DE102017220880B4 - Electric motor, heat pump with the electric motor, method of manufacturing the electric motor, and method of operating the electric motor using a labyrinth seal - Google Patents

Abstract

Motor for a compressor, with the following features: a bearing area (1000) with a rotatable section (705) attached to a motor shaft (306) and a fixed section (703) and a lifetime bearing lubrication (707) between the rotatable section (705) and the fixed portion (703); a motor portion (1100); and a compressor wheel (304) arranged in a compressor room (104), wherein the motor area (1100) is arranged between the bearing area (1000) and the compressor wheel (304), wherein the motor shaft (306) extends from the bearing area (1000) extends through the motor area (1100) to the compressor wheel (304), wherein the motor area (1100) and the compressor space (104) are designed to allow gas flow between a gas supply (310, 320) and the compressor space (104), the Gas supply (310, 320) is arranged between the storage area (1000) and the engine area (1100), wherein a labyrinth seal (1010) is arranged between the storage area (1000) and the gas supply (310, 320) to seal the storage area ( 1000) from the gas supply (310, 320), the labyrinth seal (1010) being designed in such a way that the bearing lubrication forms a partial pressure during operation through evaporation and thus stops evaporating, and that during operation of the engine forming a rotating roll of lifetime bearing lubricating vapor in a clearance gap (1017) of the labyrinth seal (1010), the bearing area (1000) having a bearing retainer (504) connected to a shell (500) of the motor via a spring assembly (510) is coupled to permit tilting deflection of the bearing retainer (504) with respect to the shell (500) of the motor about at least one tilting axis perpendicular to an axis of the motor shaft (306), the labyrinth seal (1010 ) is arranged on the bearing holder (504).

Description

The present invention relates to electric motors and in particular to electric motors which can be operated at very high speeds, such as are required when such electric motors are used as compressor motors in heat pumps which are operated, for example, with water as the working fluid.

The DE 102016203411 A1 discloses an electric motor having a motor shell, a motor shaft having a first end and a second end, a bearing portion for bearing the motor shaft with respect to the bearing holder, a driven member attached to or closer to a second end than a first end of the motor shaft, and a driving section which is arranged between the bearing section and the element to be driven and has a stator. Additionally, the bearing retainer is coupled to the motor shell via a spring assembly, the spring assembly configured to allow tilting deflection of the bearing retainer relative to the motor shell about at least one tilt axis perpendicular to an axis of the motor shaft.

This achieves a motor mounting that allows the motor to no longer rotate on an axis defined by the bearings, but instead to rotate on its axis of inertia. This means that no permanent additional force is exerted on the bearings, since the entire bearing holder can be deflected.

In addition, the electric motor includes convective shaft cooling configured to supply steam in the motor housing to a motor gap that exists between the stator and the shaft by a steam supply. In addition, the motor includes a further gap that extends from the motor gap along the radial wheel to a guide space. As a result, working steam is drawn through the motor gap and cooling of the shaft is achieved.

The problem, however, is that there can be compromises in terms of bearing life. Compromising bearing life results in reduced bearing life, which then necessitates either malfunction or frequent replacement cycles for the electric motor bearing.

The DE 10 2011 000 203 A1 discloses a seal assembly for a turbomachine having at least one arcuate plate bonded to an inner surface of a stationary housing; a circumferentially segmented seal ring disposed between a rotor and the plate; a plurality of arcuate teeth disposed between the ring and the rotor, a gap of each tooth progressively decreasing as it progresses from an upstream side of the turbomachine to a downstream side; wherein the progressive decrease in the gaps of the teeth creates a positive feedback such that when a tip gap decreases, outward radial forces cause the seal ring to move away from the rotor and when the tip gap increases, inward radial forces cause the seal ring to move toward the rotor; and a biasing member disposed between and coupled to both the arcuate plate and the ring.

The WO 2009/087274 A2 discloses a supercharger for a reciprocating engine having a compressor section and an electric machine coupled to the same axle. The electric machine is provided with a flow channel for a gas, and a suction channel of the compressor section is connected in flow communication with the gas flow channel of the electric machine, so that suction air for the compressor section passes through the gas flow channel.

The DE 816117 B discloses a lubricating device for the bearings of a high pressure compressor system. A closed lubricating oil circuit for the bearings of the compressor and possibly also the engine is connected to a gas circuit. The bearings are each enclosed in a separate chamber, the chambers being closed except for the openings through which the shaft passes, which are formed as labyrinth seals. Approximately midway between the labyrinth passages, gas is introduced into the respective chamber at a pressure in excess of the suction pressure of the compressor and discharged through a vent and fed to an oil separator.

The object of the present invention is to create an improved engine concept.

This object is achieved by an electric motor according to patent claim 1, a method for producing an electric motor according to patent claim 20, a method for operating the electric motor according to patent claim 21 or a heat pump according to patent claim 22.

An electric motor for a compressor comprises a bearing area with a rotatable section attached to a motor shaft and a fixed section and bearing lubrication between the rotatable section and the fixed one Section. The electric motor further includes a motor section and a compressor wheel arranged in a compressor room. The motor section is located between the bearing section and the compressor section, and the motor shaft extends from the bearing section through the motor section to the compressor wheel. The engine compartment and the compressor compartment are configured to allow gas flow between a gas supply and the compressor compartment, with the gas supply being located between the storage compartment and the engine compartment to provide convective shaft cooling. Furthermore, a labyrinth seal is arranged between the storage area and the gas feed line in order to seal off the storage area from the gas feed line.

The present invention is based on the finding that the labyrinth seal achieves efficient sealing of the storage area from the steam area. It is thus possible to keep the bearing lubrication, which is arranged between the fixed and the moving part of the bearing, in the bearing area much longer than in a comparative situation in which no labyrinth seal is present. During operation of the electric motor, which is operated in particular at high speeds and under a thermal load due to the high speed, evaporation of the bearing lubrication takes place constantly. Due to the labyrinth seal, there is no exchange between evaporated bearing lubrication and the gas area during operation, which on the other hand is necessary for convective shaft cooling. The evaporation process of bearing lubrication thus comes to a standstill when there is a sufficiently high partial pressure of evaporated bearing lubrication in the bearing area. What is thereby achieved is that the bearing area can run in an almost sealed atmosphere, particularly in the case of bearings lubricated for life, with the bearing lubrication forming a partial pressure during operation due to evaporation and thus evaporating. This ensures that the constant evaporation of bearing lubrication, which would take place without the labyrinth seal, is prevented.

It has been shown that the service life of the bearing can be increased by a factor of two or even up to five times due to the efficient prevention of the evaporation of bearing lubrication and the prevention of the continuous removal of evaporated bearing lubrication due to the steam flow of the convective shaft cooling.

On the one hand, this improves the reliability of the electric motor and, on the other hand, the system is kept cleaner because the evaporated bearing lubrication does not contaminate the working fluid.

In addition, the convective shaft cooling ensures that the thermal load on the motor and in particular on the motor shaft is kept within limits. At the same time, the improved retention of the bearing lubrication ensures that the lubricating situation in the bearing itself is improved, so that there is also less friction and therefore less heat generation. This achieves more efficient, better and safer operation of the electric motor.

In preferred embodiments of the present invention, the labyrinth seal is formed with a disc that extends around the motor shaft, the disc being sized to be spaced from the motor shaft by a sealing gap.

In a further embodiment, a further washer is arranged, spaced from the washer and dimensioned to be spaced from the motor shaft by a further sealing gap. In particular embodiments, the disks are spaced apart by a spacer, and the spacer has a spacing gap to the motor shaft that is larger than either sealing gap, so that a "rotating roller" can preferably form in this spacing gap to help to prevent an exchange of gases between the engine area on the one hand and the storage area on the other hand. In further embodiments, the labyrinth seal not only includes components on the fixed part of the electric motor, i.e. not only includes the washers, but also one or more interlocking washers on the motor shaft. Depending on the implementation, a meandering labyrinth seal can thus be generated. Other labyrinth seals include not only two discs, but also three, four or even more discs and, depending on the implementation, correspondingly interlocking elements, so that a labyrinth seal not only has elements on the fixed part of the motor, but also on the motor shaft. However, for reasons of simplicity, it is preferred to provide components only for the labyrinth seal on the fixed part of the shaft and not on the motor shaft, and it is further preferred that two spaced disks are used, between which is the clearance space for the rotating roller forms.

In a preferred embodiment of the present invention, the fixed bearing portion is resiliently suspended from the engine shell, so that the motor can operate on its axis of inertia and is not constrained by the bearings themselves. Furthermore, it is preferred that this resilient system is damped and that the labyrinth seal is made in one piece with the part of the fixed bearing that engages the damping element for the spring damping system. This ensures that there is no relative movement between the labyrinth seal and the motor shaft with respect to the motor casing, despite the spring-loaded fixed bearing part, but that when the entire bearing area moves, the labyrinth seal also moves.

• 1A eine Prinzipdarstellung eines Motors für einen Kompressor gemäß einem Ausführungsbeispiel der vorliegenden Erfindung;
• 1B eine schematische Ansicht einer Wärmepumpe mit dem Motor und dem Kompressor;
• 2 eine schematische Darstellung einer Wärmepumpe mit konvektiver Wellenkühlung gemäß einem Aspekt;
• 3 eine schematische Darstellung einer Wärmepumpe mit konvektiver Wellenkühlung einerseits und Motorkühlung gemäß einem weiteren Aspekt andererseits;
• 4 eine Schnittdarstellung einer Wärmepumpe gemäß einem Ausführungsbeispiel mit konvektiver Wellenkühlung einerseits und Motorkühlung andererseits unter spezieller Berücksichtigung der konvektiven Wellenkühlung;
• 5 eine Prinzipdarstellung eines alternativen Ausführungsbeispiels für die Labyrinth-Dichtung zur Trennung des Lagerschmierungsbereichs und des Dampfbereichs;
• 6 eine detaillierte Darstellung des rotierenden Systems mit Lagerhalter gemäß einem Ausführungsbeispiel der vorliegenden Erfindung;
• 7A eine detaillierte Darstellung des rotierenden Systems, das in dem Motorgehäuse angeordnet ist;
• 7B eine Detailansicht aus 7A;
• 8A eine weitere Ausführungsform eines Ausschnitts des Elektromotors mit Labyrinth-Dichtung zwischen Lagerabschnitt und Motorabschnitt;
• 8B einen Ausschnitt aus 8A;
• 9 eine Detaildarstellung des Lagerhalters gemäß einem Ausführungsbeispiel der vorliegenden Erfindung; und
• 10 eine Darstellung des rotierenden Systems samt Lagerhalter mit besonderem Verweis auf ein Kühlsystem zur Lagerkühlung; und
• 11 einen schematischen Querschnitt durch eine Motorwelle, wie sie für bevorzugte Ausführungsformen einsetzbar ist.

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

• 1A a schematic diagram of a motor for a compressor according to an embodiment of the present invention;
• 1B a schematic view of a heat pump with the engine and the compressor;
• 2 12 is a schematic representation of a convective wave cooling heat pump according to one aspect;
• 3 a schematic representation of a heat pump with convective shaft cooling on the one hand and engine cooling according to a further aspect on the other hand;
• 4 a sectional view of a heat pump according to an embodiment with convective wave cooling on the one hand and engine cooling on the other hand with special consideration of the convective wave cooling;
• 5 a schematic representation of an alternative embodiment for the labyrinth seal for separating the bearing lubrication area and the steam area;
• 6 a detailed representation of the rotating system with bearing holder according to an embodiment of the present invention;
• 7A a detailed representation of the rotating system, which is arranged in the motor housing;
• 7B a detailed view 7A ;
• 8A a further embodiment of a section of the electric motor with a labyrinth seal between the bearing section and the motor section;
• 8B a snippet 8A ;
• 9 a detailed view of the bearing holder according to an embodiment of the present invention; and
• 10 a representation of the rotating system including bearing holder with particular reference to a cooling system for bearing cooling; and
• 11 a schematic cross section through a motor shaft, as can be used for preferred embodiments.

1A Fig. 12 shows a preferred embodiment of the present invention as a motor for a compressor. The engine includes a bearing portion 1000, a motor portion 1100 and a compressor wheel 304. A motor shaft 306 extends between the compressor wheel 304, the motor portion 1100 and the bearing portion 1000. Specifically, the bearing portion has a rotatable portion 705 attached to the motor shaft 306 and a fixed portion 703, wherein a bearing lubrication 707 is arranged in the bearing area 1000, between the rotatable portion 705 and the fixed portion 703. Preferably, the bearing is a bearing with moving elements, such as with balls in the case of a ball bearing or with rollers in the case of a Rolling bearing formed, as shown schematically at 701 and 702.

like it in 1A As further shown, the motor area 1100 is arranged between the compressor wheel 304 and the bearing area 1000 . The motor section includes a stator 308 which can be powered by a power supply 1050 to drive the motor. The motor section also includes a rotor 307 which preferably has permanent magnets which are mounted on the motor shaft or embedded in the motor shaft 306 . Furthermore, a gas supply, which is indicated schematically at 310 and 320, is present in order to enable a cooling gas supply for convective wave cooling. The cooling gas feed 310 , 320 preferably pulls cooling steam and preferably vaporized working liquid through the gas feed 310 , 320 , a motor gap 311 and a further gap 313 into the compressor chamber 104 when the compressor wheel 304 is in operation. This achieves convective wave cooling of the motor shaft, the permanent magnets, the stator and the other components lying on the path of the working vapor 305. The engine area and the compressor room are thus designed to allow a gas flow between the gas supply 310, 320 and the compressor room 104, with the gas supply being arranged between the storage area 1000 and the engine area 1100. In order to obtain an effective seal between the bearing area and the engine area or the vapor area, a labyrinth seal 1010 is arranged between the storage area and the gas supply line 310, 320. This ensures that the bearing lubrication 707, even if it evaporates during operation, cannot escape from the bearing area but remains in the bearing area, although there is a continuous flow of gas through the gas supply 310 along the motor gap and the further gap into the compressor chamber.

The labyrinth seal 1010 serves to seal the bearing area 1000 against the convective shaft cooling in the engine area up to the compressor area 104 as a sealing system between the rotating system and the stationary system. The bearing area, which extends between the fixed section 703 and the movable section 705 and in which the bearing lubrication 707 is arranged, is thus sealed off. Preferably, as will be explained later, O-ring seals are provided to seal the space to the outside, ie not to the convective shaft cooling area, but to other areas of the electric motor.

The bearing section includes a lubricated-for-life bearing or multiple lubricated-for-life bearings operating in a near-closed atmosphere. During operation, the oil forms a partial pressure through evaporation and thus ceases to evaporate, i.e. due to the presence of the labyrinth seal 1010. If the labyrinth seal 1010 were not present, the oil or bearing lubrication would constantly evaporate, while if the Labyrinth seal 1010 virtually no exchange takes place during operation, so that the evaporation process of the oil or the bearing lubrication, which can also contain soap or grease depending on the implementation, comes to a standstill.

Due to the labyrinth seal 1010, a partial pressure can therefore be established in the bearing area, which permanently prevents further evaporation of lubricating oil. Without a labyrinth seal, the convective wave cooling flushes away the oil vapor that is constantly produced and the evaporation process would continue until there was no more oil for lubrication. In preferred embodiments, there is no pressure difference between the bearing area and the convective shaft cooling. The labyrinth seal disrupts the diffusion process between the two spaces. As soon as the system rotates, a "rotating roller" forms in the gap in the labyrinth seal, which prevents gas exchange through the narrow gaps between the labyrinth seal washers and the motor shaft. The "rotating roller" is the gas present in the gap of the labyrinth seal, which is set in rotation by the rapidly rotating motor shaft, thus sealing the space inside the bearing from the space outside the bearing, although the washers of the labyrinth seal the Do not touch the motor shaft.

1B shows a heat pump 100 with an evaporator for evaporating working fluid in an evaporator chamber 102. The heat pump also includes a condenser for condensing evaporated working fluid in a condenser chamber 104, which is delimited by a condenser base 106. like it in 1B 1, which can be viewed as a sectional view or as a side view, the evaporator space 102 is at least partially surrounded by the condenser space 104 . Furthermore, the evaporator chamber 102 is separated from the condenser chamber 104 by the condenser base 106 . In addition, the condenser base is connected to an evaporator base 108 to define the evaporator space 102 . In one implementation, a compressor 110 is provided above the evaporator space 102 or elsewhere, which is in 1B is not explained in more detail, but which is designed in principle to compress evaporated working liquid and to conduct it as compressed vapor 112 into the condenser space 104 . The compressor preferably includes the motor as described in 1A is shown and the compressor wheel of the engine of 1A extends in the compressor room, which is the condenser room 104 of the heat pump 1 B is.

The condenser space 104 is also delimited towards the outside by a condenser wall 114 . Like the condenser base 106 , the condenser wall 114 is fastened to the evaporator base 108 . In particular, the dimensioning of the condenser base 106 in the area that forms the interface to the evaporator base 108 is such that the condenser base in 1B shown embodiment is completely surrounded by the condenser chamber wall 114. This means that the condenser room, as shown in 1B as shown, extends to the bottom of the evaporator, and at the same time the evaporator space extends very far upwards, typically almost through almost the entire condenser space 104 .

This "crossed" or interlocking arrangement of condenser and evaporator, which is characterized by the fact that the condenser base is connected to the evaporator base, provides a particularly high heat pump efficiency and therefore allows a particularly compact heat pump design. In terms of magnitude, the dimensioning of the heat pump z. B. in a cylindrical shape so that the condenser wall 114 is a cylinder with a diameter between 30 and 90 cm and a height between 40 and 100 cm. However, the dimensioning can be selected depending on the required performance class of the heat pump, but preferably takes place in the dimensions mentioned. This achieves a very compact design, which can also be produced easily and inexpensively, because the number of interfaces, in particular for the evaporator space that is almost under vacuum, can be reduced without further ado if the evaporator base is designed in accordance with preferred exemplary embodiments of the present invention such that that it includes all liquid inlet and outlet lines and therefore no liquid inlet and outlet lines from the side or from above are necessary.

It should also be noted that the operating direction of the heat pump is as shown in 1B is shown. This means that in operation the evaporator bottom defines the lower section of the heat pump, but apart from connection lines to other heat pumps or to corresponding pump units. This means that in operation the vapor generated in the evaporator space rises and is deflected by the motor and fed into the condenser space from the top down, and the condenser liquid is passed up from the bottom and then fed into the condenser space from the top and then flows from top to bottom in the condenser space, such as through individual droplets or through small streams of liquid, to react with the preferably cross-fed compressed vapor for purposes of condensation.

In preferred exemplary embodiments, the compressor is arranged on the upper side of the condenser space in such a way that the compressed vapor is deflected by the compressor on the one hand and at the same time fed into an edge gap of the condenser space. Condensation with a particularly high efficiency is thus achieved because a cross-flow direction of the vapor to a condensation liquid flowing down is achieved. This cross-flow condensation is particularly effective in the upper area, where the evaporator space is large, and does not require a particularly large area in the lower area, where the condenser space is small in favor of the evaporator space, in order to still allow condensation of vapor particles that have penetrated to this area allow.

An evaporator base, which is connected to the condenser base, is preferably designed in such a way that it accommodates the condenser inlet and outlet and the evaporator inlet and outlet, with additional feedthroughs for sensors in the evaporator or in the Condenser can be present. This means that it is not necessary to run lines for the condenser inlet and outlet through the evaporator, which is almost under vacuum. This makes the entire heat pump less prone to failure as any passage through the evaporator would present an opportunity for a leak. For this purpose, the condenser base is provided with a respective recess at the points where the condenser inlets and outlets are, to the effect that no condenser inlets and outlets run in the evaporator space defined by the condenser base.

The condenser space is delimited by a condenser wall, which can also be attached to the evaporator bottom. The evaporator base thus has an interface for both the condenser wall and the condenser base and also has all the liquid feeds for both the evaporator and the condenser.

In the present application, the same reference numbers relate to the same elements or elements with the same effect, with not all reference numbers being presented again in all drawings, insofar as they are repeated.

2 FIG. 12 shows a heat pump according to an embodiment in connection with the convective wave cooling. Thus, the heat pump comprises of 2 a condenser having a condenser housing 114 comprising a condenser space 104 . Also attached is the compressor motor, which is represented schematically by the stator 308 in 4 is shown. This compressor motor is on in 2 attached to the condenser housing 114 in a manner not shown and comprises the stator and a rotor 307, the rotor 307 having a motor shaft 306 on which is attached a radial wheel 304 which extends into an evaporator zone which is in 2 is not shown. Furthermore, the heat pump includes a guide chamber 302 which is designed to receive the steam compressed by the radial impeller and to guide it into the condenser, as is shown schematically at 112 .

The motor further includes a motor housing 300 which encloses the compressor motor and is preferably adapted to hold a pressure at least equal to the pressure in the condenser. Alternatively, the motor housing is designed to hold a pressure that is higher than an average pressure from the evaporator and the condenser, or higher than the pressure in the further gap 313 between the radial impeller and the guide chamber 302, or greater or is equal to the pressure in the condenser. The motor housing is thus designed in such a way that a pressure drop from the motor housing along the motor shaft in Rich direction of the guide space takes place, is drawn past the motor shaft through the working steam through the motor gap and the further gap in order to cool the shaft.

This area in the motor housing with the necessary pressure is in 2 shown at 312. In addition, a vapor supply 310 is formed to supply vapor in the motor housing 300 to a motor gap 311 existing between the stator 308 and the shaft 306 . The motor also includes a further gap 313 which extends from the motor gap 311 along the radial wheel to the guide space 302 .

In the arrangement, there is a relatively high pressure p ₃ in the condenser. In contrast, there is a medium pressure p ₂ in the guideway or guide space 302 . Apart from the evaporator, the lowest pressure prevails behind the radial wheel, namely where the radial wheel is attached to the motor shaft, i.e. in the further gap 313. In the motor housing 300 there is a pressure p ₄ which is either equal to the pressure p ₃ or greater than the pressure p ₃ . As a result, there is a pressure gradient from the motor housing to the end of the further gap. This pressure drop results in steam flowing through the steam supply into the engine gap and the further gap into the duct 302 . This vapor flow takes working vapor from the motor housing past the motor shaft into the condenser. This steam flow provides for the convective wave cooling of the motor shaft through the motor gap 311 and the further gap 313, which adjoins the motor gap 311. The radial impeller thus sucks steam out downwards, past the motor shaft. This steam is drawn into the engine gap via the steam supply, which is typically implemented as specially designed bores.

3 shows a further schematic embodiment of the convective wave cooling according to a first aspect, which is preferably combined with the motor cooling according to a second aspect.

However, it should generally be pointed out at this point that the two aspects of convective shaft cooling on the one hand and motor cooling on the other hand are also used separately from one another. Motor cooling without special, separate convective shaft cooling already leads to significantly increased operational reliability. In addition, convective motor shaft cooling without the additional motor cooling leads to increased operational reliability of the heat pump. The two aspects can, however, as explained below in 3 is shown, can be connected to one another in a particularly favorable manner in order to implement both the convective shaft cooling and the motor cooling with a particularly advantageous construction of the motor housing and the compressor motor, which can additionally be supplemented in a further preferred exemplary embodiment either individually or jointly by a special ball bearing cooling system.

3 shows an embodiment with combined use of convective shaft cooling and engine cooling, wherein in the in 3 shown embodiment, the evaporator zone is shown at 102 . The evaporator zone is separated from the condenser zone, ie from the condenser area 104 , by the condenser base 106 . Working vapor, shown schematically at 314, is drawn in by the rotating radial impeller 304, shown schematically and in section, and "forced" into conduit 302. The route 302 is at the in 3 shown embodiment formed so that its cross section increases towards the outside. This means that further vapor compression takes place. The first "stage" of vapor compression already takes place through the rotation of the radial impeller and the "sucking in" of the vapor through the radial impeller. However, when the radial impeller feeds the steam into the entrance of the guideway or guide space, i.e. where the radial impeller "stops" viewed from the top, the already pre-compressed steam encounters a steam jam, so to speak. In the control chamber, the kinetic energy that the radial impeller has transferred to the steam is converted into potential energy, as the flow velocity is converted into pressure by the slow, steady widening of the control chamber. This leads to a further vapor compression, so that finally the compressed and thus heated vapor 112 flows into the condenser.

3 also shows the vapor supply openings 320, which are located in a schematically illustrated engine wall 309 in 3 are executed. This motor wall 309 has at the in 3 The exemplary embodiment shown has holes for the steam supply openings 320 in the upper area, although these holes can be made at any desired location at which steam can penetrate into the motor gap 311 and thus also into the further motor gap 313. The resulting steam flow 310 leads to the desired effect of convective wave cooling.

This in 3 The exemplary embodiment shown also comprises a working fluid inlet 330 for implementing the engine cooling, which is designed to carry liquid working fluid from the condenser to the engine wall for engine cooling. Furthermore, the motor housing is designed to provide maximum liquid during operation of the heat pump keitslevel 322 to keep liquid working fluid. In addition, the motor housing 300 is also designed to form a vapor space 323 above the maximum level. Furthermore, the motor housing has provision for directing liquid working medium into the condenser 104 above the maximum level. This version is used in the in 3 shown embodiment by a z. B. shallow channel-shaped weir 324 forming the vapor discharge and is located somewhere in the upper condenser wall and has a length that defines the maximum level 322. If too much working liquid is introduced into the motor housing, ie the liquid area 328, through the condenser liquid feed 330, the liquid working medium runs through the overflow 324 into the condenser volume. In addition, the overflow also occurs with the in 3 shown passive arrangement z. B. can also alternatively be a tube with a corresponding length, a pressure equalization between the motor housing and in particular the vapor space 323 of the motor housing and the condenser interior 104 ago. The pressure in the vapor space 323 of the motor housing is therefore always almost the same or at most slightly higher than the pressure in the condenser due to a pressure loss along the overflow. Thus the boiling point of the liquid 328 in the motor housing will be similar to the boiling point in the condenser housing. As a result, heating of the motor wall 309 due to power loss generated in the motor leads to nucleate boiling taking place in the liquid volume 328, which will be explained later.

3 also shows various seals in schematic form at reference number 326 and at similar locations between the motor housing and the condenser housing on the one hand or between the motor wall 309 and the condenser housing 114 on the other hand. These seals are intended to symbolize that there should be a liquid and pressure-tight connection here.

A separate space is defined by the motor housing, but it represents nearly the same pressure area as the capacitor. Due to the heating of the motor and the energy released as a result at the motor wall 309, this supports nucleate boiling in the liquid volume 328, which in turn results in a particularly efficient distribution of the working medium in the volume 328 and thus particularly good cooling with a small volume of cooling liquid. Furthermore, it is ensured that cooling is carried out with the working medium that is at the most favorable temperature, namely the warmest temperature in the heat pump. This ensures that all condensation problems, which always occur on cold surfaces, are ruled out both for the motor wall and for the motor shaft and the areas in the motor gap 311 and the further gap 313. Furthermore, at the in 3 In the exemplary embodiment shown, the working medium vapor 310 used for the convective shaft cooling is vapor that is otherwise in the vapor space 323 of the motor housing. Like the liquid 328, this vapor also has the optimal (warm) temperature. Furthermore, the overflow 324 ensures that the pressure in the area 323 cannot rise above the condenser pressure due to the nucleate boiling caused by the motor cooling or the motor wall 309 . Furthermore, the heat energy due to the engine cooling is removed by the vapor discharge. This means that convective wave cooling will always work in the same way. If the pressure were to increase too much, too much working medium vapor could be pressed through the motor gap 311 and the further gap 313 .

Although the electric motor according to the present invention can be used particularly well in the heat pump, as referring to the 1A until 4 As has been shown, the electric motor can also be used for other applications where a small, compact motor that can also be operated at high speeds is required. However, even at lower speeds, the motor according to the invention can bring advantages.

5 shows a schematic design according to an embodiment of the labyrinth seal 1010. The labyrinth seal preferably comprises an upper disk 1012 and a lower disk 1011 and a counterpart 1013 rotating between the two disks 1011 and 1012, which is connected to the motor shaft 306. The two disks 1012, 1011 thus enclose the rotating element 1013, with the long path into the gap between disk 1012 and motor shaft 306 along the strongly rotating part 1013 and then back to the gap between the lower disk 1011 and of the motor shaft 306 leads to an efficient separation between the bearing lubrication on the one hand and the steam area on the other hand. Only schematically is in 5 shown that the fixed area 1012, 1011 is connected to a motor casing 500, which is also shown in 1A is drawn. Further, the upper disk 1012 and the lower disk 1011 are each connected with a spacer 1016, and the members 1012, 1011 and 1016 are preferably formed integrally with each other. In preferred embodiments for the labyrinth seal 1010 as shown in 5 are shown, an arrangement of two fixed disks and one rotating disk can thus be used. Alternatively, however, only one fixed disk and one opposite rotating disc can be used. Such a seal would result if either the upper disc 1012 or the lower disc 1011 in 5 would be omitted.

A particularly preferred embodiment is in 8B shown. In 8B there are both the upper disk 1012 and the lower disk 1011 separated by the spacer 1016. However, with the in 8B In the embodiment shown, there is no disk or element that rotates and is arranged on the motor shaft 306 . This is particularly advantageous because the motor shaft 306 is driven at high speed and therefore any additional elements on the motor shaft are problematic in terms of stability. Hence the labyrinth seal in 8B is preferred which has two washers between which is formed the area 1017, also described as the "spacer gap" because it is the gap between the spacer 1016 and the motor shaft 306 where, in this particular embodiment of the labyrinth seal, the rotating roller, which is additionally formed by the narrow gaps between the first disk 1012 and the motor shaft 306 and the second disk 1011 and the motor shaft 306, effectively avoids an exchange of gases between the storage area and the vapor area.

In particular, at the in 8B illustrated embodiment particularly preferred dimensions for the labyrinth seal. The dimensions are in millimeters 8B .

The sealing gap between the two disks 1011, 1012 and the motor shaft 306 is preferably the same size and in the order of 0.05 mm. Other sizes between 0.02mm and 0.07mm are also particularly useful. Alternatively, the two sealing gaps can also have a tolerance range of ±10% of the larger of the two sealing gaps. In a particularly preferred embodiment, which is also in 8B As shown, the thickness of the top disk is greater than the thickness of the bottom disk. In particular, the thickness of the upper disc 1012 is at least 1.1 times that of the lower disc 1011. In particular, the thickness of the upper disc is between 0.8 mm and 1.2 mm and the thickness of the further disc is between 0.15 mm and 0.65mm

The spacer 1016 preferably has a thickness of 2 mm and the spacer gap 1017 is 3.75 mm. However, the clearance gap can be between 2.5 mm and 5 mm, and is preferably equal to 30 times the sealing gap, in order to allow a sufficiently efficiently sealing rotating roll to form. The distance between the two discs, which is preferably 2 mm, can also be between 1 mm and 3 mm.

In the following, reference is made to 4 describes an electric motor according to an embodiment of the present invention, which is advantageous as the electric motor 110, for example by 1B can be used, or can also be used for other applications.

The electric motor includes a motor shell 500 that encloses the motor. In contrast, the motor housing 300 in the 2 , 3 , 4 is provided in addition to the motor shell to provide the particular cooling devices set forth. Part of the engine shell 500 is the engine wall 309, which is also in the 2 , 3 , 4 is shown.

The electric motor further includes a motor shaft 306 having a first end 306a and a second end 306b, and a bearing portion 343 for supporting the motor shaft 306 with respect to a bearing holder 504. The bearing portion 343 is closer to the first end 306a than to the second end 306b on the motor shaft mounted and in particular on one side with respect to the center of gravity of the rotating system. Furthermore, the rotating system comprises an element 304 to be driven, which can be designed, for example, as a radial wheel or impeller, but which can also be implemented as any other element to be driven. Furthermore, a drive section 1100 is provided, which is arranged between the bearing section 343 and the element to be driven and has a rotor 307 and a stator 308 .

In particular, the stockist 504, who is in 6 is shown coupled to the motor shell 500 via a spring assembly 600, the spring assembly being configured to allow tilting deflection of the bearing retainer 504 relative to the motor shell at least about a tilting axis that is perpendicular to an axis of the motor shaft 306, and to reduce or avoid translational deflection in the direction of the motor shaft. The motor shaft 306 extends z. B. along the z-axis. In particular, the motor shaft 306 rotates about the z-axis during operation. A tilting deflection is possible either around the y-axis or the x-axis or preferably around both tilting axes, to the effect that the rotating system, which is formed by the motor shaft 306, the rotor 307 and the element 304 to be driven, can rotate on its axis of inertia. In order to achieve this, the tilt deflections are necessary. In contrast, the spring assembly, implemented as leaf springs, for example, is designed to be rigid in the z-axis. Preferably, the Federanord Figure 10 also defines the radial position of the bearing retainer with respect to the motor shell 500 such that there is in fact a tilting deflection of the bearing retainer but no radial displacement of the bearing retainer.

In particular, with the in 4 or 6 or 7A , 7B , 8A , 8B shown embodiment shown that the bearing portion 343 stores the motor shaft during operation only, so that between the drive portion 1100 and the element to be driven 304 no further bearing for storing the motor shaft is arranged during operation. Only, as z. B. based on 4 as set forth, an emergency bearing 344 exists, but is not operatively engaging the shaft but is spaced from the shaft and is there to engage the shaft in the event of an emergency condition such as a shock so that no excessive deflection of the shaft is allowed. The emergency bearing is thus arranged between the drive section and the element to be driven, which does not engage the motor shaft or the element to be driven during operation, but which engages the motor shaft in an emergency situation in order to prevent deflection of the motor shaft beyond an emergency bearing gap.

The rotor 307 comprises in an embodiment, for example in 6 shown, permanent magnets attached to the motor shaft. In addition, a stator as z. B. at 308 in 7A 1, windings connected to the motor shell 500 are shown.

In particular, the bearing holder 504 is connected via two or more elongate springs, e.g. B. at 600 in 6 are shown connected to the motor shell 500 with the struts each having a spring portion extending parallel to the axis of the motor shaft 306 .

Depending on the implementation, however, in the case of a bearing holder 504 that is preferably circular in plan view, the spring struts are distributed evenly over the circumference. The electric motor further includes a damping arrangement through which the bearing retainer 504 is also connected to the motor shell 500 . The damping arrangement is designed to damp mechanical vibration, which is made possible due to the spring arrangement of the bearing holder 504 with respect to the engine shell 500 . The damping strength of the damping arrangement is adjusted so that the damping arrangement prevents resonance of the oscillating bearing holder 504, while at the same time allowing the tilting motion that the rotating system must undergo in order to oscillate on its axis of inertia.

In the following, reference is made to 6 given a detailed description. The element to be driven 304 is in 6 designed as a radial wheel or impeller wheel, which in cross section 6 is shown. Various balancing holes 602 are shown, which can typically be provided with grub screws in order to balance the radial wheel or the radial wheel together with the shaft and rotor. However, balancing measures can also be achieved by other precautions, such as by removing material at a specific point as an alternative or in addition to the weight input due to the balancing screws that may be used in the balancing openings 602 6 shown embodiment, the shaft 306 is formed from a different material than the wheel 304. However, both components can be formed from the same material or can also be formed in one piece with each other. At the in 6 In the implementation shown, the radial wheel 304 is formed from aluminum and the shaft is formed from steel. The wheel 304 is held on the shaft 306 by means of a fastening section 395 which is fork-shaped in cross-section and which is shown in 6 is shown. The rotor 307 is arranged on the shaft in the drive section in the form of permanent magnets, which are held by a stabilizing sleeve 396 and stabilizing bandages 397, as also with reference to FIG 11 will be explained later.

Bearing retainer 504 is shown in bearing portion 343, with reference to FIG 7B , which shows a detailed representation of the warehouse keeper, will be discussed in more detail. In particular, the bearing holder 504 is connected via the spring arrangement, which is illustrated using a spring strut 600, to the FIG 6 not shown connected engine shell. For this purpose, the spring arrangement comprises the spring strut 600 and two further spring struts 600, which are shown in cross section in 6 are not shown, but in 9 are evident. The struts connect an attachment portion 602 to the bearing retainer 504. The attachment portion 602 is as shown again in FIG 9 better seen, is formed as a ring which is bolted to the engine shell 500 when the engine is fully assembled. The inventive labyrinth seal is at 1010 in 6 shown.

The bearing holder also includes an outer sleeve 604 and an inner sleeve 606. A space is created between the outer sleeve 604 and the inner sleeve 606, which is sealed off at the bottom by a connecting web and which is sealed off at the top by an O-ring 610 . Coolant can be fed into the bearing holder via an inlet 612, which coolant can be fed through an outlet that is shown in 10 is shown, is led out again from the cooling space. The expiration is with 614 designated. The cooling space 616 is connected via the inner sleeve 606 to the inner bearing section in which, in the case of FIG 6 illustrated embodiment, two ball bearings are arranged, namely, as in 7B shown in detail, a lower ball bearing 701 and an upper ball bearing 702. The lower ball bearing 701 has a rotating bearing portion 701a and a fixed bearing portion 701b. Further, the upper bearing 702 has a fixed bearing portion 702b and a rotating bearing portion 702a. In addition, in 7B the spring section mounting ring 602 is shown mating with the motor shell, a small portion of which is at 500 in 7B shown is connected. Between the two bearings 701 and 702 is an inner spacer sleeve 704 and an outer spacer sleeve 706. The inner spacer sleeve 704 is placed between the rotating parts 701a, 702a of the bearings, while between the outer sleeve and the fixed parts 701b, 702b is a spring washer 708 and, if necessary, another spring ring or washer 710 is attached.

To assemble the bearing, an element is first provided which consists of the outer bearing sleeve 604 and the inner bearing sleeve 606, the outer and inner bearing sleeves being connected and sealed to one another to a certain extent by the wall 608 at the bottom and by the O-ring 610 at the top. Then the warehouse is set up. For this purpose, the lower ball bearing 701 is first glued into the inner bearing sleeve. This lower bearing forms the fixed bearing. Then the sleeves 704, 706 and the spring ring 708 and, if necessary, other elements such as the washer 710 and then the bearing 702 are inserted into the inner sleeve in the in 7B shown order. The first end 306a of the shaft 306 is then pulled into the bearing holder, which has already been prepared in this way, using a special pull-in tool. There is a snug fit between the shaft and the rotating portions 701a, 702a of the bearings, for which no further attachments are typically required, such as adhesives or the like.

Then, with the shaft pulled in, the bearings are secured by securing a bearing washer 712 in a thread of the shaft 306 by a screw 713. The two bearings are thus pressed against one another, with the spring washer in particular providing the necessary suspension. This fixed bearing/floating bearing combination ensures that thermal expansion of the shaft can be easily absorbed, although the distance between the two ball bearings is so short that two fixed bearings could also be used if necessary. However, it is preferred that the fixed bearing / floating bearing combination, as for example based on 7B described, while other fixed/floating implementations with differently shaped sleeves/spring washers etc. could also be used.

7B also shows the damping system in the form of a ring 714, which is also shown in 9 is shown and may be referred to as a star ring. This ring 714 is connected to the bearing retainer 504 (in 6 or 7A) coupled via an O-ring 716. This allows movement between the inner sleeve 606 and the ring 714, it being further noted that the ring 714 is connected at its outer periphery to the engine casing 500, as e.g. Am 7A is evident. However, because the O-ring is an elastic element for which a force is required in order to deform or "flex" the O-ring, the damping function of the damping arrangement is created. The damping arrangement is thus created by the O-ring, which abuts on the one hand against the inner sleeve 606 and on the other hand against the fastening ring 714 and the star ring 714, respectively.

The rigid engine shell further includes an engine wall 309 which, as shown in 7A shown, may or may not be provided with cooling fins. In the area of the cooling fins, for example in 7A As can be seen, the drive section is formed, i.e. the stator 308, in which heat generation occurs due to the considerable current flow through the stator windings.

In addition, shows 7A further aspects of the inventive electric motor according to the preferred embodiment of the present invention in the form of a cover member 720 which is fixed by screws 722 to the motor shell 500, but with a void between the cover 720 and the screw 713 ( 7B) of the shaft exists in that the cover 720 does not interfere with the rotation of the shaft. On the other hand, the cover 720, together with another bracket 722, holds the fixed portions 701b, 702b of the bearings. Furthermore, the inner bearing area is sealed by seals 724 ( 7B) sealed to be hermetically sealed from liquid and vapor. This ensures that a bearing lubrication required for the bearings 701, 702 is retained for as long as possible and is not influenced by liquids or working vapors or generally by the external environment. On the one hand, this ensures that the bearing is well lubricated. On the other hand, due to the water cooling, the bearing is cooled right into the inner bearing area in order to obtain the longest possible service life.

Furthermore, in order to have an additional cooling functionality, namely in the form of convective wave cooling, the fastening ring or star ring 714 comprises recesses 900, which are designed to collect gas that is present around the motor shell 500, in particular working vapor, that is present within the motor housing 300 from 4 , 3 , 2 e.g. is present to flow along the shaft and motor gap 307 to the radial wheel 304. In addition, a further opening 902 is provided, which is provided for cables for supplying the stator with electricity or, if present, sensors. Furthermore, the ring 602 also includes a recess 904 through which the cable, which already runs through the recess 902, can be led out further upwards. The cable arrangements are chosen so that they run outside of the bearing holder 504 and in particular that no cable runs through the sealed hermetic area of the ball bearings, which is in 9 located at 908 and which is then finally sealed when the lid 720 located in 7A is shown mounted. The inventive labyrinth seal is at 1010 in 7A shown.

As has already been shown, and as in 10 As explained again, the damping system is constituted by the O-ring placed between the bearing retainer and the engine shell, as shown in particular in FIG 7B and also in 10 is evident. This allows relative movement, albeit dampened, between the bearing retainer and the motor shell, which causes the O-ring to be elastically deformed.

Furthermore, a preferred embodiment of the present invention, as is also based on 7B as set forth, first bearing 701 and second bearing 702. Both bearings are ball bearings in one implementation. However, these bearings can also be designed as alternatives, for example as roller bearings or something similar. These two bearings are very closely spaced, resulting in a rigid body resonance of the electric motor being below an operating speed of the motor. The electric motor is preferably operated in such a way that during operation it has an operating speed which is higher than the rigid body resonances.

One of the two bearings is designed as a fixed bearing and the other of the two bearings as a floating bearing. Due to the ease of assembly, it is preferred that the lower bearing 701, which is closer to the radial wheel 304, is designed as a fixed bearing, while the upper bearing 702 is designed as a floating bearing.

Although the spring arrangement in 6 or 9 has been shown as three spring struts 600, which extend along the axis of the motor shaft and thus achieve the necessary spring stiffness, it should be pointed out that other spring arrangements in the form of spiral springs, leaf springs or other springs can also be used, and that spring/spring arrangements can also be used. Damping systems can be used that do not connect the bearing holder to the housing at separate positions, but at one and the same position. The only important thing is that the bearing holder can perform tilting movements with respect to the motor casing, it also being preferred that the bearing holder is not only held relatively rigidly axially with respect to the motor shaft by the spring or damping arrangement, but also defines the radial position, see above that tilting movements take place, the center of which takes place within the bearing section 343.

11 shows a schematic cross section through a motor shaft 306 as can be used for preferred embodiments. Motor shaft 306 includes a shaded core as shown in FIG 11 is shown, which is supported by preferably two ball bearings 398 and 399 in its upper section, which represents the bearing section 343 . The rotor with permanent magnets 307 is formed further down on the shaft 306 . These permanent magnets are placed on the motor shaft 306 and are held in place at the top and bottom by stabilizing bandages 397, which are preferably made of carbon. Furthermore, the permanent magnets are held by a stabilizing sleeve 396, which is also preferably designed as a carbon sleeve. This securing or stabilizing sleeve ensures that the permanent magnets remain securely on the shaft 306 and cannot become detached from the shaft due to the very strong centrifugal forces due to the high speed of the shaft.

Preferably, the shaft is formed of aluminum and has a forked cross-sectional mounting portion 395 which provides support for the radial wheel 304 when the radial wheel 304 and the motor shaft are not formed as a single piece, but rather as two elements. If the radial wheel 304 is designed in one piece with the motor shaft 306, the wheel mounting section 395 is not present, but instead the radial wheel 304 then connects directly to the motor shaft. In the area of the wheel mount 395 is also located how it looks 10 can be seen, the emergency bearing 344, which is preferably also made of metal and in particular aluminum.

In a preferred embodiment, as illustrated in FIG 7B and 8B is shown, the electric motor includes both the aspects of convective shaft cooling and the resilient mounting of the bearing section and also, in particular dere like it in 10 has been shown, the additional ball bearings or bearing section cooling with liquid working fluid. In this embodiment, the labyrinth seal is located on a portion 703 of the bearing retainer which engages the resilient O-ring 716. In particular, the labyrinth seal used in 7B shared by elements 1011, 1012, 703, is located between O-ring 716 and motor shaft 306. The bearing holder 703 portion is formed integrally with the labyrinth seal and includes the first washer 1012, the second washer 1011 and the spacer 1016, the spacer being directed toward the motor shaft 306 at its front side and the O- Ring 816 engages.

In preferred embodiments, the labyrinth seal 1010 is formed of metal, and most preferably of steel or spring steel. The bearing lubrication includes oil, grease, soap or a mixture of at least two of the components mentioned.

Alternative aspects of the present invention also relate to a method for producing an electric motor with a labyrinth seal and a method for operating the electric motor with the labyrinth seal and a heat pump with a condenser, an evaporator and a compressor whose compressor wheel is driven by the motor , wherein the motor shaft 306 may be connected to the compressor wheel 304 by bolts or other fasteners, or may be integrally formed with the compressor wheel.

Reference List

100

heat pump

102

evaporator room

104

compressor room / condenser room

110

compressor

114

condenser wall

115

suction mouth

112

compressed steam

300

motor housing

302

control room

304

compressor wheel

305

cooling steam

306

wave core

307

rotor and permanent magnets

308

stator

309

engine wall

310, 320

gas supply

311

engine gap

312

area in the engine case

313

another gap

314

working steam

322

liquid level

323

steam room

324

overflow

326

seals

328

liquid area

330

working fluid supply

343

storage section

344

emergency camp

396

locking sleeve

397

carbon bandage

500

motor shell

504

storekeeper

600

feathers

602

balancing holes

604

sleeve

606

sleeve

608

Wall

610

o ring

612

Intake

614

Sequence

616

cooling room

701

Bearing element, lower ball bearing

701a

rotating bearing section

701 b

fixed bearing section of the lower ball bearing

702

Bearing element, upper ball bearing

702a

rotating bearing section

702b

fixed bearing section of the upper ball bearing

703

fixed storage section

704

inner spacer sleeve

705

rotatable bearing section

706

outer spacer sleeve ,

707

bearing lubrication

708

spring washer

710

washer

712

bearing washer

713

screw

714

ring

716

o ring

720

cover element

722

screws

724

seals

900

recesses

902

further opening

904

recess

908

sealed ball bearing area

1000

storage area

1010

Labyrinth seal

1011

another disc

1012

disc

1013

rotating disc

1016

spacers

1050

power supply

1100

engine area

Claims (22)

Motor for a compressor, with the following features: a bearing area (1000) having a rotatable portion (705) attached to a motor shaft (306) and a fixed portion (703) and lifetime bearing lubrication (707) between the rotatable portion (705) and the fixed portion (703); an engine section (1100); and a compressor wheel (304) which is arranged in a compressor room (104), wherein the motor area (1100) is arranged between the bearing area (1000) and the compressor wheel (304), wherein the motor shaft (306) extends from the bearing area (1000) through the motor area (1100) to the compressor wheel (304), wherein the motor area (1100) and the compressor room (104) are designed to allow a gas flow between a gas supply (310, 320) and the compressor room (104), the gas supply (310, 320) between the storage area (1000) and the engine area (1100) is arranged, wherein a labyrinth seal (1010) is arranged between the storage area (1000) and the gas feed (310, 320) in order to seal the storage area (1000) from the gas feed (310, 320), the labyrinth seal (1010) so is designed so that the bearing lubrication forms a partial pressure during operation through evaporation and thus stops evaporating, and that during operation of the motor a rotating roller of lifetime bearing lubrication vapor forms in a spacing gap (1017) of the labyrinth seal (1010), wherein the bearing portion (1000) includes a bearing retainer (504) coupled to a shell (500) of the engine via a spring assembly (510) to reverse tilting deflection of the bearing retainer (504) relative to the shell (500) of the engine allowing at least one tilt axis perpendicular to an axis of the motor shaft (306) with the labyrinth seal (1010) disposed on the bearing retainer (504). engine after claim 1 , in which the labyrinth seal (1010) is arranged on the fixed portion (703) of the bearing area (1000) and has at least one disc (1012) which extends around the motor shaft (306), the disc (1012) is dimensioned to be spaced from the motor shaft (306) by a sealing gap. engine after claim 2 wherein the labyrinth seal (1010) further comprises a further disc (1011) spaced from the disc (1012) and dimensioned to be spaced from the motor shaft (306) by a further seal gap. engine after claim 2 or 3 , in which the sealing gap or the further sealing gap have a radial length which is between 0.02 mm and 0.07 mm. engine after claim 3 , in which the sealing gap and the further sealing gap are of the same size within a tolerance of ± 10% of the larger of the two sealing gaps. engine after claim 3 , 4 or 5 , in which the disk (1012) is arranged closer to the storage area (1000) and the further disk (1011) is arranged closer to the gas supply (310, 320). engine after claim 3 , 5 or 6 , in which the disc (1012) has a thickness which is at least 1.1 times the thickness of the further disc (1011). engine after claim 3 , 4 , 5 , 6 or 7 , in which the disk (1012) has a thickness between 0.8 mm and 1.2 mm and the further disk (1011) has a thickness between 0.15 mm and 0.65 mm. engine after one of claims 3 until 8th , In which the disk (1012) and the further disk (1011) are arranged on a spacer (1016), the spacer gap (1017) being arranged between the spacer (1016) and the motor shaft (306) and having at least the 30 times the sealing gap. engine after claim 9 , in which the spacing gap (1017) is between 3 mm and 5 mm. engine after one of claims 3 until 10 , in which the further disk (1011) is spaced apart from the disk (1012) by a distance which is between 1 mm and 3 mm. engine after claim 1 , further comprising a damping arrangement (512) through which the bearing holder (504) is coupled to the shell (500) of the motor, the damping arrangement (512) being adapted to allow mechanical vibration caused by the spring arrangement (510). is to dampen, wherein the damping arrangement (512) comprises a damping element which is arranged between the housing (500) of the motor and the bearing holder (504) in such a way that the same upon relative movement of the bearing holder (504) and the housing (500) of the motor is elastically deformed, wherein the damping element is an elastic O-ring (716), and wherein the labyrinth seal (1010) is arranged on a portion (703) of the bearing holder (504) which contains the elastic O-ring (716 ) engages. engine after claim 12 , in which the labyrinth seal (1010) is arranged between the O-ring (716) and the motor shaft (306). engine after Claim 13 wherein the portion (703) of the bearing retainer (504) on which the labyrinth seal (1010) is located includes: a washer (1012) extending around the motor shaft (306) and dimensioned so that is spaced from the motor shaft (306) by a sealing gap, a further washer (1011) spaced from the washer (1012) and dimensioned to be spaced from the motor shaft (306) by a further sealing gap , a spacer (1016) which is arranged between the disk (1012) and the further disk (1011) and has the spacing gap (1017) to the motor shaft (306), the spacer (1016) at its front side facing the motor shaft ( 306) and at its back engages the O-ring (716), and wherein the disc (1012), the further disc (1011) and the spacer (1016) are formed in one piece. An engine as claimed in any preceding claim, wherein the labyrinth seal (1010) is of metal, steel or spring steel. An engine as claimed in any preceding claim, wherein the lifetime bearing lubrication (707) comprises oil, grease, soap or a mixture of at least two of said components. Motor according to one of the preceding claims, in which the bearing region (1000) comprises one or more ball bearings. Motor according to one of the preceding claims, in which the bearing region (1000) has one or more roller bearings. Motor according to one of the preceding claims, wherein the motor shell (500) includes a ring (714) fixedly connected to the motor shell (500) at an outer portion thereof and engaged by a damping member at an inner portion thereof, the damping member further comprising engages the bearing keeper (504), in which the ring (714) has one or more recesses (900) in its outer region in order to create the gas supply (310, 320) to the motor shaft (306), the motor being further designed to have a continuous gas channel from the Gas supply (310, 320) along the motor shaft (306) through a motor gap (311) up to the compressor wheel (304) and past the compressor wheel (304) through a further gap (313) for the gas flow. A method of making a motor having a bearing section (1000) with a rotatable portion (705) attached to a motor shaft (306) and a fixed portion (703) and lifetime bearing lubrication (707) between the rotatable portion (705) and the fixed section (703); an engine section (1100); a compressor wheel (304) which is arranged in a compressor room (104), the motor area (1100) being arranged between the bearing area (1000) and the compressor wheel (304), the motor shaft (306) extending from the bearing area (1000) extends through the engine area (1100) to the compressor wheel (304), with the following steps: forming the engine area (1100) and the compressor space (104) to allow gas flow between a gas supply (310, 320) and the compressor space (104), wherein the gas supply (310, 320) between the Lagerbe rich (1000) and the motor area (1100), and sealing the bearing area (1000) and the gas supply (310, 320) by a labyrinth seal (1010), the labyrinth seal (1010) being designed such that the bearing lubrication forms a partial pressure during operation due to evaporation and thus stops evaporating, and that during operation of the engine a rotating roll of lifetime bearing lubrication vapor forms in a clearance gap (1017) of the labyrinth seal (1010), the bearing area (1000) a bearing retainer (504) coupled to a shell (500) of the engine via a spring assembly to prevent tilting deflection of the bearing retainer (504) relative to the shell (500) of the motor about at least one tilt axis perpendicular to an axis of the motor shaft (306) with the labyrinth seal (1010) located on the bearing retainer (504). A method of operating a motor having a bearing section (1000) having a rotatable portion (705) attached to a motor shaft (306) and a fixed portion (703) and lifetime bearing lubrication (707) between the rotatable portion (705) and the fixed section (703); an engine section (1100); a compressor wheel (304) which is arranged in a compressor room (104), the motor area (1100) being arranged between the bearing area (1000) and the compressor wheel (304), the motor shaft (306) extending from the bearing area (1000) extends through the motor area (1100) to the compressor wheel (304), with the following steps: enabling gas flow between a gas supply (310, 320) and the compressor room (104), the gas supply (310, 320) being between the storage area (1000) and the engine area (1100); and Sealing of the bearing area (1000) and the gas supply (310, 320) by a labyrinth seal (1010), the labyrinth seal (1010) being designed in such a way that the bearing lubrication forms a partial pressure during operation due to evaporation and thereby stops evaporating , and that during operation of the engine, a rotating roll of lifetime bearing lubrication vapor forms in a clearance gap (1017) of the labyrinth seal (1010), wherein the bearing area (1000) has a bearing holder (504) which is coupled to a shell (500) of the engine via a spring arrangement to tilt deflection of the bearing holder (504) relative to the shell (500) of the engine by at least one tilt axis perpendicular to an axis of the motor shaft (306), the labyrinth seal (1010) being located on the bearing holder (504). Heat pump with the following features: an evaporator; a condenser; and a compressor incorporating the engine of any preceding Claims 1 until 19 wherein the engine is arranged such that during operation of the engine the compressor wheel (304) draws vapor from the evaporator and discharges compressed vapor into the condenser.

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