DE102017223128B3 - Heat transfer circuit with several cooling circuits and a heat transfer pressure control - Google Patents

Abstract

The invention relates to a heat transfer circuit (100, 200) for cooling at least two heat sources (1, 2, 3), in particular in a motor vehicle, comprising a fluid heat carrier, a first cooling circuit (10) for cooling a first, warmer heat source (1), at least one second cooling circuit (20, 30) for cooling a second, cooler heat source (2, 3), and in at least one of the cooling circuits (10, 20, 30) arranged in front of the heat source volume flow control means (13, 23, 33) and a arranged after the heat source pressure control means (14, 24, 34), and a method for adjusting a heat carrier circuit (100, 200).

Description

The invention relates to a heat carrier circuit for cooling at least two heat sources in a motor vehicle and to a method for adapting a heat transfer circuit.

In motor vehicles, heat transfer medium circuits are often used for cooling different heat sources, in particular for cooling drive components, energy storage devices or electrical consumers. In motor vehicles with internal combustion engines, this often means that with the internal combustion engine on the one hand and with electrical components (for example with a traction battery, so-called SuperCaps, a fuel cell, but also an electric drive machine of a hybrid vehicle) on the other hand heat sources with very different operating temperatures must be cooled.

In internal combustion engines must - especially because of the combustion processes - by means of the heat transfer often heat dissipated by surfaces having a surface temperature of several 100 ° C. For electrical machines, this temperature is usually not much higher than 80 ° C, because the typically used semiconductors and / or magnets could be damaged at higher temperatures. At a similar temperature level, for example, SuperCaps or fuel cells are operated with a Proton Exchange Membrane (PEM), which accordingly must also be cooled to such a temperature level. In the traction battery of hybrid vehicles often a maximum temperature in the range of 25 to 40 ° C must be maintained, with alkaline cell chemistries rather in a temperature range between 30 and 40 ° C, Li-lon-based cell chemistry rather in a temperature range below 30 ° C operated become. For the air conditioning of the passenger compartment, a heat pump has always been required.

Therefore, for example, in common hybrid vehicles, two or three or more separate cooling and / or refrigerant circuits are provided which are adapted to the temperature level of one or the other heat source in terms of their geometric design, the heat transfer volume used and / or the selection of the heat carrier used are.

Such separate cooling systems, in which the cooling circuits have different refrigerants and / or refrigerants, require that each refrigeration cycle component such as the piping, a surge tank, a heat exchanger, a compressor or a heat transfer pump, be present multiple times. This redundancy causes disadvantages in terms of cost, weight and space.

Therefore, motor vehicles are also known in which heat sources are cooled at different temperature levels with a single heat carrier circuit for heat dissipation. These integrated heat transfer medium circuits have the advantage that they require less space and less installation effort, in particular because of the common heat exchanger section and thus have less weight and lower costs.

However, these heat transfer medium circuits have the disadvantage that in the warmer, to be cooled heat source, a higher temperature difference to the heat transfer medium than in (the) cooler, to be cooled heat source (s). Because of the better heat transfer between the warmer temperature source and the heat transfer medium, it can be cooled better than the cooler heat source (s).

A sufficiently low heat carrier temperature in order to optimally cool the cooler heat source (s) due to a sufficient temperature difference can also be achieved only with great difficulty, in particular with an advantageously simple air cooling system.

The technical environment is on the DE 10 2014 115 831 A1 which shows an engine cooling system having a coolant control valve unit which as a unit separately controls the flows of the block coolant and the head coolant.

Furthermore, the technical environment on the DE 34 102 61 A1 which shows an evaporative cooling system for an internal combustion engine in which liquid coolant is sprayed by means of spray nozzles or other means on hot ions, in particular on the walls of the combustion chamber zones, wherein the amount of the sprayed coolant is controllable in dependence on the machine temperature or suitable operating parameters.

It is therefore an object of the invention to provide an improved heat carrier circuit for cooling at least two heat sources, in particular those at different temperature levels.

This object is achieved by a heat carrier circuit with the features of claim 1 and by a method for adjusting a heat carrier circuit with the features of claim 7. Advantageous embodiments are the subject of the dependent claims.

According to one aspect of the invention, a heat carrier circuit is provided for cooling at least two heat sources, in particular in a motor vehicle. The heat sources preferably have different operating temperatures of the respective surface to be cooled.

The heat transfer medium circuit comprises: a) a fluid heat transfer medium, the term heat transfer medium being understood to mean that there are generally heat transfer media which can be used in the sense of a coolant and / or a refrigerant, b) a first cooling circuit for cooling a first, warmer heat source, c) at least one second cooling circuit for cooling a second, cooler heat source, and according to an embodiment, a third cooling circuit for cooling a third, even cooler heat source, and d) in all cooling circuits, in particular in the fluid flow, arranged in front of the heat source Volume flow control means and a, in particular in the fluid flow, arranged after the heat source pressure control means. Preferably, in particular as a part of both and / or all cooling circuits, between the pressure control means and the volume flow control means, preferably designed as a condenser, heat exchanger, and optionally a heat transfer pump and / or a compressor.

Further, the heat transfer circuit e) comprises a control means which is adapted to control by means of the flow control means and by means of the pressure control means a heat transfer pressure, in particular of the heat carrier used, in a load path, in particular between the flow control means and the pressure control means, this cooling circuit, and thus preferably set a boiling temperature of the heat carrier at the heat source. The control means is adapted to adjust the heat carrier pressure so that the heat transfer medium evaporates when the operating temperature of the heat source is reached.

According to a further aspect of the invention, a method for adapting a heat carrier circuit according to an embodiment of the invention, comprising the steps: i) determining an operating temperature of the heat source of at least one cooling circuit, ii) determining a suitable boiling temperature of the heat carrier in the load path of the cooling circuit in Dependent on the specific operating temperature of the heat source, iii) determining a heat carrier pressure at which the determined boiling temperature of the heat carrier can be achieved, iv) determining - and preferably operating an operation of the cooling circuit also - each opening of the volume flow control means to a cooling demand adjust adjusted flow rate, and v) determining - and in an operation of the cooling circuit preferably also driving - a respectively suitable opening degree of the pressure control means to the determined heat carrier pressure , in particular in dependence on the opening degree of the volume flow control means to adjust.

Among other things, the invention is based on the finding that, in practice, the development of components to be cooled in the automotive industry is often the responsibility of that department for the component cooling which designs the component itself. In practice, this often means that drive components on the one hand and peripheral components on the other hand are cooled separately. With the upcoming integration of other electrical consumers or electric drive components and energy sources are added to be cooled components in the vehicle, which are often cooled separately.

In addition, there is an ever greater spread of the operating temperatures of the various surfaces to be cooled. The starting point of the invention is now the realization that, contrary to the practice often practiced in the development of motor vehicles optimally a single heat transfer medium circuit in the vehicle would have to be enough to cool several components to be cooled - even at different operating temperatures. So far, such solutions have often failed because when using a single heat carrier (which is indeed a prerequisite for the formation of a single, integrated cooling circuit), the heat removal can normally be optimal only at a certain operating temperature.

The invention is based inter alia on the idea that, on the one hand, for example, a phase transition of the heat carrier used - in particular from liquid to gaseous - can be a very good operating point for component cooling because of the absorption of the evaporation energy with respect to the operating temperature. The energy invested in the evaporation can be applied substantially completely from heat dissipated.

On the other hand, the invention is also based on the idea that with a single, defined heat transfer medium by influencing the pressure conditions on the component to be cooled (ie the heat source to be cooled at this load path) just this operating point with respect to the temperature at which the evaporation occurs, are affected can.

For example, one and the same heat carrier at a lower pressure level has a lower evaporation point (= boiling point) on than at a higher pressure level. This connection makes use of the invention by a pressure level can be adjusted for each cooling circuit by means of a volume flow control means and a pressure control means, which is tuned to the operating temperature of the surface to be cooled of the heat source (in terms of boiling point). As a heat carrier water, alcohols or in the air conditioning conventional refrigerants can be used, the latter in particular, if in one of the cooling circuits an operating case may occur in which a cooling to a temperature level below the ambient temperature is required.

In this way, it is possible, for example, with a water-glycol mixture as a heat carrier to cool by an integrated cooling circuit heat sources to very different temperature levels: this is the heat transfer, for example, with a relatively high pressure and a relatively high flow in a first load path to Cooling of the internal combustion engine introduced, with a lower pressure in a second load path for cooling electrical loads or an electric drive motor, and with even lower pressure in a third load path for cooling a traction battery of the motor vehicle.

Which combination of heat transfer pressure and heat transfer volume flow at which of the load paths (and thus the individual cooling circuits) must be able to reliably dissipate the heat generated in each case can be determined in each case according to the thermodynamics for each vehicle configuration present and according to an embodiment be predetermined by means of a control unit.

In this way, a single, integrated cooling circuit can be made available for all heat dissipations in the vehicle by means of the heat carrier. Diverse redundancies in the refrigeration cycle components and the associated disadvantages in terms of cost, weight and space are thus possibly eliminated.

According to one embodiment, such a cooling circuit can have a plurality of cooling circuits, in each case one of the cooling circuits, for example, the internal combustion engine at a temperature of up to 120 ° C, an electric machine at 80 ° C, a fuel cell at 80 ° C, SuperCaps at 40 ° C and / or a traction battery is cooled at below 30 ° C. Likewise, in one of the cooling circuits, a charge air of the internal combustion engine can be cooled, for example, at a temperature of the surface to be cooled of 20 ° C (indicated temperatures are circa values and based on the surface to be cooled).

In one embodiment, the heat carrier of the cooling circuit can be designed as, for example, water-based, coolant, if none of the components to be cooled has to be cooled at a temperature below an expected ambient temperature.

If such a cooling below the ambient temperature, however, already to be expected, such as in the cooling of batteries or the charge air, however, a refrigerant, for example, alcohol-based, must be used, which is characterized in that in the motor vehicle under economic and energy-efficient conditions, a boiling point is adjustable below the ambient temperature (in particular by means of volume flow control means and by means of the pressure control means of the corresponding cooling circuit).

In order to be able to adapt the heat carrier circuit to heat sources of different warmth, the control means is adapted to adjust the heat carrier pressure in the load path and thus in particular also the boiling temperature as a function of an operating temperature, in particular a surface to be cooled, the heat source that the cooling circuit assigned.

Preferably, the heat carrier pressure can be controlled in conjunction with a pressure sensing means. In particular, the pressure-sensing device can have a pressure sensor and / or a pressure-based, preferably experience-based, model. In particular, the pressure model may be part of an operating model of the refrigeration cycle. The pressure-detecting means is preferably set up to determine a current heat carrier pressure at at least one of the load paths, wherein the control means is arranged to take into account the determined values in the control of the heat carrier pressure.

According to one embodiment, the heat carrier pressure is controlled by the degree of opening of the volume flow control means and the pressure control means additionally determined in dependence on a currently determined value of the heat transfer fluid - and also preferably controlled in an operation of the cooling circuit - is.

So that the heat carrier pressure at the load path in each of the cooling circuits can be controlled separately, the volume flow control means and the pressure control means are arranged in a separately formed for the respective cooling circuit line section.

According to one embodiment, the heat carrier circuit has a heat exchanger, in particular with a heat exchanger section, which is part of both and / or all cooling circuits. This space can be saved, especially compared to the provision of a separate heat exchanger for each cooling circuit. The heat exchanger is preferably designed as a condenser, in particular with a condenser section, in order to convert the heat carrier, which may have been vaporized on the load paths, back into a liquid state.

According to one embodiment, the pressure of the fluid is increased before the heat exchanger by means of a compressor in order to reduce its boiling point sufficiently.

In order to be able to cool any number of heat sources at different temperature levels with an integrated heat carrier circuit, the heat transfer circuit according to one embodiment has at least one further cooling circuit for cooling a further, even cooler heat source. In this case, in the further cooling circuit in the fluid flow in front of the heat source, a flow control means and in the fluid flow to the heat source, a pressure control means is arranged, wherein the control means is adapted by means of the flow control means and by means of the pressure control means a boiling temperature of the heat carrier used in a load path of this cooling circuit between the Volume flow control means and the pressure control means to adjust.

Preferably, in at least one of the cooling circuits, the volume flow control means and / or the pressure regulating means comprises a throttle and / or a valve. For example, in the cooling circuit, all volume flow control means may each be designed as an electromagnetically actuable valve and all pressure control means may each be designed as an electrically actuable throttle.

In order optionally to support a phase change from liquid to gaseous at the load path (in particular at the surface to be cooled), according to an embodiment in at least one of the cooling circuits, the volume flow control means has a nozzle which is adapted to spray the heat carrier into the load path. Preferably, then a main spray axis of the nozzle is directed to the means of the cooling circuit to be cooled heat source.

Methods that are practiced according to an embodiment of the invention may be practiced for one or more or each of the refrigeration cycles.

In order to enable a simple adaptation of the cooling capacity of the heat carrier circuit, the opening degree of the volume flow control means and the opening degree of the pressure control means is coordinated according to one embodiment such that even with a change in the heat transfer volume flow through the load path a set heat transfer pressure remains at least substantially constant. In particular, the pressure adjustment to adjust the favorable boiling point in the interaction of the flow control means and the pressure control means. In particular, when the cooling demand increases, in particular, the cross-section (or opening degree) of the flow control means and at a suitable (determined by the control means) extent and the cross-section (or the degree of opening) of the pressure control means becomes larger, so that the pressure loss at the pressure control means a constant Pressure in the load path allows.

In order to match the cooling circuit to the heat sources to be cooled and their operating temperature, the operating temperature of the heat source 1) is determined according to an embodiment once before starting the heat transfer circuit, and / or 2) repeatedly, at regular intervals and / or determined continuously, and the respectively suitable Opening degree of the volume flow control means and the pressure control means adapted to optionally determined changes in the operating temperature.

• 1 einen Wärmeträgerkreislauf gemäß einer beispielhaften Ausführung der Erfindung mit drei parallelen Kühlkreisen und einem Wärmetauscher in einer schematischen Ansicht;
• 2 einen Wärmeträgerkreislauf gemäß einer weiteren beispielhaften Ausführung der Erfindung mit drei parallelen Kühlkreisen und einer Wärmetauscheranordnung in einer schematischen Ansicht.

Other features, advantages and applications of the invention will become apparent from the following description taken in conjunction with the figures. Show it:

• 1 a heat transfer circuit according to an exemplary embodiment of the invention with three parallel cooling circuits and a heat exchanger in a schematic view;
• 2 a heat transfer circuit according to another exemplary embodiment of the invention with three parallel cooling circuits and a heat exchanger assembly in a schematic view.

In 1 is a heat transfer circuit 100 illustrated according to an exemplary embodiment of the invention. The heat transfer circuit 100 has three parallel cooling circuits 10 . 20 and 30 on. The cooling circuit 10 is for cooling the heat source 1 set up, the cooling circuit 20 for cooling the heat source 2 and the cooling circuit 30 for cooling the heat source 3 ,

Each of the cooling circuits 10 . 20 and 30 can by means of a feed line arrangement 4 be supplied with heat transfer. The heat transfer is the individual cooling circuits 10 . 20 and 30 by means of a heat transfer compressor 9 fed under pressure.

At the feed line assembly 4 in the exemplary embodiment is an optionally provided expansion tank 40 arranged for possibly required volume compensation of the heat carrier.

The heat transfer medium is removed from the cooling circuits 10 . 20 and 30 by means of a discharge line arrangement 5 discharged and a compressor 9 fed, in which the vaporous heat carrier is compressed so that it is arranged in a downstream, preferably designed as a condenser heat exchanger 6 is cooled and condensed at a pressure-related higher boiling temperature, then again in the Zuführleitungsanordnung 4 to be provided.

The first cooling circuit 10 is set up in the exemplary embodiment, as the first heat source 1 to cool the internal combustion engine of the motor vehicle, not shown. The cooling circuit points to this 10 a first load route 11 on, which may be formed, for example, as a cooling jacket around the cylinder of the internal combustion engine. The heat carrier can be in the load path 11 by means of a heat transfer nozzle 12 be sprayed; However, a heat transfer inlet without a nozzle can also be provided.

In the heat transfer stream upstream of the load line 11 is a first volume flow control means 13 arranged, which is formed in the embodiment as a continuously controllable, electromagnetically actuated valve, but may be formed in other known manner. The volume flow control means 13 is by means of a control means 7 controllable, in particular with regard to a partial or complete release or blocking of the supply line arrangement 4 towards the heat transfer nozzle 12 (Among other things, the volume flow of the heat transfer medium is controlled).

In the heat transfer stream after the load path 11 is a first pressure regulating means 14 arranged, which is formed in the embodiment as a continuously controllable, electromagnetically actuated throttle, but can also be formed in other, known per se. Also the pressure control means 14 is by means of the control means 7 controllable, in particular with regard to a partial or complete release or blocking of the discharge line arrangement 5 towards the compressor 9 (Thus, among other things, a pressure of the heat carrier in the load path is controlled 11 ).

The second cooling circuit 20 is set up in the exemplary embodiment, as a second heat source 2 to cool an electrical load or an electric drive motor of the motor vehicle, not shown. The cooling circuit points to this 20 a second load route 21 on, which may be formed, for example, as a cooling jacket around a stator of the electric drive motor.

Analogous to the first cooling circuit 10 indicates the second cooling circuit 20 in the embodiment, a heat transfer nozzle 22 on, by means of which heat transfer medium in the load path 21 can be sprayed. In the heat transfer stream upstream of the load line 21 is a second volume flow control means 23 , After the load path, a second pressure control means 24 arranged. Both the volume flow control means 23 as well as the pressure control means 24 are preferably each formed at least substantially in the same way as the corresponding means 13 and 14 to the first cooling circuit 10 , Also the control by means of the control means 7 takes place analogously to the first cooling circuit 10 ,

The third cooling circuit 30 is set up in the exemplary embodiment, as a third heat source 3 to cool a traction battery of the motor vehicle, not shown. The cooling circuit points to this 30 a third load route 31 on, for example, as a piping system between the individual battery packs of the third heat source 3 can pass through.

Analogous to the first cooling circuit 10 and the second cooling circuit 20 indicates the third cooling circuit 30 in the embodiment, a heat transfer nozzle 32 on, by means of which heat transfer medium in the load path 31 can be sprayed. In the heat transfer stream upstream of the load line 31 is a third volume flow control means 33 , After the load path, a third pressure control means 34 arranged. Both the volume flow control means 33 as well as the pressure control means 34 are preferably each formed at least substantially in the same way as the corresponding means 13 . 14 . 23 and 24 to the first cooling circuit 10 and to the second cooling circuit 20 , Also the control by means of the control means 7 takes place analogously to the first cooling circuit 10 and to the second cooling circuit 20 ,

The following is the operation of the in 1 illustrated, exemplary cooling circuit 100 described in detail:

In the load range 11 of the cooling circuit 10 intended as a heat source 1 an internal combustion engine to be cooled. Accordingly, the surface to be cooled has a maximum temperature of about 120 ° C, possibly even more 90-80 ° C on. In the load range 21 of the cooling circuit 20 intended as a heat source 2 an electric drive motor to be cooled, the surface to be cooled has an operating temperature in the order of 80 ° C. In the load range 31 the cooling circuit 30 should as heat source 3 a traction battery of the drive motor are cooled, wherein the cooling takes place at an operating temperature of the surfaces to be cooled in the order of 30 ° C.

The absolute amount of heat to be dissipated is thus in the exemplary embodiment in most operating states in the cooling circuit 10 the biggest. Depending on the dimensions of the traction battery of the heat source 3 must also be in the cooling circuit 30 a relatively large amount of heat be removed. The electric motor of the heat source 2 produced in comparison with the other heat sources 1 and 3 in the embodiment, a significantly lower amount of heat.

According to the amount of heat to be removed in the respective cooling circuit, by means of the respective volume flow control means 13 . 23 respectively. 33 a suitable volume flow of the heat carrier can be adjusted.

To the individual cooling circuits 10 . 20 and 30 can optimally cool at the different operating temperatures mentioned above, a phase transition of the heat carrier can be used from liquid to gaseous by an additional heat dissipation is used, resulting from the application of the evaporation energy for the evaporation of the heat carrier.

It is in the exemplary embodiment in each load path 11 . 21 respectively. 31 by means of the respective pressure control means 14 . 24 respectively. 34 a pressure of the heat carrier in the load path adjusted such that there is a boiling temperature of the heat carrier below the respective operating temperature of the surface to be cooled.

Because of the cooling level at approx. 30 ° in the cooling circuit 30 comes in the embodiment as a heat carrier water-based coolant out of the question, because theoretically - but not economically and ecologically efficient in the vehicle - a pressure-induced lowering of the boiling point of a water-based coolant to less than 30 ° is possible. In other embodiments, with cool temperatures reliably above the expected ambient temperatures, a water-based coolant is of course possible. In the illustrated embodiment, an alcohol-based heat transfer medium having a generally lower boiling level and / or an industry-standard refrigerant is provided in its place.

The expected operating temperatures of the surfaces to be cooled in the individual load paths 11 . 21 and 31 are as well as those by means of individual cooling circuits 10 . 20 and 30 amount of heat to be dissipated in an operating model 8th deposited for the cooling circuit and / or entered. The operating model 8th also has an reference unit (that is to say preferably data records) in which suitable volume flows and / or suitable pressure values for the operation of the individual cooling circuits are provided for the said operating data 10 . 20 and 30 of the cooling circuit 100 are deposited.

Thus, by means of the control means 7 depending on the operating model 8th stored contexts in each cooling circuit 10 . 20 respectively. 30 a suitable interaction between the respective volume flow control means 13 . 23 . 33 and the respective pressure control means 14 . 24 . 34 be controlled.

Taking into account suitable pressure models and / or volume flow models, which are in the operating model 8th can be stored, can also be a dynamic control of the regulatory means 13 . 14 . 23 . 24 . 33 . 34 be achieved. Such a dynamic control can additionally or alternatively be achieved by the provision of suitable pressure and / or volumetric flow sensors, which are however not shown in the figures.

A heat transfer circuit 100 as in 1 illustrated in another exemplary embodiment also be adapted to only components (= heat sources 1 . 2 and 3 ) with a temperature level lower than that of the surfaces of an internal combustion engine to be cooled. For example, to a heat transfer circuit 100 be set up, an electric drive machine as a heat source 1 , electrical consumers as a heat source 2 and a traction battery as a heat source 3 to cool. In this case, the heat exchanger designed as a condenser 6 may be smaller due to the lower temperature spread of the heat sources to be cooled. Such a heat transfer circuit 100 comes, for example, in purely electrically driven vehicles in question.

In 2 is a heat transfer circuit 200 represented by the heat transfer circuit 100 according to 1 essentially differs in that for a more efficient cooling and optionally condensation of the heat carrier, a heat exchanger assembly 206 is provided, the individual, separate heat exchanger 206a . 206b and 206c for the respective cooling circuits 10 . 20 and 30 having. Accordingly, the heat transfer circuit 200 also a discharge line arrangement 205 with separate discharge lines 205a . 205b and 205 c on, in the course of which upstream of the heat exchanger assembly 206 one compressor each 209a . 209b . 209c is arranged. The feed line arrangement 4 is downstream of each one in the cooling circuits 10 . 20 and 30 after the capacitor 206a . 206b respectively. 206c arranged throttle (the throttles are controlled to maintain the different conditions in the individual capacitors).

The embodiment according to 2 allows as well as the embodiment according to 1 the use of a single heat transfer medium for all cooling circuits. The heat transfer circuit 200 according to 2 is due to the separate heat exchanger 206 for each cooling circuit, however, able to ensure a sufficient condensation of the heat carrier used even with a larger heat spread (for example, for cooling an internal combustion engine on the one hand and a lithium-ion battery on the other hand). For the benefits are visibly the simplicity of the cooling circuit less pronounced than in the embodiment according to 1 ,

For carrying out an exemplary method for adapting one of the exemplified heat transfer medium cycles 100 or 200 the following steps are performed: i) determining a respective operating temperature of the heat sources 1 . 2 and 3 in each of the cooling circuits 10 . 20 and 30 , ii) determining a suitable boiling temperature of the heat carrier in each of the load paths 11 . 21 respectively. 31 each cooling circuit 10 . 20 and 30 depending on the particular operating temperature of the heat source 1 . 2 respectively. 3 iii) determining a heat carrier pressure at which the determined boiling temperature of the heat carrier can be achieved, iv) determining and operating the refrigeration cycle 100 respectively. 200 Actuation - a respectively suitable opening degree of the respective volume flow control means 13 . 23 respectively. 33 and the respective pressure control means 14 . 24 respectively. 34 in order to set the determined necessary for sufficient cooling flow rate at the same time suitable pressure of the heat carrier.

LIST OF REFERENCE NUMBERS

100

Heat transfer circuit

1

first heat source (internal combustion engine)

2

second heat source (electric motor)

3

third heat source (traction battery)

4

Zuführleitungsanordnung

5

Abführleitungsanordnung

6

Heat exchanger (condenser)

7

control means

8th

operating model

9

Heat carrier compressor

10

first cooling circuit

11

load path

12

Wärmeträgerdüse

13

Flow control means

14

Pressure control means

20

second cooling circuit

21

load path

22

Wärmeträgerdüse

23

Flow control means

24

Pressure control means

30

third cooling circuit

31

load path

32

Wärmeträgerdüse

33

Flow control means

34

Pressure control means

40

surge tank

200

Heat transfer circuit

205

Abführleitungsanordnung

205a, b, c

discharge

206

Heat exchanger arrangement (capacitor arrangement)

206a, b, c

heat exchangers

209a, b, c

compressor

215a, b, c

throttle

Claims (10)

Heat transfer circuit (100, 200) for cooling at least two heat sources (1, 2, 3) in a motor vehicle, comprising - a fluid heat carrier, - a first cooling circuit (10) for cooling a first, warmer heat source (1), - at least one second Cooling circuit (20, 30) for cooling a second, cooler heat source (2, 3), and - in each of the cooling circuits (10, 20, 30) each arranged in front of the heat source volume flow control means (13, 23, 33) and after the Pressure control means arranged (14, 24, 34), - a control means (7) which is adapted, by means of the volume flow control means (13, 23, 33) and by means of the pressure control means (14, 24, 34) a heat transfer pressure in a load path ( 11, 21, 31) of this cooling circuit (10, 20, 30), characterized in that - the volume flow control means (13, 23, 33) and the pressure control means (14, 24, 34) respectively in a conduit section designed separately for the respective cooling circuit (10, 20, 30), and - the control means (7) is adapted to control the heat carrier pressure in the respective load path (11, 21, 31) in dependence on an operating temperature of the corresponding one Cooling circuit (10, 20, 30) associated heat source (1, 2, 3) to be adjusted so that the heat transfer evaporates when the operating temperature of the heat source. Heat transfer circuit (100, 200) according to one of the preceding claims, characterized by a heat exchanger (6) with a heat exchanger section, which is a part of both cooling circuits (10, 20, 30). Heat transfer circuit (100, 200) according to one of the preceding claims, characterized by at least one third cooling circuit (30) for cooling in each case a further, even cooler heat source (3), wherein in the further cooling circuit upstream of the heat source, a volume flow control means (33) and after Heat source, a pressure control means (34) is arranged, and wherein the control means (7) is adapted to adjust by means of the flow control means and by means of the pressure control means a boiling temperature of the heat carrier used in a load path (31) of this cooling circuit between the flow control means and the pressure control means. Heat transfer circuit (100, 200) according to one of the preceding claims, characterized in that in at least one of the cooling circuits (10, 20, 30), the volume flow control means comprises a heat transfer nozzle (12, 22, 32) which is adapted to the heat transfer in the Spraying load line (11, 21, 31). Heat transfer circuit (100, 200) according to one of the preceding claims, characterized by a pressure detecting means (8) which is adapted to determine a current heat transfer pressure on at least one of the load paths (11, 21, 31). Heat transfer circuit (100, 200) according to one of the preceding claims, characterized in that at least two of the cooling circuits (10, 20, 30) are arranged parallel to each other. Method for adapting a heat carrier circuit (100, 200) according to one of the preceding claims, characterized by the steps: - determining an operating temperature of the heat source (1, 2, 3) of at least one cooling circuit (10, 20, 30), - determining a suitable boiling temperature the heat carrier in the load path (11, 21, 31) of the cooling circuit as a function of the determined operating temperature of the heat source, - determining a heat transfer pressure at which the determined boiling temperature of the heat carrier can be achieved, - determining a respectively suitable opening degree of the volume flow control means (13, 23, 33) in order to set a volume flow adapted to the cooling requirement, and - determining a respectively suitable opening degree of the pressure control means (14, 24, 34) in order to set the determined heat carrier pressure. Method according to Claim 7 , characterized in that the degree of opening of the volume flow control means (13, 23, 33) and the degree of opening of the pressure control means (14, 24, 34) is coordinated such that even with a change in the heat transfer volume flow through the load path (11, 21, 31) a set heat transfer pressure remains at least substantially constant. Method according to one of Claims 7 or 8th , characterized in that the heat transfer pressure is controlled, in which the opening degree of the volume flow control means (13, 23, 33) and the pressure control means (14, 24, 34) is additionally determined in dependence on a current determined value of the heat transfer pressure. Method according to one of Claims 7 to 9 , characterized in that the operating temperature of the heat source (1, 2, 3) once before commissioning of the heat carrier circuit (100, 200) is determined, and / or that the operating temperature of the heat source is determined several times, at regular intervals and / or continuously, and the respectively suitable degree of opening of the volume flow control means (13, 23, 33) and the pressure control means (14, 24, 34) is adapted to any changes in the operating temperature which have been determined.

Images