WO2018029115A1

WO2018029115A1 - Electric disk motor having media separation in the motor gap

Info

Publication number: WO2018029115A1
Application number: PCT/EP2017/069851
Authority: WO
Inventors: Holger Sedlak
Original assignee: Efficient Energy Gmbh
Priority date: 2016-08-08
Filing date: 2017-08-04
Publication date: 2018-02-15
Also published as: GB2567581B; GB201901621D0; GB2567581A; DE102016214696A1

Abstract

The invention relates to an electric disk motor comprising: a rotor (10), which has an element (105) to be moved; and a stator (10), wherein the stator is arranged with respect to the rotor (20) in such a way that a motor gap (30) is present between the rotor and the stator, wherein the rotor (10) has a cut-out (40), in which the stator (20) is arranged, wherein the rotor (10) is arranged in a first region (50) having a first pressure, wherein the stator (20) is arranged in a second region (60) having a second pressure, wherein the second pressure differs from the first pressure, and wherein an encapsulating material (70) is arranged in the motor gap (30), by means of which encapsulating material the first region (50) is separated from the second region (60).

Description

Electric disc motor with media separation in the motor gap

description

The present invention relates to electric motors, and more particularly to electric disk motors,

EP 2 549 1 13 A2 discloses a magnetic rotor and a rotary pump with a magnetic rotor. The rotor is for driving a fluid in a pump housing within a stator of the rotary pump magnetically non-contact drivable and storable. In addition, the rotor is encapsulated by means of an outer encapsulation comprising a fluorinated hydrocarbon. Within the encapsulation, the rotor comprises a permanent magnet encased in a metal jacket. The rotary pump includes a pump housing having an inlet for supplying a fluid and an outlet for discharging the fluid. The fluid is, for example, a chemically aggressive acid with a proportion of a gas, e.g. As sulfuric acid with ozone. To convey the fluid, a magnetic rotor is magnetically non-contact in the pump housing. The rotor is further provided with a magnetic drive having electric coils. The stator is formed with laminated iron, which is in magnetic operative connection with the permanent magnet of the rotor. The drive is designed as a bearingless motor in which the stator is designed as a bearing stator and drive stator at the same time. The rotor is designed as a pancake, wherein the axial height of the rotor is less than or equal to half the diameter of the rotor.

The dissertation ETH No. 12870, "The Bearingless Disc Motor", N. Barletta, 1998, discloses magnetically levitated disc motors.Magnetic bearings are completely free of contact, wear, maintenance and lubricant.For the active stabilization of one degree of freedom, two controllable electromagnets including electronic control are required The bearingless disc motor is used as a bearingless disc motor with active thrust bearing, as a miniature disc motor, or as a bearingless bioreactor within a non-bearing blood pump.Through a combination of passive reluctance magnetic bearings and bearingless motor, it is possible to complete a disc rotor with only two actively stabilized radial degrees of freedom Requirements for a large air gap, which is necessary in hermetic systems, are met by the choice of a bearingless permanent magnetically excited synchronous motor suitable for driving an axial pump for cardiac support, is designed for speeds of 30,000 revolutions per minute, resulting in a smaller size.

Commercial electric disc motors are also known by the name "Pan Cake Motor" ("pancake motor"). The engine concept illustrated in the two preceding references is characterized in that the stator extends around the rotor. Such engines are also referred to as Inneniäufer.

In the case of the internal rotor concept, there is the problem that the stator always has to be larger than the rotor, that is, the size and design of the rotor is always limited by the stator housing or that the rotor dominates the formation of the stator. Thus, the field of application of such a disc motor, which is designed as an internal rotor, limited. In addition, disk motors generally have the problem that the rotor, regardless of whether it is designed as an inner or outer rotor, pressure differences or pressures in certain directions is exposed. These pressures cause a bearing to be loaded in the direction of pressure acting on the rotor, thus increasing wear, or, if rotor deflection is allowed, the rotor is deflected in that direction and thus leeway for this deflection must be provided. In particular, when the pump is used to pump a medium from a pressure area at a first pressure to a pressure area at a second pressure, or to generate such a pressure difference at all, complex design measures must be taken to either a required To achieve wear resistance, or to provide a margin for an occurring deflection.

All this means that the design effort of the disk motor increases, and thus also increases the susceptibility to errors, while at the same time the field of application is limited.

The object of the present invention is to provide a flexible disc engine concept. This object is achieved by an electric disk motor according to claim 1, a heat pump according to claim 23 or a method for producing an electric disk motor according to claim 25. According to one aspect, the electric disc motor is designed as an external rotor. This means that the rotor has a recess in which the stator is arranged. This rotates the rotor around the stator. This makes it possible that a construction of the rotor can be defined directly by the field of application of the rotor and not by the fact that always, as with an internal rotor, it must be ensured that there is still a stator housing with appropriate magnetic coils around the rotor. On the other hand, a media or pressure separation of the disc motor is made so that in the motor gap, which is arranged between the rotor and the stator, a Verkubungsiungsmatenal is provided around the stator, so that the entire stator media and pressure moderately separated from the area is, in which the rotor is located. In this way, all coil connections for the motor coils in the stator can be led out of the motor without problems, because the entire region of the stator lies in the ambient pressure or ambient medium and not in the delivery region in which the rotor is arranged. This also avoids overvoltage issues and similar effects that occur when high voltages are used in low pressure areas because the adjacent stator coils are all separated from the low pressure area by the encapsulation material located in the motor gap. This is particularly important when the rotor is operating in a low pressure area, such as a pressure range below 100 mbar, which occurs when the rotor is used as a compressor element in a heat pump that uses water as the working fluid. But even if the rotor operates at a higher pressure than the stator, the media or pressure separation is by a Verschließiungsmatenal in the motor gap of particular advantage.

By using an external rotor in conjunction with a media / pressure separation by a Verkppungsungsmatenal in the motor pairing so an electric disk motor is provided, which can be structurally made little expensive, which has no problems in terms of over-voltage effects that would occur when relatively high voltage coil be applied in areas of low pressure, and is particularly suitable for high speeds. The latter advantage results from the fact that permanent magnets, which are attached to the rotor and define the magnetic gap on the rotor side, are supported "outwards" by the rotor material itself high speeds, such as over 50,000 revolutions per minute particularly important because the centrifugal forces occurring there can be problematic, especially in internal rotors, to the extent that the permanent magnets must be secured there with great effort.

On the other hand, because the rotor is arranged around the stator, the larger rotor diameter is again particularly advantageous, especially at speeds above 50,000 revolutions per minute, because, as in a gyroscope, the rotation of the rotor itself or its axis of rotation is additionally stabilized. This effect occurs in electric disc motors with relatively small rotor diameters, as z. B. used in internal rotors, less or not on.

In another aspect, the electric disc motor is used as an external rotor or as an internal rotor. It has a rotor having a member to be moved and a stator which is arranged with respect to the rotor so that a motor gap between the rotor and the stator is formed. The electric disc motor is configured to convey a medium from a source region to a target area through the moving element, wherein a target pressure in the target area is higher than a source pressure in the source area. The pressure acting on the rotor due to the pressure difference is reduced according to this aspect by a pressure reducer, to the effect that a pressure in the engine gap, ie where the magnetic interaction between rotor and stator takes place, less than the target pressure and greater than or equal to the source pressure is. This ensures that the rotor is no longer or at least less loaded in a certain direction due to the pressure difference between source pressure and target pressure, which would lead to a resulting pressure and thus to a deflection or to an increase in wear of the bearing.

This means that although the rotor can deliver the required pressure difference between inlet and outlet, ie between the source area and the target area, there is no such or a reduced pressure difference in the engine gap and thus in the area of interaction between rotor and stator. This is the example of a bearingless motor, which is axially only passively supported, such as reduced by a magnetic bearing, an axial deflection due to the operation of the electric disc motor or even avoided. However, the example of a contact-mounted rotor, so a rotor which is mounted with a ball bearing, is avoided by the pressure reduction, that the pressure is transferred to the bearing and the bearing wear increases. The pressure reduction in the motor gap thus leads to a motor wear or bearing wear is reduced or that in the case of wear-free bearings, so non-contact bearings necessary scope for a deflection of the rotor due to the resulting pressure on the rotor in a certain direction in the axial or Even in the radial direction can be reduced because due to the operation of the rotor no such deflections or only very small deflections compared to the situation in which no special mechanical pressure reduction is made takes place.

The pressure reduction in the engine gap is equally useful for external rotor and inner rotor. Even with an internal rotor, it is advantageous that the rotor does not experience a significantly higher deflection situation during operation than in the state. Thus, even in an internal rotor, clearances can be reduced, ie clearances between the rotor and a guide element that surrounds the fluid flow region in which Rotor acts, limited to the outside.

In preferred embodiments, the pressure reduction is performed by two flow resistors, by a first flow resistance disposed between the target area and the engine gap, and a second flow resistance disposed between the engine gap and the source area. In particular, the flow resistance between the engine gap and the target area is made larger than the flow resistance between the engine gap and the source area, so that the flow resistance between the engine gap and the target area reduces a short circuit for the pressure, while the flow resistance between the engine gap and the source area ensures that the low pressure acts in the engine gap, which also acts in the source area. In particular, when the motor is designed as an external rotor, going to the fact that the stator is arranged in a recess of the rotor, it is preferred to attach the Flußwi- resistance between the target area and the motor gap as far outside the rotor, so that as possible large area of the rotor surface, which is opposite to the stator, is disposed in an area which is on the low swelling pressure or the pressure which is smaller than the target pressure. In contrast, it is preferable to attach the second flow resistance between the engine gap and the source region as centrally as possible, ie relatively centrally in the rotor in order to achieve the same conditions as possible along the circumference in the engine gap. In preferred embodiments, the pressure reducer includes a labyrinth seal between the target area and the engine gap that provides a defined and relatively large flow resistance and, alternatively or additionally, a bore in the rotor between the engine gap and the source region that provides a relatively small flow resistance. Even the use of either only one labyrinth seal or only one hole, ie the use of only one flow resistance between source area and motor gap or target area and motor gap already leads to a pressure reduction in the motor gap and thus to a reduced deflection of the rotor with respect to the stator during operation in the case of a non-contact Magnetic bearing and in particular in the case of an axially passive bearing, or to a reduction in wear in the case of a contact bearing, such as a ball bearing due to the reduced load during operation.

The first aspect of the encapsulation material in the motor gap and the second aspect of the pressure reducer may be preferably combined, such that an external rotor disc motor has both the encapsulation in the motor gap and the pressure reducer. However, the two aspects can just as well be used alternatively to one another and, with regard to the pressure reducer, not only for the external rotor, but also for an internal rotor. Moreover, both aspects can be used separately from each other or together for contact bearings, but the use of magnetically levitated rotors is preferred, and in particular of axially passive bearings, i. H. axially unregulated bearings and radially active controlled magnetic bearings. Preferred embodiments of the present invention will be explained below in detail with reference to the accompanying drawings. Show it:

1A shows an external rotor according to a first aspect; 1 B an electric disc motor according to a second aspect, as

External rotor or inner rotor is formed;

FIG. 1C shows an inner rotor according to the second aspect; FIG.

Fig. 1D shows a preferred implementation of the second aspect with two series-connected flow resistors; FIG. 2A is a cross-sectional view of an electric disc motor according to the first aspect; FIG. Fig. 2B is a cross-section through an electric disc motor according to the second aspect, in which the first aspect is also realized; a cross-section through a detailed representation of an implementation of the flow resistance by means of a labyrinth seal; a schematic representation of a rotor and the forces acting on it with respect to the second aspect; a schematic representation of a magnetic bearing on the example of an internal rotor;

6 is a cross-sectional view of an external rotor with an increased return element; and FIG. 7 shows a schematic cross section through a heat pump with the electric disk motor according to the first or second aspect.

Fig. 1A shows a cross section through a schematically illustrated electric disc motor with a rotor 10 having a member to be moved. In addition, a stator 20 is provided, with the stator 20 being arranged with respect to the rotor 10 so that a motor gap 30 exists between the rotor and the stator. The rotor 10 further includes a recess 40 in which the stator 20 is arranged.

In addition, the rotor 10 is arranged in a first area 50 with a first pressure pi. Further, the stator is disposed in a second region 60 having a second pressure p ₃ different from the first pressure. In the embodiment shown in Fig. 1A, the first pressure is exemplified by the pressure inside the electric disc motor of Fig. 1A. By contrast, the second pressure is, for example, the ambient pressure or the atmospheric pressure when the disc motor is arranged in the atmosphere or a pressure different from the atmospheric pressure when the disc engine is operating in an area with an atmospheric pressure. different pressure is arranged. Furthermore, an encapsulation material 70 is arranged in the motor gap 30, by means of which the first area 50 is separated from the second area 60. The separation takes place, for example, in that the encapsulation material completely surrounds the stator in the embodiment shown in FIG. 1A, and that leads 80 for the coils, which are attached to the stator and which are not shown in FIG. 1A, surround the coils be supplied with electrical power through the encapsulant through to the outside, ie in the second region 60. The electric disc motor is designed as a conveying motor and comprises an inlet 90 for a working medium and an outlet 100 for the working medium conveyed by the disc motor. As shown in Fig. 1A, the pressure inside the disc motor p is different from the pressure p ₃ outside the disc motor. Only preferably, the pressure p ₁ in the interior of the disc motor is lower than the pressure outside the disc motor. Similarly, the pressure outside the disc motor may be lower than the pressure inside, ie inside the motor housing.

In particular, it is further illustrated in FIG. 1A that the rotor and the stator are disposed in a motor housing 110, the motor housing having an opening through which the encapsulation material 70 extends. The encapsulation material or an element, with which the encapsulation material is connected, is attached to the motor housing 1 10 by a schematically illustrated sealing ring 120, so that a pressure-tight connection between the encapsulation material 70 and the motor housing 1 10 via the sealing ring 120, for example O-ring may be present. Thus, in Fig. 1A, an external rotor is exemplified as an electric disc type electric motor in which the rotor is moved within a motor housing, while the coils of the stator and in particular the area of the stator located at the motor gap do not communicate with the internal pressure of the disc motor but communicates with the external pressure, which is particularly advantageous with regard to an electrical supply of the coils typically mounted in the stator. In particular, when the internal pressure p- is smaller than the external pressure p ₃ , there are significant advantages in terms of coil over-shots and other effects that the coils are not in the low-pressure region but are encapsulated in the low-pressure region.

In addition, the encapsulation of the coils relative to the interior of the disc motor has advantages that the coils do not come into contact with the medium to be conveyed and therefore not exposed to corrosion due to the medium to be conveyed are, wherein the medium may be, for example, water or water vapor. 1A also shows that the rotor 10 is provided with permanent magnets 130 facing the stator-side region, which typically has stator-side poles on which magnetic coils are wound, to define the motor gap 30.

1 B shows an electric disc motor according to a second aspect, which also has a rotor 10 facing a stator 20 to define the motor gap 30. More specifically, in the second aspect shown in FIG. 1B, the electric disk motor is configured to be shown by the member to be moved connected to the rotor 10 and that shown in FIG. 1B together with the rotor 10 , a medium from an inlet 90 or a source region 90, in which there is a lower pressure to promote to a target area 100 or to an outlet 100, wherein the target area has a high pressure, or generally, a greater pressure than the source area has. Moreover, the electric shift motor is configured to include a pressure reducer 140 configured to reduce a pressure acting on the rotor due to the different pressures in the head region and in the target area. In particular, the pressure reducer is formed so that a pressure in the engine gap 30 is smaller than the target pressure or the large pressure, but greater than or equal to the swelling pressure. The pressure reducer 140 is thus designed to reduce the pressure in the engine gap 30 from the larger pressure in the target area and optimally equal to the pressure in the head region or between the target pressure, as compared to a situation in which the pressure reducer is not present and bring the swelling pressure. Fig. 1 C shows an alternative implementation of the electric disc motor of Fig. 1 B in turn, a stator 20 is present, which now forms part of the motor housing 1 10. The stator is further provided with coils 150 facing the permanent magnets 130 of the rotor 10 to again form the motor gap 30. Furthermore, the rotor 10 is connected to an element 105 which is designed here above the rotor and is connected to the rotor. The pressure reducer 140 is in turn provided to reduce the pressure in the motor gap 30, namely with respect to the pressure in the target area, ie the pressure at the outlet 100.

In embodiments, a plurality of permanent magnets 130 are attached to the rotor 10. Further, the stator 20 is provided with coils 150, wherein the coils 150 are opposed to the permanent magnet 130 via the motor gap 30. Furthermore, at Embodiments, each permanent magnet 130 has a first circular sector, and each pole has a second circular sector. The first circular sector of the permanent magnet is greater than or equal to the second circular sector of the poles. In embodiments, at least four oppositely polarized permanent magnets with respect to the motor gap 30 are mounted on the rotor 10, the permanent magnets being polarized such that a permanent magnet has its north pole directed towards the motor gap 30 and an adjacently arranged permanent magnet its south pole to the motor gap 30 has directed. As shown in FIG. 1D, the pressure reducer 140 includes, for example, a first flow resistance 10a between the target area 100 and the engine gap 30 and a second flow resistance 140b between the engine gap 30 and the source area 90 and the inlet 90, respectively. The two flow resistances 140a, 140b are preferably both present. Depending on the implementation, however, it may already be sufficient to achieve a reduction of the pressure acting on the rotor due to the operation of the disc rotor, only the first flow resistance between the target area and the motor gap or, alternatively to the first flow resistance, the second flow resistance 140b between the engine gap and the source area. Preferably, when both flow resistances 140a, 140b are provided, the first flow resistance 140a has a higher value than the second flow resistance 140b. This means that the pressure in the engine gap 30 preferably differs more from the high pressure in the target area 100 than the pressure in the engine gap 30 differs from the pressure in the head region when the electric disk motor is operated. Fig. 2A shows a preferred embodiment of the electric disc motor according to the first aspect of the example of an embodiment for a Radialradkompressor that can be used at high speeds over 50,000 revolutions per minute and up to, for example, 90,000 revolutions per minute within a heat pump with, for example, water can be operated as a working medium.

FIG. 2A shows an implementation of the disc motor according to the first aspect, wherein the stator 20 is encapsulated with the encapsulant material 70 such that the media separation between the high and low pressure region occurs across the motor gap 40. The stator 20 is provided with coils which are not shown in FIG. 2A, but which are connected via the access lines 80 which are formed by the encapsulation material 70. stretch or, if the encapsulation material! encapsulate only the motor gap and parts of the stator, already in the surrounding area 60.

The rotor, which is formed by the permanent magnets 130, a yoke element 160 comprising the permanent magnets, and a bandage 170 mounted as additional safety, is further connected to the element 105 to be moved, which is shown only schematically in FIG. 2A as a radial wheel with blades , In particular, the electric disk motor is designed to rotate the radial gear 105 and the rotor 10 within a guide element 180, which is spaced from the respective blade ends of the radial gear 105 by a clearance 190. The radial impeller is configured to typically bring vapor from an evaporator in which a lower pressure p ₀ prevails to a first pressure pi. This first pressure i typically prevails at an outlet of the radial wheel, which is also referred to as an impeller, as shown schematically in FIG. 2A. Typically, the guide member is coupled to a Leitraum, so that the accelerated by the rotation of the radial wheel steam is brought into the Leitraum, where it is brought due to the continued further promotion of steam through the radial to a higher target pressure p ₂ , in the Condenser of the heat pump prevails, as shown in Fig. 2A. In the case of the external rotor, the height of the electrically active stator 20 is smaller than a diameter of the stator and preferably smaller than half the diameter of the stator. On the other hand, when the inner rotor is considered, when referring to FIG. 1C, the height of the electrically active rotor is preferably smaller than the diameter of the electrically active rotor and more preferably smaller than half the diameter of the rotor.

Fig. 2B shows an embodiment of the electric disc motor according to the second aspect, in connection with an application for a radial wheel of a compressor of a heat pump, as has been illustrated with reference to Fig. 2A. In addition to the elements shown in FIG. 2A, the two flow resistances 140a, 140b described with reference to FIG. 1D are further formed in the embodiment shown in FIG. 2B. Specifically, in the embodiment shown in FIG. 2B, as an exemplary second flow resistor 140b, the pressure reducer 140 includes a bore 200 in the rotor 105 configured to allow media passage from the engine gap 40 to the source region or inlet 90 into the compressor. This makes it possible that a media passage is achieved by the moving member 105 which is connected to the rotor. Moreover, in the embodiment shown in FIG. 2B! the pressure reducer 140 is configured to have a plurality of structural members 210a, 210b, 210c that exist between the target area and the outlet from the radial wheel, also shown at 100 in FIG. 2B, and the engine gap 140. Thereby, by the cooperation of the plurality of constructional elements 210a-210c, a pressure drop from the target area 100 having a pressure p ₍ reaching the engine gap having only a pressure p-, which is less than the pressure pj and is greater than or equal to the pressure p ₀ in the source region, ie at the inlet 90. In particular, a first design element of the plurality of design elements is attached to the rotor 10. This design element is the design element 210b in the embodiment shown in FIG Construction element of the plurality of structural elements attached to a motor housing, such as the motor housing 1 10, this construction element is referred to as a construction element 210a or 210c Further, the two structural elements, which are shown as protruding rings, which are shown in cross-section in Fig. 2B, are formed, arranged so that they in their Zus ammenwirken cause a pressure drop. In particular, the construction elements 210a-210c form a labyrinth seal. In the embodiment shown in Fig. 2B, the construction elements are each formed as projecting rings. However, they may also be formed as alternative construction elements protruding from a surface of the motor housing 10 on the one hand and the rotor or member to be moved on the other hand to cooperate, such that the rotor can be rotated with respect to the motor housing, and such that due to the close placement of the structural members to each other, a pressure drop occurs so that the pressure p within the labyrinth seal with the structural members 210a-210c is less than the pressure outside the labyrinth seal.

Fig. 3 shows an alternative representation on an enlarged scale with respect to the embodiment of Fig. 2B. Thus, further construction elements 212a-212d are formed, wherein again the construction elements 212a, 212c are arranged on the housing 210, and the construction elements 212b, 212d are arranged on the housing 210 or the moving element 105. In contrast to the construction elements 210a to 210c and 21Od of FIG. 3, respectively, which extend radially with respect to a rotation of the rotor, the construction elements 212a to 212d are arranged axially with respect to a rotation of the rotor 10. In one implementation, both radial and axial or alternatively aligned structural elements may be used as a labyrinth seal. see, or only radial construction elements 210a-210d or only axial construction elements 212a-212d or only designed in other directions construction elements. Moreover, it is not absolutely necessary that only a relatively small number of construction elements, such as shown in Fig. 2B intermesh, but it can also more or even fewer construction elements, ie, for example, only two construction elements or four or more construction elements cooperate. In addition, it is also possible that more design elements are mounted on the rotor than on the housing or vice versa.

In one implementation, the structural elements could also be mounted between the rotor and stator outside the motor gap. However, in the application in FIG. 2B or as a whole it is preferred to mount the construction elements between the rotor / element to be moved and the motor housing, since then the construction elements or the associated flow resistance R "140a between the target area 100 and the motor gap 30 as far outside relative to the rotor is mounted, while at the same time the second flow resistance, so the bore 200 through the rotor as far inside as possible, and preferably even axially mounted directly in the rotor. This ensures that the largest possible area of the rotor, namely at the top in the orientation shown in FIG. 2B, which at the same time is a preferred orientation for this disk motor in an application of a heat pump compressor, is not exposed to the target pressure pi, but only to the reduced one Pressure ρ-, 'so that by the operation of the rotor, by the ultimately resulting different pressures and p ₀ , yet no deflection of the rotor will take place down or only a very small deflection. Thus, the clearance 190 between the guide member 180 and the radial gear 105 can be made very small, so that a compressor with a good efficiency is obtained. On the other hand, the slight downward deflection of the radial wheel in the axial direction, that is, in the example shown in FIG. 2B, allows the rotor to be magnetically supported and, in particular, with a magnetic bearing that is passive in the axial direction, ie not regulated in this direction. but that is regulated only in the radial direction. Thus, only one regulation with respect to a single, so the radial direction is necessary. This leads to an electric disk motor which, despite the considerable rotational speeds which it is capable of performing, has a simple bearing control concept, since an axial bearing regulation is not necessary, the rotor can still be operated with a small margin to the guide member 180 in order to achieve high efficiency.

Fig. 4 shows a schematic representation of the forces acting on the rotor. The rotor 10 or the element 105 to be moved is again shown schematically as a radial wheel in cross section, but the individual blades are not specifically shown for reasons of clarity, but are immediately clear to those skilled in the art. When the rotor is operated, there is a low vaporization pressure p ₀ in the source region, while in the target region there is a higher pressure pi at the outlet of the radial impeller, which is brought to the still higher condenser pressure by the guide space adjacent to the radial impeller. The output pressure Pi presses on the upper relatively large surface of the radial wheel with a force Fi, which is equal to the product of p ₁ and the surface Ai, ie the surface in the plan view of the rotor 10 from above. In addition, a small pressure F ₀ acts from below on the rotor, which is equal to the product of the low swelling pressure p ₀ and the relatively small area A ₀ .

In addition, a weight F _g acts on the rotor, which is equal to the mass of the rotor m _R times the gravitational acceleration g. In addition, a force F _M also acts upwards, which is equal to a change in the mass with time multiplied by the velocity of the mass flow, which the radial wheel sucks from the bottom to the top. The weight and the force due to the mass flow are given from the outside. The same applies to the dimensions of the areas A ₀ and A _v. However, the pressure is reduced by the pressure reducer 10 according to the present invention. Thus, the difference between Po-Ac-prAi by the pressure reducer is made as small as possible. As a result, the total acting on the rotor or the element to be moved force due to the operation of the rotor is reduced as much as possible, which in turn leads to a reduced deflection of the rotor when the rotor is operated. If no deflection due to an existing contact bearing, such as a ball bearing, is allowed, the pressure on the bearing is reduced.

Preferably, the rotor is supported relative to the stator by a magnetic bearing, as exemplified in FIG. In Fig. 5, the two directions are shown axially 250 and 260 radially. Again, there is a motor with a motor gap 40, and the rotor is held axially with respect to the stator due to the permanent magnets on the rotor side and the electrical coils on the stator side, and not specially regulated. In contrast, a radial detection device 270 and a radial control / regulation device 280 is provided. The radial detection device 270 detects the position of the rotor relative to the stator or vice versa via detection lines 271. The result of the radial detection 270 is communicated to the radial control / regulation device 280 via a sensor line 272. This generates corresponding actuator signals via actuator signal lines 273 on the rotor or the stator, depending on the implementation. However, it is preferred to drive only the rotor to position it with respect to the stator due to the actuator signal 273, such that the motor gap 40 is of similar size around the entire rotor and the rotor does not contact the stator.

In the embodiment shown in Fig. 5, the rotor may be inside and the stator may be outside. Then it is an inner rotor. At the same time, however, the inner element may be the stator and the outer element may be the rotor, so that it is an external rotor. In principle, the magnetic bearing in both cases is similar in that an axial control does not take place while a radial control by the radial detection device 270 and the radial control / regulation device 280 takes place. In embodiments, the stator is simultaneously formed as a bearing stator and drive stator.

Further, in embodiments, the electric disc motor is an external rotor, and an axial height of the electric drive effective stator is smaller than a half diameter of the stator. In other embodiments, the electric disc motor is an internal rotor, and an axial height of the rotor is less than half the diameter of the electrically driving rotor, electrically related to the region and defined by the region in which the the permanent magnets used on the rotor are opposite to the coils used for the drive or to the coils of the stator wound on the poles.

Fig. 6 shows a cross section through a preferred rotor, which is formed in several pieces. In particular, the rotor comprises the moving member 105, which in preferred embodiments of the present invention is formed of a non-ferromagnetic material, such as plastic or aluminum. The element to be moved here is for example a paddle wheel or impeller of a Turbocompressors, as it can be used for example in a heat pump.

By contrast, the rotor 10, which has the permanent magnets 130, the annular return element surrounding the permanent magnets 130 and the bandage 170 arranged above it, is formed from a different material than the element to be moved. In particular, the permanent magnets are formed of a specific material favorable for permanent magnets. The return element is annular and formed from a ferromagnetic material, and the bandage 170 is preferably formed from carbon material.

In the exemplary embodiment shown in FIG. 6, the permanent magnets 130 project partially over a first flat side 105a, in which the recess 40 is formed. The element 105 to be moved further has a second "flat" side 105b, but of smaller diameter than the first side 105a, which may also be seen as a "flat" side if, for illustrative purposes, the recess 40 is considered non-existent, and if further the board in the form of a circumferential spring 276 is also thought away. Preferably, however, the spring 276 engages an annular groove 278 provided in the inference element 160 so that the projection 276 and the groove 278 engage. Depending on the embodiment, however, a spring may also be provided in the return element and the groove may be provided in the element 105 to be moved or in the first flat side 105a Thus, the connection of return element, permanent magnet and bandage obtains a structural stability with the element 105 to be moved In addition, it is further ensured by the recess 40 that the permanent magnets and the return element press on the rotor material due to the centrifugal forces, so that the connection between the return element on the one hand and the rotor material on the other hand, the stronger the higher the rotational speed.

With regard to the dimensions, it is preferred that the motor gap 40 is smaller than 1.5 mm, wherein in the case of an encapsulation in the motor gap, the distance between the encapsulation material and the permanent magnets is less than 1.5 mm. Further, it is preferable that a diameter of the stator 20 is between 3 cm and 7 cm, or that a height of the stator is smaller than 4 cm. Further, the electric disk motor is configured to run at a speed greater than 50,000 revolutions per minute. Remote the bore 200 has a diameter preferably between 1 and 4 mm. In addition, a clearance 190 between the guide member 180 and the paddle wheel 105 is preferably less than 1, 5 mm. Moreover, as shown particularly in FIG. 6, it is preferable that the moving member 105 has the first "flat" side 105a opposite to the stator 20 and has the second flat side 105b that faces from the stator 20, wherein the diameter of the first flat side is larger than the second diameter of the second flat side Furthermore, as stated, the recess 40 is arranged in the first flat side 105a, wherein the permanent magnets 130 at least partially located in the recess 40 Further, in preferred embodiments, it is useful that the return element has the more trapezoidal cross-sectional shape as shown in Fig. 6 so that an upper edge of the return element 160 is located higher in the axial direction than an upper edge of the permanent magnets 130. Thus the permanent magnets 130 arranged as deep as possible in the recess, while the return element on the permanent magnet te 130 protrudes with respect to its side, which is connected to the bandage 170.

Furthermore, as shown more clearly e.g. As shown in FIG. 2B, the encapsulation material 70 is attached to the stator 20 not only in the motor gap 40, but also on the underside of the stator 20 in FIG. 2B, that is, the side of the stator facing the recess 40. The stator 20 is in this case preferably disc-shaped and has a normal which is parallel to the axis of rotation or coincides with the axis of rotation. The flat side of the stator is opposed to a corresponding side of the moving member via the recess 40, and the encapsulation material 70 is also mounted on the flat side of the stator in addition to the respective sides of the permanent magnets. However, it is not necessary for the encapsulation material to fill the entire area above the stator 20. Instead, it is sufficient that the encapsulation material of the stator seals against the interior of the electric disc motor.

Fig. 7 shows a preferred application of the electric disc motor to the example of a heat pump. The heat pump includes an evaporator 300, a compressor 400 and a condenser 500, the compressor 400 having the electric disk motor described with reference to FIGS. 1A to 6. In addition to the elements of the disc motor illustrated, for example, with reference to FIG. 2A, the compressor further includes a pilot space 510, which is arranged radially around the working steam conveyed by the moving member 105, which has been sucked by the evaporator 300. continue to promote and ultimately increase the pressure to the required pressure in the condensation zone in the condenser 500.

Liquid to be cooled passes through an evaporator inlet 302 into the evaporator. Cooled Arbeitsfiüssigkeit runs on an evaporator effluent 304 back from the evaporator. To ensure that the radial wheel 105 only sucks in steam and not drops of water, a mist eliminator 306 is additionally provided. Due to the low pressure in the evaporator 300, a part of the working fluid brought into the evaporator 300 via the evaporator inlet 302 is evaporated and sucked through the mist eliminator 306 via the second side 105b of the radial gear 105 and conveyed upwards and then discharged into the guide space 510. From the Leitraum 510 compressed working steam is brought into the condensation zone 510. The condensation zone 510 is further supplied via a condenser inlet 512 to be heated working fluid, which is heated by the condensation with the heated steam and discharged through a condenser outlet 514. Preferably, the condenser is designed as a condenser in the form of a "shower", so that via a distributor device 516, a liquid distribution in the condensation zone 510 is reached, so that as efficiently as possible, the compressed working steam is condensed and transfer the heat contained in it into the liquid in the condenser becomes.

In the embodiment shown in Fig. 7, the motor housing 1 10 simultaneously forms the upper housing part of the condenser or condenser 500. In addition, as is also shown in Fig. 7, the connecting line 80 for the coils of the stator 20 with a Control 600 connected to perform the corresponding speed controls and at the same time the active storage on a preferably used magnetic bearing, as has been described with reference to FIG. 5. The controller thus additionally provides the functions of the radial detection 270 and the radial control / regulation 280.

Although certain elements are described as device elements, it should be understood that this description is likewise to be regarded as a description of steps of a method and vice versa. It should also be appreciated that the controller may be implemented as software or hardware, for example, by element 600 in FIG. 7 or 280 in FIG. The implementation of the control can be carried out on a non-volatile storage medium, a digital or other storage medium, in particular a disk or CD with electronically readable control signals, which can cooperate with a programmable computer system such that the corresponding method for pumping heat or to operate a heat pump is running. In general, the invention thus also comprises a computer program product with a program code stored on a machine-readable carrier for carrying out the method when the computer program product runs on a computer. In other words, the invention can thus also be realized as a computer program with a program code for carrying out the method when the computer program runs on a computer.

LIST OF REFERENCE NUMBERS

10 rotor

20 stator

30 motor gap

40 recess

50 first area

60 second area

70 encapsulant 80 leads

90 inlet / source area

100 outlet / target area

105 element to be moved

105a first page

105b second page

110 motor housing

120 seal

130 permanent magnets

140 pressure reducer

140a first flow resistance

140b second flow resistance

150 stator coils

160 return element

170 bandage

180 guide component

190 travel

200 hole

210a-210d Construction elements 212a-212d Construction elements 250 Axial direction

260 radial direction

270 Radial detection device

271 detection line

272 control line

273 actuator line

276 lead 278 groove

280 Radial control / regulation

300 evaporators

302 evaporator feed

304 Evaporator drain

306 droplet separator

400 compressor

410 route

500 condensers

510 condensation zone

512 condenser feed

514 Condenser drain

516 condenser distributor

600 control

Claims

Paterta Brt ^j cjie

An electric disk motor comprising: a rotor (10) having a member (105) to be moved; a stator (20), wherein the stator is arranged with respect to the rotor (20), that a motor gap (30) between the rotor and the stator is present, wherein the rotor (10) has a recess (40), in which Stator (20) is arranged, wherein the rotor (10) in a first region (50) is arranged at a first pressure, wherein the stator (20) in a second region (60) is arranged at a second pressure, wherein the second pressure is different from the first pressure, and wherein in the motor gap (30) a Verkers! ungsmaterial (70) is arranged, through which the first region (50) from the second region (60) is separated.

An electric disk motor according to claim 1, further comprising: a motor housing (110) to which the encapsulation material (70) is directly or indirectly connected, such that within the motor housing the first area at the first pressure and outside the motor housing the second region is formed with the second pressure. An electric disk motor according to claim 1 or 2, wherein said stator (20) comprises a plurality of coils (150) provided with leads (80) and applied to poles, said encapsulating material (70) forming said coils (150) and surrounding the poles, and wherein the leads (80) of the encapsulant material (70) protrude into the second region (60), or in which a plurality of permanent magnets (130) is mounted on the rotor (10), in which the stator (20) is provided with coils (150), the coils (150) being applied to the permanent magnets (130) via the motor gap (30 ) are opposite.

An electric disc motor according to claim 3, wherein each permanent magnet (130) comprises a first circular sector, each pole comprising a second circular sector, and wherein the first circular sector of the permanent magnets is greater than or equal to the second circular sector of the poles.

An electric disc motor according to claim 4, wherein at least four oppositely polarized permanent magnets with respect to the motor gap (30) are mounted on the rotor (10), the permanent magnets being polarized such that a permanent magnet has directed its north pole toward the motor gap (30) adjacently arranged permanent magnet has directed its south pole towards the motor gap (30).

Electric disc motor according to one of the preceding claims, which is operable so that the first pressure is less than the second pressure.

Electric disc motor according to one of the preceding claims, in which the rotor is radially magnetically supported (270, 280) radially relative to a rotational axis of the rotor, or wherein the stator is simultaneously formed as a bearing stator and drive stator. Electric disc motor according to one of the preceding claims, wherein the rotor is mounted axially passive with respect to a rotational axis of the rotor (10). An electric disk motor according to any one of the preceding claims, wherein the rotor (10) has a plurality of permanent magnets (30) at an inner portion of the recess (40), further comprising an annular magnetic return element (160) surrounding the permanent magnets (130) the permanent magnets between the return element and the motor gap (30) are arranged.

An electric disc motor according to claim 9, further comprising a bandage (170) attached to said annular return element (160) on the side of said return element (160) facing away from said permanent magnet (130).

An electric disc motor according to any one of the preceding claims, wherein the stator (20) is disc-shaped and has a flat side whose normal is parallel to a rotation axis or coincides with the rotation axis, the flat side of the stator being fixed to one side of the member to be moved (150 ), and wherein the encapsulation material (70) is disposed on the flat side of the stator (20) and on an end face of the stator facing permanent magnets (130) of the rotor (10).

An electric disc motor according to any one of the preceding claims, wherein the member to be moved (105) has a first side (105a) facing the stator (20) and a second side (105b) facing away from the stator a first diameter of the first side is greater than a second diameter of the second side.

13. An electric disk motor according to claim 12, in which the recess (40) is arranged in the first side (105a), in which the permanent magnets (130) are at least partially arranged, wherein the permanent magnets (130) on a side facing away from the stator (20) with an annular return element ( 160) are provided.

The electric disc motor of claim 13, wherein the permanent magnets (130) at least partially protrude beyond the first side (105a), or wherein the annular return element (160) projects beyond the first side (105a), or wherein the permanent magnets (130) have a first length protrude beyond the first side (105a) and project the annular return element (160) a second length greater than the first length beyond the first side (105a).

An electric disc motor according to any one of claims 12 to 14, wherein said first side (105a) has a projection (276) and an annular return element (160) has a groove (278) formed to engage said projection (276) or in which the first side (105a) has a groove and the annular return element (160) has the projection, wherein the projection is adapted to engage the groove.

An electric disc motor according to any one of the preceding claims, wherein a motor housing (110) has a lid to which the stator (20) and the encapsulation material (70) are connected, or wherein the lid is made of the encapsulating material in one piece, or wherein the cover is releasably connected to a motor housing part, and wherein at a interface between the cover and the motor housing part, a seal (120) is formed, through which the first area (50) from the second area (60) is sealed. 17. An electric disc motor as claimed in any one of the preceding claims, wherein the member (105) to be moved is a radial wheel with vanes, the vanes being configured to deliver gas to a third region of higher pressure than the first pressure upon rotation of the radial wheel ,

The electric disc motor of claim 15, wherein the encapsulation material (70) is arranged so that the third area communicates with the first area, and that the first and third areas do not communicate with the second area.

An electric disk motor according to any one of the preceding claims, which is formed so that the motor gap (30) is smaller than 1, 5 mm, or in which a diameter of the stator (20) is between 3 cm and 7 cm, or at a height of the stator (20) is less than 4 cm, or is designed to run at a speed greater than 50,000 U / min.

An electric disc motor according to any one of the preceding claims, wherein the electric disc motor is an external rotor, and an axial height of the stator is smaller than a half diameter of the stator, or wherein the electric disc motor is an internal rotor, and an axial height of the rotor is less than half Diameter of the rotor is.

21. An electric disk motor according to one of the preceding claims, wherein the rotor (10) is connected to the element to be moved (105), wherein the element to be moved is formed of aluminum or plastic, and the rotor (10) permanent magnets (130) and a magnetic return element (160).

22. An electric disc motor according to any one of the preceding claims, adapted to convey a medium from a source region (90) to a target area (00) by the moving member, the pressure in the target area (100) being higher than a pressure in the source area (90), the electric disk motor further comprising: a pressure reducer (140) for reducing a pressure acting on the rotor due to an operation of the rotor (10).

An electric disc motor according to claim 22, wherein the pressure reducer (140) has a first finite flow resistance (140a) between the target area (100) and the engine gap (30) or a second finite flow resistance (140b) between the engine gap (30) and the source area (12). 90), wherein the first flow resistance (140a) as a labyrinth seal (210a-210c) between a motor housing (1 10) and the rotor (10) is formed, or wherein the second flow resistance (140b) as a bore (200) in the rotor is formed so that via the bore gas communication between the source region (90) and the motor gap (30) is made possible.

An electric disc motor according to claim 23, wherein the bore (200) has a diameter between 1 and 4 mm.

An electric disc motor according to any one of the preceding claims, wherein the member (105) to be moved is formed as a paddle wheel connected to the rotor, the member (105) to be moved being further rotatably disposed within a guide member (180), a Clearance (190) between the guide member (180) and the paddle wheel (105) is less than 1, 5 mm.

Heat pump with the following features; an evaporator (300); a compressor (400); and a condenser (500), wherein the compressor (400) is an electric disc motor according to any one of

Claims 1 to 25 has.

Heat pump according to one of the preceding claims, wherein the element to be moved is a paddle wheel, wherein a suction region of the evaporator (300) is connected to a guide device (180), so that in an operation of the electric disc motor vaporized working fluid is sucked, in one Operation of the heat pump, a swelling pressure in the suction of the evaporator (300) is present, wherein at a conveying end of the Radialrads the first region with the first pressure is higher than the swelling pressure, wherein in the condenser (500) is a condenser, the is greater than the first pressure, and wherein the second pressure in the second region (60) is equal to or equal to condenser pressure.

A method of manufacturing an electric disc motor having a rotor (10) having a member (105) to be moved, a stator (20), the stator being disposed relative to the rotor (20) such that a motor gap (30) is interposed between the stator Rotor and the stator is present, with the following steps:

Performing a recess (40) in the rotor (10) in which the stator (20) is arranged,

Placing the rotor (10) in a first area (50) at a first pressure;

Placing the stator (20) in a second area (60) at a second pressure, the second pressure being different from the first pressure, and

Placing encapsulant material (70) in the motor gap (30) separating the first region (50) from the second region (60).