EP4348051A1

EP4348051A1 - Device for cooling a fluid to be compressed in a compressor and compressor with the device

Info

Publication number: EP4348051A1
Application number: EP22816373.9A
Authority: EP
Inventors: Felix Girmscheid; Jörn Fröhling; Florian Bieregger
Original assignee: Hanon Systems Corp
Current assignee: Hanon Systems Corp
Priority date: 2021-06-01
Filing date: 2022-05-24
Publication date: 2024-04-10
Also published as: WO2022255714A1; CN116964329A; KR20230130738A; DE102022106259A1

Abstract

The invention relates to a device (10, 10-1, 10-2, 10-3, 10-4, 10-5) for cooling a fluid to be compressed in a compressor (1), in particular a refrigerant, with a heat carrier fluid. The device (10, 10-1, 10-2, 10-3, 10-4, 10-5) has at least one first flow channel (11, 11-1, 11-2, 11-5) for guiding the fluid, at least one second flow channel (12, 12-1, 12-2, 12-3, 12-5) for guiding the heat carrier fluid and an inlet (13) and an outlet (14) for the heat carrier fluid.

Description

DEVICE FOR COOLING A FLUID TO BE COMPRESSED IN A COMPRESSOR AND COMPRESSOR WITH THE DEVICE

The invention relates to a device for cooling a fluid to be compressed in a compressor, in particular a refrigerant, with a heat carrier fluid. The device has a first flow channel for guiding the fluid to be compressed in the compressor, a second flow channel for guiding the heat carrier fluid and an inlet and an outlet for the heat carrier fluid. The invention also relates to a compressor for compressing a vaporous fluid, in particular the refrigerant, and a method for operating the compressor. The compressor can be employed in the refrigerant circuit of an air-conditioning system of a motor vehicle.

From the prior art, compressors for mobile applications, in particular for air-conditioning systems of motor vehicles, for transporting refrigerant through a refrigerant circuit, also referred to as refrigerant compressor, are known. Such compressors are driven either via a pulley which is connected to a drive aggregate of the motor vehicle via a belt, or electrically and are often formed as a piston compressor with a variable stroke volume or as a scroll compressor, independent of the refrigerant.

Thus, for example, traditional electrically driven scroll compressors have an electric motor for driving a compression mechanism. The electric motor and the compression mechanism formed with a fixed and an orbiting spiral are arranged within a volume enclosed by a housing. In doing so, the housing can be formed of several parts, in particular of a housing element for receiving the electric motor and a housing element for receiving the compression mechanism, and preferably from a metal, in particular from an aluminum. The orbiting spiral of the compression mechanism, in which a vaporous fluid, specifically a refrigerant, is compressed, is driven via a drive shaft connected to the electric motor.

In the electrically driven refrigerant compressors known from the prior art, both the electric motor and the associated control elements or the power electronics are cooled by means of the refrigerant drawn into the housing, also referred to as suction gas. Furthermore, further heat is transferred to the suction gas heated this way through heat conduction within the wall of the housing before the suction gas flows into the compression mechanism and is then compressed in the compression mechanism.

The heat received by the refrigerant influences the density of the drawn refrigerant and thus the efficiency during operation of the compressor. The more heat is transferred to the refrigerant before entering the compression mechanism, the higher the temperature and the specific volume and the lower the density of the refrigerant in the suction state. A higher temperature of the drawn refrigerant also causes a higher temperature of the refrigerant at the outlet of the compressor. The higher temperatures of the refrigerant at the outlet of the compressor, on the other hand, cause an intense heat conduction within the wall of the housing and thus a stronger heating of the suction gas.

Thus, for example, when compressing carbon dioxide as a refrigerant, the temperature of the refrigerant at the outlet of the compressor can be up to 175°C, which places very high requirements on the refrigerant lines, in particular the flexible refrigerant lines, at the outlet of the compressor.

In order to protect temperature-critical components, in particular the refrigerant circuit, the power consumption of the electrically driven compressor is reduced when the temperature of the refrigerant at the outlet of the compressor is too high, specifically when a predetermined limit temperature is exceeded. Consequently, the refrigerant circuit is power-regulated or down-regulated, in particular when employing carbon dioxide as a refrigerant.

The down-regulation of the power of the compressor, on the other hand, leads to a noticeable reduction of a thermal comfort within the passenger compartment when employing the compressor in a refrigerant circuit of an air-conditioning system of a motor vehicle.

The object of the invention is the provision of a device for cooling a fluid to be compressed in a compressor, specifically a vaporous fluid, as a refrigerant in a refrigerant compressor. The compressor should in particular be operable with avoidance of a down-regulation of the power due to too high temperatures of the compressed fluid and with maximum efficiency. The heat discharged by the fluid is to be usable within a connected system, for example an air-conditioning system or a thermal management system of a motor vehicle. The device should be formed having a minimum installation space and in a compact manner and be able to be produced in a simple and cheap manner.

The object is achieved by the subject matters with the features of the independent claims. Further developments are stated in the dependent claims.

The object is achieved by a device according to the invention for cooling a fluid to be compressed in a compressor, in particular a refrigerant, with a heat carrier fluid. The device has at least one first flow channel for guiding the fluid to be compressed in the compressor, at least one second flow channel for guiding the heat carrier fluid and an inlet and an outlet for the heat carrier fluid.

According to the concept of the invention, a core element is formed such that the device for cooling the compressed fluid with the core element is arrangeable on a longitudinal axis between two housing elements of a modular compressor or integrable into a housing of the compressor as a separate component. As the device is in particular provided for cooling the already compressed fluid, the device is arranged in the flow direction of the fluid in the assembled state of the compressor downstream of a compression mechanism.

The arrangement between two housing elements of a modular compressor enables a retrofitting of the device into conventional compressors.

The outer contours and dimensions of the core element and the housing elements can correspond to one another. In doing so, the outer contours and dimensions of the core element and the housing elements preferably correspond.

According to a further development of the invention, the core element has the shape of a plate, in particular of a disc. The inlet and the outlet for the heat carrier fluid are preferably respectively formed as a stub and arranged on an outer casing surface of the core element.

The core element preferably has at least one through opening for the compressed fluid which runs in the direction of the longitudinal axis which corresponds to an axis of symmetry of the plate or the disc.

According to a preferred design of the invention, the core element is formed with a constant wall thickness in the direction of the longitudinal axis in the region of an outer circumference and with a flat depression of uniform depth in the direction of the longitudinal axis on at least one lateral surface in a center of the surface. A flat depression is understood to be a surface which is offset in the direction of the longitudinal axis and to the interior of the outer lateral surface in the direction of the longitudinal axis. The planes in which the outer lateral surface and the surface of the depression are spanned are oriented parallel to one another and arranged spaced apart from one another.

Alternatively, the core element can be formed as a ring circumscribing an outer circumference with a structure of stacked sheet-shaped plates formed in the center.

An advantage of the invention is that the core element has recesses on the at least one lateral surface which respectively extend into the core element starting from the surface. In doing so, the recesses are in particular formed on the at least one lateral surface in the region of the flat depression.

According to a further development of the invention, at least one plate-shaped, in particular disc-shaped intermediate element is provided, a first side of which bears against the at least one lateral surface of the core element in a plane spanned perpendicular to the longitudinal axis and covers the recesses in a fluid-tight manner. The plate-shaped intermediate element preferably has planar surfaces.

In doing so, the recesses covered with the intermediate element form the second flow channels of the heat carrier fluid. The second flow channels preferably respectively extend from an inlet distribution connected to the inlet to an outlet opening connected to the outlet and can be charged with heat carrier fluid in parallel.

According to a further advantageous design of the invention, the outer contours and dimensions of the at least one intermediate element and of the at least one depression correspond to one another such that the intermediate element is arranged within the depression. The at least one intermediate element can in particular have the shape of a planar, circular sheet and the at least one depression can have the shape of a circle. In doing so, the outer diameter of the intermediate element can correspond to an outer diameter of the depression plus a clearance for assembly and an extension of the depression in the direction of the longitudinal axis can correspond to a wall thickness of the intermediate element.

In the alternative design of the core element as a ring circumscribing the outer circumference with a structure of stacked sheet-shaped plates formed in the center, the outer contours and dimensions of the at least one intermediate element and of an inner casing surface of the ring of the core element circumscribing the outer circumference can be formed corresponding to one another.

A further advantage of the invention is that the at least one intermediate element has at least one through opening for the compressed fluid running in the direction of the longitudinal axis.

According to a further development of the invention, at least one plate-shaped outer element is formed with formations and which bears against a second side of the at least one intermediate element in a plane spanned perpendicular to the longitudinal axis. In doing so, the formations formed in the outer element are covered by the intermediate element - as fluid-tight as possible - such that the first flow channels are formed.

The core element is provided with a respective depression of uniform depth in the direction of the longitudinal axis and recesses in particular on both lateral surfaces in the center. In doing so, the recesses are respectively covered in a fluid-tight manner with a respective first side of an intermediate element of an intermediate element arranged in the depression. Furthermore, an outer element with formations bears against the respective second sides of the intermediate elements such that the formations formed in the outer element are covered - as fluid-tight as possible - by the intermediate element.

The device for cooling the fluid to be compressed in the compressor advantageously is a stacked plate heat exchanger with a performance which is scalable by the number of the stacked plates and a defined size. The device is preferably formed as a soldered or welded, in particular laser welded component of extruded and shaped elements of an aluminum. In doing so, additional sealing elements between the heat carrier fluid circuit and the fluid to be compressed in the compressor can be omitted.

Within the device, the heat carrier fluid and the fluid to be compressed in the compressor are preferably guided in a counter current or a cross counter current.

A coolant or the fluid to be compressed in the compressor, in particular the refrigerant, can be employed as the heat carrier fluid. When employing a coolant as the heat carrier fluid, the device is formed as a refrigerant-coolant heat exchanger. When using the refrigerant as a heat carrier fluid, the device corresponds to a refrigerant-refrigerant heat exchanger which is then operated as an internal circuit heat exchanger, for example.

According to a further preferred design of the invention, a first outer element is formed with an inlet opening and a second outer element is formed with an outlet opening for the compressed fluid.

The first outer element can have at least one branch such that the first flow channels respectively extend from the inlet opening to at least one branch and are charged with fluid parallel to one another. The second outer element can have at least one branch such that the first flow channels respectively extend from at least one branch to the outlet opening and are charged with fluid parallel to one another.

The at least one through opening for the compressed fluid formed in the core element, the at least one through opening for the compressed fluid formed in the intermediate element and the at least one branch provided in the first outer element and the at least one branch provided in the second outer element are in particular arranged in alignment with one another and thus along an axis such that the compressed fluid flows out of the branch of the first outer element and flows into the branch of the second outer element on a straight flow path through the through openings of the intermediate element and the core element without any deflections.

When more than one branch is formed within the outer elements, a through opening in the intermediate element, a through opening in the core element and a branch in the second outer element are assigned to each branch of the first outer element. When more than one intermediate element is formed, each intermediate element is provided with corresponding through openings.

According to an alternative design of the invention, the core element is formed in the shape of a hollow circular cylinder. In doing so, preferably a wall element shaped as a hollow circular cylinder is arranged within the core element and a cylinder-shaped central element is arranged within the wall element, which are oriented coaxially to the longitudinal axis. A diameter of an inner casing surface of the core element can correspond to a diameter of an outer casing surface of the wall element, while a diameter of an inner casing surface of the wall element can correspond to a diameter of a casing surface of the central element such that the respective casing surfaces bear against one another in a fluid-tight manner.

The wall element advantageously has a recess on the outer casing surface for the second flow channel of the heat carrier fluid. Alternatively, the recess for the second flow channel can also be formed on the inner casing surface of the core element.

The wall element preferably has a recess on the inner casing surface for the first flow channel. Alternatively, the recess for the first flow channel can also be provided on the casing surface of the central element.

A further advantage of the invention is that the recesses of the flow channels are formed in the shape of a circumferentially running helical groove, in particular an axial spiral, whose inlet and outlet are spaced apart from one another in the direction of the longitudinal axis.

According to a further preferred design of the invention, a control element, in particular a valve, for controlling the mass flow of the heat carrier fluid through the device is integrated within the core element.

The object is also achieved by a compressor according to the invention for compressing a vaporous fluid, in particular a refrigerant. The compressor has a housing, a drive device arranged within the housing and a compression mechanism driven by the drive device.

According to the concept of the invention, a device according to the invention for cooling the fluid is formed in the flow direction of the fluid downstream of the compression mechanism. Consequently, the compressor has an integrated heat exchanger.

According to a further development of the invention, the compression mechanism has an orbiting spiral and a fixed spiral. In doing so, the device for cooling the fluid which is in particular arranged between an outlet for the fluid out of the fixed spiral and an outlet of the compressor is formed as a separate component between housing elements of the housing arranged on a longitudinal axis or integrated into the housing of the compressor or formed as a component of the fixed spiral. When forming the device as a component of the fixed spiral, the fixed spiral and thus the fluid transported within the spiral are directly cooled during compression.

The device for cooling the fluid preferably has an extension in the direction of the longitudinal axis in the range from 25 mm to 30 mm such that the installation space of the compressor is enlarged only slightly through integration of the device.

According to an advantageous design of the invention, the device for cooling the fluid is arranged within a volume charged under a high pressure level of the fluid such that a pressure prevalent within the first flow channel for guiding the fluid and a pressure prevalent within a volume which borders a wall delimiting the flow channel from the outside, are substantially equal in size. The small pressure difference over the wall limiting the flow channel only requires a very small wall thickness of the outer elements. Only the wall enclosing the second flow channel for guiding the heat carrier fluid is to be constructed in a manner which is robust to withstand the high pressure of the fluid.

The object is also achieved by a method according to the invention for operating the compressor. In doing so, a performance of the device for cooling the fluid to be compressed in the compressor is regulated via a mass flow of the heat carrier fluid through the device and a supply temperature of the heat carrier fluid such that an outlet condition of the compressed fluid at an outlet of the compressor is set independent of an operating condition of the compressor.

The advantageous design of the invention enables the use of the compressor for a refrigerant of a refrigerant circuit of an air-conditioning system of a motor vehicle.

The device according to the invention for cooling a fluid to be compressed in a compressor or the compressor according to the invention for compressing a vaporous fluid with the device have, in summary, further several advantages compared to the devices of the prior art:

- reduction of the mean compressor temperature, in particular the temperature of the compressed fluid at the outlet of the compressor without reduction of the performance in the refrigerant circuit - for example, the temperature at the outlet of the compressor with carbon dioxide as a refrigerant is below 100°C instead of 175°C without the device according to the invention, thus

* reduced temperature requirement for refrigerant lines within the circuit, in particular downstream of the compressor, associated with lowering of the system costs through the employment of low temperature refrigerant lines at the high pressure side of the circuit,

* increasing the volumetric and the isotropic efficiency, (in particular when cooling the fixed spiral in the scroll compressor) - higher cooling performance in the system or lower drive performance of the compressor for comparable cooling performances, for example, enhancing the mass flow by 4　% in case of reduction of the drive performance by 6　% with carbon dioxide as the fluid to be compressed,

* increasing the electric efficiency due to the indirect cooling of the inverter and the electric motor of the drive device of the compressor,

* avoiding performance down-regulations and speed reductions at the compressor due to too high temperatures of the compressed fluid at the outlet of the compressor,

* reduction of the heat conductance in the direction of the longitudinal axis of the compressor through thermodynamic disruption of the conductance,

* reduction of the temperature of the compressed fluid at the inlet into the gas cooler/condenser due to a reduced heat load or gas cooler/condenser with lower performance as a significant part of the heat in the compressor is discharged via the heat carrier fluid circuit or no external gas cooler/condenser is required,

* maximum lifetime of internal components;

- avoiding losses through the decoupling of the heat into the heat carrier fluid circuit,

- targeted regulation of the mass flow of the heat carrier fluid and targeted use of the compressor waste heat for heating, for example of the battery, thus increasing the reach of motor vehicles driven by an electric motor and omitting additional electric heating,

- optimizing the thermal management for more comfort of the vehicle passengers, and

- decreasing the noise emission or the sound emission and the pressure pulsations in the system through the device for cooling as a result of the use of the inner cavity volume as a sound absorber.

Further details, features and advantages of designs of the invention result from the following description of example embodiments with reference to the accompanying drawings. It is shown:

Fig. 1: an electrically driven compressor with a device integrated into the compressor for cooling a fluid to be compressed in the compressor in a sectional representation,

Fig. 2: components of the compressor with a first embodiment of the integrated device for cooling the fluid in a perspective view,

Figs. 3a and 3b: the components of the compressor with the integrated device for cooling the fluid from Fig. 2 in a perspective and a lateral sectional representation,

Fig. 4a: the first embodiment of the device for cooling the fluid to be compressed in the compressor from Figs. 3a and 3b in the assembled state in a perspective view,

Figs. 4b and 4c: the first embodiment of the device for cooling the fluid to be compressed in the compressor from Figs. 3a and 3b with a core element, intermediate elements and outer elements respectively in a perspective exploded representation,

Figs. 5a to 5e: different embodiments in a combination of the first embodiment of the device from Fig. 2, a second embodiment of the device, a third embodiment of the device, a fourth embodiment of the device and a fifth embodiment of the device,

Figs. 6a and 6b: the core element of the second embodiment of the device for cooling the fluid to be compressed in the compressor from Fig. 5b with an inlet and an outlet of a heat carrier fluid respectively as an individual element in a perspective lateral view, and

Figs. 6c and 6d: the core element from Figs. 6a and 6b with the flow directions of the fluid to be compressed in the compressor and the heat carrier fluid respectively in a lateral view.

Fig. 1 indicates an electrically driven compressor 1 of a vaporous fluid, specifically for an air-conditioning system of a motor vehicle for transporting refrigerant through a refrigerant circuit, with a drive device 4 arranged in a housing 2, in particular an electric motor, for driving a compression mechanism 5 and a device 10 integrated in the compressor 1 for cooling the fluid to be compressed in the compressor 1 in a sectional representation. The housing 2 has several housing elements 2a, 2b, 2c, 2d.

The electric motor 4 and the compression mechanism 5 formed as a scroll compressor with an orbiting spiral 5a and a fixed spiral 5b are arranged within a volume enclosed by the housing 2. The spirals 5a, 5b are preferably formed from a metal, in particular from an aluminum or a steel. In doing so, a first housing element 2a for receiving the electric motor 4, a second housing element 2b for receiving a transmission mechanism for transmission of the movement from a rotor of the electric motor 4 to the orbiting spiral 5a of the compression mechanism 5 and a third housing element 2c for receiving the compression mechanism 5 are preferably formed from a metal, in particular from an aluminum.

The orbiting spiral 5a of the compression mechanism 5 in which the vaporous fluid, specifically the refrigerant, is compressed, is driven via a drive shaft connected to the rotor of the electric motor 4. The rotor of the electric motor 4, the drive shaft and the orbiting spiral 5a are arranged on a common axis of rotation which corresponds to the longitudinal axis 6 of the compressor 1.

The housing 2 is closed via a fourth housing element 2d. The fourth housing element 2d has a refrigerant outlet 7 through which the compressed refrigerant flows out of the compressor 1 at a high pressure level as a so-called hot gas with high temperature.

The housing elements 2a, 2b, 2c, 2d oriented on the longitudinal axis 6 and enclosing the common volume are coupled to one another via a connection arrangement 3. In doing so, the first housing element 2a and the fourth housing element 2d respectively are arranged on an outside formed in the axial direction.

The connection arrangement 3 is formed as a screw connection with through openings and blind holes with inner threading. In doing so, the blind holes with inner threading are exclusively provided on the first housing element 2a, while the other housing elements 2b, 2c, 2d are respectively formed with through openings for receiving screws and threaded bolts. The through openings which are correspondingly oriented in alignment with one another respectively enable the insertion of the screws or threaded bolts which are respectively received by the first housing element 2a within a blind hole. The housing elements 2a, 2b, 2c, 2d are screwed together in such a way and the housing 2 is closed.

In the direction of the longitudinal axis 6, the device 10 for cooling the fluid to be compressed in the compressor 1 is arranged between the third housing element 2c and the fourth housing element 2d. The device 10 has an outer diameter which substantially corresponds to the outer diameters of the adjacent housing elements 2c, 2d. Furthermore, the device 10 is also formed with through openings as elements of the connection arrangement 3 and for inserting the screws or threaded bolts such that the device 10 together with the housing elements 2a, 2b, 2c, 2d is connected to form the compressor 1. The device 10 is integrated within the compressor 1.

In doing so, the device 10 for cooling the fluid to be compressed in the compressor 1 is consequently formed between the compression mechanism 5 received in the third housing element 2c with the refrigerant outlet 5c and the fourth housing element 2d with the refrigerant outlet 7 of the compressor 1. The refrigerant is predominantly cooled after the operation of the compression to the high pressure level and thus as a hot gas before the refrigerant flows out of the compressor 1 through the refrigerant outlet 7.

After leaving the compression mechanism 5, the refrigerant is guided through the refrigerant outlet 5c in first flow channels 11 through the device 10, while a heat carrier fluid accepting the heat from the refrigerant flows through second flow channels 12 of the device 10 formed as a heat exchanger.

In Fig. 2, the third housing element 2c and the fourth housing element 2d are shown as components of the compressor 1 with a first embodiment of a device 10-1 for cooling the fluid to be compressed in the compressor 1 arranged between the housing elements 2c, 2d and thus integrated in the compressor 1 in a perspective view. In doing so, the third housing element 2c is represented with a see-through wall to better identify the device 10-1. In Figs. 3a and Fig. 3b, the components of the compressor 1 with the integrated device 10-1 according to Fig. 2 are indicated in a perspective and a lateral sectional view.

The device 10-1 has an inlet 13 and an outlet 14 for the heat carrier fluid, in particular a coolant. The inlet 13 and the outlet 14 of the heat carrier fluid are respectively formed as stubs and arranged on an outer casing surface of a plate-shaped core element 15-1. In doing so, the outer diameter of the plate-shaped core element 15 1 substantially corresponds to the outer diameters of the bordering housing elements 2c, 2d. Through openings 16 of the device 10-1 for inserting the screws or threaded bores of the connection arrangement 3 are provided on the core element 15-1.

The plate-shaped core element 15-1 is formed with recesses on the lateral surfaces which respectively extend into the core element 15-1 starting from the corresponding surface. The recesses are closed by plate-shaped intermediate elements 18-1a, 18-1b bearing against the surfaces in the direction of the longitudinal axis. The intermediate elements 18-1a, 18-1b bear against the surfaces of the core element 15-1 in planes respectively spanned perpendicular to the longitudinal axis 6 and cover the recesses. The recesses which are closed this way and provided in the core element 15 1 form the second flow channels 12-1 of the heat carrier fluid. The intermediate elements 18 1a, 18-1b respectively have the shape of a planar, circular sheet.

The core element 15-1 has a constant wall thickness in the direction of the longitudinal axis 6 in particular in the region of the outer diameter. In the center of the core element 15-1, the core element 15-1 is formed with a circular depression 19-1 of uniform depth on both surfaces. The outer diameter of the circular depression 19-1 respectively corresponds to the outer diameters of the circular intermediate element 18-1a, 18-1b, while the extension of the depression 19-1 in the direction of the longitudinal axis 6, which corresponds to the depth, corresponds to the thickness of the sheet-shaped intermediate element 18-1a, 18-1b. Consequently, the intermediate elements 18-1a, 18-1b can respectively be arranged with a surface facing to the outside in the direction of the longitudinal axis 6 and thus away from the core element 15-1 in alignment within the core element 15-1. The core element 15-1, in connection with the intermediate elements 18-1a, 18-1b arranged on the core element 15-1, then respectively has a planar and closed surface in the direction of the longitudinal axis 6.

The core element 15-1 is arranged between end sides of the adjacent housing elements 2c, 2d in the region of the outer diameter, while the region of the circular depressions 19-1 of the core element 15-1, in which the intermediate elements 18-1a, 18-1b are positioned, are respectively arranged in a volume enclosed by the housing elements 2c, 2d.

Plate-shaped outer elements 17a, 17b bear against the surfaces of the intermediate elements 18-1a, 18-1b which are oriented in alignment with the core element 15-1. The outer elements 17a, 17b formed as sheets have specifically created formations, in particular by means of thermoforming, which in connection with the planar surface of the intermediate element 18-1a, 18-1b provide the first flow channels 11-1 for the refrigerant in a circumferentially enclosed manner. The formations created by means of thermoforming are circumferentially closed by the plate-shaped intermediate elements 18-1a, 18-1b bearing against in the direction of the longitudinal axis 6. The intermediate elements 18-1a, 18-1b, on the other hand, bear against the outer elements 17a, 17b in planes respectively spanned perpendicular to the longitudinal axis 6 and cover the formations created by means of thermoforming. The thus closed regions formed in the outer elements 17a, 17b represent the first flow channels 11-1 of the refrigerant.

The device 10-1 for cooling the fluid to be compressed in the compressor 1 is formed as a plate heat exchanger, specifically as a refrigerant-coolant heat exchanger, with the plate-shaped core element 15-1, the sheet-shaped intermediate elements 18-1a, 18-1b, interior surfaces of which bear against both sides of the core element 15-1, and the outer elements 17a, 17b bearing against outer surfaces of the intermediate elements 18-1a, 18-1b. The formation as a plate heat exchanger enables a simple scaling of the heat performance to be transmitted. The heated coolant can be used for heating other components, for example the air-conditioning system or the drive train of the motor vehicle, such as the battery, such that other components for heating, such as an electric PTC heater, can be omitted.

According to a non-represented alternative embodiment, the device 10-1 for cooling the fluid to be compressed in the compressor 1 is integrated within the housing 2 itself, in particular within the fourth housing element 2d. The device 10-1 and the housing element 2d are integrally formed.

In Fig. 4a, the first embodiment of the device 10-1 for cooling the fluid to be compressed in the compressor 1 from Figs. 3a and 3b in the assembled state is represented in a perspective view, while in Figs. 4b and 4c, the first embodiment of the device 10-1 with the core element 15-1, the intermediate elements 18-1a, 18-1b and the outer elements 17a, 17b are respectively indicated in a perspective exploded view. In doing so, in particular in Fig. 4c, flow paths of the refrigerant and of the heat carrier fluid through the device 10-1 are suggested.

The refrigerant compressed to the high pressure level flows through an inlet opening 20 formed in the first outer element 17a in the flow direction 26 into the device 10-1 and out of the device 10-1 through an outlet opening 21 formed in the second outer element 17b. After flowing in, the refrigerant is evenly distributed to the first flow channels 11-1 formed between the first outer element 17a and the first intermediate element 18-1a.

The first flow channels 11-1, which respectively extend from the inlet opening 20 to a branch 22a, are charged with refrigerant in parallel. The first outer element 17a has two branches 22a such that the refrigerant mass flow is divided into two partial mass flows after flowing through the inlet opening 20. A first partial mass flow of the refrigerant is guided through first flow channels 11-1 ending at a first branch 22a, while a second partial mass flow of the refrigerant is guided through first flow channels 11-1 ending at a second branch 22a.

Afterwards, the partial mass flows of the refrigerant flow through through openings 23a formed in the first intermediate element 18-1a out of the first flow channels 11-1 and through through openings 24 formed in the core element 15-1 and through through openings 23b formed in the second intermediate element 18-1b to branches 22b formed in the second intermediate element 18-1b.

The through openings 23a, 23b of the intermediate elements 18-1a, 18-1b, the through openings of the core element 15-1 and the branches 22a, 22b of the outer element 17a correspond to one another with regard to arrangement and flow cross-section. In doing so, respectively one branch 22a, 22b, one through opening of an intermediate element 18-1a, 18-1b and one through opening 24 of the core element 15-1 are arranged in alignment with one another.

The first flow channels 11-1 formed between the second outer element 17b and the second intermediate element 18-1b respectively extend from a branch 22b to the outlet opening 21 and are charged with refrigerant in parallel. The second outer element 17b has two branches 22b like the first outer element 17a such that the two partial mass flows of the refrigerant are respectively evenly distributed to the first flow channels 11-1. In doing so, the first partial mass flow of the refrigerant is guided into first flow channels 11-1 opening into a first branch 22a, while the second partial mass flow of the refrigerant is guided into first flow channels 11-1 opening into a second branch 22b. The partial mass flows of the refrigerant are combined at the outlet opening 21. The refrigerant mass flow cooled during the flow through the device 10-1 flows through the outlet opening 21 out of the device 10-1 in the flow direction 26. The heat was transferred from the refrigerant to the heat carrier fluid.

The heat carrier fluid flows through the first inlet 13 formed as a stub into the device 10-1 in the flow direction 25 and out of the device 10-1 through the outlet 14 which is formed as a stub as well. After flowing in, the heat carrier fluid is evenly distributed to the second flow channels 12-1 respectively formed between the core element 15-1 and the intermediate elements 18-1a, 18-1b. In doing so, second flow channels are provided on both sides of the core element 15-1 such that the mass flow of the heat carrier fluid is divided into two partial mass flows after flowing through the inlet 13.

The second flow channels 12-1, which respectively extend from an inlet distribution 12-1a connected to the inlet 13 to an outlet opening 12-1b connected to the outlet 14, are charged with heat carrier fluid in parallel. After flowing through the inlet 13, the two partial mass flows of the heat carrier fluid are respectively divided into the second flow channels 12-1 at the inlet distribution 12-1a. The two partial mass flows of the heat carrier fluid respectively combined at the outlet opening 12-1b are together discharged out of the device 10-1 through the outlet 14. In doing so, the mass flow of the heat carrier fluid heated during the flow through the device 10-1 flows out of the device 10-1 in the flow direction 25.

In Figs. 5a to 5e, different embodiments of the device 10 for cooling a fluid to be compressed in the compressor are shown in a combination of the first embodiment of the device 10-1 from Fig. 2, a second embodiment of the device 10-2, a third embodiment of the device 10-3, a fourth embodiment of the device 10-4 and a fifth embodiment 10-5. Same elements and components of the devices 10, 10-1, 10-2, 10-3, 10-4, 10-5 are indicated with same reference numerals. Concerning their formation and functioning, reference is made to the explanations above.

The major differences between the devices 10-1, 10-2, 10-3 from Figs. 5a to 5c are in the formation of the plate-shaped core element 15-1, 15-2, 15-3 with the recesses for the second flow channels 12-1, 12-2, 12 3 of the heat carrier fluid and the recesses for the first flow channel 11-2 in the case of the core element 15-2 of the device 10-2.

The recesses of the second flow channels 12-1 of the first embodiment of the device 10-1 are, as explained for Figs. 4b and 4c, arranged on both sides of the core element 15-1 and respectively extend from the inlet distribution 12-1a to the outlet opening 12-1b in parallel to one another. Therefore, the recesses of the second flow channels 12-1 provided on both sides of the core element 15-1 are formed independent from one another, in particular without any intermediate connections through the core element 15-1. The heat carrier fluid is respectively guided in a radial flow in the second flow channels 12-1.

Compared to the first embodiment of the device 10-1 according to Fig. 5a, the recesses of the second flow channel 12-2 of the second embodiment of the device 10-2 according to Fig. 5b are formed such that the heat carrier fluid is guided through the device 10-2 as an undivided and thus integral mass flow. In doing so, the mass flow of the heat carrier fluid is guided in recesses on both sides of the core element 15-2 which are further connected to one another via intermediate connections through the core element 15 2 running in particular in the direction of the longitudinal axis 6. Consequently, the mass flow of the heat carrier fluid is guided along both sides of the core element 15-2 in an alternating manner, wherein the change of the sides is through the intermediate connections formed in the core element 15-2. When flowing through the second flow channel 12-2, the heat carrier fluid is guided in the radial direction and the axial direction in an alternating manner.

Furthermore, the refrigerant, compared to the first embodiment of the device 10-1 according to Fig. 5a, does not flow through the through openings 24 by the shortest flow path in the axial direction through the core element 15-2, but is, like the heat carrier fluid, guided in recesses through a first flow channel 11-2 provided in the core element 15-2 on both sides of the core element 15-2. The recesses are connected to one another via intermediate connections through the core element 15 2 running in the direction of the longitudinal axis 6. Thus, the mass flow of the refrigerant is also guided along both sides of the core element 15-2 in an alternating manner, wherein the change of the sides is through the intermediate connections formed in the core element 15-2.

Compared to the first embodiment of the invention 10-1 according to Fig. 5a, according to which the second flow channels 12-1 are provided on both sides of the core element 15-1 such that the mass flow of the heat carrier fluid is divided into two partial mass flows after flowing through the inlet 13, the recesses of the second flow channels 12-3 of the third embodiment of the device 10-3 according to Fig. 5c are respectively connected to one another through the core element 15 3 in the direction of the longitudinal axis 6. Consequently, the mass flow of the heat carrier fluid is guided through the second flow channel 12 3 as an undivided total mass flow. The intermediate walls delimiting the second flow channels 12-3 are connected to one another and to the core element 15-3 via individual ribs.

A further major difference between the devices 10-1, 10-3 on the one hand and the device 10-2 on the other hand is in the formation of the intermediate elements 18-1a, 18-2a, 18-1b, 18-2b in connection with the depressions 19-1, 19-2 provided in the core elements 15-1, 15-2 for receiving the intermediate elements 18-1a, 18-2a, 18-1b, 18-2b.

While the plate-shaped intermediate elements 18-1a, 18-1b of the devices 10-1, 10-3 from Figs. 5a and 5c respectively have the shape of a planar, circular sheet, the intermediate elements 18-2a, 18 2b of the device 10-2 from Fig. 5b are chamfered to the outside at the outer circumferences respectively in the direction of the longitudinal axis 6, i.e. in the direction of the direction facing away from the core element 15 2, and thus have a significantly larger depth than the intermediate elements 18 1a, 18-1b of the devices 10-1, 10-3, in particular at the outer circumferences. As the depth of the intermediate elements 18 2a, 18-2b respectively corresponds to the extension of the depression 19-2 within the core element 15-2 in the direction of the longitudinal axis 6, the depressions 19-2 also have a larger extension than the depressions 19-1 of the core elements 15-1, 15-3 of the devices 10-1, 10-3. The intermediate elements 18-2a, 18-2b of the device 10-2 can be arranged within the core element 15-2 in alignment with the end faces facing the direction of the longitudinal axis 6 respectively with the surface facing the outside in the direction of the longitudinal axis 6 and thus away from the core element 15-2.

The major difference between the devices 10-1, 10-2, 10-3 from Figs. 5a to 5c on the one hand and the device 10-4 from Fig. 5d on the other hand is in the formation of the core element 15-1, 15-2, 15-3, 15-4 in a massive shape of an individual plate of the devices 10-1, 10-2, 10-3 and as a ring circumscribing the outer circumference with a structure of individual, stacked sheet-shaped plates of the device 10-4 formed in the center. The plates are respectively oriented in a plane oriented perpendicular to the direction of the longitudinal axis 6.

The two plates which are respectively formed as a sheet and arranged at the outer sides of the center of the core element 15-4 in the direction of the longitudinal axis 6 have, similar to the outer elements 17a, 17b, specifically created formations, in particular by means of thermoforming, which respectively provide the second flow channels 12-1 for the heat carrier fluid in connection with the planar surface of the intermediate element 18-2a, 18-2b. The formations are circumferentially closed by the plate-shaped intermediate elements 18-2a, 18-2b respectively bearing against in the direction of the longitudinal axis 6. The intermediate elements 18-2a, 18-2b bear against the plates of the core element 15-4 in planes respectively spanned perpendicular to the longitudinal axis 6 and cover the formations created by means of thermoforming.

In the direction of the longitudinal axis 6, advantageously a planar, sheet-shape plate is arranged between the two plates respectively formed as a sheet with formations, which in particular increases the stability and the manufacturability of the core element 15-4. The individual plates of the core element 15-4 respectively have same outer contours with regard to shape and dimension which correspond to an inner casing surface of the ring of the core element 15 4 circumscribing the outer circumference.

The plate-shaped intermediate elements 18-2a, 18 2b of the device 10-4 from Fig. 5d are, like the intermediate elements 18-2a, 18 2b of the device 10-2 from Fig. 5b, chamfered to the outside at the outer circumferences respectively in the direction of the longitudinal axis 6, in particular in the direction of the direction facing away from the core element 15 4. The intermediate elements 18-2a, 18 2b of the device 10-4 can be arranged in alignment within the ring of the core element 15-2 with the end faces facing the direction of the longitudinal axis 6 respectively with the surfaces facing the outside in the direction of the longitudinal axis 6 and thus facing away from the ring of the core element 15-2 circumscribing the outer circumference.

The major difference between the devices 10-1, 10-2, 10-3 from Figs. 5a to 5c on the one hand and the device 10-5 from Fig. 5e on the other hand is in the formation of the first flow channels 11-1, 11-2, 11 5 for the refrigerant and the recesses for the second flow channels 12-1, 12-2, 12 3, 12-5 of the heat carrier fluid.

Compared to the devices 10-1, 10-2, 10-3, the core element 15 5 of the device 10-5 is substantially formed as a hollow circular cylinder without recesses. Within the core element 15-5, a wall element 27 shaped as a hollow circular cylinder is arranged, while within the wall element 27, a cylinder-shaped central element 28 is arranged. The core element 15-5, the wall element 27 and the central element 28 are aligned coaxially to one another, along the longitudinal axis 6, which corresponds to the axis of symmetry. In doing so, the diameter of the inner casing surface of the core element 15-5 corresponds to the diameter of the outer casing surface of the wall element 27, while the diameter of the inner casing surface of the wall element 27 corresponds to the diameter of the casing surface of the central element 28. The casing surfaces of the core element 15-5, the wall element 27 and the central element 28 bear against one another in a fluid-tight manner.

The outer casing surface of the wall element 27 is formed with a recess for the second flow channel 12-5 of the heat carrier fluid and has a recess for the first flow channel 11-5 of the refrigerant at the inner casing surface. The recess for the second flow channel 12-5 is covered by the core element 15-5 in the radial direction to the outside, in particular by means of the inner casing surface of the core element 15-5. The recess for the first flow channel 11-5 is covered by the central element 28 in the radial direction to the inside, in particular by means of the outer casing surface of the central element 28.

The recesses of the flow channels 11-5, 12-5 and thus the flow channels 11-5, 12-5 themselves are respectively formed in the shape of a helical groove or axial spiral running in the circumferential direction, the inlet and outlet of which are respectively spaced apart from one another in the direction of the longitudinal axis 6. The core element 15-5 of the device 10-5 has, in the direction of the longitudinal axis 6, a larger extension than the core elements 15-1, 15-2, 15-3 of the devices 10-1, 10-2, 10-3. The flow channels 11-5, 12-5 preferably run parallel to one another.

In Figs. 6a and 6b, the core element 15-2 of the second embodiment of the device 10-2 according to Fig. 5b for cooling the fluid to be compressed in the compressor 1 is represented with the inlet 13 and the outlet 14 of the heat carrier fluid respectively as an individual element in a perspective lateral view. In Fig. 6c, the core element 15-2 with the flow direction 29 of the fluid to be compressed in the compressor 1 is indicated in a lateral view, while Fig. 6d shows the core element 15-2 with the flow direction 30 of the heat carrier fluid in a lateral view as well.

The major difference of the core elements 15-1, 15-2 of the devices 10-1, 10-2 is in the formation of the recesses of the second flow channels 12-1, 12-2 of the heat carrier fluid on the one hand and in the formation of the recesses of the first flow channel 11-2 of the refrigerant within the core element 15-2 on the other hand. Same elements and components of the devices 10-1, 10-2 are indicated with same reference numerals. Concerning their formation and functioning, reference is made to the explanations above.

Compared to the first embodiment of the device 10-1 according to Fig. 4b, the second flow channel 12-2 is formed without division into parallel channels in the core element 15-2. The second flow channel 12-2 runs in an alternating manner on both upper surfaces of the core element 15-2 in recesses formed in the surfaces. In doing so, the alternating guidance of the second flow channel 12-2 on the upper surfaces of the core element 15-2 is enabled my means of intermediate connections facing the perpendicular direction to the upper surfaces and thus the direction of the longitudinal axis. The intermediate connections are respectively formed as circular through bores or as through bores in the shape of long holes between the upper sides. The recesses and intermediate connections are arranged with regard to one another such that the heat carrier fluid according to Fig. 6d is guided along both sides of the core element 15-2 in the flow direction 30 in an alternating manner and flows through the core element 15 2 substantially in a zigzag-shaped manner. When flowing through the second flow channel 12-2, the heat carrier fluid is guided in the radial direction and the axial direction in an alternating manner. The flow direction 30 is indicated with the arrows. In doing so, the arrows marked by means of continuous lines represent the flow of the heat carrier fluid at the visible side of the core element 15-2, while the arrows marked by means of dashed lines represent the flow of the heat carrier fluid at the covered side of the core element 15-2.

Furthermore, a first flow channel 11-2 for the refrigerant is provided in the core element 15-2 as well, which is formed in the same manner as the second flow channel 12-2. Consequently, the first flow channel 11-2 also runs in an alternating manner on both upper sides of the core element 15-2 in recesses formed in the surfaces which are connected to one another by means of intermediate connections facing the perpendicular direction to the upper surfaces and thus the direction of the longitudinal axis. The recesses and intermediate connections of the first flow channel 11-2, on the other hand, are arranged with regard to one another such that the refrigerant according to Fig. 6c is guided along both sides of the core element 15-2 in the flow direction 29 in an alternating manner and flows through the core element 15 2 substantially in a zigzag-shaped manner. When flowing through the first flow channel 11-2, the refrigerant is guided in the radial direction and the axial direction in an alternating manner. The flow direction 29, on the other hand, is indicated with the arrows. In doing so, the arrows marked by means of continuous lines represent the flow of the refrigerant at the visible side of the core element 15-2, while the arrows marked by means of dashed lines represent the flow of the refrigerant at the covered side of the core element 15-2.

Thus, the refrigerant is guided through the first flow channels 11-1 formed between the first outer element 17a and the first intermediate element 18-2a, then through the first flow channel 11-2 formed in the core element 15-2 and finally through the first flow channels 11-1 formed between the second outer element 17b and the second intermediate element 18-2b.

List of reference numerals

1 compressor

2 housing

2a first housing element

2b second housing element

2c third housing element

2d fourth housing element

3 connection arrangement

4 drive device, electric motor

5 compression mechanism

5a orbiting spiral

5b fixed spiral

5c refrigerant outlet of the compression mechanism 5

6 longitudinal axis

7 refrigerant outlet of the compressor 1

10, 10-1, 10-2, 10-3, 10-4, 10-5 device

11, 11-1, 11-2, 11-5 first flow channel of the refrigerant

12, 12-1, 12-2, 12-3, 12-5 second flow channel of the heat carrier fluid

12-1a inlet distribution

12-1b outlet opening

13 inlet for the heat carrier fluid

14 outlet for the heat carrier fluid

15-1, 15-2, 15-3, 15-4, 15-5 core element

16 through opening

17a first outer element

17b second outer element

18-1a, 18-2a first intermediate element

18-1b, 18-2b second intermediate element

19-1, 19-2 depression

20 inlet opening for the refrigerant

21 outlet opening for the refrigerant

22a, 22b branch

23a, 23b through opening

24 through opening

25 flow direction of the heat carrier fluid

26 flow direction of the refrigerant

27 wall element

28 central element

29 flow direction of the refrigerant

30 flow direction of the heat carrier fluid

Claims

A device (10, 10-1, 10-2, 10-3, 10-4, 10-5) for cooling a fluid to be compressed in a compressor (1), in particular a refrigerant, with a heat carrier fluid, having at least one first flow channel (11, 11-1, 11-2, 11-5) for guiding the fluid, at least one second flow channel (12, 12-1, 12-2, 12-3, 12-5) for guiding the heat carrier fluid and an inlet (13) and an outlet (14) for the heat carrier fluid, characterized in that a core element (15-1, 15-2, 15-3, 15-4, 15-5) is formed such that the device (10, 10-1, 10-2, 10-3, 10-4, 10-5) with the core element (15-1, 15-2, 15-3, 15-4, 15-5) can be arranged as a separate component on a longitudinal axis (6) between housing elements (2c, 2d) of a modular compressor (1) or can be integrated into a housing of the compressor.
The device (10, 10-1, 10-2, 10-3, 10-4, 10-5) according to claim 1, characterized in that the outer contours and dimensions of the core element (15-1, 15-2, 15-3, 15-4, 15-5) and the housing elements (2c, 2d) are formed corresponding to one another.
The device (10, 10-1, 10-2, 10-3, 10-4) according to claim 1 or 2, characterized in that the core element (15-1, 15-2, 15-3, 15-4) is formed in the shape of a plate.
The device (10, 10-1, 10-2, 10-3, 10-4) according to claim 3, characterized in that the core element (15-1, 15-2, 15-3, 15-4) has at least one through opening (24) for the compressed fluid running in the direction of the longitudinal axis (6).
The device (10, 10-1, 10-2, 10-3, 10-4) according to claim 3 or 4, characterized in that the core element (15-1, 15-2, 15-3) is formed with a constant wall thickness in the direction of the longitudinal axis (6) in the region of an outer circumference and with a flat depression (19-1, 19-2) of uniform depth in the direction of the longitudinal axis (6) on at least one lateral surface in a center, or in that the core element (15-4) is formed as a ring circumscribing an outer circumference with a structure of stacked sheet-shaped plates formed in the center.
The device (10, 10-1, 10-2, 10-3, 10-4) according to one of claims 3 to 5, characterized in that the core element (15-1, 15-2, 15-3, 15-4) has recesses on at least one lateral surface which are formed respectively extending into the core element (15-1, 15-2, 15-3, 15-4) starting from the surface.
The device (10, 10-1, 10-2, 10-3) according to claim 6, characterized in that the recesses are formed on the at least one lateral surface in a center with a flat depression (19-1, 19-2) of uniform depth in the direction of the longitudinal axis (6).
The device (10, 10-1, 10-2, 10-3, 10-4) according to claim 6 or 7, characterized in that at least one plate-shaped intermediate element (18-1a, 18-1b, 18-2a, 18-2b) is formed which is arranged such that a first side bears against the at least one lateral surface of the core element (15-1, 15-2, 15-3, 15-4) in a plane spanned perpendicular to the longitudinal axis (6), covering the recesses in a fluid-tight manner, wherein the covered recesses form the second flow channels (12-1, 12-2, 12-3) of the heat carrier fluid.
The device (10, 10-1) according to claim 8, characterized in that the second flow channels (12-1) are formed respectively extending from an inlet distribution (12-1a) connected to the inlet (13) to an outlet opening (12-1b) connected to the outlet (14) and charged with heat carrier fluid in parallel.
The device (10, 10-1, 10-2, 10-3) according to claim 8 or 9, characterized in that the outer contours and dimensions of the at least one intermediate element (18-1a, 18-1b, 18-2a, 18-2b) and the at least one depression (19-1, 19-2) are formed corresponding to one another such that the intermediate element (18-1a, 18-1b, 18-2a, 18-2b) is arranged within the depression (19-1, 19-2) or that the outer contours and dimensions of the at least one intermediate element (18-2a, 18-2b) and an inner casing surface of a ring of the core element (15-4) circumscribing an outer circumference are formed corresponding to one another.
The device (10, 10-1) according to claim 10, characterized in that the at least one intermediate element (18-1a, 18-1b) has the shape of a planar, circular sheet and the at least one depression　(19-1) is circularly formed, wherein an outer diameter of the intermediate element (18-1a, 18-1b) corresponds to an outer diameter of the depression (19-1) plus a clearance for assembly and an extension of the depression (19-1) in the direction of the longitudinal axis (6) corresponds to a wall thickness of the intermediate element (18-1a, 18-1b).
The device (10, 10-1, 10-2, 10-3, 10-4) according to one of claims 8 to 11, characterized in that the at least one intermediate element (18-1a, 18-1b, 18-2a, 18-2b) has at least one through opening (23a, 23b) for the compressed fluid running in the direction of the longitudinal axis (6).
The device (10, 10-1, 10-2, 10-3, 10-4) according to one of claims 8 to 12, characterized in that at least one plate-shaped outer element (17a, 17b) is formed with formations and is arranged such that it bears against a second side of the at least one intermediate element (18-1a, 18-1b, 18-2a, 18-2b) in a plane spanned perpendicular to the longitudinal axis (6), wherein the formations formed in the outer element (17a, 17b) are covered by the intermediate element (18-1a, 18-1b, 18-2a, 18-2b) and thus the first flow channels (11-1) are formed.
The device (10, 10-1, 10-2, 10-3) according to claim 13, characterized in that the core element (15-1, 15-2, 15-3) is respectively formed with a depression (19-1, 19-2) of uniform depth in the direction of the longitudinal axis (6) and recesses at the lateral surfaces in the center, wherein the recesses are respectively covered in a fluid-tight manner by an intermediate element (18-1a, 18-1b, 18-2a, 18-2b) arranged in the depression (19-1, 19-2) with a respective first side of the intermediate element (18-1a, 18-1b, 18-2a, 18-2b), and in that a respective outer element (17a, 17b) with formations is arranged such that it bears against the second sides of the intermediate elements (18-1a, 18-1b, 18-2a, 18-2b), wherein the formations are covered by the intermediate element (18-1a, 18-1b, 18-2a, 18-2b).
The device (10, 10-1, 10-2, 10-3, 10-4) according to one of claims 3 to 14, characterized in that a first outer element (17a) has an inlet opening (20) and a second outer element (17b) has an outlet opening (21) for the compressed fluid.
The device (10, 10-1, 10-2, 10-3, 10-4) according to claim 15, characterized in that the first outer element (17a) has at least one branch (22a), wherein the first flow channels (11-1) are formed respectively extending from the inlet opening (20) to at least one branch (22a) and charged with fluid in parallel to one another.
The device (10, 10-1, 10-2, 10-3, 10-4) according to claim 15 or 16, characterized in that the second outer element (17b) has at least one branch (22b), wherein the first flow channels (11-1) are formed respectively extending from at least one branch (22b) to the outlet opening (21) and charged with fluid in parallel to one another.
The device (10-5) according to claim 1 or 2, characterized in that the core element (15-5) is formed in the shape of a hollow circular cylinder.
The device (10-5) according to claim 18, characterized in that a wall element (27) shaped as a hollow circular cylinder is arranged within the core element (15-5) and a cylinder-shaped central element (28) is arranged within the wall element (27), which are oriented coaxially to the longitudinal axis (6).
The device (10-5) according to claim 18, characterized in that a diameter of an inner casing surface of the core element (15-5) corresponds to a diameter of an outer casing surface of the wall element (27) and a diameter of an inner casing surface of the wall element (27) corresponds to a diameter of a casing surface of the central element (28) and the respective casing surfaces bear against one another in a fluid-tight manner.
The device (10-5) according claim 19 or 20, characterized in that the wall element (27) is formed with a recess for the second flow channel (12-5) of the heat carrier fluid on an outer casing surface.
The device (10-5) according to one of claims 19 to 21, characterized in that the wall element (27) is formed with a recess for the first flow channel (11-5) on an inner casing surface.
The device (10-5) according to claim 21 or 22, characterized in that the recess of the flow channel (11-5, 12-5) is formed in the shape of a circumferentially running helical groove, in particular an axial spiral, whose inlet and outlet are arranged spaced apart from one another in the direction of the longitudinal axis (6).
The device (10, 10-1, 10-2, 10-3, 10-4, 10-5) according to one of claims 1 to 23, characterized in that a control element, in particular a valve, for controlling the mass flow of the heat carrier fluid, is formed integrated within the core element (15-1, 15-2, 15-3, 15-4, 15-5).
A compressor (1) for compressing a vaporous fluid, in particular a refrigerant, having a housing (2), a drive device (4) arranged within the housing (2) and a compression mechanism (5) driven by the drive device (4), characterized in that a device (10, 10-1, 10-2, 10-3, 10-4, 10-5) for cooling the fluid according to one of claims 1 to 24 is formed in the flow direction of the fluid downstream of the compression mechanism (5).
The compressor (1) according to claim 25, characterized in that the compression mechanism (5) is formed of an orbiting spiral (5a) and a fixed spiral (5b), and in that the device (10, 10-1, 10-2, 10-3, 10-4, 10-5) is formed between an outlet for the fluid out of the fixed spiral (5b) and an outlet of the compressor (1)

- as a separate element between housing elements (2c, 2d) of the housing (2) arranged on a longitudinal axis (6) or integrated into the housing of the compressor, or

as a component of the fixed spiral (5b).
The compressor (1) according to claim 25 or 26, characterized in that the device (10, 10-1, 10-2, 10-3, 10-4, 10-5) for cooling the fluid has an extension in the direction of the longitudinal axis (6) in the range from 25 mm to 30　mm.
The compressor (1) according to one of claims 25 to 27, characterized in that the device (10, 10-1, 10-2, 10-3, 10-4, 10-5) for cooling the fluid is arranged within a volume charged under a high pressure level of the fluid such that a pressure prevalent within a first flow channel (11, 11-1, 11-2, 11-5) for guiding the fluid and a pressure prevalent within a volume which borders a wall delimiting the flow channel (11, 11-1, 11-2, 11-5) are substantially equal in size.
A method for operating a compressor (1) according to one of claims 25 to 28, characterized in that a performance of the device (10, 10-1, 10-2, 10-3, 10-4, 10-5) for cooling the fluid to be compressed in the compressor (1) is regulated via a mass flow of the heat carrier fluid through the device (10, 10-1, 10-2, 10-3, 10-4, 10-5) and a supply temperature of the heat carrier fluid such that an outlet condition of the compressed fluid is set at an outlet of the compressor (1) independent of an operating condition of the compressor (1).
Use of the compressor (1) according to one of claims 25 to 28 for a refrigerant of a refrigerant circuit of an air-conditioning system of a motor vehicle.