EP3423762B1 - Heat pump with convective shaft cooling - Google Patents

Description

The present invention relates to heat pumps for heating, cooling or for any other application of a heat pump.

Figures 8A and 8B represent a heat pump, as in the European patent EP 2016349 B1 is described. The heat pump initially comprises an evaporator 10 for evaporating water as the working liquid in order to generate a steam in a working steam line 12 on the outlet side. The evaporator comprises an evaporation space (in Figure 8A not shown) and is designed to generate an evaporation pressure of less than 20 hPa in the evaporation space, so that the water evaporates at temperatures below 15 ° C. in the evaporation space. The water is, for example, groundwater, free in the ground or circulating brine in collector pipes, i.e. water with a certain salinity, river water, sea water or sea water. All types of water, i.e. calcareous water, calcareous water, saline water or saline-free water can be used. This is because all types of water, ie all of these "hydrogens", have the favorable water property, namely that water, also known as "R 718", has an enthalpy-difference ratio that can be used for the heat pump process of 6 has, which corresponds to more than 2 times the typical usable enthalpy-difference ratio of, for example, R134a.

The water vapor is fed through the suction line 12 to a compressor / condenser system 14 which has a turbomachine such as a radial compressor, for example in the form of a turbocompressor, which in Figure 8A is denoted by 16. The turbomachine is designed to compress the working steam to a steam pressure at least greater than 25 hPa. 25 hPa corresponds to a condensing temperature of around 22 ° C, which can be a sufficient heating flow temperature for underfloor heating, at least on relatively warm days. To generate higher flow temperatures, pressures greater than 30 hPa can be generated with the fluid machine 16, a pressure of 30 hPa having a condensing temperature of 24 ° C, a pressure of 60 hPa having a condensing temperature of 36 ° C, and a pressure of 100 hPa corresponds to a condensing temperature of 45 ° C. underfloor heating are designed to be able to heat sufficiently with a flow temperature of 45 ° C even on very cold days.

The turbomachine is coupled to a condenser 18, which is designed to liquefy the compressed working steam. As a result of the liquefaction, the energy contained in the working steam is fed to the liquefier 18 in order to then be fed to a heating system via the flow 20a. The working fluid flows back into the condenser via the return 20b.

According to the invention, it is preferred to extract the heat (energy) from the high-energy water vapor directly through the colder heating water, which is absorbed by the heating water, so that it heats up. So much energy is extracted from the steam that it is liquefied and also participates in the heating circuit.

This results in an introduction of material into the condenser or the heating system, which is regulated by an outlet 22, in such a way that the condenser has a water level in its condenser space which, despite the constant supply of water vapor and thus condensate, always remains below a maximum level.

As has already been stated, it is preferred to use an open circuit, ie to evaporate the water that is the heat source directly without a heat exchanger. Alternatively, however, the water to be evaporated could first be heated by an external heat source via a heat exchanger. In addition, in order to avoid losses for the second heat exchanger, which has hitherto been present on the condenser side, the medium can also be used there directly, if one thinks of a house with underfloor heating, the water that comes from the evaporator to circulate directly in the underfloor heating.

Alternatively, however, a heat exchanger can also be arranged on the condenser side, which is fed with the flow 20a and which has the return 20b, this heat exchanger cooling the water in the condenser and thus heating up a separate underfloor heating liquid, which will typically be water.

Due to the fact that water is used as the working medium and the fact that only the evaporated portion of the groundwater is fed into the turbomachine, the degree of purity of the water is irrelevant. The fluid machine is always supplied with distilled water, just like the condenser and the possibly directly coupled underfloor heating, in such a way that the system requires less maintenance than today's systems. In other words, the system is self-cleaning, since only distilled water is supplied to the system and the water in the outlet 22 is therefore not contaminated.

In addition, it should be pointed out that turbomachines have the properties that, similar to an aircraft turbine, they do not connect the compressed medium to problematic substances, such as oil. Instead, the water vapor is only compressed by the turbine or the turbocompressor, but is not associated with oil or another medium which impairs purity and is thus contaminated.

The distilled water discharged through the drain can thus - if no other regulations stand in the way - be easily returned to the groundwater. Alternatively, however, it can also e.g. seep in the garden or in an open area, or it can be fed to a sewage treatment plant via the sewer, if required by regulations.

The combination of water as a working fluid with the twice the better usable enthalpy-difference ratio compared to R134a and because of the reduced requirements for the closed system, and because of the use of the turbomachine, by which the efficiency and without impairment of cleanliness necessary compression factors are achieved, an efficient and environmentally neutral heat pump process is created.

Figure 8B shows a table to illustrate different pressures and the evaporation temperatures assigned to these pressures, from which it follows that very low pressures in the evaporator should be selected, in particular for water as the working medium.

The DE 4431887 A1 discloses a heat pump system with a lightweight, large volume, high performance centrifugal compressor. A vapor leaving a second stage compressor has a saturation temperature that exceeds the ambient temperature or that of an available cooling water, thereby allowing heat to be dissipated. The compressed steam is transferred from the second stage compressor to the condenser unit which consists of a bed layer which is inside a cooling water spray device is provided on an upper side, which is supplied by a water circulation pump. The compressed water vapor rises in the condenser through the fill layer, where it comes in direct countercurrent contact with the cooling water flowing down. The vapor condenses and the latent heat of condensation absorbed by the cooling water is expelled to the atmosphere via the condensate and cooling water, which are removed together from the system. The condenser is continuously flushed with non-condensable gases by means of a vacuum pump via a pipeline.

The WO 2014072239 A1 discloses a condenser with a condensation zone for condensing steam to be condensed in a working liquid. The condensation zone is designed as a volume zone and has a lateral boundary between the upper end of the condensation zone and the lower end. The liquefier further comprises a steam introduction zone which extends along the lateral end of the condensation zone and is designed to supply steam to be condensed laterally into the condensation zone via the lateral boundary. Thus, without increasing the volume of the condenser, the actual condensation is turned into a volume condensation, because the vapor to be liquefied is not only introduced into a condensation volume or into the condensation zone from the front, but laterally and preferably from all sides. This not only ensures that the available condensation volume with the same external dimensions is increased compared to direct countercurrent condensation, but also that the efficiency of the condenser is improved at the same time, because the steam to be liquefied in the condensation zone is a flow direction transverse to the flow direction of the condensation liquid. The WO 2014/200476 A1 discloses a heat pump having the following features: a condenser with a condenser housing; a compressor motor having a rotor and a stator, the rotor having a motor shaft to which a radial wheel is attached which extends into an evaporator zone; a control space which is designed to receive vapor condensed by the radial wheel and to conduct it into the condenser; a motor housing that surrounds the compressor motor; and a steam supply for supplying steam in the motor housing to a motor gap between the stator and the rotor, the compressor motor being designed such that a further gap extends from the motor gap along the radial wheel to the control space.

A general problem with heat pumps is the fact that moving parts and especially fast moving parts have to be cooled. The compressor motor and especially the motor shaft are particularly problematic here. Especially for heat pumps in which radial wheels are used as compressors, which are operated very quickly to achieve a small design, for example in regions greater than 50,000 revolutions per minute, shaft temperatures can reach values that are problematic because they lead to the destruction of the components can.

The object of the present invention is to provide a safe concept for a heat pump.

This object is achieved by a heat pump according to claim 1 or a method for producing a heat pump according to claim 14, or a method for operating a heat pump according to claim 15.

The heat pump according to one aspect of the present invention comprises special convective shaft cooling. This heat pump has a condenser with a condenser housing, a compressor motor which is attached to the condenser housing and has a rotor and a stator, the rotor having a motor shaft to which a radial wheel is attached, which extends into an evaporator zone, and a control space , which is designed to receive vapor condensed by the radial wheel and to conduct it into the condenser. In addition, this heat pump has a motor housing which surrounds the compressor motor and is preferably designed to maintain a pressure which is at least equal to the pressure in the condenser. However, a pressure that is greater than the pressure behind the radial wheel is also sufficient. In certain versions, this pressure adjusts to a pressure which lies in the middle between the condenser pressure and the evaporator pressure. In addition, a steam supply is provided in the motor housing to supply steam in the motor housing to a motor gap between the stator and the motor shaft. Furthermore, the motor is designed such that a further gap extends from the motor gap between the stator and the motor shaft along the radial wheel to the control space.

It is thereby achieved according to the invention that there is a relatively high pressure in the motor housing, which is higher than the mean pressure from the condenser and the evaporator and preferably equal to or higher than the condenser pressure, while in the further gap which increases along the radial wheel extends the control room, a lower pressure is located. This pressure, which is equal to the mean pressure from the condenser and the evaporator, exists due to the fact that when the vapor from the evaporator is compressed, the radial wheel has a high pressure area in front of the radial wheel and a low pressure or negative pressure area behind it Radial wheel generated. In particular, the area with high pressure in front of the radial wheel is still smaller than the high pressure in the condenser and the low pressure to a certain extent "behind" the radial wheel is even smaller than the high pressure at the outlet of the radial wheel. The high pressure then only exists at the outlet of the control space condenser pressure.

This pressure drop, which is “coupled” to the motor gap, ensures that working steam is drawn from the motor housing via the steam feed along the motor gap and the further gap into the condenser. This vapor is at or above the temperature level of the condenser working fluid. However, this is particularly advantageous because it avoids all condensation problems within the motor and in particular within the motor shaft, which would support corrosion, etc.

In this aspect of the present invention, the coldest working liquid that is present in the evaporator is not used for convective wave cooling. The cold steam is also not used in the evaporator. Instead, for convective wave cooling, the steam is used to condenser or condenser temperature, which is in the heat pump. Adequate wave cooling is still achieved, due to the convective nature, i.e. that a significant and in particular adjustable amount of steam flows around the motor shaft due to the steam supply, the motor gap and the further gap. At the same time, the fact that this steam is relatively warm compared to the steam in the evaporator ensures that no condensation takes place along the motor shaft in the motor gap or the further gap. Instead, a temperature control is always created that is higher than the coldest temperature. Condensation always arises at the coldest temperature in a volume and therefore not within the engine gap and the further gap, since the warm steam flows around them.

The present invention thus leads to sufficient convective wave cooling. This prevents excessive temperatures in the motor shaft and the associated signs of wear. It also effectively prevents condensation in the motor, e.g. when the heat pump is at a standstill. This also effectively eliminates all operational safety problems and corrosion problems that would be associated with such condensation. According to the aspect of convective shaft cooling, the present invention leads to a significantly reliable heat pump.

In another aspect of the present invention, which relates to a heat pump with motor cooling, the heat pump comprises a condenser with a condenser housing, a compressor motor, which is attached to the condenser housing and has a rotor and a stator. The rotor includes a motor shaft on which a compressor wheel for compressing working fluid vapor is attached. The compressor motor also has a motor wall. The heat pump comprises a motor housing which surrounds the compressor motor and which is preferably designed to maintain a pressure which is at least equal to the pressure in the condenser and which has a working medium inlet in order to feed liquid working medium from the condenser to the motor wall for cooling the motor , However, the pressure in the motor housing can also be lower here, since the heat is removed from the motor housing by boiling or evaporation. The thermal energy on the motor wall is thus mainly removed from the motor wall by the steam, and this heated steam is then removed, such as in the condenser. Alternatively, the steam from the engine cooling can also be brought into the evaporator or to the outside. However, the conduction of the heated steam into the condenser is preferred. In contrast to water cooling, in which an engine is cooled by water flowing past, the cooling in this aspect of the invention takes place by evaporation, so that the heat energy to be removed is removed by the steam removal provided. An advantage is that less liquid is needed for cooling and the steam can simply be carried away, e.g. B. automatically in the condenser, in which the steam then condenses again and thus releases the thermal power of the motor to the condenser liquid.

The motor housing is therefore designed to form a vapor space in the operation of the heat pump, in which the working medium due to the bubble boiling or evaporation is located. The motor housing is also designed to discharge the steam from the steam space in the motor housing by a steam discharge. This discharge preferably takes place in the condenser, so that the vapor discharge is achieved by a gas-permeable connection between the condenser and the motor housing.

The motor housing is preferably further configured to maintain a maximum level of liquid working fluid in the motor housing during operation of the heat pump and to further form a vapor space above the maximum level. The motor housing is also designed to guide working fluid into the condenser above the maximum level. This design makes it possible to keep the cooling by steam generation very robust, since the level of working fluid always ensures that there is enough working fluid on the motor wall for bubble boiling. Alternatively, instead of the level of working fluid that is always held, working fluid can also be sprayed onto the motor wall. The sprayed liquid is then dosed that it evaporates when it comes into contact with the engine wall, thereby achieving the cooling capacity for the engine.

The motor is thus effectively cooled with liquid working fluid on its motor wall. However, this liquid working fluid is not the cold working fluid from the evaporator, but the warm working fluid from the condenser. However, the use of warm working fluid from the condenser creates sufficient motor cooling. At the same time, however, it is ensured that the motor is not cooled too much and, in particular, is not cooled to the extent that it is the coldest part in the condenser or on the condenser housing. This would lead to e.g. when the engine is stopped, but also during operation, condensation of working fluid vapor would take place on the outside of the engine housing, which would lead to corrosion and further problems. Instead, it is ensured that the motor is well cooled, but at the same time is always the warmest part of the heat pump, in such a way that condensation, which always takes place at the coldest "end", does not take place on the compressor motor.

The liquid working fluid in the motor housing is preferably kept at almost the same pressure as the condenser. As a result, the working fluid that cools the motor is close to its boiling limit, since this working fluid is a condenser fluid and is at a similar temperature to that in the condenser. If the motor wall is warmed up due to friction due to motor operation, the thermal energy is transferred to the liquid working fluid. Due to the fact that the liquid working fluid is close to the boiling point, a bubble boil now starts in the motor housing in the liquid working fluid that fills the motor housing up to the maximum level.

This bubble boiling enables extremely efficient cooling due to the very strong mixing of the volume of liquid working fluid in the motor housing. This cooling assisted by boiling can also be significantly supported by a preferably provided convection element, so that in the end a very efficient engine cooling with a relatively small volume or no standing volume of liquid working fluid, which also does not have to be controlled further because it is self-controlling , is achieved. Efficient engine cooling is achieved with little technical effort, which in turn contributes significantly to the operational safety of the heat pump.

Fig. 1

eine schematische Ansicht einer Wärmepumpe mit einer verschränkten Verdampfer/Kondensierer-Anordnung;

Fig. 2

eine schematische Darstellung einer Wärmepumpe mit konvektiver Wellenkühlung gemäß einem Aspekt;

Fig. 3

eine schematische Darstellung einer Wärmepumpe mit konvektiver Wellenkühlung einerseits und Motorkühlung gemäß einem weiteren Aspekt andererseits;

Fig. 4

eine Schnittdarstellung einer Wärmepumpe gemäß einem Ausführungsbeispiel mit konvektiver Wellenkühlung einerseits und Motorkühlung andererseits unter spezieller Berücksichtigung der konvektiven Wellenkühlung;

Fig. 5

eine Schnittdarstellung einer Wärmepumpe mit einem Verdampferboden und einem Kondensatorboden gemäß dem Ausführungsbeispiel von Fig. 1;

Fig. 6

eine perspektivische Darstellung eines Verflüssigers, wie er in der WO 2014072239 A1 gezeigt ist;

Fig. 7

eine Darstellung der Flüssigkeitsverteilerplatte einerseits und der Dampfeinlasszone mit Dampfeinlassspalt andererseits aus der WO 2014072239 A1 ;

Fig. 8a

eine schematische Darstellung einer bekannten Wärmepumpe zum Verdampfen von Wasser;

Fig. 8b

eine Tabelle zur Veranschaulichung von Drücken und Verdampfungstemperaturen von Wasser als Arbeitsflüssigkeit;

Fig. 9

eine schematische Darstellung einer Wärmepumpe mit Motorkühlung gemäß dem zweiten Aspekt;

Fig. 10

eine Wärmepumpe gemäß einem Ausführungsbeispiel mit einer konvektiven Wellenkühlung gemäß dem ersten Aspekt und einer Motorkühlung gemäß dem zweiten Aspekt, wobei besonderer Wert auf die Motorkühlung gelegt ist; und

Fig. 11

einen Querschnitt durch eine Motorwelle mit einem Lagerabschnitt gemäß Ausführungsbeispielen der vorliegenden Erfindung.

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

Fig. 1

a schematic view of a heat pump with an entangled evaporator / condenser arrangement;

Fig. 2

a schematic representation of a heat pump with convective shaft cooling according to one aspect;

Fig. 3

a schematic representation of a heat pump with convective shaft cooling on the one hand and engine cooling according to another aspect on the other;

Fig. 4

a sectional view of a heat pump according to an embodiment with convective shaft cooling on the one hand and engine cooling on the other with special consideration of the convective shaft cooling;

Fig. 5

a sectional view of a heat pump with an evaporator bottom and a condenser bottom according to the embodiment of Fig. 1 ;

Fig. 6

a perspective view of a condenser, as in the WO 2014072239 A1 is shown;

Fig. 7

a representation of the liquid distribution plate on the one hand and the steam inlet zone with steam inlet gap on the other hand from the WO 2014072239 A1 ;

Fig. 8a

a schematic representation of a known heat pump for evaporating water;

Fig. 8b

a table illustrating the pressures and evaporation temperatures of water as the working liquid;

Fig. 9

a schematic representation of a heat pump with engine cooling according to the second aspect;

Fig. 10

a heat pump according to an embodiment with a convective shaft cooling according to the first aspect and an engine cooling according to the second aspect, special emphasis being placed on engine cooling; and

Fig. 11

a cross section through a motor shaft with a bearing portion according to embodiments of the present invention.

Fig. 1 shows a heat pump 100 with an evaporator for evaporating working fluid in an evaporator space 102. The heat pump further comprises a condenser for liquefying evaporated working fluid in a condenser space 104, which is delimited by a condenser bottom 106. Like it in Fig. 1 is shown, which can be viewed as a sectional view or a side view, the evaporator chamber 102 is at least partially surrounded by the condenser chamber 104. Furthermore, the evaporator space 102 is separated from the condenser space 104 by the condenser bottom 106. In addition, the condenser bottom is connected to an evaporator bottom 108 to define the evaporator space 102. In one implementation, a compressor 110 is provided above the evaporator chamber 102 or elsewhere Fig. 1 is not detailed, but is principally designed to compress vaporized working fluid and to conduct it as compressed vapor 112 into the condenser chamber 104. The condenser space is further delimited on the outside by a condenser wall 114. The condenser wall 114, like the condenser bottom 106, is also fastened to the evaporator bottom 108. In particular, the dimensioning of the condenser bottom 106 in the region which forms the interface to the evaporator bottom 108 is such that the condenser bottom in the case of the Fig. 1 The embodiment shown is completely surrounded by the capacitor chamber wall 114. This means that the capacitor compartment is as it is in Fig. 1 is shown extends to the bottom of the evaporator, and that the evaporator space at the same time extends very far up, typically almost through almost the entire condenser space 104.

This "entangled" or interlocking arrangement of condenser and evaporator, which is distinguished by the fact that the condenser bottom is connected to the evaporator bottom, delivers a particularly high heat pump efficiency and therefore allows a particularly compact design of a heat pump. The dimensioning of the heat pump, for example in a cylindrical shape, is such that the condenser wall 114 represents a cylinder with a diameter between 30 and 90 cm and a height between 40 and 100 cm. The dimensioning can, however depending on the required performance class of the heat pump, but preferably takes place in the dimensions mentioned. A very compact design is thus achieved, which is also simple and inexpensive to produce, because the number of interfaces, in particular for the evaporator space which is almost under vacuum, can be easily reduced if the evaporator base is designed according to preferred exemplary embodiments of the present invention, that it includes all liquid supply and discharge lines and therefore no liquid supply and discharge 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 Fig. 1 is shown. This means that the evaporator bottom defines the lower section of the heat pump during operation, but apart from connecting lines to other heat pumps or to corresponding pump units. This means that during operation the steam generated in the evaporator chamber rises and is deflected by the engine and is fed into the condenser chamber from top to bottom, and that the condenser liquid is conducted from bottom to top and then fed into the condenser chamber from above and then flows from top to bottom in the condenser chamber, such as through individual droplets or through small liquid flows, in order to react with the compressed steam, which is preferably fed crosswise, for the purposes of condensation.

This "entangled" arrangement, in that the evaporator is arranged almost completely or even completely within the condenser, enables a very efficient design of the heat pump with optimal use of space. After the condenser space extends to the bottom of the evaporator, the condenser space is formed within the entire "height" of the heat pump or at least within a substantial portion of the heat pump. At the same time, however, the evaporator space is as large as possible because it also extends almost almost over the entire height of the heat pump. The interlocking arrangement, in contrast to an arrangement in which the evaporator is arranged below the condenser, makes optimal use of the space. On the one hand, this enables a particularly efficient operation of the heat pump and, on the other hand, a particularly space-saving and compact structure, because both the evaporator and the condenser extend over the entire height. Thus, the "thickness" of the evaporator chamber and also the condenser chamber decrease. However, it has been found that the reduction in the "thickness" of the evaporator space that tapers within the condenser is unproblematic because the main evaporation takes place in the lower area, where the evaporator space fills almost the entire volume that is available. On the other hand, the reduction in the thickness of the condenser chamber is not critical, especially in the lower region, i.e. where the evaporator chamber fills almost the entire available area, because the main condensation takes place at the top, i.e. where the evaporator chamber is already relatively thin and therefore has sufficient space for leaves the condenser space. The interlocking arrangement is thus optimal in that each functional space is given the large volume where this functional space also requires the large volume. The evaporator compartment has the large volume at the bottom, while the condenser compartment has the large volume at the top. Nevertheless, the corresponding small volume that remains for the respective functional space where the other functional space has the large volume also contributes to an increase in efficiency compared to a heat pump in which the two functional elements are arranged one above the other, as is the case, for example, in the WO 2014072239 A1 the case is.

In preferred exemplary embodiments, the compressor is arranged on the upper side of the condenser chamber in such a way that the compressed steam is deflected by the compressor on the one hand and at the same time fed into an edge gap of the condenser chamber. Condensation is thus achieved with particularly high efficiency because a cross-flow direction of the steam to a condensation liquid flowing down is achieved. This condensation with cross flow 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 nevertheless to condense vapor particles that have penetrated up to this area allow.

An evaporator bottom, which is connected to the condenser bottom, is preferably designed in such a way that it accommodates the condenser inlet and outlet and the evaporator inlet and outlet, with additional bushings for sensors in the evaporator and in the Capacitor can be present. This ensures that no conduits for the condenser inlet and outlet through the evaporator, which is almost under vacuum, are necessary. This makes the entire heat pump less prone to failure, because any passage through the evaporator would be a possibility of a leak. For this purpose, the condenser bottom is provided with a recess at the points where the condenser inlets and outlets are, to the effect that no condenser inlets / outlets run in the evaporator space, which is defined by the condenser bottom.

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 additionally has all the liquid feeds for both the evaporator and the condenser.

In certain designs, the evaporator base is designed to have connecting pieces for the individual feeds, which have a cross section that differs from a cross section of the opening on the other side of the evaporator base. The shape of the individual connecting piece is then designed such that the shape or cross-sectional shape changes over the length of the connecting piece, but the pipe diameter, which plays a role in the flow velocity, is almost the same within a tolerance of ± 10%. This prevents water flowing through the connecting piece from cavitating. Because of the good flow conditions obtained through the shaping of the connecting piece, this ensures that the corresponding pipes / lines can be made as short as possible, which in turn contributes to a compact design of the entire heat pump.

In a special implementation of the evaporator bottom, the condenser inlet is divided almost in the form of "glasses" into a two-part or multi-part stream. This makes it possible to feed the condenser liquid in the condenser at its upper section at two or more points simultaneously. This achieves a strong and at the same time particularly uniform condenser flow from top to bottom, which enables a highly efficient condensation of the steam also introduced into the condenser from above.

Another smaller-sized supply in the evaporator bottom for condenser water can also be provided in order to connect a hose that supplies cooling fluid to the compressor motor of the heat pump, whereby the cooler liquid supplied to the evaporator is not used for cooling, but the warmer liquid supplied to the condenser Liquid that is still cool enough to cool the heat pump motor in typical operating situations.

The evaporator bottom is characterized by the fact that it has a combination functionality. On the one hand, it ensures that no condenser feed lines have to be led through the evaporator, which is at very low pressure. On the other hand, it represents an interface to the outside, which preferably has a circular shape, since a circular shape leaves as much evaporator surface as possible. All supply and discharge lines lead through one evaporator floor and run from there into either the evaporator room or the condenser room. In particular, manufacturing the evaporator base from plastic injection molding is particularly advantageous because the advantageous, relatively complicated shapes of the inlet / outlet connections can be carried out easily and inexpensively in plastic injection molding. On the other hand, due to the design of the evaporator bottom as an easily accessible workpiece, it is readily possible to produce the evaporator bottom with sufficient structural stability so that it can easily withstand the low evaporator pressure in particular.

In the present application, the same reference numerals relate to the same elements or elements having the same effect, although not all reference numerals in all the drawings, if they are repeated, are repeated.

Fig. 2 shows a heat pump according to an embodiment in connection with the first aspect, the convective shaft cooling. The heat pump from Fig. 2 a condenser with a condenser housing 114 that includes a condenser space 104. Furthermore, the compressor motor is attached, which is shown schematically in FIG Fig. 4 is shown. This compressor motor is on in Fig. 2 not shown is attached to the condenser housing 114 and includes the stator and a rotor 307, the rotor 307 having a motor shaft 306 to which is attached a radial wheel 304 that extends into an evaporator zone that is shown in FIG Fig. 2 is not shown. The heat pump further includes a control space 302 that is configured to receive steam compressed by the radial wheel and to conduct it into the condenser, as is shown schematically at 112.

The motor further includes a motor housing 300 that surrounds the compressor motor and is preferably configured to maintain a pressure that is at least equal to the pressure in the condenser. Alternatively, the motor housing is configured to hold a pressure that is higher than an average pressure from the evaporator and the condenser, or that is higher than the pressure in the further gap 313 between the radial wheel and the control space (302), or that is greater than or equal to the pressure in the condenser. The Motor housing is thus designed such that a pressure drop from the motor housing along the motor shaft in the direction of the control space takes place, through which working steam is drawn through the motor gap and the further gap past the motor shaft in order to cool the shaft.

This area in the motor housing with the necessary pressure is in Fig. 2 represented at 312. In addition, a steam supply 310 is formed to supply steam in the motor housing 300 to a motor gap 311 that is present between the stator 308 and the shaft 306. The motor further comprises a further gap 313, which extends from the motor gap 311 along the radial wheel to the control space 302.

In the arrangement according to the invention, there is a relatively high pressure p ₃ in the condenser. In contrast, there is an average pressure p ₂ in the route or control room 302. The lowest pressure, apart from the evaporator, prevails behind the radial wheel, specifically where the radial wheel is attached to the motor shaft, that is to say 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 . This creates a pressure drop from the motor housing to the end of the further gap. This pressure drop means that a steam flow takes place through the steam feed into the motor gap and the further gap up to the route 302. This steam flow takes working steam from the motor housing past the motor shaft into the condenser. This steam flow ensures the convective shaft cooling of the motor shaft through the motor gap 311 and the further gap 313, which adjoins the motor gap 311. The radial wheel sucks steam downwards, past the shaft of the motor. This steam is drawn into the engine gap via the steam supply, which is typically implemented as special bores.

Fig. 3 shows a further schematic embodiment of the convective shaft cooling according to the first aspect of the present invention, which is preferably combined there with the motor cooling according to the second aspect of the present invention.

At this point, however, it should be generally pointed out that the two aspects of convective shaft cooling on the one hand and motor cooling on the other are also used separately from one another. For example, engine cooling without a special separate convective shaft cooling already leads to considerably increased operational reliability. In addition, convective motor shaft cooling without the additional motor cooling leads to increased operational reliability of the heat pump. However, the two aspects can, as described below in Fig. 3 is shown, are 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 or additionally be supplemented in a further preferred exemplary embodiment in each case or together by a special ball bearing cooling.

Fig. 3 shows an embodiment with combined use of convective shaft cooling and engine cooling, wherein in the Fig. 3 Embodiment shown, the evaporator zone is shown at 102. The evaporator zone is separated from the condenser zone, that is to say from the condenser region 104, by the condenser bottom 106. Working steam, shown schematically at 314, is drawn in by the rotating radial wheel 304, shown schematically and in section, and "pressed" into the route 302. The route 302 is in the in Fig. 3 shown embodiment formed so that its cross section increases outwards. A further vapor compression takes place with this. The first "stage" of steam compression takes place through the rotation of the radial wheel and the "suction" of the steam through the radial wheel. However, when the radial wheel feeds the steam into the entrance of the route, ie where the radial wheel "stops" when viewed upwards, the pre-compressed steam encounters a kind of steam build-up, which is due to the tapering of the route and also due to the curvature of the Routing exists. This leads to a further vapor compression, so that finally the compressed and thus heated vapor 112 flows into the condenser.

Fig. 3 FIG. 10 also shows the steam supply openings 320 that are shown in a schematically illustrated engine wall 309 in FIG Fig. 3 are executed. This motor wall 309 has the in Fig. 3 Embodiment shown holes for the steam supply openings 320 in the upper region, but these holes can be made at any point where steam can penetrate into the motor gap 311 and thus also into the further motor gap 313. The steam flow 310 caused thereby leads to the desired effect of convective wave cooling.

This in Fig. 3 The exemplary embodiment shown furthermore includes, for implementing the motor cooling, a working medium inlet 330 which is designed to guide liquid working medium from the condenser for motor cooling to the motor wall. Furthermore, the motor housing formed to maintain a maximum liquid level 322 of liquid working fluid in the operation of the heat pump. In addition, the motor housing 300 is also designed to form a vapor space 323 above the maximum level. In addition, the motor housing has arrangements for introducing liquid working fluid into the condenser 104 above the maximum level. This version is used in the Fig. 3 embodiment shown by a z. B. formed flat channel-shaped overflow 324, which forms 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 supply 330, the liquid working medium runs through the overflow 324 into the condenser volume. In addition, the overflow at the in Fig. 3 shown passive arrangement, which can also alternatively be a tube with a corresponding length, for example, a pressure equalization between the motor housing and in particular the vapor space 323 of the motor housing and the condenser interior 104. Thus the pressure in the vapor space 323 of the motor housing is 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 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 a power loss generated in the motor leads to bubble boiling in the liquid volume 328, which will be explained later.

Fig. 3 also shows various seals in schematic form at reference numeral 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, which, however, represents almost the same pressure area as the condenser. Due to the heating of the motor and the energy thus released on the motor wall 309, this supports a bubble 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. It is also ensured that cooling is carried out with the working fluid which is at the most favorable temperature, namely the warmest temperature in the heat pump. This ensures that all condensation problems, that always occur on cold surfaces, for the motor wall as well as for the motor shaft and the areas in the motor gap 311 and the further gap 313 are excluded. Furthermore, in Fig. 3 Embodiment shown, the working fluid vapor 310 used for the convective wave cooling, which is otherwise in the vapor space 323 of the motor housing. This vapor, like liquid 328, is at the optimal (warm) temperature. Furthermore, it is ensured by the overflow 324 that the pressure in the area 323 cannot rise above the condenser pressure due to the bubble boiling caused by the engine cooling or the engine wall 309. Furthermore, the heat is dissipated due to the engine cooling through the steam discharge. This means that convective shaft cooling will always work in the same way. If the pressure rose too much, too much working fluid vapor could be forced through the motor gap 311 and the further gap 313.

The holes 320 for the steam supply will typically be formed in an array that can be arranged regularly or irregularly. The individual bores are not larger than 5 mm in diameter and can be about a minimum size of 1 mm.

Fig. 6 shows a condenser, the condenser in Fig. 6 a steam introduction zone 102 that extends completely around the condensation zone 100. In particular, in Fig. 6 shown a part of a condenser having a condenser bottom 200. A condenser housing section 202 is arranged on the condenser bottom Fig. 6 is drawn transparently, which, however, does not necessarily have to be transparent in nature, but can be formed, for example, from plastic, die-cast aluminum or something similar. The side housing part 202 rests on a sealing rubber 201 in order to achieve a good seal with the bottom 200. Furthermore, the condenser comprises a liquid outlet 203 and a liquid inlet 204 as well as a vapor supply 205 arranged centrally in the condenser, which flows from bottom to top Fig. 6 rejuvenated. It should be noted that Fig. 6 represents the actually desired installation direction of a heat pump and a condenser of this heat pump, with in this installation direction in Fig. 6 the evaporator of a heat pump is arranged below the condenser. The condensation zone 100 is delimited on the outside by a basket-like delimitation object 207, which, like the outer housing part 202, is drawn transparently and is normally configured like a basket.

Furthermore, a grating 209 is arranged, which is formed around packing elements which are in Fig. 6 not shown to wear. Like it out Fig. 6 can be seen from, the basket 207 only extends down to a certain point. The basket 207 is provided permeable to steam in order to hold packing elements, such as so-called pall rings. These packing elements are introduced into the condensation zone, specifically only inside the basket 207, but not in the steam introduction zone 102. However, the packing elements are also filled so high outside the basket 207 that the height of the packing elements either reaches the lower limit of the basket 207 or slightly above.

The liquefier from Fig. 6 includes a working liquid feeder, which is in particular by the working liquid supply 204, which, as in Fig. 6 is shown wound around the steam supply in the form of an ascending turn, is formed by a liquid transport area 210 and by a liquid distributor element 212, which is preferably designed as a perforated plate. In particular, the working fluid feeder is thus designed to feed the working fluid into the condensation zone.

In addition, a steam feeder is provided, which, as in Fig. 6 is shown, preferably composed of the funnel-shaped tapering supply area 205 and the upper steam guide area 213. A wheel of a radial compressor is preferably used in the steam line area 213 and the radial compression leads to the fact that steam is sucked in from the bottom upwards through the feed 205 and is then already deflected outward to a certain extent 90 degrees due to the radial compression by the radial wheel, that is to say from a flow from the bottom up to a flow from the center outwards in Fig. 6 regarding element 213.

In Fig. 6 another deflector is not shown, which deflects the steam which has already been deflected outwards again by 90 degrees, in order then to guide it from above into the gap 215, which to a certain extent represents the beginning of the steam introduction zone which extends laterally around the condensation zone. The steam feeder is therefore preferably of an annular design and is provided with an annular gap for supplying the steam to be condensed, the working fluid supply being formed within the annular gap.

For illustration purposes, click on Fig. 7 directed. Fig. 7 shows a view of the "lid portion" of the condenser of FIG Fig. 6 from underneath. In particular, the perforated plate 212 is from shown schematically below, which acts as a liquid distributor element. The steam inlet gap 215 is drawn schematically and it follows from Fig. 7 that the steam inlet gap is only ring-shaped, such that no steam to be condensed is fed into the condensation zone directly from above or directly from below, but only around the side. Thus, only liquid, but no steam, flows through the holes in the distributor plate 212. The vapor is only "sucked in" laterally into the condensation zone, specifically because of the liquid that has passed through the perforated plate 212. The liquid distributor plate can be made of metal, plastic or a similar material and can be designed with different hole patterns. Furthermore, as it is in Fig. 6 is shown, preferably to provide a lateral boundary for liquid flowing out of the element 210, this lateral boundary being designated by 217. This ensures that liquid, which already exits the element 210 with a swirl due to the curved feed 204 and is distributed from the inside to the outside of the liquid distributor, does not spray over the edge into the steam introduction zone, unless the liquid has already passed through the Holes in the liquid distribution plate are dripped and condensed with steam.

Fig. 5 shows a complete heat pump in a sectional view, which includes both the evaporator bottom 108 and the condenser bottom 106. Like it in Fig. 5 or also in Fig. 1 is shown, the condenser bottom 106 has a tapering cross section from an inlet for the working fluid to be evaporated to a suction opening 115, which is coupled to the compressor or motor 110, where the preferably used radial wheel of the motor sucks off the steam generated in the evaporator chamber 102 ,

Fig. 5 shows a cross section through the entire heat pump. In particular, a droplet separator 404 is arranged inside the condenser bottom. This droplet separator comprises individual blades 405. These blades are introduced into corresponding grooves 406 in order that the droplet separator remains in place Fig. 5 are shown. These grooves are arranged in the condenser bottom in a region which is directed towards the evaporator bottom, in the inside of the evaporator bottom. In addition, the condenser bottom also has various guiding features, which can be designed as rods or tongues, in order to hold hoses, which are provided for condenser water guidance, for example, which are therefore plugged onto corresponding sections and couple the feed points of the condenser water supply. This condenser water supply 402 can, depending on the implementation be trained as in the Fig. 6 and 7 is shown at reference numerals 102, 207 to 250. Furthermore, the condenser preferably has a condenser liquid distribution arrangement which has two or more feed points. A first feed point is therefore connected to a first section of a condenser inlet. A second feed point is connected to a second section of the condenser inlet. If there are more feed points for the condenser liquid distribution device, the condenser inlet will be divided into further sections.

The top of the heat pump from Fig. 5 can thus be just like the upper area in Fig. 6 be designed to the effect that the condenser water supply via the perforated plate from Fig. 6 and Fig. 7 takes place, so that downward flowing condenser water 408 is obtained, into which the working steam 112 is preferably introduced laterally, so that the cross-flow condensation, which allows a particularly high efficiency, can be obtained. As it is in Fig. 6 is shown, the condensation zone can be provided with only an optional filling, in which the edge 207, which is also designated 409, remains free of packing elements or similar things, in that the working steam 112 not only at the top but also at the bottom can laterally penetrate into the condensation zone. The imaginary boundary line 410 is said to be in Fig. 5 illustrate. At the in Fig. 5 In the exemplary embodiment shown, however, the entire region of the condenser is designed with its own condenser base 200, which is arranged above an evaporator base.

Fig. 4 shows a preferred embodiment of a heat pump and in particular a heat pump section, the "upper" area of the heat pump, as shown for example in Fig. 5 is shown. In particular, the motor corresponds to M 110 from Fig. 5 the area surrounded by a motor wall 309, which is shown in the cross-sectional view in Fig. 4 is preferably formed on the outside in the liquid region 328 with cooling fins in order to enlarge the surface of the motor wall 309. Furthermore, the area of the motor housing 300 corresponds to Fig. 4 the corresponding area 300 in Fig. 5 , In Fig. 4 radial wheel 304 is also shown in a more detailed cross section. The radial wheel 304 is attached to the motor shaft 306 in a fastening area which is fork-shaped in cross section. The motor shaft 306 has a rotor 307, which is opposite the stator 308. The rotor 307 schematically includes FIG Fig. 4 permanent magnets shown. In particular, steam path 310 is set out through engine gap 311. The motor gap 311 extends between and opens into the rotor and the stator Another gap 313, which runs along the fastening area of the shaft 306, which is fork-shaped in cross section, to the control space 302, as is also shown at 346.

In addition, in Fig. 4 an emergency camp 344 is shown, which does not support the shaft in normal operation. Instead, the shaft is supported by the bearing section shown at 343. The emergency bearing 344 is only available to support the shaft and thus the radial wheel in the event of damage, so that the rapidly rotating radial wheel cannot cause any greater damage in the heat pump in the event of damage. Fig. 4 also shows various fasteners, such as screws, nuts, etc. and various seals in the form of various O-rings. It also shows Fig. 4 an additional convection element 342, to which reference will be made later Fig. 10 is received.

Fig. 4 also shows a splash guard 360 in the vapor space above the maximum volume in the motor housing, which is normally filled with liquid working fluid. This splash guard is designed to intercept drops of liquid thrown into the vapor space during bubble boiling. Preferably, steam path 310 is as schematically shown in FIG Fig. 4 is indicated in such a way that it benefits from the splash guard 360, that is, because of the flow into the engine gap and the further gap, only working fluid vapor, but not liquid drops due to the boiling in the engine housing, are sucked in.

The heat pump with convective shaft cooling preferably has a steam supply which is designed in such a way that steam flow through the motor gap and the further gap does not pass through a bearing section which is designed to support the motor shaft with respect to the stator. This is in Fig. 4 indicated. The bearing section 343, which in the present case comprises two ball bearings, is sealed from the motor gap, namely, for. B. by O-rings 351. Thus, the working steam can only, as it through the path 310 in Fig. 4 is shown, enter through the steam supply into an area within the motor wall 309, run downward from there in a free space and pass along the rotor 307 through the motor gap 311 into the further gap 313. The advantage of this is that steam does not flow around the ball bearings, so that bearing lubrication remains in the sealed ball bearings and is not pulled through the motor gap. It also ensures that the ball bearing is not moistened, but always remains in the defined state during installation. In a further exemplary embodiment, the motor housing is as shown in Fig. 4 is shown mounted in the operating position of the heat pump on top of the condenser housing 114 so that the stator is above the radial wheel and the steam flow 310 runs through the motor gap and the further gap from top to bottom.

The heat pump further includes the bearing section 343, which is designed to support the motor shaft with respect to the stator. Furthermore, the bearing section is arranged such that the rotor 307 and the stator 308 are arranged between the bearing section and the radial wheel 304. This has the advantage that the bearing section 343 can be arranged in the steam area within the motor housing and the rotor / stator, where the greatest power loss occurs, below the maximum liquid level 322 ( Fig. 3 ) can be arranged. This creates an optimal arrangement by which each area is in the medium that is best for the area to achieve the purposes, namely motor cooling on the one hand and convective shaft cooling on the other hand and possibly ball bearing cooling, to which reference is still made Fig. 10 is received.

The motor housing also includes the working medium inlet 330 in order to guide liquid working medium from the condenser for cooling the motor to a wall of the compressor motor. Fig. 10 FIG. 12 shows a specific implementation of this work fluid inlet 362, that of inlet 330 of FIG Fig. 3 equivalent. This working fluid inlet 362 runs into a closed volume 364, which represents ball bearing cooling. A derivative emerges from the ball bearing cooling that includes a tube 366 that does not place the working fluid on top of the volume of the working fluid 328, as in FIG Fig. 3 shown, leads, but that the working medium leads down to the wall of the motor, i.e. the element 309. In particular, the tube 366 is designed to be arranged within the convection element 342, which is arranged around the motor wall 309, and at a certain distance, so that a volume increases inside the convection element 342 and outside the convection element 342 within the motor housing 300 liquid working fluid exists.

A bubble boiling due to the working fluid, which is in contact with the motor wall 309, in particular in the lower region, where the fresh working fluid inlet 366 ends, creates a convection zone 367 within the volume of working fluid 328. In particular, the boiling bubbles are torn from the bottom upwards by the bubble boiling , This leads to an ongoing "stirring" in that hot working fluid is brought from the bottom up. The energy due to the bubble boiling then passes into the vapor bubble, which then ends up in the vapor volume 323 above the liquid volume 328. The pressure generated there is brought directly into the condenser through the overflow 324, the overflow continuation 340 and the outlet 342. This means that there is constant heat removal from the motor into the condenser, which is mainly due to the discharge of steam and not due to the discharge of heated liquid.

This means that the heat, which is actually the engine's waste heat, preferably gets exactly where it should go through the steam discharge, namely into the condenser water to be heated. This keeps the entire engine heat in the system, which is particularly favorable for heating applications of the heat pump. However, heat dissipation from the motor to the condenser is also favorable for cooling applications of the heat pump, because the condenser typically has an efficient heat dissipation, e.g. in the form of a heat exchanger or a direct heat dissipation in the area to be heated. It is therefore not necessary to create a separate engine waste heat device, but the heat dissipation from the condenser to the outside, which already exists from the heat pump, is "used" to a certain extent by the engine cooling.

The motor housing is also designed to maintain the maximum level of liquid working fluid during operation of the heat pump and to create the vapor space 323 above the level of liquid working fluid. The steam feed is also designed such that it communicates with the steam space, so that the steam in the steam space for convective wave cooling through the motor gap and the further gap in Fig. 4 is directed.

At the in Fig. 10 and Fig. 4 shown heat pump, the drain is arranged as an overflow in the motor housing to guide liquid working fluid above the level in the condenser and to further create a steam path between the steam space and the condenser. The drain 324 is preferably both, namely both overflow and steam path. These functionalities can, however, be implemented by using an alternative design of the overflow on the one hand and a steam room on the other hand using different elements.

The heat pump includes the in Fig. 10 Embodiment shown a special ball bearing cooling, which is formed in particular that the sealed volume 364 is formed with liquid working fluid around the bearing portion 343. The inlet 362 enters this volume and the volume has an outlet 366 from the ball bearing cooling into the working fluid volume for engine cooling. This creates a separate ball bearing cooling, which, however, runs around the outside of the ball bearing and not within the bearing, so that cooling through this ball bearing is efficient, but does not impair the lubricating filling of the bearing.

As further stated in Fig. 10 is shown, the working fluid inlet 362 in particular comprises the line section 366, which extends almost to the bottom of the motor housing 300 or to the bottom of the liquid working fluid 328 in the motor housing or at least to a region below the maximum level, in particular to liquid working fluid out of the ball bearing cooling and the liquid working fluid to the motor wall.

Fig. 10 and Fig. 4 also show the convection element which is spaced from the wall of the compressor motor 309 in the liquid working fluid and which is more permeable to the liquid working fluid in a lower region than in an upper region. In particular, in Fig. 10 In the embodiment shown, the upper area is not permeable and the lower area is relatively permeable, and the convection element is designed in the form of a "crown", which is placed in the liquid volume in reverse. The convection zone 367 can thus be formed as shown in FIG Fig. 10 is shown. However, alternative convection elements 342 can be used which are in some way less permeable at the top than at the bottom. For example, a convection element could be used which has holes at the bottom which have a larger passage cross section in terms of shape or number than holes in the upper region. Alternative elements for generating the convection flow 367 as shown in Fig. 10 are also usable.

The emergency bearing 344, which is designed to protect the motor shaft 306 between the rotor 370 and the radial wheel 304, is provided for securing the motor in the event of a bearing problem. In particular, the further gap 313 extends through a bearing gap of the emergency camp or preferably through holes deliberately made in the emergency camp. In one implementation, the emergency camp is provided with a large number of holes, so that the emergency camp itself represents the lowest possible flow resistance for the steam flow 10 for the purposes of convective wave cooling.

Fig. 11 shows a schematic cross section through a motor shaft 306, as can be used for preferred embodiments. Motor shaft 306 includes a hatched core as shown in FIG Fig. 11 is shown, which is supported in its upper section, which represents the bearing section 343, preferably by two ball bearings 398 and 399. Further down on the shaft 306, the rotor is formed with permanent magnets 307. These permanent magnets are placed on the motor shaft 306 and are held 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 means that the permanent magnets remain securely on the shaft 306 and cannot separate from the shaft due to the very strong centrifugal forces due to the high speed of the shaft.

The shaft is preferably made of aluminum and has a fastening section 395 which is fork-shaped in cross section and which forms a holder for the radial wheel 304 if the radial wheel 304 and the motor shaft are not formed in one piece but with two elements. If the radial wheel 304 is formed in one piece with the motor shaft 306, then the wheel mounting section 395 is not present, but then the radial wheel 304 directly connects to the motor shaft. In the area of the wheel holder 395 there is also how it looks Fig. 10 can be seen, the emergency camp 344, which is preferably also made of metal and in particular aluminum.

In the following, specific preferred exemplary embodiments of the second aspect with regard to engine cooling are described with reference to FIG Fig. 10 shown. In particular, the motor housing 300, which is also shown in FIG Fig. 3 is shown, designed to obtain a pressure that is at most 20% greater than the pressure in the condenser housing in an operation of the heat pump. Furthermore, the motor housing 300 can be designed to maintain a pressure which is so low that when the motor wall 309 is heated by the operation of the motor, a bubble boiling takes place in the liquid working fluid 328 and in the motor housing 300.

Furthermore, the bearing section 343 is preferably arranged above the maximum liquid level, so that even if there is a leak in the motor wall 309, no liquid Work equipment can come into the storage section. In contrast, the area of the motor, which at least partially includes the rotor and the stator, is below the maximum level, since typically the greatest power loss occurs in the bearing area on the one hand, but also between the rotor and stator on the other hand, which can be optimally transported away by the convective bubble boiling ,

As it is particularly in Fig. 4 As shown, the overflow 324 is configured to have a first tube portion that protrudes into the motor housing, that it also has a second conduit portion 340 that extends from a curve portion 317 to a drain 342 that is further out of range is arranged in which the control space 302 introduces compressed working steam compressed by the compressor wheel 304 into the condenser.

Fig. 9 also shows a schematic representation of the heat pump for engine cooling. In particular, the working material flow 324 is alternatively to Fig. 4 or Fig. 20. The sequence does not necessarily have to be a passive sequence, but can also be an active sequence, which is controlled, for example, by a pump or another element and, depending on a level detection of level 322, sucks some working fluid out of the motor housing 300. Alternatively, instead of the tubular outlet 324, there could be a reclosable opening at the bottom of the motor housing 300 in order to allow a controlled amount of working fluid to drain from the motor housing into the condenser by briefly opening the reclosable opening.

Fig. 9 also shows the area to be heated or a heat exchanger 391, from which a condenser inlet 204 runs into the condenser and from which a condenser outlet 203 emerges. A pump 392 is also provided to drive the circuit of condenser inlet 204 and condenser outlet 203. This pump 392 preferably has a branch to the inlet 362, as is shown schematically. This means that no separate pump is required, but the pump for the condenser drain, which is present anyway, also drives a small part of the condenser drain into the feed line 362 and thus into the liquid volume 328.

It also shows Fig. 9 a general representation of the condenser 114, the compressor motor with motor wall 309 and the motor housing 300, as also shown in FIG Fig. 3 has been described.

Claims (15)

1. Heat pump comprising:

   a condenser with a condenser housing (114);

   an evaporator with an evaporator zone (102);

   a compressor with a compressor engine that is mounted to the condenser housing (114) and comprises a rotor (307) and a stator (308), the rotor comprising an engine shaft (306) to which a radial wheel (304) is mounted, extending into the evaporator zone (102);

   a routing area (302) configured to receive vapor compressed by the radial wheel (304) and to route the same into the condenser (114);

   an engine housing (300) surrounding the compressor engine; and

   a vapor supply (320) for supplying vapor (310) in the engine housing (300) to an engine gap (311) between the stator and the rotor (307),

   wherein the compressor engine is configured such that a further gap (313) extends from the engine gap (311) along the radial wheel (304) to the routing area (302), such that the vapor (310) is drawn into the condenser along the engine gap (311) and the further gap (313) from the engine housing (300) via the vapor supply (320).
2. Heat pump according to claim 1,
   wherein the vapor supply (320) is configured such that a vapor flow (10) through the engine gap (311) and the further gap (313) does not pass through a support portion (333) configured to support the engine shaft (306) with respect to the stator (308).
3. Heat pump according to claim 1 or 2, wherein the engine housing (300) is arranged on top of the condenser housing (114) in operating direction of the heat pump, such that the stator (308) is above the radial wheel (304) and the vapor flow (310) passes through the engine gap (311) and the further gap (313) from top to bottom.
4. Heat pump according to one of the preceding claims comprising a support portion (343) configured to support the engine shaft (306) with respect to the stator (308), wherein the support portion is arranged such that the rotor (307) and the stator (308) of the compressor engine are arranged between the support portion and the radial wheel.
5. Heat pump according to one of the preceding claims,
   wherein the engine housing (300) comprises a working medium feed (330, 362) to supply liquid working medium from the condenser to a wall (309) of the compressor engine for engine cooling, and wherein the engine housing (300) further comprises a vapor exhaust (324) to discharge vapor out of the vapor area (323) in the engine housing.
6. Heat pump according to claim 5,
   wherein the engine housing (300) is further configured to maintain a level (322) of liquid working medium during operation of the heat pump and to provide a vapor area (323) above the level of liquid working medium, wherein the vapor supply (320) is configured to communicate with the vapor area (323).
7. Heat pump according to claim 6,
   wherein an overflow (324) is arranged in the engine housing (300) to route liquid working medium above the level (322) into the condenser (114) and to provide, as vapor exhaust (324), a vapor path between the vapor area (323) and the condenser (114).
8. Heat pump according to one of claims 5 to 7,
   comprising a support portion configured to support the engine shaft with respect to the stator, wherein the support portion is arranged such that the rotor and the stator of the compressor engine are arranged between the support portion and the radial wheel, wherein a volume (364) sealed from the support portion (343) is configured and wherein the working medium feed (362) is configured to route the liquid working medium into the sealed volume (364) for support cooling.
9. Heat pump according to claim 8, wherein the working medium feed (362) is further configured to guide liquid working medium out of the sealed volume (366) to the wall (309) of the compressor engine.
10. Heat pump according to one of the preceding claims,
    wherein the engine housing is configured to hold a level (323) of liquid working medium during operation of the heat pump, such that the liquid working medium at least partly surrounds a wall of the compressor engine, wherein the wall of the compressor engine is configured around the stator, wherein the engine housing (300) is further configured to have an internal pressure equal to or greater than a pressure in the condenser (114), such that when heating the wall of the compressor engine, bulk boiling (367) takes place in the liquid working medium (328) due to engine power loss.
11. Heat pump according to one of claims 6 to 10, further comprising a convection element (342) that is arranged spaced apart from the wall (309) of the compressor engine in the liquid working medium (328) and that is more permeable for the liquid operating medium in a lower area than in an upper area.
12. Heat pump according to claim 11, wherein the convection element (342) is crown-shaped, wherein an area of the convection element defines the bottom area with crown prongs and the upper area of the convection element (342) is impermeable for the liquid working medium.
13. Heat pump according to one of the preceding claims, wherein an emergency support (344) for securing the engine shaft (306) is arranged between the rotor (307) and the radial wheel (304), wherein the further gap extends through bores in the emergency support (344) or through a support gap of the emergency support.
14. Method for producing a heat pump, comprising: a condenser with a condenser housing (114); an evaporator with an evaporator zone (102); a compressor with a compressor engine that is mounted to the condenser housing (114) and comprises a rotor (307) and a stator (308), the rotor comprising an engine shaft (306) to which a radial wheel (304) is mounted, extending into the evaporator zone (102); a routing area (302) configured to receive vapor compressed by the radial wheel (304) and to route the same into the condenser (114); an engine housing (300) surrounding the compressor engine, and a vapor supply (320) for supplying vapor (310) in the engine housing (300) to an engine gap (311) between the stator and the rotor (307), the method comprising:
    forming the compressor engine such that a further gap (313) extends from the engine gap (311) along the radial wheel (304) to the routing area (302), such that the vapor (310) is drawn into the condenser along the engine gap (311) and the further gap (313) from the engine housing (300) via the vapor supply (320).
15. Method for operating a heat pump, comprising: a condenser with a condenser housing (114); an evaporator with an evaporator zone (102); a compressor with a compressor engine that is mounted to the condenser housing (114) and comprises a rotor (307) and a stator (308), the rotor comprising an engine shaft (306) to which a radial wheel (304) is mounted, extending into the evaporator zone (102); a routing area (302) configured to receive vapor compressed by the radial wheel (304) and to route the same into the condenser (114); an engine housing (300) surrounding the compressor engine; an engine gap (311) between the stator and the rotor (307), wherein the compressor engine is configured such that a further gap (313) extends from the engine gap (311) along the radial wheel (304) to the routing area (302); the method comprising:
    supplying vapor (310) in the engine housing (300) through a vapor supply (320) in the engine gap (311) and the further gap (313) to the radial wheel (304) and into the routing area (302), wherein the vapor (310) is drawn into the condenser along the engine gap (311) and the further gap (313) from the engine housing (300) via the vapor supply (320).

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