DE102022106259A1 - Device for cooling a fluid to be compressed in a compressor and compressor with the 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 a compressor (1), in particular a refrigerant, with a heat transfer 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 conducting the fluid, at least one second flow channel (12, 12-1, 12-2, 12-3, 12-5) for conducting the heat transfer fluid and an inlet (13) and an outlet (14) for the heat transfer fluid. In addition, a core element (15-1, 15-2, 15-3, 15-4, 15-5) is designed in such a way 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) as a separate component on a longitudinal axis (6) between housing elements (2c, 2d) of a modular compressor (1 ) can be arranged or integrated into a housing of the compressor. The invention also relates to a compressor for compressing a vaporous fluid, in particular the refrigerant, with the device and a method for operating the compressor. The compressor can be used in the refrigerant circuit of an air conditioning system of a motor vehicle.

Description

The invention relates to a device for cooling a fluid to be compressed in a compressor, in particular a refrigerant, with a heat transfer fluid. The device has a first flow channel for conducting the fluid to be compressed in the compressor, a second flow channel for conducting the heat transfer fluid, and an inlet and an outlet for the heat transfer 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 used in the refrigerant circuit of an air conditioning system of a motor vehicle.

Compressors for mobile applications, in particular for air conditioning systems in motor vehicles, for conveying refrigerant through a refrigerant circuit, also referred to as refrigerant compressors, are known from the prior art. Such compressors are driven either via a belt pulley, which is connected to a drive unit of the motor vehicle via a belt, or electrically and are often designed as piston compressors with variable displacement or as scroll compressors, regardless of the refrigerant.

For example, conventional electrically driven scroll compressors have an electric motor for driving a compression mechanism. The electric motor and the compression mechanism formed with a fixed scroll and an orbiting scroll are arranged within a volume enclosed by a housing. The housing can be multi-part, in particular made of a housing element for accommodating the electric motor and a housing element for accommodating the compression mechanism, and preferably made of a metal, in particular aluminum. The orbiting scroll of the compression mechanism, in which a vaporous fluid, specifically a refrigerant, is compressed, is driven by a drive shaft connected to the electric motor.

In the case of the 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 the refrigerant sucked into the housing, also referred to as suction gas. In addition, further heat is transferred to the suction gas heated in this way by thermal 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 absorbed by the refrigerant affects the density of the refrigerant sucked in and thus the efficiency of the compressor's operation. The more heat is transferred to the refrigerant before it enters the compression mechanism, the higher the temperature and specific volume and the lower the density of the refrigerant in the suction condition. A higher temperature of the sucked-in 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 in turn cause more intensive heat conduction within the wall of the housing and thus greater heating of the suction gas.

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 demands 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, especially when a predetermined limit temperature is exceeded. As a result, the refrigerant circuit, especially when using carbon dioxide as a refrigerant, is power-controlled or limited.
When the compressor is used in a refrigerant circuit of an air conditioning system of a motor vehicle, the regulation of the output of the compressor in turn leads to a perceptible reduction in thermal comfort within the passenger compartment.

The object of the invention is to provide a device for cooling a fluid to be compressed in a compressor, specifically a vaporous fluid as refrigerant in a refrigerant compressor. The compressor should be able to be operated with maximum efficiency, in particular while avoiding derating of the output due to excessively high temperatures of the compressed fluid. The heat removed from the fluid should be usable within a connected system, for example an air conditioning system or a thermal management system of a motor vehicle. The device should have a minimum installation space and be of compact design and be able to be produced in a simple manner and at low cost.

The object is solved by the objects with the features of the independent patent claims. Further developments are specified in the dependent patent 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 transfer fluid. The device has at least one first flow channel for conducting the fluid to be compressed in the compressor, at least one second flow channel for conducting the heat transfer fluid, and an inlet and an outlet for the heat transfer fluid.

According to the conception of the invention, a core element is designed such that the device for cooling the compressed fluid with the core element can be arranged as a separate component on a longitudinal axis between two housing elements of a modular compressor or can be integrated into a housing of the compressor. Since the device is provided in particular for cooling the already compressed fluid, the device is arranged in the flow direction of the fluid in the assembled state of the compressor following a compression mechanism.
The arrangement between two housing elements of a modular compressor allows the device to be retrofitted in conventional compressors.

The outer contours and dimensions of the core element and the housing elements can correspond to one another. The outer contours and dimensions of the core element and the housing elements preferably match.

According to a development of the invention, the core element is in the form of a plate, in particular a disk. The inlet and the outlet of the heat transfer fluid are preferably each designed as a socket and arranged on an outer surface of the core element.
The core element preferably has at least one passage opening for the compressed fluid running in the direction of the longitudinal axis, which corresponds to an axis of symmetry of the plate or disk.

According to a preferred embodiment of the invention, the core element is formed in the area of an outer circumference with a constant wall thickness in the direction of the longitudinal axis and on at least one lateral surface in a center of the surface with a flat depression of uniform depth in the direction of the longitudinal axis. A flat depression is understood to mean a surface that is offset inward in the direction of the longitudinal axis with respect to 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 aligned parallel to one another and arranged at a distance from one another.
Alternatively, the core element can be designed as a ring running around on an outer circumference with a structure made of stacked sheet-metal plates in the center.

One advantage of the invention is that the core element has recesses on the at least one lateral surface, each of which extends from the surface into the core element. The recesses are formed in particular on the at least one lateral surface in the area of the flat depression.

According to a development of the invention, at least one plate-shaped, in particular disc-shaped, intermediate element is provided, which rests in a plane perpendicular to the longitudinal axis with a first side on the at least one lateral surface of the core element and covers the recesses in a fluid-tight manner. The plate-shaped intermediate element preferably has flat surfaces.
The recesses covered with the intermediate element form the second flow channels of the heat transfer fluid. The second flow channels preferably each extend from an inlet distributor connected to the inlet to an outlet opening connected to the outlet and can be acted upon in parallel with heat transfer fluid.

According to a further advantageous embodiment of the invention, the outer contours and dimensions of the at least one intermediate element and the at least one depression correspond to one another, so that the intermediate element is arranged within the depression. The at least one intermediate element can in particular have the shape of a flat, circular metal sheet and the at least one depression can have the shape of a circle. An outer diameter of the intermediate element can correspond to an outer diameter of the depression plus a clearance for assembly and an expansion of the depression in the direction of the longitudinal axis can correspond to a wall thickness of the intermediate element.
In the alternative configuration of the core element as a ring running around the outer circumference with a structure made of stacked sheet-metal plates in the center, the outer contours and dimensions of the at least one intermediate element and an inner lateral surface of the ring running around the outer circumference of the core element can be designed to correspond to one another.

A further advantage of the invention is that the at least one intermediate element has at least one passage 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, which rests on a second side of the at least one intermediate element in a plane spanned perpendicularly to the longitudinal axis. The formations formed in the outer element are covered by the intermediate element—as fluid-tight as possible—in such a way that the first flow channels are formed.

The core element is provided in particular on both lateral surfaces in the center with a depression of uniform depth in the direction of the longitudinal axis and recesses. The recesses are each covered in a fluid-tight manner by an intermediate element arranged in the recess, each having a first side of the intermediate element. In addition, an outer element with formations rests on the second side of the intermediate elements, so that the formations formed in the outer element are covered by the intermediate element—as fluid-tight as possible.

The device for cooling the fluid to be compressed in the compressor is advantageously a stacked plate heat exchanger with a capacity that can be scaled by the number of stacked plates and a defined size. The device is preferably designed as a soldered or welded, in particular laser-welded, component made of extruded and formed elements made of aluminum. In this way, additional sealing elements between the heat transfer fluid circuit and the fluid to be compressed in the compressor can be dispensed with.
Within the device, the heat transfer fluid and the fluid to be compressed in the compressor are preferably conducted in a countercurrent or a cross-countercurrent.
A coolant or the fluid to be compressed in the compressor, in particular the refrigerant, can be used as the heat transfer fluid. When a coolant is used as the heat transfer fluid, the device is designed as a refrigerant/coolant heat exchanger. If the refrigerant is used as a heat transfer fluid, the device corresponds to a refrigerant-refrigerant heat exchanger, which is then operated, for example, as a circuit-internal heat exchanger.

According to a further preferred embodiment 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 each extend from the inlet opening to at least one branch and are supplied with fluid parallel to one another. The second outer element can have at least one branch such that the first flow channels each extend from at least one branch to the outlet opening and are supplied with fluid parallel to one another.

The at least one passage opening for the compressed fluid formed in the core element, the at least one passage 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 aligned with one another and thus along an axis arranged so that the compressed fluid flows out of the branch of the first outer element and flows without deflections on a straight flow path through the passage openings of the intermediate element and the core element into the branch of the second outer element.
If more than one branch is formed within the outer elements, each branch of the first outer element is assigned a passage opening in the intermediate element, a passage opening in the core element and a branch in the second outer element. If more than one intermediate element is formed, each intermediate element is provided with corresponding passage openings.

According to an alternative embodiment of the invention, the core element is designed in the shape of a hollow circular cylinder. A wall element in the form of a hollow circular cylinder and a cylindrical central element are preferably arranged inside the core element and are aligned coaxially with the longitudinal axis. A diameter of an inner lateral surface of the core element can correspond to a diameter of an outer lateral surface of the wall element, while a diameter of an inner lateral surface of the wall element can correspond to a diameter of a lateral surface of the central element, so that the respective lateral surfaces abut against one another in a fluid-tight manner.

The wall element advantageously has a recess for the second flow channel of the heat transfer fluid on the outer lateral surface on. Alternatively, the recess for the second flow channel can also be formed on the inner lateral surface of the core element.
The wall element preferably has a recess for the first flow channel on the inner lateral surface. Alternatively, the recess for the first flow channel can also be provided on the lateral surface of the central element.

A further advantage of the invention is that the recesses of the flow channels are designed in the form of a helical groove running in the circumferential direction, in particular an axial spiral, the inlet and outlet of which are spaced apart from one another 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 heat transfer fluid mass flow 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 in the housing, and a compression mechanism driven by the drive device.

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

According to a development of the invention, the compression mechanism has an orbiting scroll and a fixed scroll. The device for cooling the fluid, which is arranged in particular between an outlet of the fluid from the fixed scroll and an outlet of the compressor, is integrated as a separate component between housing elements of the housing arranged on a longitudinal axis or in the housing of the compressor, or as a component of the fixed scroll educated. When the device is formed as a component of the fixed scroll, the fixed scroll and thus the fluid conveyed within the scroll 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 of 25 mm to 30 mm, so that the installation space of the compressor is increased only insignificantly by integrating the device.

According to an advantageous embodiment of the invention, the device for cooling the fluid is arranged within a volume subjected to a high-pressure level of the fluid, so that a pressure prevailing within the first flow channel for conducting the fluid and a pressure within a volume which is at a wall delimiting the flow channel of externally adjacent, prevailing pressures are essentially the same. The low pressure difference over the wall delimiting the flow channel requires only a very small wall thickness of the outer elements. Only the wall enclosing the second flow channel for conducting the heat transfer fluid has to be designed to be robust enough 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 this case, a performance of the device for cooling the fluid to be compressed in the compressor is regulated by the device via a heat transfer fluid mass flow and a flow temperature of the heat transfer fluid, so that an exit state of the compressed fluid at an outlet of the compressor is set independently of an operating state of the compressor.

The advantageous embodiment of the invention allows the use of the compressor for a refrigerant of a refrigerant circuit of an air conditioning system of a motor vehicle.

• - Reduktion der mittleren Verdichtertemperatur, insbesondere der Temperatur des verdichteten Fluids am Auslass des Verdichters ohne Reduktion der Leistung im Kältemittelkreislauf - beispielsweise liegt die Temperatur am Auslass des Verdichters mit Kohlenstoffdioxid als Kältemittel unter 100°C anstelle von 175 °C ohne die erfindungsgemäße Vorrichtung, dadurch
  • - reduzierte Temperaturanforderung an Kältemittelleitungen im Kreislauf, insbesondere nach dem Verdichter, verbunden mit dem Senken der Systemkosten durch den Einsatz von Niedertemperaturkältemittelleitungen auf der Hochdruckseite des Kreislaufs,
  • - Erhöhen des volumetrischen und des isentropen Wirkungsgrades, (insbesondere bei Kühlung der feststehenden Spirale im Scrollverdichter)
    • - höhere Kälteleistung im System beziehungsweise geringere Antriebsleistung des Verdichters bei vergleichbaren Kälteleistungen, beispielsweise Steigern des Massenstroms um 4 % bei Reduktion der Antriebsleistung um 6 % mit Kohlenstoffdioxid als zu verdichtendes Fluid,
  • - Erhöhen des elektrischen Wirkungsgrads aufgrund der indirekten Kühlung von Inverter und Elektromotor der Antriebsvorrichtung des Verdichters,
  • - Vermeiden von Leistungsabregelungen und Drehzahlverringerungen am Verdichter infolge zu hoher Temperaturen des verdichteten Fluids am Auslass des Verdichters,
  • - Reduktion der Wärmeleitung in Richtung der Längsachse des Verdichters durch thermodynamische Unterbrechung der Leitung,
  • - Reduktion der Temperatur des verdichteten Fluids am Einlass in den Gaskühler/Kondensator infolge einer reduzierten Wärmelast beziehungsweise Gaskühler/Kondensator mit geringerer Leistung, da ein signifikanter Anteil der Wärme im Verdichter über den Wärmeträgerfluidkreislauf abgeführt oder kein externer Gaskühler/Kondensator benötigt wird,
  • - maximale Lebensdauer interner Komponenten,
• - Vermeiden von Verlusten durch die Auskopplung der Wärme in den Wärmeträgerfluidkreislauf,
• - gezielte Regelung des Wärmeträgerfluidmassenstroms und gezieltes Nutzen der Verdichterabwärme zum Heizen, beispielsweise der Batterie, dadurch Erhöhen der Reichweite bei elektromotorisch angetriebenen Kraftfahrzeugen und Verzicht auf zusätzliche elektrische Beheizung,
• - Optimierung des Thermomanagements für mehr Komfort der Fahrzeuginsassen sowie
• - Verringern der Geräuschemission beziehungsweise der Schallemission und der Druckpulsationen im System durch die Vorrichtung zum Kühlen infolge des Nutzens des inneren Hohlraumvolumens als Schalldämpfer noch gesteigert.

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 various advantages compared to the devices from the prior art:

• - Reduction of the average compressor temperature, in particular the temperature of the compressed fluid at the outlet of the compressor without reducing the performance in the refrigerant circuit - for example, the temperature at the outlet of the compressor with carbon dioxide as the refrigerant is below 100°C instead of 175°C without the device according to the invention, as a result
  • - reduced temperature requirement on refrigerant lines in the circuit, especially after the compressor, combined with lowering of system costs through the use of low-temperature refrigerant lines on the high-pressure side of the circuit,
  • - Increase in volumetric and isentropic efficiency (especially when cooling the fixed scroll in scroll compressors)
    • - higher cooling capacity in the system or lower drive power of the compressor with comparable cooling capacities, for example increasing the mass flow by 4% with a reduction in drive power by 6% with carbon dioxide as the fluid to be compressed,
  • - increase in electrical efficiency due to indirect cooling of the inverter and electric motor of the compressor drive device,
  • - Avoidance of power derating and speed reductions on the compressor due to high temperatures of the compressed fluid at the compressor outlet,
  • - Reduction of heat conduction in the direction of the longitudinal axis of the compressor through thermodynamic interruption of the line,
  • - Reduction of the temperature of the compressed fluid at the inlet to the gas cooler/condenser as a result of a reduced heat load or gas cooler/condenser with lower capacity, since a significant proportion of the heat in the compressor is dissipated via the heat transfer fluid circuit or no external gas cooler/condenser is required,
  • - maximum lifespan of internal components,
• - Avoidance of losses due to the decoupling of the heat in the heat transfer fluid circuit,
• - targeted control of the heat transfer fluid mass flow and targeted use of the compressor waste heat for heating, for example the battery, thereby increasing the range of electric motor vehicles and dispensing with additional electrical heating,
• - Optimization of the thermal management for more comfort of the vehicle occupants as well
• - Reducing the noise emission or the sound emission and the pressure pulsations in the system by the device for cooling as a result of the use of the inner cavity volume as a sound absorber is increased.

• 1: einen elektrisch angetriebenen Verdichter mit einer im Verdichter integrierten Vorrichtung zum Kühlen eines in dem Verdichter zu verdichtenden Fluids in einer Schnittdarstellung,
• 2: Komponenten des Verdichters mit einer ersten Ausführungsform der integrierten Vorrichtung zum Kühlen des Fluids in einer perspektivischen Ansicht,
• 3a und 3b: die Komponenten des Verdichters mit der integrierten Vorrichtung zum Kühlen des Fluids aus 2 in einer perspektivischen sowie einer seitlichen Schnittdarstellung,
• 4a: die erste Ausführungsform der Vorrichtung zum Kühlen des im Verdichter zu verdichtenden Fluids aus den 3a und 3b im montierten Zustand in einer perspektivischen Ansicht,
• 4b und 4c: die erste Ausführungsform der Vorrichtung zum Kühlen des im Verdichter zu verdichtenden Fluids aus den 3a und 3b mit einem Kernelement, Zwischenelementen und Außenelementen jeweils in einer perspektivischen Explosionsdarstellung,
• 5a bis 5e: mit der ersten Ausführungsform der Vorrichtung aus 2, einer zweiten Ausführungsform der Vorrichtung, einer dritten Ausführungsform der Vorrichtung, einer vierten Ausführungsform der Vorrichtung und einer fünften Ausführungsform der Vorrichtung verschiedene Ausführungsformen in einer Zusammenstellung,
• 6a und 6b: das Kernelement der zweiten Ausführungsform der Vorrichtung zum Kühlen des im Verdichter zu verdichtenden Fluids aus 5b mit einem Einlass und einem Auslass eines Wärmeträgerfluids jeweils als ein Einzelelement in einer perspektivischen Seitenansicht sowie
• 6c und 6d: das Kernelement aus den 6a und 6b mit den Strömungsrichtungen des im Verdichter zu verdichtenden Fluids und des Wärmeträgerfluids jeweils in einer Seitenansicht.

Further details, features and advantages of embodiments of the invention result from the following description of exemplary embodiments with reference to the associated drawings. Show it:

• 1 : an electrically driven compressor with a device integrated in the compressor for cooling a fluid to be compressed in the compressor, in a sectional view,
• 2 : components of the compressor with a first embodiment of the integrated device for cooling the fluid in a perspective view,
• 3a and 3b : the components of the compressor with the integrated device for cooling the fluid 2 in a perspective and a lateral sectional view,
• 4a : the first embodiment of the device for cooling the fluid to be compressed in the compressor from the 3a and 3b in the assembled state in a perspective view,
• 4b and 4c : the first embodiment of the device for cooling the fluid to be compressed in the compressor from the 3a and 3b with a core element, intermediate elements and outer elements, each in a perspective exploded view,
• 5a until 5e : with the first embodiment of the device 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 different embodiments in one combination,
• 6a and 6b : the core element of the second embodiment of the device for cooling the fluid to be compressed in the compressor 5b with an inlet and an outlet of a heat transfer fluid, each as a single element in a perspective side view and
• 6c and 6d : the core element from the 6a and 6b with the directions of flow of the fluid to be compressed in the compressor and of the heat transfer fluid, each in a side view.

Out of 1 is an electrically driven compressor 1 of a vaporous fluid, especially for an air conditioning system of a motor vehicle for conveying 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 integrated in the compressor 1 10 for cooling the fluid to be compressed in the compressor 1 in a sectional view. The housing 2 has several housing elements 2a, 2b, 2c, 2d.

The electric motor 4 and the compression designed as a scroll compressor with an orbiting scroll 5a and a fixed scroll 5b mechanism 5 are arranged within a volume enclosed by the housing 2 . The spirals 5a, 5b are preferably made of a metal, in particular aluminum or steel. A first housing element 2a for accommodating the electric motor 4, a second housing element 2b for accommodating a transmission mechanism for transmitting the movement from a rotor of the electric motor 4 to the orbiting scroll 5a of the compression mechanism 5, and a third housing element 2c for accommodating the compression mechanism 5 and preferably made of a metal, in particular made of aluminum.
The orbiting scroll 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 scroll 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 by 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 so-called hot gas at a high temperature.
The housing elements 2a, 2b, 2c, 2d, which are aligned on the longitudinal axis 6 and enclose the common volume, are coupled to one another via a connection arrangement 3. The first housing element 2a and the fourth housing element 2d are each arranged on an outside formed in the axial direction.

The connection arrangement 3 is designed as a screw connection with through openings and blind holes with an internal thread. The blind bores with an internal thread are provided exclusively on the first housing element 2a, while the other housing elements 2b, 2c, 2d are each designed with through-openings for receiving screws or threaded bolts. The passage openings, which are correspondingly aligned with one another, allow the screws or threaded bolts to be passed through, which are each accommodated within a blind hole in the first housing element 2a. 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, 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 essentially corresponds to the outer diameters of the adjacent housing elements 2c, 2d. In addition, the device 10 is also designed with through openings as elements of the connection arrangement 3 and for passing through the screws or threaded bolts, so 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 .
The device 10 for cooling the fluid to be compressed in the compressor 1 is consequently formed between the compression mechanism 5 accommodated 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 primarily cooled after the compression process to the high pressure level and thus as hot gas, before the refrigerant flows out of the compressor 1 through the refrigerant outlet 7 .

After leaving the compression mechanism 5 through the refrigerant outlet 5c, the refrigerant is conducted through the device 10 in first flow channels 11, while a heat transfer fluid absorbing the heat from the refrigerant flows through the second flow channels 12 of the device 10 designed as a heat exchanger.

In 2 The third housing element 2c and the fourth housing element 2d are 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, which is arranged between the housing elements 2c, 2d and is therefore integrated in the compressor 1, in a perspective view shown. The third housing element 2c is shown with a transparent wall for better identification of the device 10-1. From the 3a and 3b follow the components of the compressor 1 with the integrated device 10-1 2 in a perspective and a lateral sectional view.

The device 10-1 has an inlet 13 and an outlet 14 for the heat transfer fluid, in particular a coolant. The inlet 13 and the outlet 14 of the heat transfer fluid are each designed as a socket and are arranged on an outer lateral surface of a plate-shaped core element 15-1. The outer diameter of the plate-shaped core element 15-1 essentially corresponds to the outer diameters of the adjacent housing elements 2c, 2d. Through openings 16 of the device 10-1 for passing through the screws or threaded bolts of the connection arrangement 3 are provided on the core element 15-1.

The plate-shaped core element 15-1 is formed on the side surfaces with recesses which each extend from the corresponding surface into the core element 15-1. The recesses are closed by plate-shaped intermediate elements 18 - 1 a , 18 - 1 b resting on the surfaces in the direction of the longitudinal axis 6 . The intermediate elements 18-1a, 18-1b rest in planes perpendicular to the longitudinal axis 6 on the surfaces of the core element 15-1 and cover the recesses. The recesses provided in the core element 15-1 that are closed in this way form the second flow channels 12-1 of the heat transfer fluid. The intermediate elements 18-1a, 18-1b each have the shape of a flat, circular metal sheet.

The core element 15-1 has a constant wall thickness in the direction of the longitudinal axis 6, particularly in the area of the outer diameter. In the center of the core member 15-1, the core member 15-1 is formed on both surfaces with a circular recess 19-1 having a uniform depth. The outer diameter of the circular indentation 19-1 corresponds to the outer diameter of the circular intermediate element 18-1a, 18-1b, while the extent of the indentation 19-1 in the direction of the longitudinal axis 6, which corresponds to the depth, corresponds to the thickness of the sheet-like intermediate element 18 -1a, 18-1b corresponds. The intermediate elements 18-1a, 18-1b can consequently each be arranged in alignment within the core element 15-1 with a surface pointing outwards in the direction of the longitudinal axis 6 and thus away from the core element 15-1. The core element 15-1 then has a flat and closed surface in the direction of the longitudinal axis 6 in connection with the intermediate elements 18-1a, 18-1b arranged on the core element 15-1.

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

Plate-shaped outer elements 17a, 17b rest against the surfaces of the intermediate elements 18-1a, 18-1b aligned in alignment with the core element 15-1. The outer elements 17a, 17b embodied as sheets have special formations, produced in particular by means of deep-drawing, which, in conjunction with the flat surface of the intermediate element 18-1a, 18-1b, provide the first flow channels 11-1 for the refrigerant, enclosing the circumference. The formations produced by deep-drawing are circumferentially closed by the plate-shaped intermediate elements 18 - 1 a , 18 - 1 b that bear in the direction of the longitudinal axis 6 . The intermediate elements 18-1a, 18-1b in turn rest on the outer elements 17a, 17b in planes perpendicular to the longitudinal axis 6 and cover the formations produced by deep-drawing. The areas formed in the outer elements 17a, 17b that are closed in this way 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 equipped with the plate-shaped core element 15-1, the sheet-like intermediate elements 18-1a, 18-1b which rest on the core element 15-1 on both sides with inner surfaces and the outer surfaces of the intermediate elements 18- 1a, 18-1b adjacent outer elements 17a, 17b as a plate heat exchanger, specifically as a refrigerant-coolant heat exchanger. The design as a plate heat exchanger enables easy scaling of the heat output to be transferred. The heated coolant can be used to heat other components, for example the air conditioning system or the drive train of the motor vehicle, such as the battery, so that other components for heating, such as an electric PTC heater, can be dispensed with.

According to an alternative embodiment that is not shown, 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 formed in one piece.

In 4a is the first embodiment of the device 10-1 for cooling the fluid to be compressed in the compressor 1 from the 3a and 3b shown in the assembled state in a perspective view, while from the 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 is shown in a perspective exploded view. In particular, in 4c Flow paths of the refrigerant and the heat transfer fluid indicated by the device 10-1.

The refrigerant compressed to the high pressure level flows through an inlet opening 20 formed in the first outer element 17a in the direction of flow 26 into the device 10-1 and through an outlet opening 21 formed in the second outer element 17b out of the device 10-1. After flowing in, the refrigerant is on between the first outer member 17a and the first intermediate element 18-1a formed first flow channels 11-1 evenly distributed.
The first flow channels 11-1, which each 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 in such a way that the refrigerant mass flow is divided into two partial mass flows after it has flowed through the inlet opening 20 . A first partial mass flow of the refrigerant is conducted through first flow channels 11-1 ending at a first branch 22a, while a second partial mass flow of refrigerant is conducted through first flow channels 11-1 ending at a second branch 22a.

The partial mass flows of the refrigerant then flow out of the first flow channels 11-1 through passage openings 23a formed in the first intermediate element 18-1a and through passage openings 24 formed in the core element 15-1 and through passage openings 23b formed in the second intermediate element 18-1b to the second intermediate element 18-1b formed branches 22b.
The passage openings 23a, 23b of the intermediate elements 18-1a, 18-1b, the passage openings of the core element 15-1 and the branches 22a, 22b of the outer element 17a correspond to one another in arrangement and flow cross section. In this case, a branch 22a, 22b, a passage opening of an intermediate element 18-1a, 18-1b and a passage opening 24 of the core element 15-1 are aligned with one another.

The first flow channels 11-1 formed between the second outer element 17b and the second intermediate element 18-1b each extend from a branch 22b to the outlet opening 21 and are charged with refrigerant in parallel. The second outer element 17b, like the first outer element 17a, has two branches 22b in such a way that the two partial mass flows of the refrigerant are divided equally between the first flow channels 11-1. The first partial mass flow of the refrigerant is conducted into first flow channels 11-1 opening at a first branch 22a, while the second partial mass flow of refrigerant is conducted into first flow channels 11-1 opening at a second branch 22b. The partial mass flows of the refrigerant are brought together at the outlet opening 21 . The refrigerant mass flow, which has been cooled as it flows through the device 10-1, flows out of the device 10-1 in the direction of flow 26 through the outlet opening 21. The heat was transferred from the refrigerant to the heat transfer fluid.

The heat transfer fluid flows through the inlet 13 designed as a socket in the flow direction 25 into the device 10-1 and through the outlet 14, also designed as a socket, out of the device 10-1. After flowing in, the heat transfer fluid is evenly distributed to the second flow channels 12-1 formed between the core element 15-1 and the intermediate elements 18-1a, 18-1b. In this case, second flow channels are provided on both sides of the core element 15 - 1 , so that the heat transfer fluid mass flow is divided into two partial mass flows after it has flowed through the inlet 13 .
The second flow channels 12-1, which each extend from an inlet distributor 12-1a connected to the inlet 13 to an outlet opening 12-1b connected to the outlet 14, are acted upon in parallel with heat transfer fluid. After flowing through the inlet 13, the two partial mass flows of the heat transfer fluid are each divided into the second flow channels 12-1 at the inlet distribution 12-1a. The two partial mass flows of the heat transfer fluid brought together at the outlet opening 12-1b are discharged together through the outlet 14 from the device 10-1. The heat transfer fluid mass flow, which is heated as it flows through the device 10-1, flows out of the device 10-1 in the direction of flow 25.

In the 5a until 5e are out with the first embodiment of the device 10-1 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 different embodiments of the device 10 for cooling a fluid to be compressed in the compressor in a compilation shown. Identical elements and components of the devices 10, 10-1, 10-2, 10-3, 10-4, 10-5 are provided with the same reference symbols. Regarding their design and function, reference is made to the statements made above.

The main differences between the devices 10-1, 10-2, 10-3 from the 5a until 5c lie in the design 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 transfer fluid and in the case of the core element 15-2 of the device 10- 2 the recesses for the first flow channel 11-2.

The recesses of the second flow channels 12-1 of the first embodiment of the device 10-1 are, as for the 4b and 4c executed, arranged on both sides of the core element 15-1 and each extend from the inlet manifold 12-1a to the outlet port 12-1b parallel to each other. The recesses of the second flow channels 12-1 provided on both sides of the core element 15-1 are formed independently of one another, in particular without intermediate connections through the core element 15-1. The heat transfer fluid is guided in a radial flow in each of the second flow channels 12-1.

Compared to the first embodiment of the device 10-1 after 5a are the recesses of the second flow channel 12-2 of the second embodiment of the device 10-2 5b designed in such a way that the heat transfer fluid is passed through the device 10-2 as an undivided and thus one-part mass flow. The heat transfer fluid mass flow is guided into recesses on both sides of the core element 15-2, which are also connected to one another via intermediate connections running in particular in the direction of the longitudinal axis 6 through the core element 15-2. The heat transfer fluid mass flow is consequently conducted alternately on both sides along the core element 15-2, the change of sides taking place through the intermediate connections formed in the core element 15-2. The heat transfer fluid is guided alternately in the radial direction and axial direction as it flows through the second flow channel 12-2.
In addition, compared to the first specific embodiment, the refrigerant flows after the device 10-1 5a , not through the passage openings 24 on the shortest flow path in the axial direction through the core element 15-2, but, like the heat transfer fluid, is guided through a first flow channel 11-2 provided in the core element 15-2 into recesses on both sides of the core element 15-2. The recesses are connected to one another via intermediate connections running in the direction of the longitudinal axis 6 through the core element 15 - 2 . The refrigerant mass flow is thus also conducted alternately on both sides along the core element 15-2, with the change of sides taking place through the intermediate connections formed in the core element 15-2.

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

Another essential difference between the devices 10-1, 10-3 on the one hand and the device 10-2 on the other hand lies in the design of the intermediate elements 18-1a, 18-2a, 18-1b, 18-2b in connection with the core elements 15-1, 15-2 provided depressions 19-1, 19-2 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 the 5a and 5c each have the shape of a flat, circular metal sheet, the intermediate elements 18-2a, 18-2b of the device 10-2 are made 5b on the outer circumferences are folded outwards in the direction of the longitudinal axis 6, i.e. in the direction pointing away from the core element 15-2, and thus have a significantly greater depth, in particular on the outer circumferences, than the intermediate elements 18-1a, 18-1b of the devices 10-1, 10-3. Since the depth of the intermediate elements 18-2a, 18-2b 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 greater extent 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 aligned with the end edges pointing in the direction of the longitudinal axis 6, each with the surface pointing outwards in the direction of the longitudinal axis 6 and thus away from the core element 15-2 within the core element 15-2 be arranged.

The main difference between the devices 10-1, 10-2, 10-3 from the 5a until 5c on the one hand and the device 10-4 5d on the other hand, in the formation of the core element 15-1, 15-2, 15-3, 15-4 in a solid form of a single plate of the devices 10-1, 10-2, 10-3 and as a ring running around the outer circumference a structure formed in the center of individual, stacked sheet-like plates of the device 10-4. The plates are each aligned in a plane aligned perpendicular to the direction of the longitudinal axis 6 .
The two plates, each designed as sheet metal and arranged on 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, special formations, produced in particular by deep drawing, which are each connected to the flat Surface of the intermediate element 18-2a, 18-2b provide the second flow channels 12-1 for the heat transfer fluid. The formations are through each in the direction of Longitudinal axis 6 adjacent, plate-shaped intermediate elements 18-2a, 18-2b closed peripherally. The intermediate elements 18-2a, 18-2b each lie in planes perpendicular to the longitudinal axis 6 on the plates of the core element 15-4 and cover the formations produced by deep-drawing.
In the direction of the longitudinal axis 6, a flat, sheet-like plate is advantageously arranged between the two plates, each designed as a sheet metal with formations, 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 contours in terms of shape and dimensions, which correspond to an inner lateral surface of the ring of the core element 15-4 running around the outer circumference.

The plate-shaped intermediate elements 18-2a, 18-2b of the device 10-4 5d are, as well as the intermediate elements 18-2a, 18-2b of the device 10-2 5b , folded at the outer circumferences outwards in the direction of the longitudinal axis 6, in particular in the direction pointing away from the core element 15-4. The intermediate elements 18-2a, 18-2b of the device 10-4 can be aligned with the end edges pointing in the direction of the longitudinal axis 6, each with the surfaces pointing outwards in the direction of the longitudinal axis 6 and thus away from the ring of the core element 15-4 running around the outer circumference be arranged inside the ring of the core element 15-4.

The main difference between the devices 10-1, 10-2, 10-3 from the 5a until 5c on the one hand and the device 10-5 5e on the other hand lies 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 transfer fluid.
In comparison to the devices 10-1, 10-2, 10-3, the core element 15-5 of the device 10-5 is designed essentially as a hollow circular cylinder without recesses. A wall element 27 in the form of a hollow circular cylinder is arranged inside the core element 15 - 5 , while a cylindrical central element 28 is arranged inside the wall element 27 . The core element 15-5, the wall element 27 and the central element 28 are aligned coaxially with one another along the longitudinal axis 6, which corresponds to the axis of symmetry. The diameter of the inner surface area of core element 15 - 5 corresponds to the diameter of the outer surface area of wall element 27 , while the diameter of the inner surface area of wall element 27 corresponds to the diameter of the surface area of central element 28 . The core element 15-5, the wall element 27 and the central element 28 are in fluid-tight contact with one another with their lateral surfaces.

The wall element 27 is formed on the outer lateral surface with a recess for the second flow channel 12-5 of the heat transfer fluid and has a recess on the inner lateral surface for the first flow channel 11-5 of the refrigerant. The recess for the second flow channel 12-5 is covered outwards in the radial direction by the core element 15-5, in particular by means of the inner lateral surface of the core element 15-5. The recess for the first flow channel 11 - 5 is covered inward in the radial direction by the central element 28 , in particular by means of the outer lateral 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 each in the form of a helical groove or axial spiral running in the circumferential direction, the inlet and outlet of which are spaced apart from one another in the direction of the longitudinal axis 6 are. The core element 15-5 of the device 10-5 has a greater extent 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 run parallel to one another.

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

The main difference between the core elements 15-1, 15-2 of the devices 10-1, 10-2 lies on the one hand in the design of the recesses of the second flow channels 12-1, 12-2 of the heat transfer fluid and on the other hand in the design of the recesses in the first flow channel 11-2 of the refrigerant within the core member 15-2. The same elements and components of the devices 10-1, 10-2 are provided with the same reference numbers. Regarding their design and function, reference is made to the statements made above.

Compared to the first embodiment of the device 10-1 after 4b the second flow passage 12-2 is formed in the core member 15-2 without being divided into parallel passages. The second Flow channel 12-2 runs alternately on both upper sides of the core element 15-2 in recesses formed in the surfaces. The alternating guidance of the second flow channel 12-2 on the upper sides of the core element 15-2 is made possible by means of intermediate connections pointing in the direction perpendicular to the upper sides and thus in the direction of the longitudinal axis. The intermediate connections are each designed as circular through-holes or as through-holes in the form of elongated holes between the upper sides. The recesses and interconnections are arranged to each other that the heat transfer fluid according to 6d is guided alternately along both sides of the core element 15-2 in the direction of flow 30 and flows essentially in a zigzag shape through the core element 15-2. The heat transfer fluid is guided alternately in the radial direction and axial direction as it flows through the second flow channel 12-2. The direction of flow 30 is illustrated by the arrows. The arrows marked with a solid line represent the flow of the heat transfer fluid on the visible side of the core element 15-2, while the arrows marked with a broken line represent the flow of heat transfer fluid on the hidden side of the core element 15-2.

In addition, a first flow channel 11-2 for the refrigerant is also provided in the core element 15-2, which is designed in the same way as the second flow channel 12-2. The first flow channel 11-2 consequently also runs alternately 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 pointing in the direction perpendicular to the upper sides and thus in the direction of the longitudinal axis. The recesses and interconnections of the first flow channel 11-2 are in turn arranged to one another in such a way that the refrigerant according to 6c in the flow direction 29 alternately on both sides along the core element 15-2 and flows through the core element 15-2 essentially in a zigzag shape. When flowing through the first flow channel 11-2, the refrigerant is guided alternately in the radial direction and in the axial direction. The direction of flow 29 is again illustrated using the arrows. Here, the arrows indicated by the solid line represent the flow of the refrigerant on the visible side of the core member 15-2, while the arrows indicated by the broken line represent the flow of refrigerant on the concealed side of the core member 15-2.
The refrigerant thus flows 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 between the second outer element 17b and the second Between element 18-2b trained first flow channels 11-1 passed.

Reference List

1

compressor

2

Housing

2a

first housing element

2 B

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 compression mechanism 5

6

longitudinal axis

7

Refrigerant outlet compressor 1

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

contraption

11, 11-1, 11-2, 11-5

first flow channel refrigerant

12, 12-1, 12-2, 12-3, 12-5

second flow channel heat transfer fluid

12-1a

inlet distribution

12-1b

outlet mouth

13

Heat transfer fluid inlet

14

Heat transfer fluid outlet

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

core element

16

passage 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

deepening

20

Inlet port refrigerant

21

Refrigerant outlet port

22a, 22b

branch

23a, 23b

passage opening

24

passage opening

25

Direction of flow of heat transfer fluid

26

direction of flow of refrigerant

27

wall element

28

central element

29

direction of flow of refrigerant

30

Direction of flow of heat transfer fluid

Claims (30)

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 transfer fluid, having at least one first flow channel (11, 11-1, 11-2, 11-5) for conducting the fluid, at least one second flow channel (12, 12-1, 12-2, 12-3, 12-5) for conducting the heat transfer fluid and an inlet (13) and an outlet (14) for the heat transfer fluid, characterized in that a core element (15-1, 15-2, 15-3, 15-4, 15-5) is designed 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) as a separate component on a Longitudinal axis (6) between housing elements (2c, 2d) of a modular compressor (1) can be arranged or integrated into a housing of the compressor. device (10, 10-1, 10-2, 10-3, 10-4, 10-5). 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 designed to correspond to one another. device (10, 10-1, 10-2, 10-3, 10-4). claim 1 or 2 , characterized in that the core element (15-1, 15-2, 15-3, 15-4) is plate-shaped. device (10, 10-1, 10-2, 10-3, 10-4). claim 3 , characterized in that the core element (15-1, 15-2, 15-3, 15-4) has at least one passage opening (24) running in the direction of the longitudinal axis (6) for the compressed fluid. device (10, 10-1, 10-2, 10-3, 10-4). claim 3 or 4 , characterized in that the core element (15-1, 15-2, 15-3) in the area of an outer circumference with a constant wall thickness in the direction of the longitudinal axis (6) and on at least one lateral surface in a center with a flat recess (19 -1, 19-2) of uniform depth in the direction of the longitudinal axis (6), or that the core element (15-4) is designed as a ring running around an outer circumference with a structure made of stacked sheet-metal plates in the center. Device (10, 10-1, 10-2, 10-3, 10-4) according to one of claims 3 until 5 , characterized in that the core element (15-1, 15-2, 15-3, 15-4) has recesses on at least one lateral surface, which each extend from the surface into the core element (15-1, 15-2 , 15-3, 15-4) are formed extending inward. device (10, 10-1, 10-2, 10-3). 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). device (10, 10-1, 10-2, 10-3, 10-4). 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 extends in a plane perpendicular to the longitudinal axis (6) with a first side on the at least one lateral surface of the core element (15-1, 15-2, 15-3, 15-4), the recesses is arranged to cover fluid-tight, the covered recesses the second flow channels (12-1, 12-2, 12-3) of the heat transfer fluid form. Device (10, 10-1) according to claim 8 , characterized in that the second flow channels (12-1) each of a with the Inlet (13) connected to the inlet manifold (12-1a) to one with the outlet (14) connected to the outlet port (12-1b) are formed extending and acted upon in parallel with heat transfer fluid. device (10, 10-1, 10-2, 10-3). 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 designed to correspond to one another, so 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 lateral surface of a ring of the core element (15-4) running around an outer circumference are designed to correspond to one another. 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 flat, circular sheet metal and the at least one recess (19-1) is circular, with an outer diameter of the intermediate element (18-1a, 18-1b) correspond to an outer diameter of the recess (19-1) plus a clearance for assembly and an extension of the recess (19-1) in the direction of the longitudinal axis (6) to a wall thickness of the intermediate element (18-1a, 18-1b). Device (10, 10-1, 10-2, 10-3, 10-4) according to one of Claims 8 until 11 , characterized in that the at least one intermediate element (18-1a, 18-1b, 18-2a, 18-2b) has at least one passage opening (23a, 23b) running in the direction of the longitudinal axis (6) for the compressed fluid. Device (10, 10-1, 10-2, 10-3, 10-4) according to one of Claims 8 until 12 , characterized in that at least one plate-shaped outer element (17a, 17b) is formed with formations, which is in a plane perpendicular to the longitudinal axis (6) on a second side of the at least one intermediate element (18-1a, 18-1b, 18-2a , 18-2b) is arranged in abutting manner, the formations formed in the outer element (17a, 17b) being covered by the intermediate element (18-1a, 18-1b, 18-2a, 18-2b) and in this way the first flow channels (11-1) are trained. device (10, 10-1, 10-2, 10-3). Claim 13 , characterized in that the core element (15-1, 15-2, 15-3) on the lateral surfaces in the center each with a depression (19-1, 19-2) of uniform depth in the direction of the longitudinal axis (6) and recesses is formed, wherein the recesses are each provided with a first side of the intermediate element (18- 1a, 18-1b, 18-2a, 18-2b) are covered in a fluid-tight manner, and that on the second sides of the intermediate elements (18-1a, 18-1b, 18-2a, 18-2b) an outer element (17a, 17b ) is arranged in abutting manner with formations, the formations being covered by the intermediate element (18-1a, 18-1b, 18-2a, 18-2b). Device (10, 10-1, 10-2, 10-3, 10-4) according to one of claims 3 until 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. device (10, 10-1, 10-2, 10-3, 10-4). claim 15 , characterized in that the first outer element (17a) has at least one branch (22a), the first flow channels (11-1) each extending from the inlet opening (20) to at least one branch (22a) and being acted upon in parallel with fluid are trained. device (10, 10-1, 10-2, 10-3, 10-4). claim 15 or 16 , characterized in that the second outer element (17b) has at least one branch (22b), the first flow channels (11-1) each extending from at least one branch (22b) to the outlet opening (21) and being acted upon in parallel by fluid are. Device (10-5) according to claim 1 or 2 , characterized in that the core element (15-5) is designed in the form of a hollow circular cylinder. Device (10-5) according to Claim 18 , characterized in that inside the core element (15-5) a hollow circular cylindrical wall element (27) and inside the wall element (27) a cylindrical central element (28) are arranged, which are aligned coaxially to the longitudinal axis (6). Device (10-5) according to Claim 18 , characterized in that a diameter of an inner lateral surface of the core element (15-5) corresponds to a diameter of an outer lateral surface of the wall element (27) and a diameter of an inner lateral surface of the wall element (27) corresponds to a diameter of a lateral surface of the central element (28) and the respective lateral surfaces abut against one another in a fluid-tight manner. Device (10-5) according to claim 19 or 20 , characterized in that the wall element (27) is formed on an outer jacket surface with a recess for the second flow channel (12-5) of the heat transfer fluid. Device (10-5) according to one of claims 19 until 21 , characterized in that the wall element (27) is formed on an inner lateral surface with a recess for the first flow channel (11-5). Device (10-5) according to Claim 21 or 22 , characterized in that the recess of the flow channel (11-5, 12-5) is designed in the form of a helical groove running in the circumferential direction, in particular an axial spiral, the inlet and outlet of which are arranged at a distance from one another in the direction of the longitudinal axis (6). . Device (10, 10-1, 10-2, 10-3, 10-4, 10-5) according to one of Claims 1 until 23 , characterized in that within the core element (15-1, 15-2, 15-3, 15-4, 15-5) a control element, in particular a valve, for controlling the heat transfer fluid mass flow is integrated. Compressor (1) for compressing a vaporous fluid, in particular a refrigerant, having a housing (2), a drive device (4) arranged in the housing (2) and a compression mechanism (5) driven by the drive device (4), characterized in that in the flow direction of the fluid after the compression mechanism (5) a device (10, 10-1, 10-2, 10-3, 10-4, 10-5) for cooling the fluid according to one of Claims 1 until 24 is trained. Compressor (1) after Claim 25 , characterized in that the compression mechanism (5) is formed of an orbiting scroll (5a) and a fixed scroll (5b), and that the device (10, 10-1, 10-2, 10-3, 10-4, 10-5) between an outlet of the fluid from the fixed scroll (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 in the housing of the compressor is formed integrally or - is formed as a component of the fixed scroll (5b). Compressor (1) after 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 expansion in the direction of the longitudinal axis (6) in the range from 25 mm to 30 mm. Compressor (1) according to one of Claims 25 until 27 , characterized in that the device (10, 10-1, 10-2, 10-3, 10-4, 10-5) is arranged for cooling the fluid within a volume acted upon under a high pressure level of the fluid, so that a within a first flow channel (11, 11-1, 11-2, 11-5) for conducting the fluid and a pressure prevailing within a volume which delimits the flow channel (11, 11-1, 11-2, 11-5). Wall adjacent, prevailing pressure are essentially the same size. Method for operating a compressor (1) according to one of Claims 25 until 28 , characterized in that an output 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) via a heat transfer fluid mass flow through the device ( 10, 10-1, 10-2, 10-3, 10-4, 10-5) and an inlet temperature of the heat transfer fluid is regulated, so that an exit state of the compressed fluid at an outlet of the compressor (1) is independent of an operating state of the compressor (1) is set. Use of the compressor (1) according to one of Claims 25 until 28 for a refrigerant of a refrigerant circuit of an air conditioning system of a motor vehicle.

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