Bearing holder for holding a bearing

Abstract

Stockholder (10) including: an inner section (30) and an outer section (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), wherein a transition area (25) between the inner section (30) and the outer section (20) has a spring (55), wherein the transition area (25) lies at least partially in a plane perpendicular to an axial axis (70) of the recording contour (32) and lies at least partially in a plane with at least a part of the inner and outer sections (20, 30), wherein the transition region (25) has a damper (80) and 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, characterized by the fact that the damper (80) has an elastomer (81), and Cover plates (91) are arranged in a form-fitting manner between the inner and outer sections (20, 30) and an end of the outer section (20), an end of the inner section (30), the elastomer (81) and a surface of the cover plate (91) form a planar surface.

Description

[0001] The present invention relates to a bearing holder for receiving a bearing which can receive a rotor of an electric motor, wherein such an electric motor is used as a compressor motor in heat pumps which is operated with water as the working fluid.

[0002] Fig. Figure 1 shows a bearing holder known from DE 10 2016 203 411 A1. The bearing holder is held on a motor housing by means of a spring assembly (not shown). The spring assembly is designed to allow a tilting deflection of the bearing holder relative to the motor housing about at least one, preferably two, tilting axes perpendicular to an axis of the motor shaft, while preferably hindering or preventing translational deflection in the direction of the motor shaft. Thus, due to the spring assembly, the bearing section can yield to the tilting of the motor shaft, allowing it to rotate on its axis of inertia. This prevents any permanent additional force from being exerted on the bearings, as the entire bearing holder is deflectable.

[0003] Furthermore, the bearing holder is coupled to the motor housing not only by a spring assembly but also by an additional damping system. This ensures that undesirable vibrations of the bearing holder relative to the motor housing, such as those that would lead to resonance amplification, are suppressed or that resonances are dampened. The damping system is particularly useful in the event of an impact to the motor, allowing the motor shaft to return to its axis of inertia relatively quickly. The damping system has also proven especially effective during motor startup, when the motor shaft passes through rigid body resonances.

[0004] The bearing holder 10 of DE 10 2016 203 411 A1 has an outer section 20 and an inner section 30 as well as a spring assembly 40. The spring assembly 40 further comprises two or more spring struts 50 evenly distributed around the circumference of a circle. The damping system (not shown) is implemented by one or more elastic damping elements, such as O-rings, which are continuously "flexed" due to the tilting deflection of the bearing holder relative to an engine housing, so that the bearing holder can, in a sense, dissipate energy due to a vibration via the work done on the damping element.

[0005] In Fig. Figure 1 shows that the spring arrangement 40 of the bearing holder 10 has two or more elongated springs 50, wherein the spring legs each have a spring section extending parallel to the axis of a motor shaft not shown.

[0006] US Patent 8,282,285 B2 discloses a bearing holder comprising a circumferentially extending structure for substantially transferring a radial bearing load to a housing when any radial deflection or deformation of the circumferentially extending structure caused by the radial bearing load remains within a predetermined limit. For this purpose, the bearing holder comprises an inner section and an outer section. A corrugated structure is arranged between the inner and outer sections, which transfers the bearing load to the housing.

[0007] US Patent 6,224,533 B1 describes a support device for a centrifuge rotor, which is provided between a frame element and a bearing holder and is arranged to absorb relative movements between the centrifuge rotor and the frame element.

[0008] EP 2 800 913 B1 discloses a turbomachine which includes, among other things, a bearing holder. The bearing holder is secured to a housing at a first section, while a second section is radially movable relative to the first section. The second section is connected to a radial bearing and is configured to move axially in order to eliminate axial loads on the radial bearing.

[0009] EP 1 890 041 B1 discloses an arrangement for supporting the shaft of a vacuum pump, comprising a housing with a first bearing and a second bearing. The first bearing generates forces in the direction of the shaft axis and possesses axial stiffness. The second bearing is designed as a rolling bearing and is arranged in a bearing holder with axial and radial stiffness. The bearing holder is designed such that its axial stiffness is greater than its radial stiffness, with the axial stiffness of the bearing holder being greater than that of the first bearing.

[0010] DE 10 2016 212 552 A1 discloses an electric compressor designed as an electrically driven 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 are rotationally fixed to the rotor shaft. The rotor shaft is rotatably mounted about the rotor axis of rotation only in a region between the compressor impeller and the rotor by means of a bearing arrangement, wherein the bearing arrangement is received in a bearing receptacle of a one-piece bearing receptacle housing part, and at least one vibration-damping component is arranged between the bearing arrangement and the bearing receptacle.

[0011] WO 2018 181 186 A1 discloses a bearing assembly with a rotating shaft, a bearing mounted in a housing such that it supports the rotating shaft with respect to the housing. The bearing assembly further comprises an inner race through which the rotating shaft is inserted, and an outer race having an annular groove section formed on an outer circumferential surface facing an inner wall surface of the housing. The bearing assembly also includes an O-ring arranged on the groove section of the outer race of the bearing, projecting outwards in a radial direction with respect to the outer circumferential surface and contacting the inner wall surface of the housing. A gap is formed between the inner wall surface of the housing and the outer circumferential surface of the bearing. This gap is larger than the radial offset of the O-ring.

[0012] JP 2017 - 166 553 A discloses a bearing device with a bearing, a bearing holder and an elastic element, wherein the bearing has a horizontal axis and is provided for supporting a shaft extending in a horizontal direction.

[0013] GB 2 173 867 A discloses a storage holder on which the preamble of claim 1 is based.

[0014] JP 2009 - 174 692 A discloses a sliding bearing device for receiving a radial load of a rotating shaft, a bearing device that is able to maintain a holding state of a shaft even when a holding shaft is deflected, and a centrifugal compressor with such a bearing device.

[0015] A general problem with bearing mounts for electric motors, and especially with electric motors operating at high speeds, is the heating and the resulting vibrations or oscillations in the bearing area. Contact bearings, such as ball bearings or roller bearings, are typically used. These contact bearings generate friction, which leads to power loss. This power loss is problematic in two ways: firstly, it must be dissipated, and secondly, if it is not dissipated, or not sufficiently, it increases bearing wear and thus reduces the service life of the bearing and the entire electric motor. Simultaneously, problems with imbalances become increasingly pronounced as the speed of the electric motors increases, because the bearing mount itself begins to vibrate.This means that at high speeds, such contact bearings experience vibrations that must be dampened to reduce the mechanical stress on the bearing housing. Otherwise, the service life of the bearing and the entire electric motor will be reduced. Generally, power loss increases with higher speeds and greater imbalances.

[0016] High rotational speeds are necessary, however, to operate a heat pump that uses water as its working fluid, for example, within a reasonably manageable volume. Water has the property of producing a large amount of water vapor relative to a given volume of liquid water. While this is generally advantageous for the overall efficiency of the heat pump, this large quantity of vapor must be extracted and, in particular, compressed. Therefore, compressor motors are required, which, if they are not to be excessively large, must operate at very high speeds, such as speeds exceeding 50,000 rpm. The problem with such high-speed motors, however, is the power loss in the bearings and ultimately the bearing lifespan. The faster the motor operates, the more power loss it generates and the shorter its lifespan.All these points are disadvantageous because high power loss means that the efficiency of the electric motor is reduced. Furthermore, a shorter service life leads to higher costs, or conversely, to achieve a sufficient service life despite these drawbacks, extreme demands are placed on the components, such that the components, and especially the bearings, must withstand the high power losses with minimal wear.

[0017] 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 operating a bearing holder.

[0018] This problem is solved by a bearing holder according to claim 1, an electric motor according to claim 25, or a method for operating the bearing holder according to claim 27.

[0019] The bearing holder according to the present technical teaching comprises an inner section and an outer section; the inner section having a receiving contour for receiving a bearing and the outer section being configured to be mounted on a housing. A transition area between the inner and outer sections includes a spring. This 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 a portion of the inner and outer sections. Furthermore, the transition area includes a damper, which is configured to dampen vibrations of the inner section in order to reduce, and ideally eliminate, the transmission of vibrations from the inner section to the outer section.

[0020] The spring provided in the transition region can comprise several spring elements, each of which is considered a separate spring. The springs are preferably arranged along a circumference in the transition region between the inner and outer sections. Preferably, the springs are formed along a transition surface. The springs are preferably flat. In particular, "flat" here means that the springs extend in a plane perpendicular to the axial axis of an inserted rotor. When the springs are set into oscillation, for example by the movement of the rotor, the springs oscillate in the plane perpendicular to the axial axis.

[0021] The transition zone comprises a transition volume, and thus a multitude of transition planes, extending from a lower surface of a cover plate to an upper surface of a cover plate between the inner and outer sections. The transition volume contains the spring(s). The transition zone, or transition volume, therefore comprises a multitude of transition planes perpendicular to the axial axis. In other words, the transition volume forms a gap between the inner and outer sections. The springs can consequently oscillate within the transition zone and thus in the parallel transition planes. The transition volume, or transition zone, is therefore defined by an outer circumference of the inner section, an inner circumference of the outer section, and by the upper and lower surfaces of two opposing cover plates.In other words, the transition zone lies at least partially in a plane perpendicular to an axial axis of the recording contour and lies at least partially in a plane with at least a portion of the inner and outer sections. The transition planes of the transition zone are thus horizontally extending planes in which the spring(s) oscillate. Even though the spring(s) oscillate in the transition planes of the transition zone, the spring(s) extend parallel to the axial axis, particularly between the opposing cover plates. Each individual spring is, in fact, a three-dimensional structure, with the oscillation of a spring occurring in a plane parallel to the axial axis.

[0022] The transition volume or transition zone is filled with a coolant, such as water or a refrigerant. This allows each spring to be damped on the one hand, and on the other hand, heat can be dissipated from the spring via the coolant. The transition volume forms a gap between the inner and outer sections. During operation, the coolant is continuously introduced into and removed from the transition zone. In other words, the transition zone acts as a damper, namely the coolant within it, and this damper is designed to dampen vibrations in the inner section, thus reducing the transmission of these vibrations from the inner to the outer section.The vibrations of the individual springs are attributed to the inner section, since a vibration from a moving rotor is first transferred to the inner section, causing the springs to begin to vibrate.

[0023] The receiving contour for a bearing into which a rotor can be inserted preferably has a hollow cylindrical shape. The hollow cylindrical shape allows a bearing to be inserted into the bearing holder. However, the receiving contour can also have a geometry other than a cylindrical shape. The important thing is 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.

[0024] The proposed bearing holder enables the decoupling of the occurring vibrations by means of a spring arrangement or a contour arrangement, which can be implemented in a small installation space.

[0025] The proposed bearing holder can be mounted on the housing of a turbo compressor or a refrigeration unit. Generally, the proposed bearing holder can be attached to devices that include rotating shafts, spindles, or a rotor to support them. In other words, the proposed bearing holder can be used wherever vibrations occur that need to be decoupled or damped from another element, often the device itself. The proposed bearing holder can improve the service life of the bearing. This is because, on the one hand, it can dampen vibrations, and on the other hand, it can dissipate heat generated or occurring in the area of ​​the bearing holder. Damping and heat dissipation can be achieved compactly in a confined space with the proposed bearing holder. The damping means (elastomer in the transition area and, if necessary, a [missing information]) are described here.The system synergistically utilizes the vibration damping elements (coolant, springs) and the means for heat dissipation (elastomer in the transition zone and, if applicable, coolant), resulting in a bearing holder with a smaller dimension (i.e., extent) compared to bearing holders known from the prior art. In particular, the extent along the axial axis of the rotor is reduced, thus also reducing the transmission area between the rotor and the bearing holder. By decoupling the rapidly rotating system, for example, the rotor of a radial turbo compressor, from the housing, noise generation and stress on the bearing can be reduced, thereby increasing the service life of the bearing holder and the rotating system as a whole.

[0026] With the bearing holder proposed herein, predetermined damping levels can be achieved or implemented, so that, among other things, bending-critical frequencies of the system in which the bearing holder is installed can be placed in specific ranges, depending on the planned operating range of the system or the electric motor.

[0027] Another aspect of the present technical teaching concerns an electric motor in which a rotor is operatively connected to the proposed bearing holder. An electric motor equipped with the proposed bearing holder can, for example, be operated at high speeds, since the bearing holder is designed to reduce and, ideally, eliminate vibrations. This can extend the service life of an electric motor and thus the intervals at which maintenance is required.

[0028] Another aspect of the present technical teaching concerns a method for operating the warehouse keeper.

[0029] Preferred embodiments of the present invention are explained in detail below with reference to the accompanying drawings. These show: Fig. 1 a bearing holder known from the prior art, Fig. 2a a bearing holder with an indicated outer section, Fig. 2b an enlargement of a section of the bearing holder according to Fig. 2a, Fig. 3 a warehouse keeper in accordance with the technical teaching proposed herein, Fig. 4. Another perspective of the warehouse keeper according to Fig. 3, Fig. 5a a perspective view of a warehouse keeper in accordance with the technical teaching proposed herein, Fig. 5b a top view of the warehouse holder according to Fig. 5a, Fig. 6. An enlargement of a section of the bearing holder according to the Fig. 3 and Fig. 4, Fig. 7 a perspective view of a warehouse keeper in accordance with the technical teaching proposed herein, Fig. 8 a top view of the bearing holder according to Fig. 7, and Fig. 9 a schematic representation of an electric motor in a turbo compressor with a bearing holder according to the technical teaching proposed herein.

[0030] Individual aspects of the technical doctrine described herein are detailed below. Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5, Fig. 6, Fig. 7, Fig. 8 to Fig. 9 described. In the present application, identical reference numerals refer to identical or equivalent elements, and not all reference numerals are repeated in all drawings.

[0031] The Fig. 2, Fig. 3, Fig. 4 to Fig. 5 and Fig. 7 and Fig. Figure 8 each shows a bearing holder. The bearing holder shown in DE 10 2016203411 A1, which is in Fig. As shown in point 1, this was already described in the introductory part of the application. The information contained in the Fig. 3, Fig. 4 to Fig. 5 and Fig. 7 and Fig. The bearing holders 10 shown in Figure 8 each have an inner section 30 and an outer section 20; the inner section 30 having a receiving contour 32 for receiving a bearing, which in turn can be used to receive a rotor (not shown). As shown in Fig. 2 and Fig. As shown in Figure 5, for example, a receiving contour 32 for receiving a bearing is arranged within the inner section 30. This is also the case in the other figures, with the exception of... Fig. Figure 9 shows such a recording contour, which is not marked with a reference symbol in order to avoid overloading the individual figures. The one in Fig. The second depicted bearing holder 10 shows the inner section 30 completely, while the outer section 20 is only partially shown in sketch form. As in the Fig. 2, Fig. 3, Fig. 4 to Fig. 5 and Fig. 7 and Fig. As can be seen in Figure 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 unit. 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 attached to the housing 90. For example, the outer section can be screwed onto the housing 90. In such a case, the bores 92 can be threaded.

[0032] 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, in particular connects, the inner section 30 and the outer section 20. The transition area 25 between the inner section 30 and the outer section 20 has a spring 55. The spring 55 can also be provided as a spring arrangement 40 consisting of several springs 55, as shown in the Fig. 2, Fig. 5, Fig. 7 and Fig. 8, for example, can be seen. Furthermore, the spring 55 can have straight contours 56, so that the webs 57 formed by the contours 56 form spokes 58, as in Fig. 7 and Fig. Figure 8 shows that, alternatively, the spring 55 can have curved contours 56, such that the webs 57 formed by the contours 56 have a curved profile 59. The curved profile 59 can be wavy, as shown in Figure 8. Fig. 2a and Fig. Figure 2b shows a wave with periodicity similar to a sine wave. In this case, the wave's shape defines the ratio of the radial to the axial stiffness of the resulting spring 55. Alternatively, the curved shape 59 can be such that webs 57 are formed with a curved pattern that does not exhibit periodicity like a sine wave, as is the case, for example, in Fig. 5a and Fig. 5b is shown. Fig. 2b shows three springs 55. For example, the ones shown in Fig. 5a and Fig. The three springs 55 shown in 5b each exhibit only one period of the curved path 59. Also in Fig. 5a and Fig. Figure 5b shows three springs 55 with webs 57, each spring 55 having a non-periodic curved profile 59. The three springs according to Fig. 7 and Fig. 8 are designed as spokes 58 with straight contour 56, which forms the webs 57.

[0033] Each spring 55 is formed by a first contour 56 and a second contour 56, with each of the first contour 56 and the second contour 56 forming a web 57. The webs 57 are connected at a first end to the inner section 30 and at a second end 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. Thus, the transition region 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 a part of the inner and outer sections 20, 30.

[0034] As in the Fig. 2, Fig. 3, Fig. 4 to Fig. 5 and Fig. 7 and Fig. As can be seen in Figure 8, the springs 55 are symmetrically distributed around 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, for example, spanned by an xy plane, while the axial axis 70 runs longitudinally in 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 springs 55 extend in the transition region 25 and are designed to oscillate in a plane, in particular an xy plane, parallel to the transition surface 35. This is shown in Figure 8. Fig. 2b, for example, is indicated by arrows 110 and 120. The xy plane(s) define(s), for example, a horizontal plane(s).

[0035] The transition area 25 also features a damper 80, as described in the Fig. 3 and Fig. Figure 4 shows that the damper 80 is designed to dampen vibrations in the inner section 30, thereby reducing the transmission of vibrations from the inner section 30 to the outer section 20. Ideally, the vibrations are not only damped but eliminated. Damping or elimination can occur particularly with vibrations at very high frequencies. The vibration of the individual springs 55 is attributed to the inner section 30, since the vibration from a moving rotor (not shown) is initially transmitted to the inner section 30, causing the springs 55 to begin oscillating. The springs 55 begin to oscillate in the transition surface 35, i.e., in an xy plane, or more specifically, in a horizontal plane.

[0036] The damper 80 comprises an elastomer 81 and optionally a squeeze fluid damper 82. The squeeze fluid damper 82 comprises a squeeze fluid 85, which, for example, can be continuously fed into and discharged from a gap 84 during operation. The elastomer 81 can be in the form of O-rings 83 or rectangular rings, also called K-rings. The elastomer 81 can be arranged at various positions. This means that a number of O-rings 83 or K-rings can be provided, for example, to provide a seal or damping, particularly of the inner section 30. The inner section 30 and the outer section 20 are spaced apart from each other by the gap 84 in which the squeeze fluid damper 82 is arranged. The gap 84 defines a transition volume.In other words, a transition volume is created by the gap 84, extending from the transition surface 35 parallel to the axial axis 70. The squeeze fluid damper 82 can also be a squeeze fluid damper, i.e., a squeeze fluid 85, particularly if a gas is used in the damper 82 instead of a liquid. In both cases, a squeeze fluid is introduced into the transition volume of the gap 84. In other words, the squeeze fluid damper 82 for damping vibrations is filled with a squeeze 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 squeeze fluid 85 is suitable for damping vibrations and dissipating heat. The squeeze fluid 85 acts as a coolant, which can additionally dampen vibrations. For example, the coolant can be a system medium such as a refrigerant or water.

[0037] The transition volume of the squeeze fluid damper 82 is configured as the gap 84 between the inner and outer sections 20, 30, into which coolant can be continuously supplied during operation of the bearing holder 10 to dampen vibrations and dissipate heat. Continuous supply and discharge of the coolant or squeeze fluid 85 into and out of the gap 84 can be effected via a coolant inlet 87 and a coolant outlet 88. The gap 84 of the squeeze fluid 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 thermal expansion.

[0038] In Fig. 3 and Fig. Figure 4 shows, for example, that the elastomer 81 is arranged in the form of O-rings 83 at various positions. For example, one O-ring 83 is provided at the upper and one at the lower transition between the upper and lower cover plate 91 and the inner section 30, respectively. Furthermore, one O-ring 83 is provided at each of the upper and lower transitions between the upper and lower cover plate 91 and the outer section 20, respectively.

[0039] Fig. Figure 4 further 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 enclosed by a border 2 in Fig. 4 and in enlarged view in Fig. Figure 6 is highlighted. The coolant can penetrate the cover gap 95. The coolant that has penetrated the cover gap 95 can, on the one hand, support the damping of vibrations during operation and, on the other hand, 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 therefore designed as an elastic O-ring 83 and arranged on an outer circumference of the inner section 30. Furthermore, the elastomer 81 is designed as an elastic O-ring 83 and arranged on an inner circumference of the outer section 30.

[0040] It is also conceivable that the squeeze fluid damper 82 contains a cooling gas or a permanent cooling fluid, which is introduced into the gap 84 during the manufacture of the bearing holder 10 by means of the elastomer 81 and sealed. If a permanent cooling fluid or even no cooling fluid but a cooling gas is provided in the gap 84, no coolant inlet 87 and no coolant outlet 88 need to be provided. Rather, the permanent cooling fluid or the cooling gas is introduced into the gap 84 during the manufacture of the bearing holder 10 and closed, in particular sealed, by means of the cover plates 91 and the elastomer 81.

[0041] The Fig. 2, Fig. 5, Fig. 7 and Fig. Figure 8 shows that the spring 55 and one or more further springs 55 are arranged in the transition area 25, which is formed in an annular shape and surrounds the squeeze fluid damper 82. Preferably and according to the Fig. 5, Fig. 7 and Fig. 8 Three springs 55 are arranged in the transition area 25.

[0042] The Fig. 3 and Fig. Figure 4 shows how cover plates 91 are arranged in a form-fitting manner between the inner and outer sections 30, 20, and how an end of the outer section 20, an end of the inner section 30, the elastomer 81, and a surface of the cover plate 91 form a planar surface 93. The cover plates 91 extend perpendicular to the axial axis 70. The cover plates 91 are spaced apart from each other by the extension of the springs 55 parallel to the axial axis 70. This defines a volume of the squeeze fluid damper that corresponds to the volume of the gap 84. For by means of 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 fluid damper 82 is defined in which the coolant can be introduced via the at least one coolant inlet 87.

[0043] Preferably, the outer section 20 has a coolant inlet 87 and a coolant outlet 88, wherein the coolant inlet 87 is provided for supplying a coolant between the inner and outer sections 20, 30. In other words, the coolant inlet 87 is provided for supplying a coolant to the transition area or to the squeeze fluid damper. The coolant outlet 88 is provided for discharging the coolant between the inner and outer sections 20, 30. Preferably, a single coolant inlet 87 and a single coolant outlet 88 are provided, which can be arranged diametrically opposite each other. It is also conceivable that the single coolant inlet 87 and the single coolant outlet 88 are arranged at two positions on the annular shape of the outer section 20 such that the single coolant inlet 87 and the single coolant outlet 88 form an angle between 90° and 175°.It is also conceivable that more than one coolant inlet 87 and more than one coolant outlet 88 are provided in the outer section 20 (see . Fig. 4, Fig. 5, Fig. 7 and Fig. 8) These are then, for example, arranged symmetrically on the circular ring shape. For example, an even number of coolant inlets 87 and an even number of coolant outlets 88 can be provided. Preferably, two coolant inlets 87 and two coolant outlets 88 can be provided, wherein the coolant inlets 87 and the coolant outlets 88 are arranged diametrically opposite each other. A coolant inlet 87 and a coolant outlet 88 can be formed by a bore 92 or by a recess 94. Fig. Figure 2 shows the coolant inlet 87 or the coolant outlet 88 as a recess 94, which can also be located in the inner section. Fig. 4, Fig. 5, Fig. 7 and Fig. Figure 8 shows the coolant inlet 87 and the coolant outlet 88 as bores 92. The bores and recesses can be formed, for example, with a thread, in particular milled, so that, depending on requirements, the coolant inlet 87 and / or the coolant outlet 88 can be closed by screwing in a screw.

[0044] Preferably, at least a portion of the coolant inlet 87 and at least a portion of the coolant outlet 88, as well as the spring 55, lie 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 built more compactly. In particular, the proposed bearing holder 10 has a smaller dimension along the axial axis 70 compared to bearing holders known from the prior art. For example, the proposed bearing holder, with the same stiffness as a conventional bearing holder, may have a dimension that is essentially four times smaller. This results in a smaller contact area for an inserted ball bearing in which a rotor (not shown) is inserted. This, in turn, leads to less friction between the rotor and the bearing holder, thus reducing the power loss of the rotor.the electric motor's power consumption can be reduced.

[0045] Preferably, the inner section 30, the outer section 20, the spring 55, the elastomer 81, and the squeeze fluid damper 82 or the damper 80 are designed such that, in the event of vibrations, particularly at frequencies above 40 Hz or between 40 and 1000 Hz, the inner section is decoupled from the outer section. It is especially preferred that the inner section 30 is decoupled from the outer section 20 when vibrations occur in the frequency range of the rotor's natural frequencies. This prevents damage to the bearing holder or the electric motor. In damped systems, a natural frequency can correspond to a potential resonant vibration. Resonant vibrations should be avoided to prevent damage to the electric motor.

[0046] In the Fig. 2, Fig. 3, Fig. 4 to Fig. 5 and Fig. 7 and Fig. Figure 9 also shows the base 34. The base 34 preferably has bores through which the bearing holder 10 can be attached to a housing 90 (only in Fig. (shown in 9) can be mounted, in particular screwed on.

[0047] Fig. Figure 9 shows a schematic representation of a compressor comprising a proposed electric motor and the proposed bearing holder 10. The proposed electric motor comprises a motor housing 290, which is a housing 90 for the electric motor. The electric motor also comprises a motor shaft 260 with a first end and a second end. The proposed electric motor further comprises a bearing holder 10, described herein, in particular a first bearing holder 10, which is coupled to the motor housing 290 or to the housing 90 of the electric motor. Preferably, the bearing holder 10 is screwed to the motor housing 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 identical to a first rotor end 62. For attaching the bearing holder 10 to the housing 90, the base 34 of the bearing holder 10 has bores 92.

[0048] Furthermore, the electric motor has a bearing section 280 for supporting the motor shaft 260 or a rotor 60 with the bearing holder 10. The electric motor also includes a driven element 300, 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 shown in Fig. As can be seen in Figure 9, the driven element 300 is attached. The driven element 300 can be, for example, an impeller or another element known to those skilled in the art. The driven element 300 can be secured at the second end of the motor shaft to the motor shaft 260 by a shaft nut 220.

[0049] A drive section 320 is arranged between the bearing section 280 and the driven element 300 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 shown, for example, in Fig. Figure 9 shows that the driven element 300, which is arranged at one end, particularly the second end, on the motor shaft 260, is spaced apart from a further, particularly a second, bearing holder 10 by one or more spacer sleeves 310. The first bearing holder 10 is arranged at the first rotor end 62, and the second bearing holder 10 is arranged at the second rotor end 64. In other words, a further, i.e., second, bearing holder 10 described herein is arranged between the drive section 320 and the driven element 300. The drive section 320 is arranged between the first bearing holder 10 and the second bearing holder 10, i.e., between a bearing holder 10 and a further bearing holder 10. 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 to a loose bearing 270 via its inner section 30.The springs 55 of the bearing holders 10 are in . Fig. 9 schematically sketched, the bearing holders, however, having the springs 55 described herein, as they are, for example, in the Fig. 2 to 5 and 7 and 8 are shown.

[0050] Another aspect of the present technical teaching relates to a method for manufacturing a bearing holder 10 with an inner section 30 and an outer section 20, wherein the inner section 30 has a receiving contour 32 for receiving a bearing in which a rotor 60 can be received, and the outer section 20 is configured to be attached to a housing 90 and includes a spring 55 in a transition area 25 between the inner section 30 and the outer section 20. The method for manufacturing 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 a portion of the inner and outer sections 20 and 30. For example, the bearing holder 10 can consist of a single-piece element comprising the inner and outer sections 20 and 30.The transition area 25, which has springs 55 and is located between the inner and outer sections 20, 30, can be produced, for example, by 3D laser cutting or waterjet cutting. Contours 56, which form the springs 55, can be cut into the transition area 25 by 3D laser cutting or waterjet cutting. The method for manufacturing a bearing holder 10 further comprises arranging a damper 80 in the transition area 25, wherein the damper 80 dampens vibrations of the inner section 30 and thereby reduces the transmission of vibrations from the inner section 30 to the outer section 20. Preferably, the springs 55 and the elastomer 81 or the damper 80 of the bearing holder 10 are matched in their properties such that vibrations, particularly at certain frequencies, can preferably be eliminated.

[0051] The method for manufacturing a bearing holder 10 further comprises specifying an intensity of damping and / or heat dissipation of the occurring vibrations, and determining a geometry and coolant composition of the squeeze fluid damper 82, which is contained in the damper 80. The method also includes a step of determining a geometry and composition of the spring 55. Depending on the specified damping intensity, for example, the shape of the spring 55 may be different and / or the number of springs 55 may vary. Furthermore, the method includes selecting a suitable elastomer 81 whose physical properties are matched to the specified damping intensity. For this purpose, the method includes the step of determining an elastomer designed for damping vibrations.After all these determination steps have been completed, or after each individual determination step has been completed, the manufacturing steps can be carried out together or each manufacturing step can be carried out individually. In other words, the manufacturing of the determined compression damper and / or the determined spring and / or the determined elastomer only takes place after the desired properties of the aforementioned components have been determined. This allows a bearing holder to be manufactured that is tailored to the specific conditions in which the bearing holder 10 is used.After the individual components have been identified and manufactured, the next step is to assemble the bearing holder 10, which includes the identified squeeze fluid damper, the identified spring and the identified elastomer, wherein the bearing holder 10 dampens a vibration at the specified intensity and / or dissipates heat at the specified intensity.

[0052] Another aspect of the present technical teaching concerns 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 area 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 receiving and attaching can also be reversed in their sequence. After the steps of receiving and attaching have been carried out, the rotor 60, which is in operative connection with the bearing holder 10, can be set into rotation, i.e., into 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 damping intensity, the step of damping the vibrations that occur, in order to reduce the transmission of the vibration from the inner section 30 to the outer section 20, is carried out automatically by the bearing holder 10, i.e., without any further external influence.

[0053] Depending on the situation, vibrations of different frequencies and amplitudes typically occur, whereby a bearing holder 10 can be modeled situation-dependently in a method for manufacturing the bearing holder 10 with respect to the specific situation. In other words, a bearing holder 10 described herein can first be manufactured using the method for manufacturing a bearing holder 10 described herein, in order to subsequently use the bearing holder 10 in a method for operating a bearing holder 10 proposed herein, whereby its functionality can be utilized.

[0054] 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 a squeeze fluid damper 82, wherein the intensity of the damping is 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 damping. c) Decoupling by means of elastomers 81.

[0055] These three mechanisms a) to c) can be used together or separately, or any 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, damping or decoupling could be provided by means of elastomers 81 and by means of a squeeze fluid damper 82. Alternatively, damping by means of elastomers 81 alone could be provided.

[0056] However, implementing all three mechanisms is particularly preferred, as this allows for a synergistic reduction of system vibrations. In other words, the three mechanisms interact in such a way that damping and heat dissipation are enhanced by their combined effect, in addition to their additive superposition. Each of the three mechanisms can be individually modified to a greater or lesser degree during the manufacturing of the proposed bearing holder 10, thereby enabling targeted control of damping and / or heat dissipation.

[0057] A further advantage of the proposed bearing holder 10 is that water, which can be introduced into the squeezing fluid damper 82 via the coolant inlet 87 and discharged from the squeezing fluid damper 82 via the coolant outlet 88, can be used as a refrigerant or system medium. Furthermore, the bearing holder 10 can be cooled simultaneously with the water or refrigerant; that is, the refrigerant is used for heat dissipation. By cooling the bearing holder 10, the ball bearings that are in contact with it can also be cooled. Otherwise, due to the low water vapor atmosphere, heat dissipation from the bearing holder 10 is minimal, if not nonexistent, in a vacuum.

[0058] As previously described, the springs 55 are manufactured using 3D laser cutting or waterjet cutting. This allows for very precise tolerancing and alignment of the components, which are preferably made of metal. Reference symbol list 2 Ellipse 10 bearing holders 20 outer section 25 Transition area 30 inner section 32 Recording contour 32a Relief 34 sockets 35 Transition area 40 Spring arrangement 50 shock absorbers 55 spring 56 contour 57 Bridge 58 spokes 59 curved course 60 Rotor 62 first rotor end 64 second rotor end 70 Axial axis 80 dampers 81 Elastomer 82 Squeeze fluid dampers 83 O-ring 84 gap 85 Squeeze fluid 87 Coolant flow 88 Coolant drain 90 cases 91 Cover plate 92 bore 93 planar area 94 Exclusion 95 Cover gap 110 arrows 120 arrows 200 compressors 210 impellers 220 shaft nut 230 Spacer sleeve 240 fixed storage 250 Stator 260 Motor shaft 270 Lotlager 280 storage section 290 Engine casing 300 element to be driven 310 Distance Houses 320 Drive section

Claims

[1] Stockholder (10) comprising: an inner section (30) and an outer section (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), wherein a transition area (25) between the inner section (30) and the outer section (20) has a spring (55), wherein the transition area (25) lies at least partially in a plane perpendicular to an axial axis (70) of the recording contour (32) and lies at least partially in a plane with at least a part of the inner and outer sections (20, 30), wherein the transition region (25) has a damper (80) and 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, characterized by , that the damper (80) has an elastomer (81), and Cover plates (91) are arranged in a form-fitting manner between the inner and outer sections (20, 30) and an end of the outer section (20), an end of the inner section (30), the elastomer (81) and a surface of the cover plate (91) form a planar surface. [2] Bearing holder (10) according to claim 1, wherein the transition area (25) has a transition surface (35) which couples the inner section (30) and the outer section (20) together. [3] Bearing holder (10) according to claim 2, wherein the spring (55) extends in the transition area (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). [5] Bearing holder (10) according to claim 4, wherein the web (57) is connected at a first end to the inner section (30) and at a second end to the outer section (20). [6] Bearing holder (10) according to claim 4 or 5, wherein the spring (55) has straight contours (56) so that the webs (56) form spokes (58), or has curved contours so that the webs (56) have a curved profile (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 a squeeze fluid damper (82). [9] Bearing holder (10) according to claim 8, wherein the inner section (30) and the outer section (20) are spaced apart from each other by the squeeze fluid damper (82), wherein the squeeze fluid damper (82) has a transition volume which extends from the transition surface (35) parallel to the axial axis (70). [10] Bearing holder (10) according to claim 8 or 9, wherein the squeeze fluid damper (82) is filled with a squeeze fluid for damping vibrations. [11] Bearing holder (10) according to one of claims 8 to 10, wherein the squeeze fluid damper (82) is a gap (84) between the inner and outer sections (20, 30) into which coolant can be continuously supplied during operation of the bearing holder (10) to dampen vibrations and to dissipate heat. [12] Bearing holder (10) according to claim 11, wherein the gap (84) of the squeeze fluid damper (82) is sealed with the elastomer (81), which is simultaneously designed to dampen the vibrations occurring. [13] Bearing holder (10) according to claim 12, wherein the squeeze fluid damper (84) comprises a cooling gas or a permanent cooling fluid which is introduced into the gap (84) in a sealed manner by means of the elastomer (81) during the manufacture of the bearing holder (10). [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 area (25) which is formed in an annular shape and surrounds the squeeze fluid damper (82). [15] Bearing holder (10) according to one of the preceding claims, wherein the elastomer (81) is designed as an elastic O-ring (83) or as an elastic K-ring and 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) is designed as an elastic O-ring (83) or as an elastic K-ring and is arranged on an inner circumference of the outer section (20). [17] Bearing holder (10) according to one of the preceding claims, wherein the outer section (20) has a coolant inlet (87) and a coolant outlet (88), wherein the coolant inlet (87) is provided for supplying a coolant between the inner and outer sections (20, 30). [18] Bearing holder (10) according to claim 17, wherein at least a part of the coolant inflow (87) and at least a part of the coolant outflow (88) and the spring (55) are located in at least one cross-sectional plane perpendicular to the axial axis (70) of the receiving contour (32). [19] Bearing holder (10) according to one of claims 17 or 18, wherein the coolant is a system medium such as a refrigerant or water. [20] Bearing holder (10) according to one of the preceding claims 17 to 19, each in combination with claim 8, wherein a volume of the squeeze fluid damper (82) is enclosed by an outer circumference of the inner section (30) and an inner circumference of the outer section (20) and by at least one cover plate (91) arranged at the ends of the inner and outer sections (20, 30), in which the coolant can be introduced via the at least one coolant inlet (87). [21] Bearing holder (10) according to any one of the preceding claims 17 to 20, wherein the coolant inlet (87) is arranged diametrically to the coolant outlet (88) in the outer section (20). [22] Bearing holder (10) according to any one of the preceding claims 17 to 21, wherein the at least one coolant inlet (87) and the at least one coolant outlet (88) are each formed as a bore (92) or as a recess (94) in the outer section (20). [23] Bearing holder (10) according to any one of claims 8 to 22, each in combination with claim 8, wherein the inner section (30), the outer section (20), the spring (55), the elastomer (81) and the squeeze fluid damper (82) are designed such that when vibrations occur, in particular at frequencies above 40 Hz or between 40 Hz and 1000 Hz, the inner section (30) is decoupled from the outer section (20). [24] Bearing holder (10) according to one of the preceding claims, wherein the receiving contour (32) for receiving the bearing is a hollow cylinder. [25] Electric motor, with the following features: an engine casing (290); a motor shaft (260) with a first end and a second end; a bearing holder (10) according to one of claims 1 to 24, which is coupled to the motor casing (290); a bearing section (280) for supporting the motor shaft (290) with the bearing holder (10); a driven element (300) which is attached to or near one end of the motor shaft (260); and 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 stator (250). [26] Electric motor according to claim 25, wherein a further bearing holder (10) according to one of claims 1 to 24 is arranged between the drive section (320) and the driven element (300). [27] Method for operating a warehouse keeper (10) according to any one of claims 1 to 24, the method comprising; Receiving a rotor (60) by a bearing in the receiving contour (32) in the inner section (30), Attaching the outer section (20) to a housing (90) which is in operative communication with the rotor (60), Setting the rotor (60) in motion so that vibrations occur, and Damping of occurring vibrations in order to reduce transmission of the vibration from the inner section (30) to the outer section (20).

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