CN116964329A - Device for cooling fluid to be compressed in compressor and compressor with device - Google Patents

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 particular a refrigerant, in a compressor (1) by means of 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 a fluid, at least one second flow channel (12, 12-1, 12-2, 12-3, 12-5) for guiding a heat carrier fluid, and an inlet (13) and an outlet (14) for the heat carrier fluid.

Description

Device for cooling fluid to be compressed in compressor and compressor with device

Technical Field

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

Background

Compressors for mobile applications, in particular for air conditioning systems of motor vehicles, are known from the prior art, which compressors serve for conveying a refrigerant through a refrigerant circuit, also referred to as refrigerant compressors. Such compressors are driven via a pulley or electrically driven, which pulley is connected via a belt to the driving member of the motor vehicle, and are usually formed as piston compressors with variable stroke volume or as scroll compressors, independently of the refrigerant.

Thus, for example, a conventional electrically driven scroll compressor has an electric motor for driving a compression mechanism. The electric motor and the compression mechanism formed with the fixed scroll and the movable scroll are disposed within a volume enclosed by the housing. In so doing, the housing may 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 of metal, in particular of aluminum. The orbiting scroll of a compression mechanism in which a gaseous fluid, particularly a refrigerant, is compressed is driven via a drive shaft connected to an electric motor.

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

The heat received by the refrigerant affects the density of the pumped refrigerant and, thus, the efficiency during compressor operation. The more heat transferred to the refrigerant before entering the compression mechanism, the higher the temperature and specific volume of the refrigerant in the suction state and the lower the density. The higher temperature of the pumped refrigerant also results in a higher temperature of the refrigerant at the compressor outlet. On the other hand, the higher temperature of the refrigerant at the compressor outlet results in a strong heat conduction within the wall of the housing and thus in a stronger heating of the suction gas.

Thus, for example, when compressing carbon dioxide as refrigerant, the temperature of the refrigerant at the compressor outlet may be as high as 175 ℃, which places very high demands on the refrigerant lines at the compressor outlet, in particular the flexible refrigerant lines.

Disclosure of Invention

Technical problem

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 compressor outlet is too high, in particular when a predetermined limit temperature is exceeded. Thus, particularly when carbon dioxide is used as the refrigerant, the refrigerant circuit is power or down regulated.

On the other hand, when a compressor is employed in the refrigerant circuit of an air conditioning system of a motor vehicle, a downward regulation of the compressor power results in a significant reduction of thermal comfort in the passenger compartment.

Solution to the problem

The object of the present invention is to provide a device for cooling a fluid to be compressed in a compressor, in particular a gaseous fluid as a refrigerant in a refrigerant compressor. The compressor should in particular be able to operate with maximum efficiency and avoiding a downward regulation of the power due to the temperature of the compressed fluid being too high. The heat dissipated by the fluid can be used within a connection system, such as an air conditioning system or a thermal management system of a motor vehicle. The device should be formed with minimal installation space and in a compact manner and be able to be manufactured in a simple and inexpensive manner.

This object is achieved by the subject matter having the features of the independent claims. Further developments are stated in the dependent claims.

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

According to the inventive concept, the core element is formed such that the means for cooling the compressed fluid with the core element can be arranged between two housing elements of the modular compressor on the longitudinal axis or can be integrated as a separate component into the housing of the compressor. Since the device is provided in particular for cooling a fluid that has been compressed, the device is arranged downstream of the compression mechanism in the flow direction of the fluid in the assembled state of the compressor.

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

The outer contour and dimensions of the core element and the outer contour and dimensions of the shell element may correspond to each other. In so doing, the outer contour and dimensions of the core element preferably correspond to the outer contour and dimensions of the shell element.

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

The core element preferably has at least one through opening for the compressed fluid, which extends in the direction of a longitudinal axis corresponding to the symmetry axis of the plate or 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 the outer circumference and with flat depressions of uniform depth in the direction of the longitudinal axis on at least one lateral surface located centrally of the surface. A flat recess is understood to be a surface that is offset in the direction of the longitudinal axis and offset in the direction of the longitudinal axis with respect to the interior of the lateral surface. The planes spanned by the outer lateral surface and the surface of the recess are oriented parallel to each other and are arranged spaced apart from each other.

Alternatively, the core element may be formed as a ring around the outer circumference with a centrally formed stacked sheet structure.

The advantage of the invention is that the core element has recesses on at least one lateral surface, which recesses each extend from the surface into the core element. In so doing, a recess is formed on at least one lateral surface, in particular in the region of the planar recess.

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

In so doing, the recess covered by the intermediate element forms a second flow channel for the heat carrier fluid. The second flow channels preferably extend from an inlet distribution connected to the inlet to an outlet opening connected to the outlet, respectively, and may be filled with a heat carrier fluid in parallel.

According to a further advantageous embodiment of the invention, the outer contour and the dimensions of the at least one intermediate element and the outer contour and the dimensions of the at least one recess correspond to one another such that the intermediate element is arranged in the recess. The at least one intermediate element may particularly have the shape of a flat circular sheet, and the at least one recess may have the shape of a circle. In so doing, the outer diameter of the intermediate element may correspond to the outer diameter of the recess plus the gap for assembly, and the extension of the recess in the direction of the longitudinal axis may correspond to the wall thickness of the intermediate element.

In an alternative design of the core element as a ring around the outer circumference with a structure of stacked sheet plates formed in the center, the outer contour and dimensions of the at least one intermediate element and the outer contour and dimensions of the inner shell surface of the ring around the outer circumference of the core element may be formed in correspondence with each other.

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

According to a further development of the invention, the at least one plate-like outer element is formed with a configuration and is supported against the second side of the at least one intermediate element in a plane spanned perpendicular to the longitudinal axis. In so doing, the formation formed in the outer element is covered by the intermediate element as fluid-tightly as possible, so that a first flow channel is formed.

The core element is provided with corresponding recesses of uniform depth in the direction of the longitudinal axis and in particular with recesses on both lateral surfaces located centrally. In so doing, the recesses are respectively covered in a fluid-tight manner by the respective first sides of the intermediate element arranged in the recess. Furthermore, the outer element with the formation is supported against the respective second side of the intermediate element, such that the formation formed in the outer element is covered by the intermediate element, as fluid-tightly as possible.

The means for cooling the fluid to be compressed in the compressor is advantageously a stacked plate heat exchanger having a performance that can be expanded by the number of stacked plates and by a defined size. The device is preferably formed as a part for brazing or welding, in particular laser welding, of extruded and shaped elements of aluminum. In so doing, additional sealing elements between the heat carrier fluid circuit and the fluid to be compressed in the compressor may be omitted.

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

The coolant or fluid to be compressed in the compressor, in particular the refrigerant, can be used as a heat carrier fluid. When a coolant is used as the heat carrier fluid, the device is formed as a refrigerant-to-coolant heat exchanger. For example, when using a refrigerant as the heat carrier fluid, the apparatus corresponds to a refrigerant-to-refrigerant heat exchanger and then operates as an inner loop heat exchanger.

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

The first outer element may have at least one branch such that the first flow channels extend from the inlet opening to the at least one branch, respectively, and are filled with fluid in parallel with each other. The second outer element may have at least one branch such that the first flow channels extend from the at least one branch to the outlet opening, respectively, and are filled with fluid in parallel with each other.

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 each other and thus along the axis such that the compressed fluid flows out of the branches of the first outer element and into the branches of the second outer element on a straight flow path through the through openings of the intermediate element and the core element without any deflection.

When more than one branch is formed within the outer element, 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 a respective through opening.

According to an alternative design of the invention, the core element is formed in the shape of a hollow circular cylinder. In so doing, preferably, a wall element shaped as a hollow circular cylinder is arranged within the core element, and a cylindrical central element is arranged within the wall element, the wall element and the central element being coaxially oriented with respect to the longitudinal axis. The diameter of the inner shell surface of the core element may correspond to the diameter of the outer shell surface of the wall element, while the diameter of the inner shell surface of the wall element may correspond to the diameter of the shell surface of the central element, such that the respective shell surfaces bear against each other in a fluid-tight manner.

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

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

Another advantage of the invention is that the recess of the flow channel is formed in the shape of a circumferentially extending helical groove, in particular an axial helical shape, the inlet and the outlet of the flow channel being spaced apart from each other in the direction of the longitudinal axis.

According to a further preferred embodiment 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 in the core element.

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

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

According to another refinement of the invention, the compression mechanism has an orbiting scroll and a non-orbiting scroll. In so doing, the means for cooling fluid, which are arranged in particular between the outlet for the fluid flowing out of the non-orbiting scroll and the outlet of the compressor, are formed as separate components located between the housing elements of the housing arranged on the longitudinal axis or integrated into the housing of the compressor, or as components of the non-orbiting scroll. When the device is formed as part of a non-orbiting scroll, the non-orbiting scroll, and thus the fluid being conveyed within the scroll, is 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 25mm to 30mm, so that the installation space of the compressor is only slightly enlarged by the integration of the device.

According to an advantageous design of the invention, the means for cooling the fluid are arranged in the volume filled at a high pressure level of the fluid such that the pressure prevailing in the first flow channel for guiding the fluid and the pressure prevailing in the volume adjoining the wall delimiting the flow channel from the outside are substantially equal in magnitude. The small pressure difference over the wall of the restricted flow channel requires only a very small wall thickness of the outer element. Only the wall enclosing the second flow channel for guiding the heat carrier fluid is constructed in a sturdy manner to withstand the high pressure of the fluid.

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

The advantageous design of the invention enables the use of the compressor for the refrigerant in the refrigeration 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 gaseous fluid with the device in general also has several advantages compared to prior art devices:

reducing the average compressor temperature, in particular the temperature of the compressed fluid at the compressor outlet, without reducing the performance in the refrigerant circuit-for example, in the case of carbon dioxide as refrigerant, the temperature at the compressor outlet is lower than 100 ℃, instead of 175 ℃ in the case of no use of the device according to the invention, and therefore

* By employing a low temperature refrigerant line at the high pressure side of the circuit, the temperature requirements on the refrigerant line within the circuit, particularly downstream of the compressor, are reduced, which is associated with reduced system costs,

* Improving volumetric and isotropic efficiency, especially when cooling the non-orbiting scroll in a scroll compressor, improving the cooling performance of the system, or reducing the driving performance of the compressor in case of comparable cooling performance, for example, in case of 6% reduction in driving performance with carbon dioxide as fluid to be compressed, a 4% increase in mass flow,

* The electrical efficiency is improved due to the indirect cooling of the inverter and the electric motor of the compressor driving device,

* Avoiding downregulation and speed reduction of compressor performance due to excessive temperature of the compressed fluid at the compressor outlet,

* The thermal conductivity in the direction of the longitudinal axis of the compressor is reduced by thermodynamic destruction of the conductivity,

* The temperature of the compressed fluid at the inlet into the gas cooler/condenser is reduced due to reduced heat load or reduced performance of the gas cooler/condenser, because most of the heat in the compressor is vented via the heat carrier fluid circuit, or no external gas cooler/compressor is required,

* The maximum lifetime of the internal components;

avoiding losses by decoupling the pyrolysis into the heat carrier fluid circuit,

selectively adjusting the mass flow of the heat carrier fluid and selectively using the waste heat of the compressor, for example heating the battery, thereby increasing the mileage of the motor vehicle driven by the electric motor and eliminating additional electric heating,

optimizing thermal management to make the vehicle occupants more comfortable, and

by using the inner cavity volume as sound absorber, noise emissions or sound emissions and pressure pulsations in the system are reduced by the means for cooling.

Drawings

Additional details, features and advantages of the design of the present invention will be made apparent from the following description of example embodiments with reference to the accompanying drawings. Shown as:

fig. 1: an electrically driven compressor is shown in cross-section, with means integrated into the compressor for cooling the fluid to be compressed in the compressor,

fig. 2: the components of the compressor of the first embodiment with integrated means for cooling the fluid are shown in perspective view,

fig. 3a and 3b: the components of the compressor with integrated means for cooling fluid from figure 2 are shown in perspective and side cross-section,

fig. 4a: a first embodiment of the device for compressing a fluid to be compressed in a compressor from figures 3a and 3b is shown in a perspective view in an assembled state,

fig. 4b and 4c: a first embodiment of a device for cooling a fluid to be compressed in a compressor with a core element, an intermediate element and an outer element from figures 3a and 3b respectively is shown in a perspective exploded view,

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

Fig. 6a and 6b: a core element of a second embodiment of a device for cooling a fluid to be compressed in a compressor, from fig. 5b with an inlet and an outlet for a heat carrier fluid as separate elements, respectively, is shown in a perspective side view, and

fig. 6c and 6d: the core elements from fig. 6a and 6b with the flow direction of the fluid to be compressed and the heat carrier fluid in the compressor are shown in side view, respectively.

Detailed Description

Fig. 1 shows an electrically driven compressor 1 for gaseous fluids in a sectional view, the electrically driven compressor 1 being in particular for an air conditioning system for a motor vehicle for delivering a refrigerant through a refrigerant circuit, the electrically driven compressor 1 having a drive device 4 and a device 10, the drive device 4 being arranged in a housing 2, in particular an electric motor, for driving a compression mechanism 5, the device 10 being integrated in the compressor 1 for cooling a fluid to be compressed in the compressor 1. 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 having an orbiting scroll 5a and a non-orbiting scroll 5b are arranged within a volume enclosed by the housing 2. The scroll members 5a, 5b are preferably formed of metal, in particular aluminum or steel. In so doing, the first housing element 2a for receiving the electric motor 4, the second housing element 2b for receiving a transmission mechanism for transmitting motion from the rotor of the electric motor 4 to the orbiting scroll 5a of the compression mechanism 5, and the third housing element 2c for receiving the compression mechanism 5 are preferably formed of metal, in particular of aluminum.

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

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

The housing elements 2a, 2b, 2c, 2d oriented on the longitudinal axis 6 and enclosing the common volume are coupled to each other via the connection means 3. In so doing, the first housing element 2a and the fourth housing element 2d are respectively arranged on the outer side portions formed in the axial direction.

The connecting means 3 are formed as a threaded connection with a through-going opening and a blind hole with an internal thread. In so doing, blind holes with internal threads are provided exclusively on the first housing element 2a, while the other housing elements 2b, 2c, 2d are each formed with through openings for receiving screws and threaded bolts. The through openings correspondingly oriented in alignment with each other enable insertion of a screw or threaded bolt respectively received by the first housing element 2a into the blind hole. The housing elements 2a, 2b, 2c, 2d are screwed together in this way and the housing 2 is closed.

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

In so doing, the means 10 for cooling the fluid to be compressed in the compressor 1 is thus 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 cooled mainly to a high pressure level after the compression operation and is thus cooled as hot gas before the refrigerant exits the compressor 1 through the refrigerant outlet 7.

After leaving the compression mechanism 5, the refrigerant is guided through the device 10 in a first flow channel 11 through a refrigerant outlet 5c, while a heat carrier fluid receiving heat from the refrigerant flows through a second flow channel 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 in a perspective view as components of the compressor 1, wherein a first embodiment of the device 10-1 for cooling a fluid to be compressed in the compressor 1 is arranged between the housing elements 2c, 2d and is thus integrated in the compressor 1. In so doing, the third housing element 2c is represented by a perspective wall to better identify the device 10-1. In fig. 3a and 3b, the components of the compressor 1 with the integrated device 10-1 according to fig. 2 are shown in a perspective view and in a side sectional view.

The device 10-1 has an inlet 13 and an outlet 14 for a heat carrier fluid, in particular a coolant. The inlet 13 and the outlet 14 of the heat carrier fluid are formed as short tubes, respectively, and are arranged on the outer shell surface of the plate-like core element 15-1. In so doing, the outer diameter of the plate-like core element 15 1 substantially corresponds to the outer diameter of the adjoining housing elements 2c, 2 d. The core element 15-1 is provided with through openings 16 of the device 10-1 for inserting screws or threaded holes of the connecting device 3.

The plate-like core element 15-1 is formed with recesses on the lateral surfaces, the recesses extending into the core element 15-1 from the corresponding surfaces, respectively. The recess is closed by a plate-like intermediate element 18-1a, 18-1b bearing against the surface in the direction of the longitudinal axis. The intermediate elements 18-1a, 18-1b bear against the surface of the core element 15-1 and cover the recess in planes spanned perpendicular to the longitudinal axis 6, respectively. The recess closed in this way and provided in the core element 15 1 forms the second flow channel 12-1 for the heat carrier fluid. The intermediate elements 18 a, 18-1b each have the shape of a flat 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 member 15-1, the core member 15-1 is formed with circular recesses 19-1 of uniform depth on both surfaces. The outer diameter of the circular recess 19-1 corresponds to the outer diameter of the circular intermediate element 18-1a, 18-1b, respectively, while the extension of the recess 19-1 in the direction of the longitudinal axis 6, corresponding to the depth, corresponds to the thickness of the sheet-like intermediate element 18-1a, 18-1 b. The intermediate elements 18-1a, 18-1b may thus each be arranged with a surface facing outwards in the direction of the longitudinal axis 6 and thus being aligned away from the core element 15-1 within the core element 15-1. The core element 15-1 is then connected with the intermediate elements 18-1a, 18-1b arranged on the core element 15-1 and then has a flat and closed surface in the direction of the longitudinal axis 6, respectively.

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

The plate-like outer elements 17a, 17b bear against surfaces of the intermediate elements 18-1a, 18-1b oriented in alignment with the core element 15-1. The outer elements 17a, 17b formed as sheets have specially formed formations, in particular by means of thermoforming, which, in connection with the flat surfaces of the intermediate elements 18-1a, 18-1b, supply the first flow channel 11-1 with refrigerant in a Zhou Xiangfeng-peripheral manner. The configuration formed by means of thermoforming is circumferentially closed by the plate-like intermediate elements 18-1a, 18-1b bearing against in the direction of the longitudinal axis 6. On the other hand, the intermediate elements 18-1a, 18-1b bear against the outer elements 17a, 17b in planes spanned perpendicular to the longitudinal axis 6, respectively, and cover the formation formed by means of thermoforming. The closed area thus formed in the outer member 17a, 17b represents the first flow passage 11-1 of the refrigerant.

The device 10-1 for cooling a fluid to be compressed in the compressor 1 is formed as a plate heat exchanger, in particular as a refrigerant-coolant heat exchanger, having a plate-shaped core element 15-1, plate-shaped intermediate elements 18-1a, 18-1b, the inner surfaces of which are supported against both sides of the core element 15-1, and outer elements 17a, 17b, which are supported against the outer surfaces of the intermediate elements 18-1a, 18-1b, and outer elements 17a, 17 b. The construction as a plate heat exchanger enables a simple expansion of the thermal properties to be transferred. The heated coolant can be used to heat other components, for example an air conditioning system or a drive train of a motor vehicle, such as a battery, so that other components for heating, such as an electrical PTC heater, can be omitted.

According to an alternative embodiment, not shown, the device 10-1 for cooling the fluid to be compressed in the compressor 1 is integrated in the housing 2 itself, in particular in the fourth housing element 2 d. The device 10-1 and the housing element 2d are integrally formed.

In fig. 4a, a first embodiment of a device 10-1 for cooling a fluid to be compressed in a compressor 1 from fig. 3a and 3b in an assembled state is shown in perspective view, while in fig. 4b and 4c, a first embodiment of a device 10-1 with a core element 15-1, intermediate elements 18-1a, 18-1b and outer elements 17a, 17b is shown in perspective exploded view, respectively. In so doing, and in particular in FIG. 4c, a flow path for the refrigerant and heat carrier fluid through the device 10-1 is proposed.

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

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

Then, part of the mass flow of the refrigerant flows out of the first flow passage 11-1 through the through opening 23a formed in the first intermediate member 18-1a, and flows to the branch 22b formed in the second intermediate member 18-1b through the through opening 24 formed in the core member 15-1 and through the through opening 23b formed in the second intermediate member 18-1 b.

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

The first flow channels 11-1 formed between the second outer element 17b and the second intermediate element 18-1b extend from the branches 22b to the outlet opening 21, respectively, and are filled with refrigerant in parallel. The second outer element 17b has two branches 22b as the first outer element 17a so that two partial mass flows of the refrigerant are uniformly distributed to the first flow channels 11-1, respectively. In so doing, a first partial mass flow of refrigerant is directed into the first flow channel 11-1 leading to the first branch 22a, and a second partial mass flow of refrigerant is directed into the first flow channel 11-1 leading to the second branch 22 b. Part of the mass flow of the refrigerant is combined at the outlet opening 21. The mass flow of refrigerant cooled during flow through the device 10-1 exits the device 10-1 through the outlet opening 21 in the flow direction 26. Heat is transferred from the refrigerant to the heat carrier fluid.

The heat carrier fluid flows into the device 10-1 in a flow direction 25 through a first inlet 13 formed as a short tube and out of the device 10-1 through an outlet 14 also formed as a short tube. After inflow, the heat carrier fluid is uniformly distributed to the second flow channels 12-1 formed between the core element 15-1 and the intermediate elements 18-1a, 18-1b, respectively. In so doing, the 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 split into two partial mass flows after flowing through the inlet 13.

The second flow channels 12-1, which extend from the inlet distribution portion 12-1a connected to the inlet 13 to the outlet opening 12-1b connected to the outlet 14, respectively, are filled with the heat carrier fluid in parallel. After flowing through the inlet 13, the two partial mass flows of the heat carrier fluid are each split into the second flow channel 12-1 at the inlet distributor 12-1 a. The two partial mass flows of the heat carrier fluid, which are respectively combined at the outlet openings 12-1b, exit the device 10-1 together through the outlet 14. In so doing, the mass flow of the heated heat carrier fluid exits the device 10-1 in the flow direction 25 during flow through the device 10-1.

In fig. 5a to 5e, different embodiments of the device 10 for cooling a fluid to be compressed in a compressor are shown in a combination from the first embodiment of the device 10-1, the second embodiment of the device 10-2, the third embodiment of the device 10-3, the fourth embodiment of the device 10-4 and the fifth embodiment 10-5 of fig. 2. The same elements and components of the devices 10, 10-1, 10-2, 10-3, 10-4, 10-5 are designated with the same reference numerals. With respect to their construction and function, reference is made to the description above.

The main difference between the devices 10-1, 10-2, 10-3 from fig. 5a to 5c is the configuration of the plate-shaped core elements 15-1, 15-2, 15-3, the plate-shaped core elements 15-1, 15-2, 15-3 having recesses for the second flow channels 12-1, 12-2, 12 3 of the heat carrier fluid and recesses for the first flow channels 11-2 in the case of the core element 15-2 of the device 10-2.

As explained in fig. 4b and 4c, the recesses of the second flow channel 12-1 of the first embodiment of the device 10-1 are arranged on both sides of the core element 15-1 and extend from the inlet distribution 12-1a to the outlet opening 12-1b, respectively, parallel to each other. Thus, the recesses of the second flow channels 12-1 provided on both sides of the core element 15-1 are formed independently of each other, in particular not through any intermediate connection of the core element 15-1. The heat carrier fluid is guided in radial flow in the second flow channels 12-1, respectively.

In contrast to the first embodiment of the device 10-1 according to fig. 5a, the recess of the second flow channel 12-2 according to the second embodiment of the device 10-2 of fig. 5b is formed such that the heat carrier fluid is guided through the device 10-2 as an undivided and thus integrated mass flow. In so doing, the mass flow of the heat carrier fluid is guided into recesses on both sides of the core element 15-2, which recesses are further connected to each other via intermediate connections extending through the core element 15, in particular in the direction of the longitudinal axis 6. The mass flow of the heat carrier fluid is thus guided along both sides of the core element 15-2 in an alternating manner, wherein the change of both sides is performed by means of intermediate connections formed in the core element 15-2. The heat carrier fluid is directed in an alternating manner in the radial and axial directions as it flows through the second flow channel 12-2.

Furthermore, in contrast to the first embodiment of the device 10-1 according to fig. 5a, the refrigerant does not flow through the through-openings 24 by means of the shortest flow path in the axial direction through the core element 15-2, but is guided, like the heat carrier fluid, into recesses on both sides of the core element 15-2 by means of the first flow channels 11-2 provided in the core element 15-2. The recesses are connected to each other via an intermediate connection extending through the core element 15 in the direction of the longitudinal axis 6. The mass flow of the refrigerant is thus also guided in an alternating manner along both sides of the core element 15-2, wherein the change of both sides is performed by means of an intermediate connection formed in the core element 15-2.

In contrast to the first embodiment 10-1 of the invention according to fig. 5a, according to this embodiment the second flow channels 12-1 are arranged on both sides of the core element 15-1 such that the mass flow of the heat carrier fluid after flowing through the inlet 13 is divided into two partial mass flows, the recesses of the second flow channels 12-3 of the third embodiment of the device 10-3 according to fig. 5c being connected to each other in the direction of the longitudinal axis 6 by the core element 15 3, respectively. The mass flow of the heat carrier fluid is thus guided through the second flow channel 12 as an undivided total mass flow. The intermediate walls defining the second flow channels 12-3 are connected to each other and to the core element 15-3 via separate ribs.

Another major difference between the devices 10-1, 10-3 on the one hand and the devices 10-2 on the other hand is that the configuration of the intermediate elements 18-1a, 18-2a, 18-1b, 18-2b is related to the recesses 19-1, 19-2 provided in the core elements 15-1, 15-2 for receiving the intermediate elements 18-1a, 18-2a, 18-1b, 18-2 b.

Although the plate-like intermediate elements 18-1a, 18-1b of the device 10-1, 10-3 from fig. 5a and 5c, respectively, have the shape of a flat, circular sheet, the intermediate elements 18-2a, 18 2b of the device 10-2 from fig. 5b, respectively, are outwardly beveled on the outer circumference in the direction of the longitudinal axis 6, i.e. in the direction away from the core element 15 2, and thus have a significantly greater depth compared to the intermediate elements 18 1a, 18-1b of the device 10-1, 10-3, in particular at the outer circumference. Since the depth of the intermediate elements 18 2a, 18-2b corresponds to the extension of the recess 19-2 in the core element 15-2 in the direction of the longitudinal axis 6, respectively, the recess 19-2 also has a larger extension than the recess 19-1 of the core element 15-1, 15-3 of the device 10-1, 10-3. The intermediate elements 18-2a, 18-2b of the device 10-2 may be arranged within the core element 15-2 in alignment with the end faces facing in the direction of the longitudinal axis 6, respectively, wherein the surfaces face outwardly in the direction of the longitudinal axis 6 and thus away from the core element 15-2.

The main difference between the devices 10-1, 10-2, 10-3 from fig. 5a to 5c on the one hand and the device 10-4 from fig. 5d on the other hand is the construction of the core elements 15-1, 15-2, 15-3, 15-4, the core elements 15-1, 15-2, 15-3 being constructed in the form of a block of individual plates of the devices 10-1, 10-2, 10-3, and the core elements 15-4 being constructed as a ring around the outer circumference with the structure of the device 10-4 forming a centrally individual stacked sheet-like plate. The plates are each oriented in a plane oriented in a direction perpendicular to the longitudinal axis 6.

Like the outer elements 17a, 17b, the two plates, which are respectively formed as sheets and which are arranged outside the centre of the core element 15-4 in the direction of the longitudinal axis 6, have specially formed formations, in particular by means of thermoforming, which provide the second flow channels 12-1 for the heat carrier fluid connected with the intermediate elements 18-2a, 18-2b, respectively. The construction is circumferentially closed by plate-like intermediate elements 18-2a, 18-2b bearing against each other 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 formation formed by means of thermoforming.

In the direction of the longitudinal axis 6, advantageously, a flat sheet-like plate is arranged between the two plates, each formed as a sheet with a configuration, which in particular increases the stability and manufacturability of the core element 15-4. The individual plates of the core element 15-4 each have the same outer contour in terms of shape and size, which outer contours correspond to the inner shell surface of the ring of the core element 15 around the outer circumference.

Like the intermediate elements 18-2a, 18-2b of the device 10-2 from fig. 5b, the plate-like intermediate elements 18-2a, 18 2b of the device 10-4 from fig. 5d are each outwardly chamfered on the outer circumference in the direction of the longitudinal axis 6, in particular in the direction facing away from the core element 15 4. The intermediate elements 18-2a, 18 2b of the device 10-4 may be arranged in the ring of the core element 15-2 in alignment with the end faces facing in the direction of the longitudinal axis 6, respectively, wherein the surfaces face outwards in the direction of the longitudinal axis 6 and thus away from the ring of the core element 15-2 around the outer circumference.

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

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

The outer shell surface of the wall element 27 is formed with a recess for the second flow channel 12-5 of the heat carrier fluid and at the inner shell surface with a recess for the first flow channel 11-5 of the refrigerant. The recess for the second flow channel 12-5 is covered by the core element 15-5 outwards in the radial direction, in particular by means of the inner shell surface of the core element 15-5. The recess for the first flow channel 11-5 is covered by the central element 28 inwards in the radial direction, in particular by means of the housing 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 spiral grooves or axial spirals extending in the circumferential direction, the inlet and outlet of the flow channels being respectively spaced apart from each other in the direction of the longitudinal axis 6. The core element 15-5 of the device 10-5 has a larger extension in the direction of the longitudinal axis 6 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 extend parallel to each other.

In fig. 6a and 6b, the core element 15-2 of the second embodiment of the device 10-2 for cooling a fluid to be compressed in a compressor 1 according to fig. 5b is shown as separate elements in a perspective side view with the inlet 13 and the outlet 14, respectively, of a heat carrier fluid. In fig. 6c, the core element 15-2 with the flow direction 29 of the fluid to be compressed in the compressor 1 is shown in a side view, while fig. 6d also shows the core element 15-2 with the flow direction 30 of the heat carrier fluid in a side view.

The main difference between the core elements 15-1, 15-2 of the device 10-1, 10-2 is on the one hand the configuration of the recesses of the second flow channels 12-1, 12-2 of the heat carrier fluid and on the other hand the configuration of the recesses of the first flow channels 11-2 of the refrigerant in the core element 15-2. The same elements and components of the devices 10-1, 10-2 are designated with the same reference numerals. With respect to their construction and function, reference is made to the explanations above.

In contrast to the first embodiment of the device 10-1 according to fig. 4b, the second flow channel 12-2 is formed so as not to divide into parallel channels in the core element 15-2. The second flow channels 12-2 extend in an alternating manner in recesses formed in the surfaces on both upper surfaces of the core element 15-2. In so doing, the alternating guidance of the second flow channels 12-2 on the upper surface of the core element 15-2 is achieved by means of intermediate connections facing in a direction perpendicular to the upper surface and thus facing in a direction of the longitudinal axis. The intermediate connection portion is formed as a circular through hole or a long hole shaped through hole between the upper side portions, respectively. The recesses and the intermediate connections are arranged relative to each other such that the heat carrier fluid according to fig. 6d is guided in an alternating manner along both sides of the core element 15-2 in the flow direction 30 and flows through the core element 15 2 substantially in a zigzag manner. The heat carrier fluid is directed in an alternating manner in the radial and axial directions as it flows through the second flow channel 12-2. The flow direction 30 is indicated with arrows. In so doing, the flow of the heat carrier fluid at the visible side of the core element 15-2 is indicated by means of continuous line-marked arrows, while the flow of the heat carrier fluid at the covered side of the core element 15-2 is indicated by means of dashed line-marked arrows.

In addition, a first flow passage 11-2 for refrigerant is also provided in the core member 15-2, and the first flow passage 11-2 is formed in the same manner as the second flow passage 12-2. The first flow channels 11-2 thus also extend in an alternating manner in recesses formed in the surface on both upper sides of the core element 15-2, which recesses are connected to each other by means of intermediate connections facing in a direction perpendicular to the upper surface and thus facing in the direction of the longitudinal axis. On the other hand, the recesses and the intermediate connections of the first flow channel 11-2 are arranged relative to each other such that the refrigerant according to fig. 6c is guided in an alternating manner along both sides of the core element 15-2 in the flow direction 29 and flows through the core element 15 2 substantially in a zigzag manner. The refrigerant is guided in an alternating manner in the radial direction and the axial direction while flowing through the first flow channel 11-2. On the other hand, the flow direction 29 is indicated with an arrow. In so doing, the flow of refrigerant at the visible side of the core element 15-2 is indicated by means of continuous line-marked arrows, while the flow of refrigerant at the covered side of the core element 15-2 is indicated by means of dashed line-marked arrows.

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

List of reference numerals

1 compressor

2 shell body

2a first housing element

2b second housing element

2c third housing element

2d fourth housing element

3 connection device

4 drive device and electric motor

5 compression mechanism

5a moving scroll

5b non-orbiting scroll

5c refrigerant outlet of compression mechanism 5

6 longitudinal axis

7 refrigerant outlet of compressor 1

10. 10-1, 10-2, 10-3, 10-4, 10-5 devices

11. 11-1, 11-2, 11-5 refrigerant first flow path

12. 12-1, 12-2, 12-3, 12-5 second flow path for the heat carrier fluid

12-1a inlet distributor

12-1b outlet opening

13 inlet for heat carrier fluid

14 outlet for heat carrier fluid

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

16 through openings

17a first external element

17b second external element

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

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

19-1, 19-2 recesses

20 inlet opening for refrigerant

21 outlet opening for refrigerant

22a, 22b branches

23a, 23b through openings

24 through openings

25 flow direction of the heat carrier fluid

26 flow direction of refrigerant

27 wall element

28 central element

29 direction of flow of refrigerant

30 flow direction of the heat carrier fluid

Claims (30)

1. A device (10, 10-1, 10-2, 10-3, 10-4, 10-5) for cooling a fluid to be compressed, in particular a refrigerant, in a compressor (1) with a heat carrier fluid, the device (10, 10-1, 10-2, 10-3, 10-4, 10-5) 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, 15-5) with the core element (15-1, 15-2, 15-3, 15-5) can be arranged as a housing (2) in a longitudinal direction between the compressor housing (1), or as an integrated part (2) in the longitudinal direction.

2. The device (10, 10-1, 10-2, 10-3, 10-4, 10-5) according to claim 1, characterized in that the outer contour and dimensions of the core element (15-1, 15-2, 15-3, 15-4, 15-5) and the outer contour and dimensions of the housing element (2 c, 2 d) are formed in correspondence with each other.

3. 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.

4. A 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 compressed fluid flowing in the direction of the longitudinal axis (6).

5. 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 the outer circumference and with flat depressions (19-1, 19-2) of uniform depth in the direction of the longitudinal axis (6) on at least one lateral surface located centrally, or that the core element (15-4) is formed as a ring around the outer circumference with a structure of stacked sheet-like plates formed centrally.

6. 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 the at least one lateral surface, which recesses are formed to extend from the surface into the core element (15-1, 15-2, 15-3, 15-4), respectively.

7. The device (10, 10-1, 10-2, 10-3) according to claim 6, characterized in that the recess is formed on the at least one lateral surface which centrally has a flat recess (19-1, 19-2) of uniform depth in the direction of the longitudinal axis (6).

8. The device (10, 10-1, 10-2, 10-3, 10-4) according to claim 6 or 7, characterized in that at least one plate-like intermediate element (18-1 a, 18-1b,18-2a, 18-2 b) is formed, which intermediate element (18-1 a, 18-1b,18-2a, 18-2 b) 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), so as to cover the recess in a fluid-tight manner, wherein the covered recess forms the second flow channel (12-1, 12-2, 12-3) of the heat carrier fluid.

9. The device (10, 10-1) according to claim 8, characterized in that the second flow channels (12-1) extend from an inlet distribution (12-1 a) connected to the inlet (13) to an outlet opening (12-1 b) connected to the outlet (14) and are filled with the heat carrier fluid in parallel, respectively.

10. The device (10, 10-1, 10-2, 10-3) according to claim 8 or 9, characterized in that the outer contour and the dimensions of at least one of the intermediate elements (18-1 a, 18-1b,18-2a, 18-2 b) are formed in correspondence with each other with the outer contour and the dimensions of at least one of the recesses (19-1, 19-2) such that the intermediate element (18-1 a, 18-1b,18-2a, 18-2 b) is arranged within the recess (19-1, 19-2) or the outer contour and the dimensions of at least one of the intermediate elements (18-2 a, 18-2 b) are formed in correspondence with each other with the outer contour and the dimensions of the inner shell surface of the ring of the core element (15-4) around the outer circumference.

11. The device (10, 10-1) according to claim 10, characterized in that at least one of the intermediate elements (18-1 a, 18-1 b) has the shape of a flat circular sheet and at least one of the recesses (19-1) is formed in a circular manner, wherein the outer diameter of the intermediate element (18-1 a, 18-1 b) corresponds to the outer diameter of the recess (19-1) plus a gap for assembly and the extension of the recess (19-1) in the direction of the longitudinal axis (6) corresponds to the wall thickness of the intermediate element (18-1 a, 18-1 b).

12. The device (10, 10-1, 10-2, 10-3, 10-4) according to one of claims 8 to 11, characterized in that at least one of the intermediate elements (18-1 a, 18-1b,18-2a, 18-2 b) has at least one through opening (23 a, 23 b) for the compressed fluid flowing in the direction of the longitudinal axis (6).

13. 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-like outer element (17 a, 17 b) is formed with a construction and is arranged such that the outer element (17 a, 17 b) bears against a second side of at least one intermediate element (18-1 a, 18-1b,18-2a, 18-2 b) in a plane spanned perpendicular to the longitudinal axis (6), wherein the construction formed in the outer element (17 a, 17 b) is covered by the intermediate element (18-1 a, 18-1b,18-2a, 18-2 b) and thus forms the first flow channel (11-1).

14. 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 formed with the recess (19-1, 19-2) of uniform depth in the direction of the longitudinal axis (6) and with the recess at the centrally located lateral surface, respectively, wherein the recess is covered in a fluid-tight manner by the intermediate element (18-1 a, 18-1b,18-2a, 18-2 b) arranged with a respective first side of the intermediate element (18-1 a, 18-1b,18-2a, 18-2 b) in the recess (19-1, 19-2), and the outer element (17 a, 17 b) with the configuration is arranged such that the outer element (17 a, 17 b) is supported against the intermediate element (18-1 a, 18-1b,18-2a, 18-2 b) with the second side of the intermediate element (18-1 a, 18-2 b) being covered by the intermediate element (1 a, 18-2).

15. The device (10, 10-1, 10-2, 10-3, 10-4) according to one of claims 3 to 14, characterized in that the first outer element (17 a) has an inlet opening (20) and the second outer element (17 b) has an outlet opening (21) for the compressed fluid.

16. The device (10, 10-1, 10-2, 10-3, 10-4) according to claim 15, characterized in that the first outer element (17 a) has at least one branch (22 a), wherein the first flow channels (11-1) are each formed extending from the inlet opening (20) to the at least one branch (22 a) and are filled with fluid in parallel to each other.

17. The device (10, 10-1, 10-2, 10-3, 10-4) according to claim 15 or 16, characterized in that the second outer element (17 b) has at least one branch (22 b), wherein the first flow channels (11-1) are each formed extending from the at least one branch (22 b) to the outlet opening (21) and are filled with fluid in parallel to each other.

18. The device (10-5) according to claim 1 or 2, wherein the core element (15-5) is formed in the shape of a hollow circular cylinder.

19. Device (10-5) according to claim 18, characterized in that a wall element (27) shaped as a hollow circular cylinder is arranged in the core element (15-5), and a cylindrical central element (28) is arranged in the wall element (27), the wall element (27) and the central element (28) being coaxially oriented with respect to the longitudinal axis (6).

20. The device (10-5) according to claim 18, characterized in that the diameter of the inner shell surface of the core element (15-5) corresponds to the diameter of the outer shell surface of the wall element (27), and the diameter of the inner shell surface of the wall element (27) corresponds to the diameter of the shell surface of the central element (28), and the respective shell surfaces bear against each other in a fluid-tight manner.

21. Device (10-5) according to 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 the housing surface.

22. 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 the inner housing surface.

23. Device (10-5) according to claim 21 or 22, characterized in that the recess of the flow channel (11-5, 12-5) is formed as a circumferentially extending spiral groove, in particular in the shape of an axial spiral, the inlet and outlet of the flow channel (11-5, 12-5) being arranged spaced apart from each other in the direction of the longitudinal axis (6).

24. 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 in the core element (15-1, 15-2, 15-3, 15-4, 15-5).

25. Compressor (1) for compressing a gaseous fluid, in particular a refrigerant, the compressor (1) 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 downstream of the compression mechanism (5) in the flow direction of the fluid.

26. The compressor (1) of claim 25, wherein the compression mechanism (5) is formed by an orbiting scroll (5 a) and a non-orbiting scroll (5 b), and the means (10, 10-1, 10-2, 10-3, 10-4, 10-5) is formed between an outlet for the fluid exiting the non-orbiting scroll (5 b) and an outlet of the compressor (1) as follows:

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

Is formed as a component of the fixed scroll (5 b).

27. Compressor (1) according to claim 25 or 26, characterized in that the means (10, 10-1, 10-2, 10-3, 10-4, 10-5) for cooling the fluid have an extension in the direction of the longitudinal axis (6) in the range from 25mm to 30 mm.

28. The compressor (1) according to one of claims 25 to 27, characterized in that the means (10, 10-1, 10-2, 10-3, 10-4, 10-5) for cooling the fluid are arranged in a volume filled at a high pressure level of the fluid such that the pressure prevailing in the first flow channel (11, 11-1, 11-2, 11-5) for guiding the fluid and the pressure prevailing in the volume adjoining the wall delimiting the flow channel (11, 11-1, 11-2, 11-5) are substantially equal in magnitude.

29. Method for operating a compressor (1) according to one of claims 25 to 28, characterized in that the performance of the means (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 the mass flow of the heat carrier fluid through the means (10, 10-1, 10-2, 10-3, 10-4, 10-5) and the supply temperature of the heat carrier fluid such that the outlet state of the compressed fluid is set at the outlet of the compressor (1) independently of the operating state of the compressor (1).

30. Use of a 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.