FIG. 2b an enlargement of a section of the bearing holder according to FIG. 2a,

3 shows a bearing holder according to the technical teaching proposed herein,

FIG. 4 shows another perspective of the bearing holder according to FIG. 3,

5a shows a perspective view of a bearing holder according to the technical teaching proposed herein,

FIG. 5b shows a plan view of the bearing holder according to FIG. 5a,

6 shows an enlargement of a section of the bearing holder according to FIGS. 3 and 4, p _j g a perspective view of a bearing holder according to the technical teaching proposed herein,

Fig. 8 is a plan view of the bearing holder according to Fig. 7, and Fig. 9 is a schematic representation of an electric motor in a Turboverdich ter with a bearing holder according to the technical teaching proposed herein.

Individual aspects of the technical teaching described herein are shown below in FIGS. 1 to 9. In the present application, the same reference numerals relate to the same or equivalent elements, although not all reference numerals in all drawings, if they are repeated, are presented again.

Figs. 2 to 5 and Figs. 7 and 8 each show a warehouse keeper. The bearing holder shown in DE 10 2016203411 A1, which is shown in FIG. 1, has already been described in a leading part of the application. The in Figs. 3 to 5 and Figs. 7 and 8 shown bearing holder 10 each have an inner portion 30 and an outer portion 20 from; wherein the inner section 30 has a receiving contour 32 for receiving a bearing, which in turn can be used for receiving a rotor (not shown). As shown in FIGS. 2 and 5, for example, a receiving contour 32 for receiving a bearing is arranged within the inner section 30. Such a recording contour can also be seen in the other figures, with the exception of FIG. 9, although it is not provided with a reference number in order not to overload the individual figures. The bearing holder 10 shown in Fig. 2 shows the inner section 30 completely, while the outer section 20 is only partially shown in sketch. As shown in Figs. 2 to 5 and Figs. 7 and 8, the receiving contour 32 can be designed as a hollow cylinder which has a relief 32a for receiving the bearing. The outer section 20 is designed to be attached to a housing, in particular a turbo compressor or a refrigeration device. For this purpose, for example, bores 92 are provided on a base 34, which can be part of the outer section 20, so that the outer section 20 can be fastened to the housing 90. For example, the outer section can be screwed to the housing 90. In such a case, the bores 92 can be threaded.

The area between the outer section 20 and the inner section 30 defines a transition area 25. The transition area 25 has a transition surface 35 which couples the inner section 30 and the outer section 20 to one another, in particular connects them. The transition region 25 between the inner section 30 and the outer section 20 has a spring 55. Here, the spring 55 can also can be provided as a spring arrangement 40 made up of several springs 55, as can be seen in FIGS. 2, 5, 7 and 8, for example. Furthermore, the spring 55 can have straight contours 56, so that the webs 57 formed by the contours 56 form spokes 58, as shown in FIGS. 7 and 8 is shown. Alternatively, the spring 55 can have curved contours 56, so that the webs 57 formed by the contours 56 have a curved course 59. The curved course 59 can be wave-shaped, as shown in FIGS. 2a and 2b, which, like a sine wave, has a periodicity. In this case, the course of the wave defines the ratio of the radial to the axial stiffness of the resulting spring 55. Alternatively, the curved course 59 can run in such a way that webs 57 are formed with a curved pattern that does not have any periodicity like a sine wave like this for example in Figs. 5a and 5b is shown. In Fig. 2b three springs 55 are shown. For example, the in Figs. 5a and 5b, the three springs 55 shown each have only one period of the curved course 59. Also in Figs. 5a and 5b show three springs 55 with webs 57, each spring 55 having a non-periodic curved profile 59. The three springs according to Figs. 7 and 8 are designed as spokes 58 with a straight contour 56 which forms the webs 57.

Each spring 55 is formed by a first contour 56 and a second contour 56, the first contour 56 and the second contour 56 each forming a web 57. The webs 57 are connected at a first end to the inner section 30 and at one end second end connected to the outer section 20. The webs 57, which form the springs 55, are formed in the transition surface 35 in the transition region 25. The transition area thus lies at least partially in a plane perpendicular to an axial axis 70 of the receiving contour 32 and lies at least partially in a plane with at least part of the inner and outer sections 20, 30.

As shown in Figs. 2 to 5 and Figs. 7 and 8, the springs 55 are distributed symmetrically about the axial axis 70 between the inner section 30 and the outer section 20. The springs 55 are distributed, in particular, in a plane perpendicular to the axial axis 70. The plane perpendicular to the axial axis 70 is spanned, for example, by an xy plane, while the axial axis 70 runs longitudinally to a z-direction. In such a case, the springs 55 oscillate in the xy plane with deflections in the xy plane. Up to six, preferably three, springs 55 can be arranged symmetrically distributed around the axial axis 70. The spring 55 or the springs 55 extend or extend in the transition area 25 and is or are designed to oscillate in a plane, in particular an xy plane, parallel to the transition surface 35. This is indicated in FIG. 2b by arrows 110 and 120, for example. The xy plane (s) defines, for example, a horizontal plane (s).

The transition area 25 also has a damper 80, as can be seen in FIGS. 3 and 4. The damper 80 is designed to dampen a vibration of the inner section 30 in order to reduce a transmission of the vibration from the inner section 30 to the outer section 20. Ideally, the vibrations are not only dampened, but also eliminated. Damping or elimination can occur in particular with vibrations with very high frequencies. The oscillation of the individual springs 55 is assigned to the inner section 30, since the oscillation is first transmitted from a moving rotor (not shown) to the inner section 30, so that the springs 55 begin to oscillate. The springs 55 begin to oscillate in the transition surface 35, that is to say in an x-y plane or in particular in a horizontal plane.

The damper 80 comprises an elastomer 81 and / or a squeeze liquid damper 82. The squeeze liquid damper 82 comprises a squeeze fluid 85 which, for example, can be continuously fed into a gap 84 and removed from the gap 84 during operation. The elastomer 81 can be designed in the form of O-rings 83 or rectangular rings, wel che are also called K-rings. The elastomer 81 can, for example, be arranged in different positions. This means that a number of O-rings 83 or K-rings can be provided in order, for example, to provide a seal or damping, in particular of the inner section 30. The inner section 30 and the outer section 20 are spaced apart from one another by the gap 84 in which the squeeze liquid damper 82 is arranged. The gap 84 defines a transition volume. In other words, a transition volume is spanned through the gap 84, which, starting from the transition surface 35, extends parallel to the axial axis 70. The squeeze fluid damper 82 can also be a squeeze fluid damper, that is, a squeeze fluid 85, in particular when a gas is used in the damper 82 instead of a liquid. In both cases, a squeezing fluid is introduced into the transition volume of the gap 84. In other words, the squeezing fluid damper 82 for damping vibrations is filled with a squeezing fluid 85. The squeeze fluid 85 is preferably a liquid. However, it is also conceivable to use a gas as the squeeze fluid. It is advantageous if the squeezing fluid 85 is suitable for damping vibrations and transporting away heat. The squeeze fluid 85 functions as a coolant that can also dampen vibrations. For example, the coolant can be a system medium such as a refrigerant or water.

The transition volume of the squeeze fluid damper 82 is formed as the gap 84 between the inner and outer sections 20, 30, in which cooling fluid can be continuously supplied during operation of the bearing holder 10 in order to dampen vibrations and to dissipate heat. A continuous supply and removal of the coolant or the squeeze fluid 85 into and out of the gap 84 can take place via a coolant inflow 87 and a coolant outflow 88. The gap 84 of the squeeze liquid damper 82 is sealed with the elastomer 81, which is simultaneously designed to dampen the vibrations and / or absorb heat. When absorbing heat, the elastomer 81 and the material surrounding the elastomer expand according to their coefficients of expansion.

In Figs. 3 and 4 it is shown, for example, that the elastomer 81 is arranged in the form of O-rings 83 at different positions. For example, an O-ring 83 is provided at the upper and lower transition between the upper and lower cover plate 91 and the inner section 30. In addition, an O-ring 83 is provided at the upper and lower transition between the upper and lower cover plate 91 and the outer section 20, for example.

FIG. 4 also shows a transition between a lower cover plate 91 and the inner section 30, which has a further cover gap 95. The cover gap 95 is highlighted by a border 2 in FIG. 4 and in an enlarged illustration in FIG. 6. The cooling liquid can penetrate into the cover gap 95. The liquid that has penetrated into the cover gap 95 can on the one hand support the damping of the vibrations during operation and on the other hand the cooling liquid can simultaneously cool the O-ring 83 or the elastomer 81 and / or the outer circumference of the inner section 30. The elastomer 81 is consequently arranged as an elastic O-ring 83 on an outer circumference of the inner section 30. Furthermore, the elastomer 81 is designed as an elastic O-ring 83 and is arranged on an inner circumference of the outer section 30.

It is also conceivable that the squeeze liquid damper 82 has a cooling gas or a permanent cooling liquid, which is introduced into the gap 84 in a sealed manner when the bearing holder 10 is manufactured by means of the elastomer 81. Is a permanent one If cooling liquid or no cooling liquid at all but a cooling gas is provided in the gap 84, no coolant inflow 87 and no coolant outflow 88 need to be provided. Rather, the permanent cooling liquid or the cooling gas is introduced into the gap 84 during manufacture of the bearing holder 10 and closed, in particular sealed, by means of the cover plates 91 and the elastomer 81.

Figs. 2, 5, 7 and 8 show that the spring 55 and one or more further springs 55 are arranged in the transition region 25, which is designed in a circular ring shape and encloses the squeeze liquid damper 82. Preferably and according to FIGS. 5, 7 and 8, three springs 55 are arranged in the transition area 25.

Figs. 3 and 4 show how cover plates 91 are positively arranged between the inner and outer sections 30, 20 and how one end of the outer section 20, one end of the inner section 30, the elastomer 81 and one surface of the cover plate 91 form a planar surface 93 form. Here, the cover plates 91 extend perpendicular to the axial axis 70. The cover plates 91 are spaced apart from one another by an expansion of the springs 55 parallel to the axial axis 70. In this way, a volume of the squeeze liquid damper is determined which corresponds to the volume of the gap 84. Because by an outer circumference of the inner section 30 and an inner circumference of the outer section 20 as well as by at least one cover plate 91 arranged at the ends of the inner and outer sections 20, 30, a volume of the squeeze liquid damper 82 is spanned in which the coolant over the at least a coolant inflow 87 can be introduced.

The outer section 20 preferably has a coolant inflow 87 and a coolant outflow 88, the coolant inflow 87 being provided for supplying a coolant between the inner and outer sections 20, 30. In other words, the coolant inflow 87 is provided for feeding a coolant into the transition region or into the squeeze liquid damper. The coolant outflow 88 is provided for discharging the coolant between the inner and outer sections 20, 30. A single coolant inflow 87 and a single coolant outflow 88 are preferably provided, which can be arranged diametrically to one another. It is also conceivable that the single coolant inflow 87 and the single coolant outflow 88 are arranged at two positions of the circular shape of the outer section 20 in such a way that the single coolant inflow 87 and the single coolant outflow 88 form an angle between see 90 ° and 175 ° span. It is also conceivable that more than one coolant inlet 87 and more than one coolant outlet 88 is provided in the outer section 20 (see FIGS. 4, 5, 7 and 8). These are then arranged, for example, symmetrically on the circular ring shape. For example, an even number of coolant inflows 87 and an even number of coolant outflows 88 can be provided. Preferably, two coolant inflows 87 and two coolant outflows 88 can be provided, the coolant inflows 87 being arranged diametrically to one another and the coolant outflows 88 being arranged diametrically to one another. A coolant inflow 87 and a coolant outflow 88 can be formed by a bore 92 or by a recess 94. FIG. 2 shows the coolant inflow 87 or the coolant outflow 88 as a recess 94, which can also be arranged in the inner section. FIGS. 4, 5, 7 and 8 show the coolant inflow 87 and the coolant outflow 88 as a bore 92. The bores or the recesses can for example be designed with a thread, in particular milled, so that the coolant inflow 87 and / or the coolant drain 88 can be closed by screwing in a screw.

At least part of the coolant inflow 87 and at least part of the coolant outflow 88 and the spring 55 are preferably located in at least one cross-sectional plane perpendicular to the axial axis 70 of the receiving contour 32. This allows the bearing holder 10 to be made more compact. In particular, the proposed bearing holder 10 has a smaller extension along the axial axis 70 compared to the bearing holders known from the prior art. It can be the case, for example, that the proposed bearing holder, with the same rigidity as a classic bearing holder, has an extension which is essentially four times smaller than the classic bearing holder. This has the consequence that the contact surface of an introduced ball bearing, in which a rotor (not shown) is introduced, turns out to be smaller. This in turn results in less friction between the rotor and the bearing holder, as a result of which a power loss of the rotor or the electric motor can be reduced.

The inner section 30, the outer section 20, the spring 55, the elastomer 81 and the squeeze liquid damper 82 or the damper 80 are preferably designed in such a way that when vibrations occur, in particular at frequencies from 40 Hz or between 40 and 1000 Hz, the inner section is decoupled from the outer section. The inner section 30 is particularly preferably decoupled from the outer section 20 when oscillations in the frequency range of the natural oscillations of the rotor occur. This can prevent the bearing holder or the electric motor from being destroyed. Because in damped systems a natural oscillation can correspond to a possible resonance oscillation. However, resonance vibrations should be avoided in order to avoid destruction of the electric motor.

In Figs. 2 to 5 and Figs. 7 and 9, the base 34 can also be seen. The base 34 preferably has bores through which the bearing holder 10 can be mounted, in particular screwed, onto a housing 90 (only shown in FIG. 9).

9 shows a schematic illustration of a compressor which comprises a proposed electric motor and the proposed bearing holder 10. The proposed electric motor comprises a motor casing 290 which is a housing 90 for the electric motor. The electric motor also includes a motor shaft 260 having a first end and a second end. The proposed electric motor also includes a, in particular first, bearing holder 10 described herein, which is coupled to the motor casing 290 or to the housing 90 of the electric motor. The bearing holder 10 is preferably screwed to the motor casing 290. In particular, a first bearing holder 10 is arranged at or near the first end of the motor shaft 260, the first end of the motor shaft being the same as a first rotor end 62. To attach the bearing holder 10 to the housing 90, the base 34 of the bearing holder 10 has bores 92.

In addition, the electric motor has a bearing section 280 for bearing the motor shaft 260 or a rotor 60 with the bearing holder 10. Furthermore, the electric motor comprises an element 300 to be driven, which is attached to or near one, in particular a second, end of the motor shaft. The second end of the motor shaft 260 does not correspond to a second rotor end 64. Between the second rotor end 64 and the second end of the motor shaft 260, as can be seen in FIG. 9, the element 300 to be driven is placed. The element 300 to be driven can be, for example, an impeller or another element known to a person skilled in the art. The driven element 300 may be secured to the motor shaft 260 at the second end of the motor shaft with a shaft nut 220.

A drive section 320 is arranged between the bearing section 280 and the element 300 to be driven and has a rotor 60 and a stator 250. The stator 250 and the rotor 60 of the motor shaft 260 are enclosed by the housing 90, as can be seen, for example, in FIG. 9. The element to be driven 300, which is attached to a in particular the second end is arranged on the motor shaft 260, is spaced apart by one or more spacer sleeves 310 from a further, in particular second, bearing holder 10. The first bearing holder 10 is arranged on the first rotor end 62 and the second bearing holder 10 is arranged on the second rotor end 64. In other words, a further, ie second, bearing holder 10 described herein is arranged between the drive section 320 and the element 300 to be driven. The drive section 320 is between the first bearing holder 10 and the second bearing holder 10, that is, a bearing holder 10 and a further bearing holder 10, is arranged. The further bearing holder 10 can, for example, be coupled with its inner section 30 to a fixed bearing 240 of the rotor 60. The first bearing holder 10 can be coupled with its inner section 30 to a floating bearing 270. The springs 55 of the bearing holders 10 are sketched schematically in FIG. 9, but the bearing holders have the springs 55 described herein, as they are, for example, shown in FIGS. 2 to 5 and 7 and 8 are shown.

Another aspect of the present technical teaching relates to a method for producing a bearing holder 10 with an inner section 30 and an outer section 20, the inner section 30 having a receiving contour 32 for receiving a bearing in which a rotor 60 can be received and the outer section 20 is designed to be attached to a housing 90 and has a spring 55 in a transition region 25 between the inner section 30 and the outer section 20. The method for producing a bearing holder 10 comprises arranging the transition area 25 at least partially in a plane perpendicular to an axial axis 70 of the receiving contour 32 and at least partially in a plane with at least part of the inner and outer sections 20, 30. For example, the Bearing holder 10 consist of a one-piece element which comprises the inner and outer sections 20, 30. The arrangement of the transition region 25, which has springs 55 and which is arranged between the inner and outer sections 20, 30, can be produced, for example, by 3D laser cutting or by water jet cutting. Contours 56, which form the springs 55, can be cut in the transition region 25 by 3D laser cutting or by water jet cutting. The method for producing a bearing holder 10 further comprises arranging a damper 80 in the transition region 25, the damper 80 damping an oscillation of the inner section 30 and thereby reducing a transmission of the oscillation from the inner section 30 to the outer section 20. The properties of the springs 55 and the elastomer 81 or the damper 80 of the bearing holder 10 are preferably matched to one another in such a way that Vibrations, especially at certain frequencies, can preferably be eliminated.

In this case, the method for producing a bearing holder 10 further comprises specifying an intensity of a damping and / or a heat dissipation of the vibrations that occur; and determining a geometry and a coolant composition of the squeeze liquid damper 82 included in the damper 80. In addition, the method comprises a step of determining a geometry and composition of the spring 55. Depending on the predetermined intensity of the damping, the shape of the spring 55 can be different and / or the number of springs 55 can be different, for example. Furthermore, a selection of a suitable elastomer 81 is included, the physical properties of which are matched to the predetermined intensity of the damping. For this purpose, the method includes the step of determining an elastomer which is designed to dampen vibrations. After all these steps of determining have been carried out, or after each individual step of determining has been carried out, the steps of manufacturing can occur together or each step of manufacturing can be performed individually. In other words, the determined squeeze liquid damper and / or the determined spring and / or the determined elastomer are only produced after the desired properties of the components mentioned have been determined. In this way, a bearing holder can be produced which is matched to the special conditions in which the bearing holder 10 is used. After the individual components have been determined and manufactured, the step of assembling the bearing holder 10, which comprises the determined squeeze liquid damper, the determined spring and the determined elastomer, takes place, the bearing holder 10 damping an oscillation in the specified intensity and / or heat in the dissipates given intensity.

Another aspect of the present technical teaching relates to a method for operating a bearing holder 10 with an inner section 30 and an outer section 20 and a spring 55 and a damper 80 in a transition region 25 between the inner section 30 and the outer section 20. The method for operating a bearing holder 10 comprises the steps of receiving a rotor 60 through the inner section 30, in particular through a bearing in the receiving contour 32 on the inner section 30, and attaching the outer section 20 to a housing 90 which is in operative connection with the rotor 60 . The steps of recording and The order of attachment may also be reversed. After the steps of picking up and attaching have been carried out, the rotor 60, which is in operative connection with the bearing holder 10, can be set in rotation, that is to say in motion. For this purpose, the step of setting the rotor in motion is provided so that vibrations can occur. However, due to the previously determined bearing holder 10 with its determined intensity of damping, the step of damping occurring vibrations in order to reduce a transmission of the vibration from the inner section 30 to the outer section 20 takes place automatically by the bearing holder 10 used, ie without any further external influence.

Depending on the situation, vibrations of different frequencies and different amplitudes usually occur, with a bearing holder 10 being able to be modeled depending on the situation in a method of manufacturing the bearing holder 10 in relation to the specific situation. In other words, a bearing holder 10 described herein can first be produced with the method described herein for manufacturing a bearing holder 10 in order to then be able to use the bearing holder 10 in a method proposed herein for operating a bearing holder 10, whereby its functionality can be used.

For the bearing holder 10 proposed herein, up to three mechanisms for targeted damping or decoupling of the vibrations between the outer and inner sections (20, 30) are disclosed, namely: a) decoupling by means of a spring 55, which is formed by contours 56 and lies in a plane perpendicular to the axial axis 70 of the rotor 60. b) Decoupling by means of squeeze liquid damper 82, the intensity of the damping being adjustable over a width of the gap 84 and / or over a component height of the bearing holder 10. In addition, circulating system water can be used as a medium for steaming. c) Decoupling by means of elastomers 81.

These three mechanisms a) to c) can be used together or separately, or two of the three mechanisms can be used to decouple the vibrations of the system. For example, if only two mechanisms are to be used, both For example, damping or decoupling by means of elastomers 81 and by means of a squeeze liquid damper 82 can be provided. Or damping by means of elastomers 81 alone could be provided.

However, it is particularly preferred to implement all three mechanisms, since this allows system vibrations to be reduced in a synergetic manner. In other words, the three mechanisms presented interact in such a way that damping and heat dissipation are promoted by the interaction of the three mechanisms in addition to the additive superimposition of the three mechanisms. The three mechanisms can each be made stronger or weaker individually when producing the proposed bearing holder 10, so that damping and / or heat dissipation can be controlled in a targeted manner.

Another advantage of the proposed bearing holder 10 is that water, which can be introduced as squeeze liquid into the squeeze liquid damper 82 via the coolant inflow 87 and brought back out of the squeeze liquid damper 82 via the coolant outflow 88, can be used as a refrigerant or system medium. In addition, the bearing holder 10 can be cooled simultaneously with the water or the refrigerant, i.e. the refrigerant is used to dissipate heat. By cooling the bearing holder 10, in turn, the ball bearings which are in contact with the bearing holder 10 can be cooled. For the bearing holder 10, due to the low water vapor atmosphere, the heat in the vacuum is otherwise little, in particular hardly, dissipatable.

As already described, the springs 55 are produced by means of 3D laser cutting or water jet cutting. This enables very precise tolerancing and alignment of the components, which are preferably made of metal.

List of reference symbols

2 ellipse

10 warehouse keepers

20 outer section

25 transition area

30 inner section

32 mounting contour

32a relief

34 base

35 transition surface

40 spring arrangement

50 struts

55 spring

56 contour

57 bridge

58 spoke

59 curved course

60 rotor

62 first rotor end

64 second rotor end

70 axial axis

80 dampers

81 elastomer

82 squeeze liquid damper

83 O-ring

84 gap

85 squeeze fluid

87 Coolant inflow

88 Coolant drain

90 housing

91 cover plate

92 bore

93 planar surface 94 recess

95 cover gap

110 arrows 120 arrows

200 Compressor 210 Impeller 220 Shaft nut 230 Spacer sleeve

240 fixed bearing 250 stator 260 motor shaft 270 floating bearing 280 bearing section

290 engine cover

300 driven element 310 spacer 320 drive section

Claims

A bearing retainer (10) comprising: an inner portion (30) and an outer portion (20); wherein the inner section (30) has a receiving contour (32) for receiving the bearing and the outer section (20) is designed to be attached to a housing (90), with a transition region (25) between the inner section (30 ) and the outer section (20) has a spring (55), the transition region (25) at least partially in a plane perpendicular to an axial axis (70) of the receiving contour (32) and at least partially in a plane with at least part of the inner and outer sections (20, 30), the transition region (25) having a damper (80) and the damper (80) being designed to dampen a vibration of the inner section (30) in order to transmit the vibration from the inner section (30) to the outer section.

2. Bearing holder (10) according to claim 1, wherein the transition region (25) has a transition surface (35) which couples the inner section (30) and the outer section (20) to one another.

3. Bearing holder (10) according to claim 2, wherein the spring (55) extends in the transition region (25) and is designed to oscillate in a plane parallel to the transition surface (35).

4. Bearing holder (10) according to one of the preceding claims, wherein the spring (55) is formed by a first and a second contour (56) and the spring (55) has a web (57) between the first and the second contour (56) ) having.

5. Bearing holder (10) according to claim 4, wherein the web (57) is connected at a first end to the inner section (30) and is connected at a second end to the outer section (20).

6. bearing holder (10) according to claim 4 or 5, wherein the spring (55) rectilinear Kontu Ren (56), so that the webs (56) form spokes (58), or curved Has contours, so that the webs (56) have a curved course (59).

7. Bearing holder (10) according to one of the preceding claims, which has up to six, preferably three, springs (55) distributed symmetrically about the axial axis (70).

8. Bearing holder (10) according to one of the preceding claims, wherein the damper (80) comprises an elastomer (81) and / or a squeeze liquid damper (82).

9. Bearing holder (10) according to claim 8, wherein the inner section (30) and the outer section (20) are spaced apart from one another by the squeeze liquid damper (82), the squeeze liquid damper (82) having a transitional volume which extends from the transition surface (35) extends parallel to the axial axis (70).

10. Bearing holder (10) according to claim 8 or 9, wherein the squeeze fluid damper (82) for damping vibrations is filled with a squeeze fluid.

11. Bearing holder (10) according to one of claims 8 to 10, wherein the squeeze liquid damper (82) is a gap (84) between the inner and outer sections (20, 30) in which the bearing holder (10) is continuously in operation Cooling liquid can be supplied to dampen vibrations and to dissipate heat.

12. Bearing holder (10) according to one of claims 8 to 11, wherein the gap (84) of the squeeze liquid damper (82) is sealed with an elastomer (81) wel Ches is simultaneously designed to dampen the vibrations occurring.

13. Bearing holder (10) according to one of claims 8 to 12, wherein the squeeze liquid damper (84) has a cooling gas or a permanent cooling liquid, wel che when the bearing holder (10) is produced by means of the elastomer (81) sealed in the gap (84 ) is introduced.

14. Bearing holder (10) according to one of claims 8 to 13, wherein the spring (55) and one or more further springs (55) are arranged in the transition region (25) which is designed in an annular shape and the squeeze liquid damper (82) encloses.

15. Bearing holder (10) according to one of the preceding claims, wherein the elastomer (81) designed as an elastic O-ring (83) or as an elastic K-ring is arranged on an outer circumference of the inner section (30).

16. Bearing holder (10) according to one of the preceding claims, wherein the elastomer (81) designed as an elastic O-ring (83) or as an elastic K-ring is arranged on an inner circumference of the outer section (20).

17. Bearing holder (10) according to one of the preceding claims, wherein cover plates (91) form-fitting between the inner and outer sections (20, 30) are angeord net and one end of the outer section (20), one end of the inner section (30 ), the elastomer (81) and a surface of the cover plate (91) form a planar surface.

18. Bearing holder (10) according to one of the preceding claims, wherein the outer section (20) has a coolant inflow (87) and a coolant outflow (88), the coolant inflow (87) for supplying a coolant between the inner and the outer section ( 20, 30) is provided.

19. Bearing holder (10) according to claim 18, wherein at least part of the coolant inflow (87) and at least part of the coolant outflow (88) and the spring (55) in at least one cross-sectional plane perpendicular to the axial axis (70) of the receiving contour (32) lie.

20. Bearing holder (10) according to one of claims 18 or 19, wherein the coolant is a system medium such as a refrigerant or water.

21. Bearing holder (10) according to one of the preceding claims 18 to 20, wherein by an outer circumference of the inner section (30) and an inner circumference of the outer section (20) and by at least one at the ends of the inner and outer sections (20, 30) arranged cover plate (91) a volume of the squeeze liquid damper (82) is spanned, in which the coolant can be introduced via the at least one coolant inflow (87).

22. Bearing holder (10) according to one of the preceding claims 18 to 21, wherein the coolant inflow (87) is arranged diametrically to the coolant outflow (88) in the outer section (20).

23. Bearing holder (10) according to one of the preceding claims 18 to 22, wherein the at least one coolant inflow (87) and the at least one coolant outflow (88) each as a bore (92) or as a recess (94) in the outer section (20) are trained.

24. Bearing holder (10) according to any one of the preceding claims, wherein the inner portion (30), the outer portion (20), the spring (55), the elastomer (81) and the squeeze liquid damper (82) are designed such that at Occurrence of vibrations, in particular at frequencies from 40 Hz or between 40 Hz and 1000 Hz, the inner section (30) is decoupled from the outer section (20).

25. Bearing holder (10) according to one of the preceding claims, wherein the receiving contour (32) for receiving the bearing is a hollow cylinder.

26. Electric motor, having the following features: a motor casing (290); a motor shaft (260) having a first end and a second end; a bearing holder (10) according to any one of claims 1 to 25 coupled to the motor shell (290); a bearing section (280) for bearing the motor shaft (290) with the bearing holder

(10); a driven member (300) attached to or near one end of the motor shaft (260); a drive section (320) which is arranged between the bearing section (280) and the element to be driven (300) and has a rotor (60) and a Sta tor (250).

27. Electric motor according to claim 26, wherein a further bearing holder (10) according to one of claims 1 to 25 between the drive section (320) and the element to be driven (300) is arranged.

28. A method for manufacturing a bearing holder (10) with an inner section (30) and an outer section (20), the inner section (30) having a receiving contour (32) for receiving a bearing and the outer section (20) to it is designed to be attached to a housing (90) and has a spring (55) in a transition region (25) between the inner section (30) and the outer section (20), the method comprising the following steps:

Arranging the transition area (25) at least partially in a plane perpendicular to an axial axis (70) of the receiving contour (32) and at least partially in a plane with at least part of the inner and outer sections (20, 30); and

Arranging a damper (80) in the transition area (25), the damper (80) damping an oscillation of the inner section (30) and thereby reducing a transmission of the oscillation from the inner section (30) to the outer section (20).

29. The method of claim 28 which comprises:

Specifying an intensity of a damping and / or a heat dissipation of the occurring vibrations border;

Determining a geometry and coolant composition of a squeeze liquid damper (82);

Determining a geometry and composition of the spring (55); and or

Determining an elastomer (81) which is designed to dampen vibrations; Producing the determined squeeze liquid damper (82), the determined spring (55) and / or the determined elastomer (81); and

Assembling the bearing holder (10), which comprises the determined squeeze liquid damper (82), the determined spring (55) and the determined elastomer (81), the bearing holder (10) damping a vibration in the specified intensity and / or heat in the specified Intensity dissipates.

30. The method according to claim 28 or 29, wherein contours (56) of the spring (55) are produced by 3D laser cutting or by water jet cutting.

31. A method for operating a bearing holder (10) with an inner section (30) and an outer section (20) and a spring (55) and a damper (80) in a transition region (25) between the inner section (30) and the outer portion (20), the method comprising;

Receiving a rotor (60) by a bearing in a receiving contour (32) in the inner section (30),

Attaching the outer section (20) to a housing (90) which is in operative connection with the rotor (60),

Setting the rotor (60) in motion so that vibrations occur, and

Damping occurring vibrations in order to reduce a transmission of the vibrations from the inner section (30) to the outer section (20).

32. The method according to claim 31, wherein a bearing holder (10) according to one of claims 1 to 25 is used and its functionality is used.