DE102022213576A1 - HEAT PUMP WITH MULTI-STAGE COMPRESSOR AND SPIRAL CASINGS - Google Patents

Abstract

A heat pump (100) is described with the following features: an evaporator (10) for evaporating working fluid to obtain a working vapor; a compressor (20) for compressing the working vapor to obtain a compressed working vapor; and a condenser (30) for condensing the compressed working steam, wherein the compressor (20) has a first compressor stage (70-1) and a second compressor stage (70-2), wherein the first compressor stage (70-1) has a first spiral housing (78-1), a first drive motor (80-1) and a first drive shaft (86-1), wherein the second compressor stage (70-2) has a second spiral housing (78-2), a second drive motor (80-2) and a second drive shaft (86-2), wherein the first drive shaft (86-1) is separate from the second drive shaft (86-2), and wherein the first drive shaft (86-1) is designed to be upright in an operating direction of the heat pump (100). Furthermore, a method for producing such a heat pump (100) and a method for operating such a heat pump (100) are described.

Description

The present invention relates to a heat pump with a multi-stage compressor and spiral casings, a method for producing such a heat pump and a method for operating such a heat pump.

In the publication ( Tadayoshi et al.: Centrifugal turbo chiller using water ras refrigerant and lubricant, The 11th International Conference on Compressors and their System, Journal of Process Mechanical Engineering, published on July 1, 2020, DOI: 10.1177/0954408920938197 ) is a water-cooled heat pump system 7' (see 27 ) with a steam turbo compressor, in which the compressor and the spiral casing are directly connected to the evaporator and compressor vessels. The water refrigerant heat pump system has vertical spiral casings with a horizontal shaft, with the spiral casings being arranged above the evaporator and the condenser. Both impellers are arranged on a drive shaft 5' and therefore cannot be controlled separately. The evaporator and the condenser are arranged next to each other. The intercooler is located above the evaporator. 28 shows - as described in the publication - a spraying of the water vapor through nozzles. The water coolant heat pump system is elaborately manufactured with steam nozzles and several chambers (chamber 1', chamber 2`, chamber 3`) of the intercooler, whereby no separation of the intercooler from its collecting tank 4' is provided.

Since both impellers are arranged on a horizontal drive shaft, the impellers cannot be controlled separately. The system can therefore only be operated in two stages. Single-stage operation without the second impeller is not possible. In addition, the water-cooled heat pump system has a relatively large installation height due to the spiral housings located above the evaporator and condenser. Because the evaporator and condenser are arranged next to each other, the water-cooled heat pump system also has a relatively large installation width. Overall, the installation space is poorly utilized.

The WO 2013 085 969 A1 discloses a refrigeration machine which uses a centrifugal compressor whose impellers are mounted on a shaft which in turn is rotatably mounted using rolling bearings. 29 shows the refrigeration machine, which is a centrifugal refrigeration machine, and its basic components are shown. The refrigeration machine 10' consists of a compressor section 12', a condenser 14' and an evaporator 16'. The refrigerant gas is compressed in the compressor section 12'. This refrigerant gas is led from the outlet coil 18' into the pipe 20', which connects the compressor to the condenser 14'. The refrigeration machine of the WO 2013 085 969 A1 has a vertical spiral casing and consequently a horizontal shaft, whereby the spiral casing is arranged above the evaporator and the condenser. Both impellers are located on a drive shaft. The impellers cannot therefore be controlled separately. Furthermore, the impeller is arranged vertically.

Since both impellers are on a horizontal drive shaft, the impellers cannot be controlled separately. The system can therefore only be operated in two stages. Single-stage operation without the second impeller is not possible. In addition, there is no intermediate cooling. In addition, the refrigeration machine from the publication has a relatively high installation height due to the vertical spiral casing compressor.

The object of the present invention is to provide an improved heat pump concept.

This object is achieved by a heat pump according to claim 1, a method for producing a heat pump according to claim 25 or a method for operating a heat pump according to claim 26.

A core idea of the present invention is to arrange individual components of the heat pump in such a way that the components are arranged closer together in a smaller installation space and at the same time to provide a separate shaft for each drive motor so that each impeller can be specifically controlled by the associated drive motor. This allows the heat pump to work more efficiently in a smaller installation space.

According to the proposal, the heat pump comprises an evaporator for evaporating working fluid to obtain a working vapor; a compressor for compressing the working vapor to obtain a compressed working vapor; and a condenser for condensing the compressed working vapor, wherein the compressor has a first compressor stage and a second compressor stage. The first compressor stage has a first spiral housing, a first drive motor and a first drive shaft. The second compressor stage has a second spiral housing, a second drive motor and a second drive shaft. According to the proposal, the first drive shaft is separate from the second drive shaft, and wherein the first drive shaft is in a Operating direction of the heat pump is designed to be upright. In particular, the second drive shaft is designed to be horizontal or upright in an operating direction of the heat pump. Preferably, "upright" means a vertical direction to a base area of the heat pump, while "lying" means a horizontal direction to the base area of the heat pump. According to the proposal, each drive motor of the heat pump has its own drive shaft, so that each drive motor can be controlled independently of the other drive motor. Because the drive shafts are designed to be horizontal or upright, the individual components of the heat pump can be arranged closer to one another, i.e. in less space, whereby the heat pump as such takes up less volume, i.e. becomes smaller.

A further aspect of the present invention relates to a method for operating the heat pump just described and a method for manufacturing the heat pump just described.

The method for producing a heat pump with an evaporator for evaporating working fluid to obtain a working vapor; a compressor for compressing the working vapor to obtain a compressed working vapor; and a condenser for condensing the compressed working vapor, wherein the compressor has a first compressor stage and a second compressor stage, wherein the first compressor stage has a first spiral housing, a first drive motor and a first drive shaft, wherein the second compressor stage has a second spiral housing, a second drive motor and a second drive shaft, comprises the following steps: arranging the drive shafts so that the first drive shaft is separate from the second drive shaft, and forming the first drive shaft in a vertical direction in an operating direction of the heat pump.

The method for operating a heat pump with an evaporator for evaporating working fluid to obtain a working vapor; a compressor for compressing the working vapor to obtain a compressed working vapor; and a condenser for condensing the compressed working vapor, wherein the compressor has a first compressor stage and a second compressor stage, wherein the first compressor stage has a first spiral housing, a first drive motor and a first drive shaft, wherein the second compressor stage has a second spiral housing, a second drive motor and a second drive shaft, wherein the first drive shaft is separate from the second drive shaft, comprises the following steps: setting up the heat pump in an operating direction; and operating the heat pump in the operating direction so that the first drive shaft is designed to be upright in the operating direction of the heat pump.

The heat pump concept according to the invention is advantageous in that the installation space of the heat pump is better utilized, and the heat pump is also smaller. The heat pump concept according to the invention allows the heat pump to be used efficiently, since the components of the heat pump are at least partially made smaller or shorter by utilizing the installation space.

It goes without saying that individual aspects described in relation to the heat pump can also be implemented as a process step and vice versa. Further details are discussed in the following image description.

• 1 eine perspektivische Ansicht der erfindungsgemäßen Wärmepumpe;
• 2 eine Seitenansicht der erfindungsgemäßen Wärmepumpe;
• 3 eine Frontansicht der erfindungsgemäßen Wärmepumpe;
• 4 ein Hydraulikschema der erfindungsgemäßen Wärmepumpe;
• 5 eine perspektivische Ansicht einer weiteren Ausführungsform der erfindungsgemäßen Wärmepumpe;
• 6 eine Seitenansicht der weiteren Ausführungsform der erfindungsgemäßen Wärmepumpe;
• 7 eine perspektivische Ansicht einer Ausführungsform der erfindungsgemäßen Wärmepumpe, bei welcher der Ansaugtrichter außerhalb des Verdampfers angeordnet ist;
• 8 einen Ausschnitt der erfindungsgemäßen Wärmepumpe mit zylinderförmiger Ausführung des Zwischenkühlers;
• 9 eine Anordnung des Ausgangs des ersten Verdichters außermittig am Zwischenkühler in einer Ausführungsform der erfindungsgemäßen Wärmepumpe;
• 10 eine Anordnung des Zwischenkühlers in der erfindungsgemäßen Wärmepumpe;
• 11 eine Anordnung des Zwischenkühlers in der erfindungsgemäßen Wärmepumpe;
• 12 eine Ansicht zu Wasserrohren im Zwischenkühler;
• 13 eine Schneidringverschraubung;
• 14 eine weitere Ansicht zu Wasserrohren im Zwischenkühler;
• 15 eine Ansicht eines gewendelten Kühlrohres im Zwischenkühler;
• 16 eine Verbindung zwischen den Austrittsrohren der ersten und zweiten Verdichterstufen der erfindungsgemäßen Wärmepumpe;
• 17 eine Anordnung des Bypass-Rohres in der erfindungsgemäßen Wärmepumpe;
• 18 eine Anordnung des Zwischenkühlers und des Zwischenkühler-Sammelbehälters (siehe 7) in der erfindungsgemäßen Wärmepumpe;
• 19 deutet einen Tropfenabscheider vor dem zweiten Verdichter in der erfindungsgemäßen Wärmepumpe an;
• 20a-d einen schematischen Aufbau eines Spiralgehäuses;
• 21 einen schematischen Aufbau einer Platte des Spiralgehäuses;
• 22 einen schematischen Aufbau einer Evolute des Spiralgehäuses;
• 23 Ansichten des Spiralgehäuses;
• 24 weitere Ansichten des Spiralgehäuses;
• 25 Ablaufschema des Verfahrens zum Herstellen der erfindungsgemäßen Wärmepumpe;
• 26 Ablaufschema des Verfahrens zum Betreiben der erfindungsgemäßen Wärmepumpe;
• 27 ein Wasserkältemittel-Wärmepumpensystem aus dem Stand der Technik
• 28 schematisch eine Besprühung des Wasserdampfes durch Düsen, die aus dem Stand der Technik bekannt ist; und
• 29 eine aus dem Stand der Technik bekannte Kältemaschine.

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

• 1 a perspective view of the heat pump according to the invention;
• 2 a side view of the heat pump according to the invention;
• 3 a front view of the heat pump according to the invention;
• 4 a hydraulic diagram of the heat pump according to the invention;
• 5 a perspective view of another embodiment of the heat pump according to the invention;
• 6 a side view of the further embodiment of the heat pump according to the invention;
• 7 a perspective view of an embodiment of the heat pump according to the invention, in which the intake funnel is arranged outside the evaporator;
• 8th a section of the heat pump according to the invention with a cylindrical design of the intercooler;
• 9 an arrangement of the outlet of the first compressor off-center on the intercooler in an embodiment of the heat pump according to the invention;
• 10 an arrangement of the intercooler in the heat pump according to the invention;
• 11 an arrangement of the intercooler in the heat pump according to the invention;
• 12 a view of water pipes in the intercooler;
• 13 a cutting ring fitting;
• 14 another view of water pipes in the intercooler;
• 15 a view of a coiled cooling tube in the intercooler;
• 16 a connection between the outlet pipes of the first and second compressor stages of the heat pump according to the invention;
• 17 an arrangement of the bypass pipe in the heat pump according to the invention;
• 18 an arrangement of the intercooler and the intercooler collecting tank (see 7 ) in the heat pump according to the invention;
• 19 indicates a droplet separator in front of the second compressor in the heat pump according to the invention;
• 20a -d a schematic structure of a spiral casing;
• 21 a schematic structure of a plate of the spiral casing;
• 22 a schematic structure of an evolute of the spiral casing;
• 23 Views of the spiral casing;
• 24 further views of the spiral casing;
• 25 Flow chart of the method for producing the heat pump according to the invention;
• 26 Flow chart of the method for operating the heat pump according to the invention;
• 27 a state-of-the-art water coolant heat pump system
• 28 schematically a spraying of the water vapor through nozzles, which is known from the prior art; and
• 29 a refrigeration machine known from the state of the art.

Individual aspects of the invention described herein are described below in the 1 to 26 In the present application, identical reference symbols refer to identical or equivalent elements, whereby not all reference symbols need to be shown again in all drawings if they are repeated. 27 to 29 branches are known from the state of the art heat pumps and have already been described in the introductory part.

1 shows a perspective view of the heat pump 100 according to the invention, 2 shows a side view of the heat pump 100 according to the invention and 3 shows a front view of the heat pump 100 according to the invention. The heat pump 100 is in summary of the 1 to 3 according to a first embodiment. The heat pump 100 is shown in conjunction with the 5 and 6 according to a second embodiment.

The proposed heat pump 100 according to the embodiments described herein comprises the following features: an evaporator 10 for evaporating working fluid to obtain a working vapor; a compressor 20 for compressing the working vapor to obtain a compressed working vapor; and a condenser 30 for condensing the compressed working vapor. According to the proposal, the compressor 20 comprises a first compressor stage 70-1 and a second compressor stage 70-2, wherein the first compressor stage 70-1 has a first spiral housing 78-1, a first drive motor 80-1 and a first drive shaft 86-1, wherein the second compressor stage 70-2 has a second spiral housing 78-2, a second drive motor 80-2 and a second drive shaft 86-2. Further, according to the proposal, the first drive shaft 86-1 is separated from the second drive shaft 86-2, wherein the first drive shaft 86-1 is designed to be vertical in an operating direction of the heat pump 100. In the present case, the operating direction refers to the direction along which the working fluid is evaporated, compressed and liquefied again. The operating direction is therefore not a fixed, unchanged direction, but can vary depending on the structural arrangement of the individual components of the heat pump 100. With regard to the first compressor stage 70-1, which has the first spiral housing 78-1, the first drive motor 80-1 and the first drive shaft 86-1, the first drive shaft 86-1 is designed to be vertical, ie for example along a z-direction, if the 1 to 3 and 5 and 5 drawn coordinate system is used. Standing in the operating direction can mean, for example, parallel or antiparallel to the z-direction. Antiparallel to the z-direction therefore means in (minus) "-z" direction. As suggested, each of the drive motors 80-1, 80-2 has its own drive shaft 86-1, 86-2, wherein one of the drive shafts 86-1, 86-2 is designed to be standing, in particular parallel to the z-direction. The other drive shaft 86-, 86-2 can also be standing, in particular parallel to the z-direction (see for example 1 to 3 ), or lying down (see for example 5 and 6 ), in particular parallel to the x-direction or the y-direction or parallel to an xy plane. The drive shafts 86-1, 86-2 run in particular through their associated drive motor 80-1, 80-2 in such a way that the associated drive motor 80-1, 80-2 drives the corresponding drive shaft 86-1, 86-2 when the drive motor 80-1, 80-2 is operating.

1 and 2 show a horizontal arrangement of the first and second spiral casing 78-1, 78-2. Consequently, the impellers according to the heat pump according to 1 to 3 arranged horizontally. Due to the horizontal arrangement of the first and second spiral housing 78-1, 78-2, the height, in particular along the z-direction, of the heat pump 100 can be limited. Furthermore, 1 and 2 a standing arrangement of the drive shafts 86-1, 86-2 of the first and second spiral casings 78-1, 78-2. According to the heat pump 100 as shown in 1 to 3 As shown, the first compressor stage 70-1 and the second compressor stage 70-2 can be controlled separately from one another, in particular can be regulated separately from one another. In addition, the impellers each run on a different drive shaft 86-1, 86-2. The compressor 20 has a compressor tank 21, which is in particular cylindrical. The compressor tank 21 opens into an evaporator tank 11 at one end. At an opposite other end, the compressor tank opens into an intake port 52. In particular, the evaporator tank 11 is cylindrical. The compressor tank 21 can, as in 1 and 2 shown, be formed perpendicular to the evaporator tank 11, in particular, compressor tank 21 and the evaporator tank 11 can be connected to each other or formed as one piece. The condenser 30 has a condenser tank 31. In particular, the condenser tank 31 is formed cylindrically. As further shown in the 1 and 2 As can be seen, the evaporator tank 11 and the condenser tank 31 are each designed horizontally, with a length of the evaporator tank 11 and the condenser tank 31 extending along an x-direction. The evaporator tank 11 and the condenser tank 31 are arranged offset from one another, so that the evaporator tank 11 and the condenser tank 31 do not overlap along an x-direction ( 2 ) and partially overlapping (along the z-direction) (see 3 ). Furthermore, the evaporator tank 11 and the condenser tank 31 do not overlap along a y-direction (see 3 ). Furthermore, 1 can be removed, the evaporator tank 11 and the condenser tank 31 are arranged at an angle to each other. In particular, the evaporator tank 11 and the condenser tank 31 do not overlap along the y-direction (see 1 or 3 ). 1 shows the oblique arrangement of the evaporator tank 11 and the condenser tank 31 by means of the drawn slope 200. 1 and 2 further show that the heat pump 100 has an intercooler 42 which comprises an intercooling collecting tank 44, wherein the intercooling collecting tank 44 is formed as a unit with the intercooler 42. In particular, the intercooling collecting tank 44 and the intercooler 42 are each cylindrical.

Preferably, the evaporator 10 is designed as a horizontal evaporator cylinder 15. Furthermore, the condenser 30 is preferably designed as a horizontal condenser cylinder 35, wherein the horizontal condenser cylinder 35 is arranged obliquely above the horizontal evaporator cylinder 15 in the operating direction of the heat pump 100 and wherein in particular the evaporator cylinder 15 and the condenser cylinder 35 at least partially overlap vertically, ie overlap in the z-direction. For example, the 1 and 2 As can be seen, both the horizontal condenser cylinder 35 and the horizontal evaporator cylinder 15 are each arranged in an xy plane, with these xy planes being spaced apart along the z-direction. The horizontal evaporator cylinder 15 and the horizontal condenser cylinder 35 partially overlap along the z-direction. The at least partial vertical overlap means that the xy plane of the horizontal evaporator cylinder 15 and the xy plane of the horizontal condenser cylinder 35 partially overlap when viewed along the z-direction (see 2 ). Seen along the y-direction (see 1 ), the evaporator cylinder 15 and the condenser cylinder 35 preferably do not overlap. In the present case, the condenser cylinder 35 is also referred to as the condenser tank 31. The evaporator cylinder 15 is also referred to as the evaporator tank 11.

3 shows a front view of the heat pump 100 according to the invention. 3 shows the first spiral casing 78-1 lying with a standing first drive shaft 80-1. Furthermore, the slope 200 is also shown in Fig. to show the offset arrangement between the condenser cylinder 35 or the condenser tank 31 and the evaporator cylinder 15 or the evaporator tank 11. In the view according to 3 the first drive motor 80-1 is covered with a bursting bucket 90. Preferably, the first drive shaft 86-1 is also covered with the bursting bucket 90.

4 shows a hydraulic diagram of the heat pump 100 according to the invention, as shown in the 1 to 3 and 5-6 According to the hydraulic diagram according to 4 the first and second spiral casing 78 are arranged horizontally, in particular in an xy plane. The first compressor stage 70-1 is connected via an intercooler 42 is connected to the second compressor stage 70-2. The intercooler 42 has an intercooling chamber 43 through which the compressed working fluid passes and is cooled within the intercooling chamber 43. The intercooling chamber 43 has an inlet 47 to the intercooling chamber 43 and an outlet 46 from the intercooling chamber 43 to the second compressor stage 70-2. A bypass pipe 84 extends from the outlet 46 from the intercooling chamber 43 to the second compressor stage 70-2. If only the first

If the second compressor stage 70-1 is to be operated, the compressed working fluid does not pass through the intercooler 42, but rather through a pipe 45 which leads directly into the condenser 30. The intercooler outlet pipe 45 has a flap 82 which is closed when the working fluid is also to pass through the second compressor stage 70-2, or which is open when the working fluid from the first compressor stage 70-1 is to be led directly into the condenser 30. The flap 82 can be controllable or can be designed as a thermocouple. The flap 82 is preferably controlled so that it opens as soon as the second compressor stage is operated. The intercooler 42 has an intercooling collecting tank 44. A bypass pipe or bypass branch 85, which also has a flap 82, is arranged between the condenser 30 and the evaporator 10. The flap 82 in the bypass line 85 can be controlled or designed as a thermocouple. Preferably, the flap 82 in the bypass line 85 is controlled so that it opens as soon as the second compressor stage 70-2 is operated in idle mode.

Preferably, the intercooling collecting tank 44 of the intercooler 42 is arranged below the condenser sump 36 and above the evaporator sump 16, in particular for reasons of saving space, so that the condensed working fluid, i.e. the condensed water, can flow back due to gravity. The working fluid flows from the condenser sump 36 via the intercooling collecting tank 44 back to the evaporator sump 16 under the influence of gravity.

Preferably, the intercooler 42 is arranged between the first compressor stage 70-1 and the second compressor stage 70-2, which has an intercooling chamber 43 and an intercooling collecting tank 44, wherein the intercooling chamber 43 is formed integrally with the intercooling collecting tank 44, and/or wherein the intercooling chamber 43 is arranged above the evaporator 10 (see 1 and 2 ), or wherein the intercooling sump 44 is below the condenser sump 36 formed in the condenser 30 and above the evaporator sump 16 formed in the evaporator 10 (see 4 ), is arranged. As in 4 As shown, the intercooling collecting tank 44 is arranged separately from the intercooler 42. The arrangement of the intercooler 42 with its intercooling collecting tank 44 can be integrated into one another or designed separately from one another, depending on the available installation space.

5 shows a perspective view of another embodiment of the heat pump 100 according to the invention and 6 shows a side view of the further embodiment of the heat pump 100 according to the invention. How 5 and 6 can be removed, the second drive shaft 86-2 is preferably arranged horizontally in the operating direction of the heat pump 100, wherein the first spiral housing 78-1 is arranged horizontally and the second spiral housing 78-2 is arranged vertically (see 5 and 6 ). Taking the coordinate system into account, this means that the second drive shaft 86-2 and the horizontally arranged first spiral casing 78-1 extend along the x-direction, while the vertically arranged second spiral casing 78-2 and the first drive shaft 86-1 extend along the z-direction. The first spiral casing 78-1 and the second spiral casing 78-2 are connected to one another via the intercooler 42 (see also 4 as well as 1 and 2 According to the heat pump 100 according to 5 and 6 the first spiral casing 78-1 and the second spiral casing 78-2 are connected via the intercooler 42, while in the heat pump 100 according to 1 and 2 via first spiral casing 78-1 and the second spiral casing 78-2 via the intercooler 42 and a bypass pipe 84. Preferably, a further droplet separator 55 is arranged in the bypass pipe 84.

Preferably, the intermediate cooling space 43 is arranged above the condenser 30 (see 1 , 2 , 5 and 6 ) or is at least partially overlapped with the condenser 30 vertically, in particular along the z-direction (see 1 , 2 , 5 and 6 ). Furthermore, the intermediate cooling space 43 is preferably arranged between the first spiral casing 78-1 and the second spiral casing 78-2S (see 1 , 2 , 5 and 6 ). Alternatively or additionally, the intermediate cooling collecting tank 44 is arranged separately from the intermediate cooling chamber 43 below the condenser 30 (see 5 and 6 ), or a substantially straight or substantially U-shaped bypass pipe 85 is arranged between the condenser 30 and the evaporator 10 in a region in which the condenser 30 and the evaporator 10 at least partially overlap vertically in the operating direction of the heat pump 100 (see 1 and 2 ). The bypass pipe 84 is preferably bent, whereby the operating direction of the working fluid takes a different direction with respect to the coordinate system shown, provided that the evaporated working fluid passes through the bypass pipe 84. If only the first compressor stage 70-1 is operated, the working fluid can be led directly to the condenser 30 by the working fluid passing through the pipe connection 45 (see next to 1 , 2 , 5 and 6 also 4 ).

Like the 5 and 6 As can be seen, the first compressor housing 78-1 is lying, while the second compressor housing 78-2 is standing. Only the intercooler 42 is arranged between the first and second compressor housings 78-1, 78-2. This can improve the flow of the steam, ie the compressed working fluid, since the flow between the first and second compressor stages 70-1, 70-2 can take place without any additional pipes arranged in between. 5 and 6 It can also be seen that a bypass line 85 is arranged from the condenser 30 to the evaporator 10. The bypass line 85 allows a direct guidance of the working fluid from the condenser sump 36 into the evaporator sump 16. Furthermore, the heat pump 100 according to the 5 and 6 a separate intercooling collection tank 44 which is arranged separately from the intercooler 42. The intercooling collection tank 44 is connected to the intercooler 42 for receiving working fluid from the intercooler 42 (see also 4 ).

A comparison of the 2 with the Fig, 6 shows that according to the 2 the first and second spiral casings 78-1, 78-1 are each arranged horizontally, while according to 6 the first spiral casing 78-1 is arranged vertically and the second spiral casing 78-2 is arranged horizontally. In both embodiments, ie in the heat pump 100 according to 2 and after 6 , a Stage 1 operation is possible, in which only the first compressor stage 70-1 is operated. Both embodiments can also be operated in a Stage 2 operation, in which the first and second compressor stages 70-1, 70-2 are operated. The heat pump 100 according to 6 has an intercooler 42 which is arranged separately from its intercooling collecting tank 44. Preferably, the intercooler 42 has horizontally arranged, indirect heat transfer pipes which are arranged in particular wound as a coil in the intercooling space 43. According to the heat pump 100 according to 2 the intercooler 42 and the intercooling collecting tank 44 are connected, in particular cylindrical, in design.

The heat pump 100 after 6 has the bypass line 85 as a direct connection between the condenser 30 and the evaporator 10. The heat pump 100 according to 2 has the bypass line 85 as a direct connection between the condenser 30 and the evaporator 10, wherein the bypass line 85 is arranged around the intake port 52 of the first compressor stage 70-1. Both heat pumps 100 are each arranged in a frame 40.

Preferably, an intake port 52 is arranged between the evaporator 10 and the first compressor stage 70-1, which is arranged outside the evaporator 10, as is shown for example in 7 can be seen. Alternatively or additionally, an intake port 52 is arranged between the evaporator 10 and the first compressor stage 70-1, which is arranged outside the evaporator 10, wherein a droplet separator 54 is arranged in the intake port 52. Furthermore, alternatively or additionally, an intake port 52 is arranged between the evaporator 10 and the first compressor stage 70-1, which is arranged outside the evaporator 10 and which has a length which is at least as great as half the diameter of the condenser 30 and/or wherein the intake port 52 is arranged upright, in particular along the z-direction. Because the droplet separator 54 is arranged in the intake port 52, the droplet separator 54 can only be indicated by its reference number. 7 shows a perspective view of an embodiment of the heat pump according to the invention, in which the intake funnel 52 is arranged outside the evaporator. This simplifies the manufacture and assembly of the heat pump 100 according to the invention. In addition, the evaporator 10, in particular the evaporator tank 11, can be made smaller. Because the droplet separator 54 is arranged in the intake port 52, which is arranged outside the evaporator 10, arranging and maintaining the droplet separator 54 in the intake port 52 is simplified. In addition, the risk of a malfunction of the droplet separator 54 can be reduced, since the height difference between the water line of the evaporator tank 11 and the inlet to the compressor is greater than if the intake funnel is arranged in the tank in order to arrange the first spiral housing compressor at the height of the second spiral housing compressor. In addition, the evaporator 10, in particular its evaporator tank 11, can be made smaller or shorter. By arranging the individual components or modules, in particular the containers 11, 15, 21, 31 44 and the spiral casings 78-1, 78-2, of the heat pump 100, on the one hand installation space can be saved and on the other hand the flow guidance of the working fluid can be improved.

Preferably, an inlet 79-1 of the horizontally arranged first spiral casing 78-1 is in the Operating direction of the heat pump 100 is arranged at the top of the intake port 52. Preferably, an outlet 77-1 of the first spiral housing 78-1 is connected to an inlet 47 of an intermediate cooling space 43 of an intercooler 42. Furthermore, preferably, an outlet 46 of the intermediate cooling space 43 is connected to an inlet 79-2 of the second spiral housing 78-2, which is arranged vertically, and an outlet 77-2 of the second spiral housing 78-2 is connected to an inlet 36 of the condenser 30 (see 6 ), wherein the respective connections are preferably made directly, in particular without a further component in between. Alternatively or additionally, the first spiral housing 78-1, the second spiral housing 78-2 and the condenser 30 are arranged such that, during operation of the heat pump 100, a steam flow is caused through the intake port 52 in a first direction, a steam flow is caused through the intercooling space 43 in a second direction which is substantially perpendicular to the first direction, and a steam flow from the second spiral housing 78-2 into the condenser 30 is caused in a third direction which has at least one directional component which is directed substantially opposite to the first direction, and wherein the first spiral housing 78-1 and the second spiral housing 78-2 are arranged and designed to each cause a steam flow direction change of substantially 90 degrees. For example, as in the 6 As can be seen from the coordinate system shown, the first direction can be parallel to the z-direction, while the second direction can be parallel to the -x-direction. The third direction, however, has (x,y,z) coordinates. As also shown in the 1 and 2 As can be seen, the outlet 46 of the intermediate cooling chamber 43 is connected to the inlet 79-2 of the second spiral casing 78-2 via the bypass pipe 84. Both in the heat pump according to 1 and 2 as well as the heat pump 100 after 5 and 6 the intermediate cooling space 43 is connected to the condenser 30 via a pipe connection 45.

Preferably, the first compressor stage 70-1 has a first impeller wheel which is arranged on the first drive shaft 86-1, in which the second compressor stage 70-2 has a second impeller wheel which is attached to the second drive shaft 86-2, wherein in the operating direction of the heat pump 100 the first drive shaft 86-1 and the second drive shaft 86-2 are arranged substantially parallel to one another (see 1 and 2 ), wherein the first impeller wheel and the second impeller wheel are arranged at substantially the same height, or wherein in the operating direction of the heat pump 100, the first drive shaft 86-1 and the second drive shaft 86-2 are arranged substantially perpendicular to one another and the first impeller wheel has a length and the second impeller wheel has a diameter, wherein the first impeller wheel and the second impeller wheel are arranged such that the length of the first impeller wheel and the diameter of the second impeller wheel substantially at least partially overlap. In particular, the length of the first impeller wheel and the diameter of the second impeller wheel substantially overlap along at least one direction of the coordinate system shown in the figures.

Preferably, the heat pump 100 has an intercooler 42 with an intercooling chamber 43, wherein an outlet 77-1 of the first spiral housing 78-1 is arranged in an upper region 210 of the intercooling chamber 43 in the operating direction of the heat pump 100 and an inlet 79-2 of the second spiral housing 78-2 is arranged in a lower region 220 of the intercooling chamber 43 in the operating direction of the heat pump 100, such that during operation of the heat pump 100 a steam flow in the intercooler 42 takes place from top to bottom (see 8th ). From top to bottom means at least along the negative z-direction, if the coordinate system shown in the figures is observed. This arrangement allows the installation space in the heat pump to be used in a space-saving manner.

8th shows a section of the heat pump 100 according to the invention with a cylindrical design of the intercooler 42. As in 8th As shown, the intercooler 42 consists of two parts, which define the upper area 210 and the lower area 220. The upper area 210 is connected to the outlet 77-1 of the first spiral housing 78-1. The lower area 220 is connected to an inlet 79-2 of the second spiral housing 78-2 via the bypass pipe 84. Preferably, the upper area 210 and the lower area 220 are constructed identically except for the inlets and outlets. The upper and lower areas 210, 220 can thus be easily manufactured and assembled. The intercooling, ie the intercooler 42, can be flexibly exchanged, the cooling tubes or the cooling rods 48 (see 14 ) with direct intermediate cooling can be achieved, for example, by means of coiled cooling tubes 115 (see 15 ) with indirect intercooling.

9 shows an arrangement of the outlet 77-1 of the first compressor stage 70-1 off-center on the intercooler 42 in an embodiment of the heat pump 100 according to the invention. The outlet 77-1 is arranged in the upper area 210. This achieves an optimized swirling of the steam, which leads to a rotation of the steam in the cylindrical intercooler 42 and thus leading to improved cooling of the steam. The upper region 210 is defined by an upper element 210 and the lower region 220 is defined by a lower element 220. 12 also shows this off-center arrangement.

Preferably, the intermediate cooling space 43 is formed from the upper element 210 and the lower element 220, wherein the upper element is connected to the outlet 77-1 of the first spiral casing 78-1 and the lower element is connected to the inlet 79-2 of the second spiral casing 78-2, and wherein the two elements are connected to one another, in particular directly connected to one another (see 1 , 2 and 9 and 12 ). Alternatively or additionally, in the operating direction of the heat pump 100, the intercooler 42 further comprises the intercooling collecting tank 44, which is arranged below the bottom of the intercooling space 43 and via which a pipe 230 is connected to the intercooling space 43 ( 5 to 7 ), or which is integrally connected to the intermediate cooling chamber 43 ( 1 and 2 ), wherein a pump is provided for pumping coolant from the intercooling collecting tank 44 into the intercooling space 43.

10 and 11 each show an arrangement of the intercooler 42 in the heat pump 100 according to the invention. 10 and 11 show two different perspectives on the heat pump 100. Like the 10 and 11 As can be seen, the intercooler 42 is divided into two parts. This allows the installation space in the heat pump 100 to be better utilized, since the two-part intercooler 42, 44 can be mounted at different locations on the heat pump. The actual intercooler 42 for cooling the steam is preferably located next to the condenser 30. The intercooling collecting tank 44 of the intercooler 42 is located below the condenser 30, in particular next to the evaporator 10 (see 11 ). The intercooler 42 and its intercooling collecting tank 44 are connected to each other via a line (hose).

Preferably, the outlet 77-1 of the first spiral casing 78-1 is designed as a pipe connection which is attached eccentrically to the upper element 210 of the intermediate cooling chamber 43 with respect to a central axis of the intermediate cooling chamber 43, so that the axis of the pipe connection passes the central axis of the intermediate cooling chamber 43 without an intersection point, wherein the upper element 210 of the intermediate cooling chamber 43 is designed essentially cylindrical, wherein in particular the outer surface of the pipe connection is attached to the outer part of the cylindrically designed intermediate cooling chamber 43. The axis of the pipe connection refers in particular to an axis running centrally through the pipe connection. This is shown, for example, in the 9 and 10 to see.

12 shows a view of cooling rods 48 in the intercooler 42, whereby for mounting the cooling rods 48 a cutting ring screw connection, as shown in 13 shown is used. 14 shows a further view of cooling rods 48 in the intercooler 42. Preferably, the intercooler 42 has one or more cooling rods 48 (see 8th , 12 and 14 ), which extend in the intercooling space 43 from top to bottom in the operating direction of the heat pump 100, wherein nozzle openings 49 are perforated in a lower region of the one or more cooling rods 48 and fewer or no nozzle openings are perforated in an upper region, wherein a coolant supply line is designed to supply coolant to the one or more cooling rods 48 at the upper region, so that the coolant can be sprayed through the nozzle openings 49 into the intercooling space 43 during operation of the heat pump 100. As a result, working fluid can be intercooled in the intercooler 42. The cooling rods 48 are preferably designed as water pipes with holes (nozzle openings 49). The nozzle openings are used to spray the steam flowing out in the intercooler 42, ie to cool the steam flowing out in the intercooler 42. Fig.s 12 to 14 each show cooling rods 48. The cooling rods 48 are connected via base elements 134 by means of cutting ring connections 130 to a cover plate 132 of the intercooler 42. In 12 and 14 an outer wall of the intercooler 42 is only indicated schematically in order to reveal the interior of the intercooler 42.

The use of an intercooler 42, which is arranged in particular between the first compressor stage 70-1 and the second compressor stage 70-2, allows cooling of the vapor of the working fluid both in Stage-1 operation and in Stage-2 operation of the heat pump 100.

Preferably, the one or more cooling rods 48 are closed in the operating direction of the heat pump 100 below the nozzle openings 49, in particular the one or more cooling rods 48 are squeezed together below the nozzle openings 49 (see for example 14 ). As a result of the squeezing, the one or more cooling rods 48 have a conical shape in at least one side view. Alternatively or additionally, the one or more cooling rods 48 are made of stainless steel, copper or plastic. Stainless steel and copper are good heat conductors, while plastic is lighter than metal. In In any case, the materials mentioned are robust and therefore durable. Preferably, the one or more cooling rods 48 is/are connected via one or more base elements 134 to a cover element 132 (cover plate 132) of the upper element of the intermediate cooling space 43, wherein the base elements 134 extend through the cover element 132 and have coolant connections outside the intermediate cooling space 43. Preferably, the one or more cooling rods 48 is/are attached by one or more cutting ring connections 130 to the base elements 134, which are connected to the cover element 132 of the intermediate cooling space 43.

13 shows a cutting ring connection 130. Cutting ring screw connections are standardized according to DIN EN ISO 8434 (parts 1..4) or DIN 2353 and are used primarily in hydraulics. The components of a cutting ring screw connection are: union nut, clamping cone and cutting ring. It has a 24° sealing cone, the nut has a metric thread (see Wikipedia). The cutting ring screw connection 130 is used in particular for metal cooling rods 48. Other mounting options for attaching the cooling rods 48 to the intercooler 42 are also conceivable.

Preferably, the one or more cooling rods 48 have no perforations 148 in one, in particular upper, section 140 and have the perforations 148 in another, in particular lower, section 142, wherein the one, in particular upper, section 140 is dimensioned for indirect cooling and the other, in particular lower, section 142 is dimensioned for direct cooling. Direct cooling comprises spraying with coolant, while indirect cooling only comprises heat transfer between the one or more cooling rods 48. Preferably, the upper section 140 is longer than the lower section 142. Additionally or alternatively, the one or more cooling rods 48 have a more inhomogeneous surface in the upper section 140 compared to the lower section 142. The more inhomogeneous surface can have a higher roughness and thus a larger surface area compared to the surface of the lower section 142 in order to improve the heat transfer between an interior of the one or more cooling rods 48 and the intermediate cooling space 43. The perforations 148 are designed as nozzle openings 49, which can have varying opening diameters. The perforations 148 or the nozzle openings 49 are preferably designed as lasered holes. By changing the proportion of indirect cooling (without perforations 148 in one section 140) and direct cooling (with perforations 148 in the other section 142) of the cooling rods 48, the cooling capacity of the intermediate cooler 42 can be variably adjusted. Preferably, three cooling rods 48 are provided in the intermediate cooler 42. However, more or fewer than three cooling rods 48 can also be provided. Instead of straight cooling rods 48, more or fewer cooling tubes can be present. The cooling pipe can then be designed in a spiral or coiled manner, for example. In the area of indirect cooling (in the one area 140), the pipes can also be finned, i.e. have ribs, or be designed with a rough surface in order to increase the heat exchanger surface.

Alternatively, the intermediate cooling space 43 preferably has one or more coiled cooling tubes 115 (see 15 ). Preferably, according to an alternative, the heat pump 100 described herein comprises cooling rods 48, wherein the one or more cooling rods 48 are designed as coiled cooling tubes 115, wherein the one or more coiled cooling tubes 115 have an end arranged in the intermediate cooling space 43, which is or are arranged in such a way that cooling liquid exiting through the end or ends can be sprayed from bottom to top in the operating direction of the heat pump 100 into the intermediate cooling space 43 (see arrow 116 in 15 ), or wherein the one or more coiled cooling tubes 115 have nozzle openings 49 which are designed to spray coolant from bottom to top into an intermediate cooling space 43. The arrow 116 in 15 shows schematically an injection of cooling liquid into the intermediate cooling chamber 43. The arrow 117 shows the vapor direction of the compressed working fluid. How 15 shows, for example, instead of the cooling rods 48, which "hang" downwards, a coiled cooling pipe 115 can be used, which has a greater length than the straight cooling rods 48 for the indirect cooling of the steam. The cooling water emerging from the cooling pipe 115 (in the direction of the arrow 116) is then injected against the steam direction 117, which results in better cooling of the steam (see 15 ).

Preferably, the second spiral casing 78-2 has a second outlet pipe 145, wherein the intercooler 42 has an intercooler outlet pipe 45 which opens into the condenser 30. The second outlet pipe 145 is connected to the first intercooler outlet pipe 45. Alternatively or additionally, the second outlet pipe 145 can be directly in the condenser 30. In 16 Both possibilities are shown. The second outlet pipe 145 can be interpreted as a “Stage 2 outlet pipe” that the second outlet pipe 145 leads the steam exiting from the second compressor stage 70-2 to the condenser 30 directly and/or via the intercooler outlet pipe 45. The intercooler outlet pipe 45 can be interpreted as a “stage 1 outlet pipe” that the intercooler outlet pipe 45 leads the steam exiting from the first compressor stage 70-1 directly to the condenser 30. By docking the second outlet pipe 145 to the intercooler outlet pipe 45, for example, a connection to the condenser 30 can be saved, provided that the second outlet pipe 145 does not have a direct connection to the condenser (in 16 not shown). This also allows the installation space to be better utilized through the arrangement of the other components of the heat pump.

17 shows an arrangement of a bypass pipe 84 in the heat pump 100 according to the invention. Preferably, the heat pump 100 has the bypass pipe 84, wherein a first end 151 of the bypass pipe 84 opens into the condenser 30, wherein a second end 152 of the bypass pipe 84 opens into the evaporator 10, and wherein the second end 152 of the bypass pipe 84 opens into the evaporator 10 below a sprinkler in the evaporator 10 and above a level of an evaporator sump 16 (see reference numeral 161 in 17 ), and/or wherein the first end 151 of the bypass pipe 84 opens into the condenser 30 below the upper end of the condenser 30 and above the level of the condenser sump 36 (see reference numeral 161 in 17 ). The reference numerals 161 and 162 indicate the regions in which the first and second ends 151, 152 can be arranged, respectively.

18 shows similar to 11 an arrangement of the intercooler 42 in the heat pump 100 according to the invention, wherein the intercooler collecting tank 44 (see 10 ) is arranged separately from the intercooler 42. In 18 the intercooler 42 is shown with its lower edge 143. The intercooling collecting tank 44 of the intercooler 42 can basically be arranged anywhere in the heat pump 100 below the lower edge 143 of the intercooler 42 (compare 18 and 11 ). The intermediate cooling collecting tank 44 can be made of plastic or stainless steel or another metal that does not react or reacts only slightly with water.

Preferably, the second spiral casing 78-2 has an inlet port 26 which is connected to a connecting pipe 28 (see 19 ), wherein a further droplet separator 55 is formed in the connecting pipe 28 in order to reduce or eliminate working fluid droplets in a steam flow into the second spiral casing 78-2. The steam flow in particular determines the operating direction of the heat pump 100. The droplet separators 55 arranged in the heat pump 100 serve to separate working fluid droplets from the working steam. 19 shows schematically the arrangement of a droplet separator 55 (indicated by its reference number) in front of the second compressor in the connecting pipe 28 in the heat pump 100 according to the invention. The connecting pipe 28 is also referred to as a bypass pipe 84. A second droplet separator 55 is arranged between the outlet of the intercooler 42 and the second compressor stage 70-2 in order to prevent drops from the water vapor or from the intercooler 42 from being sucked into the second compressor stage 70-2 and damaging it. A first droplet separator 55 is arranged in the intake port 52 (see 19 ).

19 also shows a burst bucket 90, which is placed over the first drive motor 80-1 of the first compressor stage 70-1. Preferably, the first spiral housing 78-1 and/or the second spiral housing 78-2 is attached to a frame 40 of the heat pump 100 via at least one elastic damping element 94. Preferably, a securing element 95 is arranged between the frame 40 and the first spiral housing 78-1 and/or the second spiral housing 78-2 in the heat pump 100 in order to hold the first spiral housing 78-1 and/or the second spiral housing 78-2 essentially in place, in particular within the frame 40, in the event of destruction of the at least one elastic damping element 94. The securing element 95 is preferably arranged in the area of the drive motors 80-1, 80-2 in order to protect the first spiral housing 78-1 and/or the second spiral housing 78-2 from flying parts of the drive motors 80-1, 80-2 or the impeller in the event that the drive motors 80-1, 80-2 are no longer functional.

If the impeller bursts due to material failure, etc., the impeller will become stuck or wedged in the spiral housing 78-1, 78-2 and exert a torque 190 on the spiral housing 78-1, 78-2. The damping element 94 will be the weakest point in this case. The compressor stage 70-1, 70-2 with the spiral housing 78-1, 78-2 will tumble in the opening of the frame 40 and possibly come loose. A safety element 95 between the frame 40 and the spiral housing 78-1, 78-2 is therefore proposed, for example a safety cable, a screw connection, a safety device 98 or the like, which "catches" the spiral housing 78-1, 78-2 in the event of the impeller bursting.

The 20 to 21 show various schematic views of the spiral casing 78-1, 78-2 to illustrate the structure of such a casing. 20 shows various views of a schematic structure of a spiral casing 78-1, 78-2. 20a shows a perspective three-dimensional view of a spiral casing 78-1, 78-2 on which a drive motor 80-1, 80-1 is mounted. 20b shows a plan view of the spiral casing 78-1, 78-2 on which the drive motor 80-1, 80-1 is mounted. 20 b a diameter 205 of the evolute of, for example, about 500mm can be taken, whereby an exit 201 of the evolute has a diameter 205 of about 90mm. The exit 201 of the evolute corresponds to the exits 77-1, 77-2 of the spiral housings 78-1, 78-2, which are also in 20c you can see. 20c and 20d each show a side view of the spiral casing 78-1, 78-2, where 20c shows the inlets 79-1, 79-2 of the spiral casings 78-1, 78-2. The inlets 79-1, 79-2 have a diameter 205 of approximately 10 mm. 20d shows in detail the shape of the spiral casing 78-1, 78-2, which has an upper part 202 in the form of a plate and a lower part 203 with a U-profile, whereby the diameter of the U-profile increases up to the exit 201 of the evolute. 21 shows an enlarged schematic structure of the upper part 202 of the plate of the spiral casing 78-1, 78-2, wherein the upper part 201 has a recess 204 or opening 204 for receiving the drive motor 80-1, 80-2. 22 shows an enlarged schematic structure of the lower part 203 of the spiral casing 78-1, 78-2, wherein a center of the steam inlet (air inlet 56) and a center of the spiral casing 78-1, 78-2 lie on an axis N. 23 and 24 show further details in top and side views of the spiral casings 78-1, 78-2.

Preferably, the first spiral housing 78-1 or the second spiral housing 78-1 has the following features: a central air inlet 56; a lateral air outlet 57; a flat connecting channel 66 which adjoins the air inlet 56; and an evolute channel 62 which connects the flat connecting region 66 to the air outlet 57, wherein the evolute channel 62 has a cross-sectional area which increases continuously from the air inlet 56 to the air outlet 57, and wherein the evolute channel 62 is curved and extends from the air inlet 56 to the air outlet 57 by more than 180 degrees and by less than 360 degrees (see 20 to 24 ).

Preferably, the evolute channel 62 has a diameter of more than 70 mm and less than 110 mm at the air inlet opening or at the air inlet 56, wherein a diameter of the first spiral housing 78-1 and/or the second spiral housing 78-2 is between 400 and 600 mm, or a ratio between the diameter of the first or the second spiral housing 78-1, 78-2 and the diameter of the air outlet 57 is between (two) 2 and (ten) 10, in particular between (three) 3 and (eight) 8, in particular between (four) 4 and (seven) 7 (see 20 to 24 ).

Preferably, the flat connection region 66 or the flat connection channel 66 extends around the air inlet 56 by more than 270 degrees and less than 360 degrees, and has a height that is at most half as large as a height of the evolute channel 62 at the air outlet or air outlet 57 (see 20 to 24 ).

Preferably, the evolute channel 62 increases in a cross-sectional area along a direction of rotation, wherein the direction of rotation is the same as the direction of rotation of the first compressor motor 17 and/or the second compressor motor 18. The first compressor motor 17 corresponds to the first drive motor 80-1. The second compressor motor 18 corresponds to the second drive motor 80-2.

Preferably, the first spiral housing 78-1 and/or the second spiral housing 78-2 is/are formed from a base plate 64 and an evolute plate 63, wherein the evolute plate 63 has a circumferential U-profile for defining the evolute channel 62, the cross section of which increases continuously, or the first spiral housing 78-1 and/or the second spiral housing 78-2 is/are formed from a one-piece cast part 65, wherein the evolute channel 62 and the flat connecting channel 66 are defined by a sacrificial core 67. The evolute plate 63 corresponds to the lower part 203 and the base plate 64 corresponds to the upper part 202.

The heat pump 100 described here has a space-saving arrangement of its individual components. In addition, the individual components of the heat pump 100 are arranged in such a way that the flow of the working fluid during operation of the heat pump 100, in particular through the containers and through the spiral housings 79-1, 79-2, is flow-optimized.

A further aspect of the present invention relates to a method 250 for producing a heat pump 100 with an evaporator 10 for evaporating working fluid to obtain a working vapor; a compressor 20 for compressing the working vapor to obtain a compressed working vapor; and a condenser 30 for condensing the compressed working vapor, wherein the compressor 20 has a first compressor stage 70-1 and a second compressor stage 70-2, wherein the first compressor stage 70-1 has a first spiral housing 78-1, a first drive motor 80-1 and a first drive shaft 86-1, wherein the second compressor stage 70-2 has a second spiral casing 78-2, a second drive motor 80-2 and a second drive shaft 86-2. In step 252, the method 250 includes arranging the drive shafts 86-1, 86-2 such that the first drive shaft 86-1 is separated from the second drive shaft 86-2. This allows the drive motors 80-1, 80-1 to be operated independently of one another. In step 254, the method 250 includes forming the first drive shaft 86-1 in a vertical position in an operating direction of the heat pump 100. The vertical position corresponds to arranging the first drive shaft 86-1 substantially perpendicular to an earth's surface from which the heat pump 100 is erected. The operating direction of the heat pump is the direction in which a working fluid is evaporated or compressed or condensed. The operating direction of the heat pump 100 indicates a flow direction of the working fluid. Thus, the operating direction of the heat pump 100 is not constant, but depends on the spatial conditions of the individual components of the heat pump 100, which the working fluid passes during operation of the heat pump. The method 250 is in 25 reproduced.

Another aspect of the present invention relates to a method 260 for operating a heat pump 100 with an evaporator 10 for evaporating working fluid to obtain a working vapor; a compressor 20 for compressing the working vapor to obtain a compressed working vapor; and a condenser 30 for condensing the compressed working vapor, wherein the compressor 20 has a first compressor stage 70-1 and a second compressor stage 70-2, wherein the first compressor stage 70-1 has a first spiral housing 78-1, a first drive motor 80-1 and a first drive shaft 86-1, wherein the second compressor stage 70-2 has a second spiral housing 78-2, a second drive motor 80-2 and a second drive shaft 86-2, wherein the first drive shaft 86-1 is separate from the second drive shaft 86-2. The method 260 includes, in step 262, setting up the heat pump 100 in an operating direction. In particular, the heat pump is arranged on the earth's surface. At the beginning of a working cycle of the heat pump, the operating direction of the heat pump 100 is preferably substantially perpendicular to the earth's surface. In step 264, the method 260 includes operating the heat pump 100 in the operating direction, so that the first drive shaft 86-1 is designed to be upright in the operating direction of the heat pump 100, in particular substantially perpendicular to the earth's surface. The method 260 is in 26 reproduced.

Both the method 250 and the method 260 include steps for manufacturing and operating the heat pump 100 as described in connection with its device features herein.

Although some aspects have been described in connection with a device or a system, it is understood that these aspects also represent a description of a corresponding method, so that a block or a component of a device or a system can also be understood as a corresponding method step or as a feature of a method step. A representation of the present invention in the form of method steps is omitted here for reasons of redundancy.

In the foregoing Detailed Description, various features have been grouped together in examples in order to streamline the disclosure. This type of disclosure should not be interpreted as an intention that the claimed examples include more features than are expressly recited in each claim. Rather, as the following claims reflect, subject matter may be in fewer than all of the features of a single disclosed example. Accordingly, the following claims are hereby incorporated into the Detailed Description, with each claim being able to stand as its own separate example. While each claim may stand as its own separate example, it should be noted that although dependent claims in the claims refer to a specific combination with one or more other claims, other examples also include a combination of dependent claims with the subject matter of any other dependent claim or a combination of any feature with other dependent or independent claims. Such combinations are intended to be encompassed unless it is stated that a specific combination is not intended. Furthermore, a combination of features of a claim with any other independent claim is also intended to be encompassed, even if that claim is not directly dependent on the independent claim.

List of reference symbols

10

Evaporator

11

Evaporator tank

15

Evaporator cylinder

16

Evaporator sump

17

first compressor engine

18

second compressor motor

20

compressor

21

Compressor tank

26

Input connector

28

Connecting pipe

30

Condenser

36

Condenser sump

31

Condenser tank

35

Condenser cylinder

36

Condenser inlet

40

frame

42

Intercooler

43

Intermediate cooling room

44

Intermediate cooling tank

45

Intercooler outlet pipe

46

Exit of the intercooling room

47

Entrance of the intercooling room

48

Cooling rod

49

Nozzle opening

52

Intake manifold

54

Droplet separator

55

additional droplet separator

56

Air intake

57

Air outlet

62

Evolute channel

63

Evolute plate

64

Base plate

65

Casting

66

Connecting channel

67

Sacrificial core

70-1

first compressor stage

70-2

second compressor stage

77-1

Outlet of the first spiral casing

77-2

Outlet of the second spiral casing

78

Spiral casing

78-1

first spiral casing

78-2

second spiral casing

79-1

Entrance of the first spiral casing

79-2

Entrance of the second spiral casing

80

Drive motor

80-1

first drive motor

80-2

second drive motor

82

flap

84

Bypass pipe

85

Bypass line

86-1

first drive shaft

86-2

second drive shaft

90

Bursting bucket

94

elastic damping element

95

Securing element

98

Safety gear

100

Heat pump

115

coiled cooling tube

116

Arrow

117

Arrow

130

Cutting ring connection

132

Cover plate of the intercooler

134

Base element

151

first end

152

second end

161

Area

162

Area

190

Torque

200

Slope

201

Exit of the Evolute

202

Top

203

Bottom part

204

Recess/Opening

205

Diameter of the evolute

210

upper element

220

lower element

140

a section

142

other section

143

Lower edge of the intercooler

145

second outlet pipe

148

Perforation

1'

chamber

2'

chamber

3'

chamber

4'

Collection container

5'

Impellers are mounted on a drive shaft

6'

Evaporator

7'

Water refrigerant heat pump system

10'

Refrigeration machine

12'

Compressor part

14'

Condenser

16'

Evaporator

18'

Outlet spiral

20'

Pipeline

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions.

Cited patent literature

• WO 2013085969 A1 [0004]

Cited non-patent literature

• Tadayoshi et al.: Centrifugal turbo chiller using water ras refrigerant and lubricant, The 11th International Conference on Compressors and their System, Journal of Process Mechanical Engineering, published on July 1, 2020, DOI: 10.1177/0954408920938197 [0002]

Claims (26)

Heat pump (100) with the following features: an evaporator (10) for evaporating working fluid to obtain a working vapor; a compressor (20) for compressing the working vapor to obtain a compressed working vapor; and a condenser (30) for condensing the compressed working steam, wherein the compressor (20) has a first compressor stage (70-1) and a second compressor stage (70-2), where the first compressor stage (70-1) has a first spiral housing (78-1), a first drive motor (80-1) and a first drive shaft (86-1), where the second compressor stage (70-2) has a second spiral housing (78-2), a second drive motor (80-2) and a second drive shaft (86-2), wherein the first drive shaft (86-1) is separate from the second drive shaft (86-2), and wherein the first drive shaft (86-1) is designed to be upright in an operating direction of the heat pump (100) Heat pump (100) to Claim 1 , in which the evaporator (10) is designed as a horizontal evaporator cylinder (15), and in which the condenser (30) is designed as a horizontal condenser cylinder (35), wherein the horizontal condenser cylinder (35) is arranged obliquely above the horizontal evaporator cylinder (15) in the operating direction of the heat pump (100) and wherein in particular the evaporator cylinder (15) and the condenser cylinder (35) at least partially overlap vertically (to the operating direction). Heat pump (100) to Claim 1 or 2 , in which an intercooler (42) is arranged between the first compressor stage (70-1) and the second compressor stage (70-2), which has an intercooling space (43) and an intercooling collecting tank (44), wherein the intercooling space (43) is formed integrally with the intercooling collecting tank (44), and/or wherein the intercooling space (43) is arranged above the evaporator (10), or wherein the intercooling collecting tank (44) is arranged below the condenser sump (36) formed in the condenser (30) and above the evaporator sump (16) formed in the evaporator (10). Heat pump (100) according to one of the preceding claims, in which the second drive shaft (86-2) is arranged horizontally in the operating direction of the heat pump (100), the first spiral housing (78-1) being arranged horizontally and the second spiral housing (78-2) being arranged vertically Heat pump (100) to Claim 3 or 4 , wherein the intermediate cooling space (43) is arranged above the condenser (30) or at least partially overlaps it vertically and wherein the intermediate cooling space (43) is arranged between the first spiral housing (78-1) and the second spiral housing (78-2S), and/or wherein the intermediate cooling collecting container (44) is arranged separately from the intermediate cooling space (43) below the condenser (30), or wherein a substantially straight or U-shaped bypass pipe (84) is arranged between the condenser (30) and the evaporator (10) in a region in which the condenser (30) and the evaporator (10) at least partially overlap vertically in the operating direction of the heat pump (100). Heat pump (100) according to one of the preceding claims, in which an intake port (52) is arranged between the evaporator (10) and the first compressor stage (70-1), which is arranged outside the evaporator (10), or in which an intake port (52) is arranged between the evaporator (10) and the first compressor stage (70-1), which is arranged outside the evaporator (10), wherein a droplet separator (54) is arranged in the intake port (52), or in which an intake port (52) is arranged between the evaporator (10) and the first compressor stage (70-1), which is arranged outside the evaporator (10) and which has a length that is at least as large as half the diameter of the condenser (30) and/or wherein the intake port (52) is arranged upright. Heat pump (100) to Claim 6 , in which an inlet (79-1) of the horizontally arranged first spiral housing (78-1) is arranged at the top of the intake port (52) in the operating direction of the heat pump (100), in which an outlet (77-1) of the first spiral housing (78-1) is connected to an inlet (47) of an intermediate cooling space (43) of an intermediate cooler (42), in which an outlet (46) of the intermediate cooling space (43) is connected to an inlet (79-2) of the second spiral housing (78-2), which is arranged vertically, and an outlet (77-2) of the second spiral housing (78-2) is connected to an inlet (36) of the condenser (30), wherein the respective connections are preferably made directly, and/or wherein the first spiral housing (78-1), the second spiral housing (78-2) and the condenser (30) are so are arranged such that, during operation of the heat pump (100), a steam flow is effected through the intake port (52) in a first direction, a steam flow is effected through the intercooling space (43) in a second direction which is substantially perpendicular to the first direction, and a steam flow from the second spiral housing (78-2) into the condenser (30) is effected in a third direction which has at least one directional component which is directed substantially opposite to the first direction, and wherein the first spiral housing (78-1) and the second spiral housing (78-2) are arranged and designed to each effect a steam flow direction change of substantially 90 degrees. Heat pump (100) according to one of the preceding claims, in which the first compressor stage (70-1) has a first impeller wheel which is arranged on the first drive shaft (86-1), in which the second compressor stage (70-2) has a second impeller wheel which is attached to the second drive shaft (86-2), wherein in the operating direction the first drive shaft (86-1) and the second drive shaft (86-2) are arranged substantially parallel, wherein the first impeller wheel and the second impeller wheel are arranged at a substantially equal height, or wherein in the operating direction of the heat pump (100) the first drive shaft (86-1) and the second drive shaft (86-2) are arranged substantially perpendicular to one another and the first impeller wheel has a length and the second impeller wheel has a diameter, wherein the first impeller wheel and the second impeller wheel are arranged such that the length of the first impeller wheel and the diameter of the second impeller wheel substantially at least partially overlap. Heat pump (100) according to one of the preceding claims, which has an intercooler (42) with an intercooling space (43), wherein an outlet (77-1) of the first spiral housing (78-1) is arranged in an upper region of the intercooling space (43) in the operating direction of the heat pump (100) and an inlet (79-2) of the second spiral housing (78-2) is arranged in a lower region of the intercooling space (43) in the operating direction of the heat pump (100), such that during operation of the heat pump (100) a steam flow in the intercooler (42) takes place from bottom to top. Heat pump (100) to Claim 9 , in which the intercooling space (43) is formed from an upper element and a lower element, wherein the upper element is connected to the outlet (77-1) of the first spiral casing (78-1) and the lower element is connected to the inlet (79-2) of the second spiral casing (78-2), and wherein the two elements are connected to one another, in particular directly connected to one another, and/or wherein in the operating direction of the heat pump (100), the intercooler (42) further comprises the intercooling collecting tank (44) which is arranged below the bottom of the intercooling space (43) and via which a pipeline is connected to the intercooling space (43), or is integrally connected to the intercooling space (43), wherein a pump is provided for pumping coolant from the intercooling collecting tank (44) into the intercooling space (43). Heat pump (100) to Claim 9 or 10 , in which the outlet (77-1) of the first spiral casing (78-1) is designed as a pipe connection which is attached eccentrically to the upper element of the intermediate cooling chamber (43) with respect to a central axis of the intermediate cooling chamber (43), so that the axis of the pipe connection passes the central axis of the intermediate cooling chamber (43) without an intersection point, wherein the upper element of the intermediate cooling chamber (43) is designed substantially cylindrically, wherein in particular the outer surface of the pipe connection is attached to the outer part of the cylindrically designed intermediate cooling chamber (43) Heat pump (100) according to one of the Claims 9 until 11 , in which the intercooler (42) has one or more cooling rods which extend in the intercooling space (43) from top to bottom in the operating direction of the heat pump (100), wherein nozzle openings are perforated in a lower region of the one or more cooling rods and fewer or no nozzle openings are perforated in an upper region, wherein a coolant supply line is designed to supply coolant to the one or more cooling rods at the upper region, so that the coolant can be sprayed through the nozzle openings into the intercooling space (43) during operation of the heat pump (100). Heat pump (100) to Claim 12 , in which the one or more cooling rods are closed in the operating direction of the heat pump (100) below the nozzle openings, in particular in which the one or more cooling rods are squeezed together below the nozzle openings, and/or in which the one or more cooling rods are made of stainless steel, copper or plastic, and/or in which the one or more cooling rods are connected via one or more base elements to a cover element of the upper element of the intermediate cooling space (43), wherein the base elements extend through the cover element and have coolant connections outside the intermediate cooling space (43), and/or wherein the one or more cooling rods are attached to the base elements, which are connected to the cover element of the intermediate cooling space (43), by one or more cutting ring connections. Heat pump (100) to Claim 12 or 13 , wherein the one or more cooling rods have no perforations in one section and have the perforations in another section, wherein the one upper section is dimensioned for indirect cooling and the other lower section is dimensioned for direct cooling, and/or wherein the upper section is longer than the lower section, and/or wherein the one or more cooling rods have a more inhomogeneous surface in the upper section compared to the lower section. Heat pump (100) according to one of the Claims 9 until 11 , in which the intermediate cooling space (43) has one or more coiled cooling tubes, or a heat pump (100) according to one of the Claims 12 until 14 , in which the one or more cooling rods are designed as coiled cooling tubes, wherein the one or more coiled cooling tubes has or have an end arranged in the intermediate cooling space (43), which is or are arranged such that cooling liquid emerging through the end or ends can be sprayed from bottom to top in the operating direction of the heat pump (100) into the intermediate cooling space (43), or wherein the one or more coiled cooling tubes has or have nozzle openings which are designed to spray coolant from bottom to top into an intermediate cooling space (43). Heat pump (100) according to one of the preceding claims, wherein the second spiral casing (78-2) has a second outlet pipe, wherein the intercooler (42) has an intercooler outlet pipe (45) which opens into the condenser (30), and wherein the second outlet pipe is connected to the first intercooler outlet pipe (45). Heat pump (100) according to one of the preceding claims, which has a bypass pipe (84), wherein a first end of the bypass pipe (84) opens into the condenser (30), wherein a second end of the bypass pipe opens into the evaporator (10), and wherein the second end of the bypass pipe (84) opens into the evaporator (10) below a sprinkler in the evaporator (10) and above a level of an evaporator sump (16), and/or wherein the first end of the bypass pipe (84) opens into the condenser (30) below the upper end of the condenser (30) and above the level of the condenser sump (36). Heat pump (100) according to one of the preceding claims, wherein the second spiral casing (78-2) has an inlet connection (26) which is connected to a connecting pipe (28), wherein a further droplet separator (55) is formed in the connecting pipe (26) in order to reduce or eliminate working fluid droplets in a vapor flow into the second spiral casing (78-2). Heat pump (100) according to one of the preceding claims, in which the first spiral housing (78-1) and/or the second spiral housing (78-2) is attached to a frame (40) via at least one elastic damping element (94), and in which a securing element (95) is arranged between the frame (40) and the first spiral housing (78-1) and/or the second spiral housing (78-2) in order to hold the first spiral housing (78-1) and/or the second spiral housing (78-2) substantially in place, in particular within the frame (40), in the event of destruction of the at least one elastic damping element (94). Heat pump (100) according to one of the preceding claims, in which the first spiral housing (78-1) or the second spiral housing (78-1) has the following features: a central air inlet (56); a lateral air outlet (57); a flat connecting channel (66) which adjoins the air inlet (56); an evolute channel (62) which connects the flat connecting region (66) to the air outlet (57), wherein the evolute channel (62) has a cross-sectional area which increases continuously from the air inlet (56) to the air outlet (57), and wherein the evolute channel (62) is curved and extends from the air inlet (56) to the air outlet (57) by more than 180 degrees and by less than 360 degrees. Heat pump (100) to Claim 20 , in which the evolute channel (62) at the air inlet opening has a diameter of more than 70 mm and less than 110 mm, wherein a diameter of the first spiral housing (78-1) and/or the second spiral housing (78-2) is between 400 and 600 mm, or in which a ratio between the diameter of the first or the second spiral housing (78-2) and the diameter of the air outlet is between 2 and 10, in particular between 3 and 8, in particular between 4 and 7. Heat pump (100) to Claim 20 or 21 , wherein the planar connection region extends around the air inlet by more than 270 degrees and less than 360 degrees, and has a height which is at most half as large as a height of the evolute channel (62) at the air outlet. Heat pump (100) according to one of the Claims 20 until 22 , in which the evolute channel increases in a cross-sectional area along (62) a direction of rotation, wherein the direction of rotation is the same as the direction of rotation of the first compressor motor (17) and/or the second compressor motor (18). Heat pump (100) according to one of the Claims 20 until 23 , in which the first spiral housing (78-1) or the second spiral housing (78-2) is formed from a base plate (64) and an evolute plate (63), the evolute plate (63) having a circumferential U-profile for defining the evolute channel (62), the cross section of which increases continuously, or in which the first spiral housing (78-1) or the second spiral housing (78-2) are formed from a one-piece cast part (65), the evolute channel (62) and the flat connecting channel (66) being defined by a sacrificial core (67). Method for producing a heat pump (100) comprising: an evaporator (10) for evaporating working fluid to obtain a working vapor; a compressor (20) for compressing the working vapor to obtain a compressed working vapor; and a condenser (30) for condensing the compressed working steam, wherein the compressor (20) has a first compressor stage (70-1) and a second compressor stage (70-2), wherein the first compressor stage (70-1) has a first spiral housing (78-1), a first drive motor (80-1) and a first drive shaft (86-1), wherein the second compressor stage (70-2) has a second spiral housing (78-2), a second drive motor (80-2) and a second drive shaft (86-2), with the following steps: arranging the drive shafts (86-1, 86-2) so that the first drive shaft (86-1) is separated from the second drive shaft (86-2), and forming the first drive shaft (86-1) in a vertical direction in an operating direction of the heat pump (100). Method for operating a heat pump (100) with: an evaporator (10) for evaporating working fluid to obtain a working vapor; a compressor (20) for compressing the working vapor to obtain a compressed working vapor; and a condenser (30) for condensing the compressed working steam, wherein the compressor (20) has a first compressor stage (70-1) and a second compressor stage (70-2), wherein the first compressor stage (70-1) has a first spiral housing (78-1), a first drive motor (80-1) and a first drive shaft (86-1), wherein the second compressor stage (70-2) has a second spiral housing (78-2), a second drive motor (80-2) and a second drive shaft (86-2), wherein the first drive shaft (86-1) is separated from the second drive shaft (86-2), with the following steps: Setting up the heat pump (100) in an operating direction; and Operating the heat pump (100) in the operating direction so that the first drive shaft (86-1) is designed to be upright in the operating direction of the heat pump (100).

Images