KR102080807B1 - Device for heat transfer for a refrigerant circuit of an air conditioning systme of a motor vehicle and air conditioning system with the device - Google Patents

Abstract

FIELD OF THE INVENTION The present invention relates to heat transfer devices 9a, 9b for coolant circuits 2 ', 2 "of air conditioning systems 1', 1" of automobiles, in particular coolant-air-heat transferers operating as vaporizers. The inlet 54 and outlet 55, the first collection tubes 50a, 50b and the second collection tubes 51a, 51b, as well as between the collection tubes 51a, 51b and Tube members 52-1 and 52-2 arranged in parallel and aligned with respect to each other. In the devices 9a and 9b for heat transfer, devices 57a and 57b for the deposition of the gas coolant from the liquid coolant are formed integrally. In this case, the apparatuses 9a and 9b for heat transfer include vaporization regions 64a and 64b solely for the action of the liquid coolant and overflow regions 65a and 65b solely for the action of the gas coolant.
The present invention also relates to an automotive air conditioning system 1 ', 1 "having a coolant circuit 30 and a coolant circuit 2', 2", wherein the coolant circuits 2 ', 2 " Heat transfer devices 9a, 9b according to the invention.

Description

Heat transfer device for coolant circuit of automotive air conditioning system and air conditioning system with the device

The present invention relates to a heat transfer device for a coolant circuit of an air conditioning system of a motor vehicle, in particular a coolant-air-heat transferer operating as a vaporizer. The apparatus includes inlets and outlets for coolant, first and second collection tubes, as well as tube members extending between the collection tubes and arranged in parallel with one another.

The invention also relates to an air conditioning system for regulating the air in a passenger space of a motor vehicle having a coolant circuit and a coolant circuit. The coolant circuit is formed with the heat transfer device.

In automobiles known in the art, the waste heat of the engine is used to heat the supply air for the passenger compartment. This waste heat is transferred to the air conditioning system by the coolant circulating in the engine coolant circuit, where it is transferred to the air flowing into the passenger space through the heater heat transfer. Known devices having a coolant-air-heat transferer which relates heating performance from the cooling water circuit of an efficient combustion engine of the vehicle drive are required for the pleasant heating of the passenger space to meet the overall heating needs of the passenger space when the ambient temperature is low. You no longer reach the level. The same applies to air conditioning installations in automobiles using hybrid drives, ie electric motor drives as well as automobiles using combustion engine drives.

If the overall heating demand of the passenger compartment cannot be met by heating from the engine's cooling water circuit, for example, an additional, such as an electrical resistance heater or fuel heater, which is abbreviated in English abbreviation as PTC ("Positive Temperatur Coefficient-Thermistor"). Heating measures are required. The same applies to air conditioning equipment in automobiles or fuel cell vehicles which are driven purely by electric motors. A more efficient means for heating the air for the passenger space is a heat pump using air as the heat source, in which case the coolant circuit is used not only as a means of heating but also as an additional heating measure.

An air conditioning system in which an electrical resistance heater is connected downstream can, on the one hand, be manufactured cost-effectively and used in any vehicle, but involves a very large demand for electrical energy because of the passenger space upon overflow of the carburetor of the coolant circuit. This is because the supply air for the air is first cooled and / or dehumidified and then heated by an electrical resistance that directly transfers heat to the supply air or cooling water circuit.

The operation of conventional air conditioning systems operating as heat pumps is practically efficient, but also requires very large structural spaces to be placed inside the vehicle where no structural space for the air conditioning system is secured. In particular, not only is the cost of manufacture and maintenance rising but also the need for a large structural space is a hindrance.

For the combined cooling plant mode and the heat pump mode, that is to say not only for the heating mode but also for the subsequent heating mode, also referred to as reheating-operation, the air-air-heating pump of the prior art is designed to draw heat from the ambient air. Absorb. Thus, ambient air is used as a heat source for vaporization of the coolant. Conventional air-air-heating pumps employ heat transfer for heat transfer between the coolant and the surroundings, heat transfer to supply heat to the coolant to be regulated in the passenger space, and heat from the coolant to the air to be regulated for the passenger space. Heat transfer for delivery. Performance is transferred between coolant and air, respectively.

The air to be supplied to the passenger space in the so-called "reheat" or subsequent heating mode is cooled, in this case dehumidified, and then slightly heated again. In this mode of operation the subsequent heating performance required is lower than the cooling performance required for cooling and dehumidification of the air.

DE 10 2012 111 672 A1 describes a coolant circuit in an air conditioning system for regulating the air in the passenger compartment of a motor vehicle. The coolant circuit is formed for combined operation in the cooling plant mode and the heat pump mode and for the subsequent heating mode, and control of the passenger space as well as heat transfer, first expander for transferring heat between the compressor and the coolant and the surroundings. A heat transfer for supplying heat to the coolant to the coolant, a heat transfer for transferring heat from the coolant to the air to be regulated for the passenger space, and a second expander following in the flow direction of the coolant.

DE 10 2011 100 301 A1 describes a vehicle air conditioning system with a coolant circuit capable of operating as a heat pump. The coolant circuit includes a compressor, a valve body disposed between the inlet side of the external heat transfer under the action of the air and the internal space condenser, an expander for expansion of the coolant, a three-way valve, as well as an internal vaporizer.

The coolant circuits comprise one branched system each consisting of connecting lines that are not easy to integrate into existing structural space. In addition, additional valves and coolant reservoirs arranged at low pressure levels, designed for large volumes, each require a large construction space. In addition, the valve includes a very high internal density which results in increased system cost.

In this case, a heat transfer for transferring heat between the ambient air of the air-air-heating pump and the coolant, also referred to as an external heat transfer or ambient heat transfer under the action of air, is provided outside the housing of the air conditioning system at the front side of the vehicle. In particular, it is arranged outside the air conditioning system, in particular through the wind through the action of the air.

Ambient heat transfer is operated as a condenser / gas cooler to provide heat from the coolant to the ambient air during operation of the coolant circuit in the cooling plant mode, and absorbs heat from the ambient air as a vaporizer during operation of the coolant circuit in the heat pump mode. To work. Thus, the ambient heat transfer is designed to operate in two functions, but as a result such a design is not optimally designed for either function, and therefore must find some sort of compromise.

These different functions result in partially contradictory design criteria for heat transfer. The heat transfer operating as a condenser / gas cooler, for example, must be designed for high coolant pressure, where the wall thickness must be set very large with respect to the flow cross section, so that the flow cross section for the condenser / gas cooler, It is provided substantially smaller than the flow cross section of a heat transferer operating as a vaporizer at a lower coolant pressure level. The small flow cross section of the ambient heat transferr results in high pressure losses when the heat transferer operates as a vaporizer, which is a significant design criterion that severely degrades the overall performance and efficiency of the air conditioning system.

In addition, during operation of the coolant circuit in the heat pump mode, the coolant is introduced into the ambient heat transfer with a vapor content in the range of 20% to 60%. The vapor content of the coolant is included only to an insignificant amount to transfer heat from the ambient air to the coolant, but it crucially causes pressure loss during perfusion of the ambient heat transfer.

The pressure loss of the coolant during the operation of the ambient heat transfer as a vaporizer results in a decrease in the temperature of the coolant, and consequently the coolant at the inlet to the ambient heat transfer has a higher temperature at the outlet. In order to avoid the risk of freezing the ambient heat transfer, the maximum temperature difference between the temperature of the air entering the ambient heat transfer and the temperature of the coolant is in particular limited to the range of 2K to 10K. The maximum allowable temperature difference is then related to the temperature of the air entering the ambient heat transfer and the temperature of the coolant at the location with the lowest temperature in the vaporizer, ie at the outlet. Thus, the largest temperature difference occurs between the air entering the ambient heat transfer and the temperature of the coolant at the outlet of the coolant from the vaporizer. Possible overheating of the coolant is not taken into account. In this case, the inlet of the coolant entering the ambient heat transfer is provided with a temperature difference smaller than the allowable temperature difference. The greater the pressure loss on the coolant side, the smaller the temperature difference at the inlet at which the coolant enters the surrounding heat transfer, and then less heat can be absorbed from the ambient air used to heat the passenger space.

In systems known in the art, at least partially gaseous coolants are introduced into the ambient heat transferr, resulting in unwanted pressure losses and consequently limiting the heat that can be transferred to the maximum from ambient air by the coolant, For example, it occupies up to 3 kW.

At temperatures in the range of 0 ° C. and at temperatures of air below 0 ° C., the heat transfer surface of the vaporizer can be frozen. As a result of absorbing heat from the air, the relative air humidity of the cooled air rises. Upon reaching the dew point temperature, water vapor present in the air condenses and is deposited as water on the heat transfer surface. In this case, water condensed from air at the heat transfer surface is fixed with ice when the surface temperature is 0 ° C and below 0 ° C. As the ice layer increases, the heat transfer surface on the air side and the heat transfer on the air side decrease, resulting in a decrease in heat transfer between the air and the vaporized coolant.

US 6 457 325 B1 has an air conditioning system with a vaporizer to control the air to be supplied to the passenger space, as well as a device for the deposition of ambient heat transfer, expander, gas coolant which can act as a compressor, gas cooler / condenser. It is described. The device for deposition of gas coolant, which is arranged between the gas cooler / condenser and the vaporizer, comprises a chamber with an inlet connected to the gas cooler / condenser, as well as a vapor outlet connected to the vaporizer via a bypass line, as well as a liquid coolant connected to the vaporizer. For the discharge. By forming a device for the deposition of the gaseous coolant from the liquid coolant, it is ensured that only the liquid coolant is directed towards the vaporizer.

Using only a device for the deposition of gas coolant from the liquid coolant, which is arranged before the vaporizer in the flow direction of the coolant, only the liquid coolant is guided in the vaporizer, and consequently the coolant circuit can be operated efficiently. On the other hand, a coolant circuit having an apparatus for such a deposition, a bypass line having an expansion valve disposed in the line, a vaporizer, and a connection line disposed between the deposition apparatus and the vaporizer includes a plurality of components formed separately from each other. In addition, these parts can impart a high mass to the vehicle and even take a large place in the structural space of a very limited vehicle. In addition, additional regulators are needed along with the inflator disposed in the bypass line, which further increases the complexity of the system and, in addition, makes it difficult to match the regulation strategy.

It is therefore an object of the present invention to provide an ambient heat transferr that can only act as a vaporizer, which is the minimum heat loss on the coolant side during operation and thus the maximum heat that can be transferred from the ambient air to the coolant. It includes. As a heat transferr for absorbing heat from ambient air, the ambient heat transferer must be optimally designed.

The ambient heat transferr must be able to be integrated into an air conditioning system for a motor vehicle, where the air conditioning system absorbs heat from the surroundings through the ambient heat transfer as needed and releases heat to the surroundings through components other than the surrounding heat transfer. The air conditioning system can be operated in the cooling installation mode and the heat pump mode as well as in the subsequent heating mode. In this case, the ambient air must be used according to each mode of operation, for example as a heat source during operation in the heat pump mode, as well as as a heat sink during operation in the cooling plant mode for example. In addition, the air conditioning system should be able to be operated efficiently and compactly, minimizing the risk of freezing of the vaporizer in the coolant circuit, for example for heat transfer by air.

In this case, the coolant circuit of the air conditioning system not only incurs the smallest operating costs, manufacturing costs and maintenance costs, but also must be structurally simple and contain the minimum number of components necessary to cover the minimum construction space. Should be.

This problem is solved by an object or method having the features of the independent claims of the claims. Further refinements are described in the dependent claims.

This problem is solved by a heat transfer device, in particular a coolant-air-heat transferer, which acts as a vaporizer for a coolant circuit of an automotive air conditioning system. The apparatus includes inlets and outlets for the coolant, first and second collection tubes, as well as tube members extending between the collection tubes and arranged parallel to each other.

According to the concept of the invention, an apparatus for the deposition of gaseous coolant from liquid coolant is formed integrally in the device for heat transfer. To this end, the apparatus for heat transfer comprises only a vaporization zone for the action of the liquid coolant and a convection zone for the action of the gas coolant only.

Preferably, the outlet for the coolant is formed in the second collection tube.

According to a first alternative embodiment of the invention, the collection tubes are arranged aligned in a vertical direction and are connected to each other via tube members arranged in a horizontal direction parallel to each other.

According to one refinement of the invention, an apparatus for the deposition of gas coolant from liquid coolant is integrated in the first collection tube.

The inlet for the coolant is advantageously formed in the first collection tube.

Also preferably, the invasion apparatus comprises a separating member arranged in a vertical direction, which separates the internal volume of the first collecting tube into a liquid region and a gas region.

A further advantage of the invention is that the tube member connecting the liquid region of the first collection tube with the second collection tube forms a vaporization region and the tube member connecting the gas region of the first collection tube with the second collection tube is overflowed. To form an area. In this case, the tube member forming the vaporization region and the tube member forming the overflow region are formed differently and / or arranged separately from each other.

According to a second alternative embodiment of the invention, the collecting tubes are aligned in a horizontal direction and connected to each other via tube members arranged in a direction perpendicular to one another.

According to one refinement of the invention, an apparatus for the deposition of gas coolant from the liquid coolant is arranged to connect the collection tubes to each other between the first collection tube and the second collection tube.

Preferably, the inlet for the coolant is formed in the apparatus for the deposition of the gas coolant from the liquid coolant.

Advantageously, the device for the deposition of the gaseous coolant from the liquid coolant is arranged in the vertical direction and parallel to the tube members.

According to one preferred embodiment of the present invention, the apparatus for the deposition of gas coolant from liquid coolant comprises a liquid region and a gas region. In this case, the liquid region is connected to the first collection tube and the gas region is connected to the second collection tube.

Advantageously, as well as the first collection tube, the tube members connecting the first collection tube with the second collection tube form a vaporization region, and the second collection tube forms the overflow region.

The various advantages of the device according to the invention for transferring heat of the coolant circuit, in particular of the air conditioning system of an automobile, are summarized as follows:

-Minimum coolant side pressure loss,

Maximum heat absorption from ambient air, and

-Minimal risk of freezing of the heat transfer surface on the ambient air side by maintaining the required temperature difference.

Furthermore, the object of the present invention is, in particular in the cooling installation mode, according to the invention for regulating the air in the passenger space of an automobile equipped with a coolant circuit and a coolant circuit for operation in a heating pump mode as well as in a subsequent heating mode. Solved by the air conditioning system.

According to the concept of the invention, the coolant circuit is formed with a heat transfer device having the above mentioned features.

According to one refinement of the invention, the coolant circuit comprises only a coolant-coolant-heat transfer, first expander which can act as a condenser / gas cooler for heat transfer between the coolant and coolant in the coolant circuit in the flow direction of the coolant. But also a first coolant-air-heat transfer for air conditioning of the supply air for the passenger space. The coolant circuit is formed with a transfer device for circulation of coolant, a first coolant-air-heat transferr for heating the supply air for the passenger space, a second coolant-air-heat transferr, as well as a coolant-coolant-heat transferr do.

The coolant circuit also includes a device for heat transfer as a second coolant-air-heat transferr that can only act as a vaporizer. In this case, the second expander is located upstream of the second coolant-air-heat transfer unit in the flow direction of the coolant. The second coolant-air-heat transfer as well as the second expander are jointly disposed in the first flow path.

The cooling installation mode is used above all for cooling, the heat pump mode is used for heating, and the subsequent heating mode is used for the subsequent heating of the supply air in the passenger space to be adjusted. For subsequent heating modes, the feed air was cooled and / or dehumidified prior to subsequent heating.

Heat transfer is referred to as a condenser when the coolant is in liquid phase, for example, during sub-critical operation of a coolant circuit such as using coolant R134a or at certain ambient conditions with carbon dioxide. Part of the heat transfer occurs at a constant temperature. In the case of over-critical operation or over-critical heat transfer in the heat transfer, the temperature of the coolant continues to decrease. In this case the heat transfer is also referred to as a gas cooler. Operation above the threshold may occur using, for example, carbon dioxide coolant in certain ambient conditions or in the manner in which the coolant circuit operates.

The second coolant-air-heat transferr of the coolant circuit and the second coolant-air-heat transferr of the coolant circuit are advantageously arranged inside the plant module and subjected to the action of air in turn in the order mentioned in the flow direction of the air. Is arranged.

According to one refinement of the invention, the installation module, in particular arranged in the front area of the vehicle, is capable of perfusion by air discharged from the passenger space, or ambient air, or mixed air consisting of air and ambient air discharged from the passenger space. Is formed.

According to a first alternative embodiment of the invention, the first coolant-air-heat transfer unit and the second coolant-air-heat transfer unit are arranged in a flow-through manner with respect to each other in the coolant circuit.

Advantageously the coolant circuit comprises a second flow path with a valve. In this case the first flow path extends with the second expander as well as the second coolant-air-heat transfer, and the second flow paths each extend from the branch position to the confluence position, so that the second flow path results in the first flow. It is formed as a bypass parallel to the path.

According to a second alternative embodiment of the invention, the first coolant-air-heat transfer unit and the second coolant-air-heat transfer unit are arranged to be able to flow through in parallel to each other in the coolant circuit.

A further advantage of the present invention is that the first flow path with the second expander and the second coolant-air-heat transferr extends from the branching position to the joining position. In this case, the first expander, the first coolant-air-heat transferr, and the third expander are formed in the second flow path. The third expander is disposed downstream of the coolant-air-heat transferr. The second flow path is likewise formed to extend from the branched position to the joined position.

The various advantages of the air conditioning system according to the invention with a heat transfer device according to the inventive concept are summarized as follows:

By using a lossy heat flow chart for heating the passenger compartment, using a minimum of energy to regulate, in particular cooling, dehumidifying and / or heating the supply air in the passenger compartment,

A coolant-air-heat transferer specially formed for operation as a vaporizer is used, especially for use in operation in a heat pump mode to absorb heat from the environment at low external temperatures, where higher external temperatures and cooling are required Heat is released to the environment through different components than the coolant-air-heat transfer,

Not only increases performance, efficiency and service life,

Providing sufficient comfort inside the passenger compartment,

Use of structurally simple coolant circuits that can be integrated for use in the known construction of existing vehicles and in the construction space provided, including minimum construction space, minimum weight and minimum component count.

Minimum operating costs, manufacturing costs and maintenance costs are achieved.

Further additional details, features and advantages of embodiments of the present invention are presented from the description of the following embodiments with reference to the corresponding drawings.

1 and 2 show a coolant circuit comprising internal heat transfer as well as first and second coolant-air-heat transfers, a coolant circuit comprising first and second coolant-air-heat transfers, a coolant circuit and a coolant, respectively. An air conditioning system having a coolant-coolant-heat transferr for thermally connecting circuits is shown.
1 shows a coolant-air-heat transferer arranged in series with respect to each other,
2 shows a coolant-air-heat transferer disposed in parallel with respect to each other,
3 and 4 respectively show a heat transfer device, in particular a coolant-air-heat transferer, having an overflow zone and a vaporization zone for the gas coolant, as well as an integrated device for the deposition of the gas coolant from the liquid coolant, respectively.
3 shows that the deposition apparatus is formed inside the collection tube,
4 shows an invasion apparatus formed and disposed between two collection tubes.

1 shows an air conditioning system 1 ′ having a coolant circuit 2 ′ and a coolant circuit 30. The coolant circuit 2 'is a coolant-coolant-heat transferr 4, a first inflator 5, and supply air for the passenger space which can act as a compressor 3, a condenser / gas cooler in the direction of flow of the coolant. A first coolant-air-heat transferer 6 for the control of the < RTI ID = 0.0 > The coolant circuit 2 'is also formed with second coolant-air-heat transferers 9a and 9b which act as vaporizers to transfer heat of air to the coolant, and the second coolant-air-heat transferr Upstream of the second inflator 8 is located. The first coolant-air-heat transferer 6 and the second coolant-air-heat transferers 9a, 9b are arranged in series or in turn with respect to each other. Second coolant-air-heat transferers 9a, 9b and second expanders 8 assigned thereto are formed in the first flow path 12. Advantageously, the second coolant-air-heaters 9a, 9b comprise the structural space of a conventional coolant-air-heater which acts as a condenser / gas cooler under the action of air.

A collector 11 is arranged between the second coolant-air-heat transferers 9a and 9b and the compressor 3. The collector 11, which is arranged in front of the compressor 3 and thus on the low pressure side in the flow direction of the coolant, is also referred to as an accumulator and is used for the deposition and collection of the coolant liquid. The compressor 3 draws gaseous coolant from the collector 11. The coolant circuit 2 'is closed. According to an alternative embodiment, not shown, the collector is integrated inside the coolant-coolant-heat transferer 4 as a coolant reservoir, whereby it is placed at the high pressure level of the coolant. In this case, the collector 11 arranged at the low pressure level can be omitted. In addition, the coolant-coolant-heat transfer machine 4 may be formed with a device for drying the coolant.

The coolant circuit 2 ′ further comprises a second flow path 13 in addition to the first flow path 12, each of which extends from the branch position 14 to the confluence position 15. The second flow path 13 formed in parallel with respect to the first flow path 12, in particular with respect to the second coolant-air-heat transferers 9a, 9b, comprises a valve 16, in particular a shut-off valve 16. And bypass the second coolant-air-heat transferers 9a and 9b to guide the mass flow of the coolant.

In the first flow path 12 a backflow preventing member 10, in particular a check valve, is arranged between the second coolant-air-heat transferers 9a, 9b and the confluence position 15. The backflow preventing member 10 returns the coolant mass flow guided through the second flow path 13 to bypass the coolant-air-heat transferers 9a and 9b into the coolant-air-heat transferers 9a and 9b. To prevent flow.

The coolant circuit 2 ′ is also formed with an internal heat transferr 7, which is provided at the high pressure side of the coolant-coolant-heat transferr 4 and the first coolant-air-heat transferr 6. Not only between the first inflator 5, but also between the confluence position 15 and the collector 11 or the compressor 3 on the low pressure side. In this case, the internal heat transferr 7 is used for heat transfer between the coolant at high pressure and the coolant at low pressure, whereby on the one hand the liquid coolant discharged from the heat transfer 4 acting as a condenser / gas cooler is additionally added. The coolant discharged from the heat transfers 6, 9a, 9b which are cooled and on the other hand act as vaporizers is superheated before the vaporizer 3 as intake gas.

In addition to the protection of the compressor 3 against liquid striking action, the operation of the coolant circuit 2 'with the internal heat transferr 7 reduces not only the specific compressor performance, but also the non-cooling performance and thus air conditioning. The operating efficiency of the system 1 'can be improved.

The cooling water circuit 30 serves as a heat transfer device (31) as a first cooling water-air-heat transfer device for the heating of the supply air for the passenger space as well as a conveying device 31, in particular a pump, for circulation of the cooling water in the direction of cooling water flow. 32). In addition, the heating heat transferr 32 is connected to the coolant-coolant-heat transferr 4. The cooling water circuit 30 is closed. As a result, the coolant-coolant-heat transferr 4, which acts as a condenser / gas cooler on the coolant side, is cooled by the coolant.

In addition, the connection line formed between the heating heat transferr 32 and the coolant-coolant-heat transferr 4 is provided with a joining position 34 as well as a three-way valve 33 as a branching position, between which air The second flow path as a bypass bypassing the coolant-air-heat transferr 36 as well as the first flow path 35 with a second coolant-air-heat transferr 36 for transferring heat to the 37) are formed respectively.

As the first coolant-air-heat transferr 32, the heat transfer heat carrier and the second coolant-air-heat transferr 36 are arranged in a flow-through manner by the coolant in series with each other.

The second coolant-air-heat transferr 36 of the coolant circuit 30 and the second coolant-air-heat transferers 9a, 9b which operate as vaporizers of the coolant circuit 2 'are installed in the installation module 42. In the vehicle's existing structural space and in turn in the air flow direction 43. In this case, the facility module 42 disposed in the front region of the vehicle can be perfused by air discharged from the passenger space, ambient air, or a mixture of air discharged from the passenger space and the ambient air. As a result, the air conditioning system 1 'uses as a heat source the potential heat of the air discharged from the passenger space, as well as the heat from the surroundings.

In this case, the air is first guided through the coolant-air-heat transferr 36 and then through the coolant-air-heat transferers 9a and 9b, and consequently the arrangement of these heat transferers 9a, 9b and 36 is a coolant. Reduce the risk of freezing of the heat transfer surfaces of the air-heaters 9a, 9b.

In addition, air for entering the coolant-air-heat transferr 36 is also used for entering the coolant-air-heat transferr 9a, 9b.

The coolant-air-heat transferr 6 of the coolant circuit 2 'and the heating heat transferr 32 of the coolant circuit 30 are arranged inside the air conditioner 40 and the flow direction 41 of the supply air in the passenger space. It is arranged to receive the action in turn. In this way, the supply air for the passenger space, cooled and / or dehumidified during the overflow of the vaporizer 6, may be heated during the overflow of the heating heat transfer 32 as required. First, the controlled air entering into the heat transfer heat 32 during the overflow of the coolant-air heat transfer 6 can be controlled by a temperature valve (not shown).

The coolant-coolant-heat transferr 4 is used to thermally connect the coolant circuit 2 'with the coolant circuit 30. In this case, the heat of the coolant is transferred to the coolant.

The air conditioning system 1 ′ is a coolant-air-operating as a vaporizer even when the outside air temperature value is less than 0 ° C., especially during operation with circulating air, ie during operation with air discharged from the passenger space as a heat source. The heat transfer surfaces of heat transferers 9a and 9b can be operated without the risk of freezing.

To ensure this operation, the coolant-air-heat transferer 6 disposed in the air conditioning apparatus 40 is operated by the coolant at an intermediate pressure level and operated as a vaporizer. The potential heat released from the air during the dehumidification of the air entering the carburetor in this case is used in conjunction with the ability to supply the coolant during compression in the compressor 3 to heat the supply air for the passenger space to the desired discharge temperature. do. In this case, the heat absorbed by the coolant is transferred to the coolant in the coolant-coolant-heat transferer 4 cooled by the coolant, and the coolant transfers the absorbed heat to the supply air during perfusion of the heat transfer machine 32. Release.

When operating in the cooling installation mode or in the subsequent heating mode for dehumidification of the supply air, excess heat absorbed by the coolant and transferred to the cooling water is guided through the first flow path 35 of the cooling water circuit 30, It is released to the air in a second coolant-air-heat transferr 36, also referred to as a low temperature cooler, in the front region of the motor vehicle. The coolant is circulated regardless of the mode of operation and is heated during perfusion of the coolant-coolant-heat transferr 4.

When the air conditioning system 1 ′ is operating in the heat pump mode or in the subsequent heating mode, the heat that can be transferred to the supply air of the passenger compartment in the heat transfer unit 32 reaches a sufficient temperature of the supply air for the passenger compartment. To do this, from the energy delivered to the coolant in the first coolant-air-heat transferer 6 acting as a vaporizer or in the second coolant-air-heat transferrs 9a and 9b acting as a vaporizer and in the compressor 3 Combined, the energy is transferred to the coolant as a sum in coolant-coolant-heat transfer (4).

In this case, the coolant-air-heaters 9a, 9b configured only for the absorption of heat and thus for acting as a vaporizer are subjected to coolant action at low pressure levels.

If necessary, in other words, the heat provided for heating of the supply air in the passenger compartment in the coolant circuit 2 'is sufficient during operation in the subsequent heating mode to add it in the second coolant-air-heat transferr 9a, 9b. If no heat absorption of is required, the second coolant-air-heat transferers 9a, 9b may be isolated from the coolant circuit 2 'and bypass the second flow path 13 in the bypass. The valve 16 is open while the inflator 8, which is formed as an expansion valve, is closed.

When the air conditioning system 1 'is operating in the heat pump mode, the expander 8 located upstream of the second coolant-air-heat transferr 9a, 9b has an inlet temperature of the coolant, in particular ambient air. The coolant can be controlled to swell at low pressure levels that occupy only slightly below the temperature of. At a temperature corresponding to the low pressure level, the coolant is vaporized.

In this case, the first coolant-air-heat transferer 6 acting as a condenser / gas cooler is able to preheat the air for the passenger space entering the air conditioning system 40 under the action of the coolant at the intermediate pressure level and, if necessary, into the air conditioning system 40. have. The supply air is further heated during the overflow of the heating heat transferr 32, which is operated by cooling water.

Two-stage heating of the feed air reduces the operating efficiency of the air conditioning system 1 'by increasing the possible enthalpy deviation of the coolant prior to expansion and thus vaporization in the second coolant-air-heat transferers 9a, 9b. Improve.

2, an air conditioning system 1 ″ with a coolant circuit 2 ″ and a coolant circuit 30 is shown. The air conditioning system 1 "differs from the air conditioning system 1 'of FIG. 1 only in the configuration of the coolant circuits 2', 2".

The coolant circuit 2 "adjusts the supply air for the compressor 3, the coolant-coolant-heat transferr 4, the first expander 5 and the passenger space in the flow direction of the coolant, acting as a condenser / gas cooler. And a first coolant-air-heat transferer 6. A third expander 20, in particular an expansion valve, is arranged downstream of the coolant-air-heat transferer 6. First expander 5, The combination of the first coolant-air-heat transferer 6 and the third expander 20 is arranged in a second flow path 17 extending from the branched position 18 to the joined position 19.

The coolant circuit 2 " is also formed with second coolant-air-heat transferers 9a and 9b which act as vaporizers to transfer heat of air to the coolant, upstream of the heat transfer unit. (8) is located, the first coolant-air-heat transferr 6 and the second coolant-air-heat transferr 9a, 9b are arranged in parallel to each other. 9a, 9b and the second inflator 8 assigned thereto are formed in the first flow path 12, which extends from the branch position 18 to the confluence position 19, like the second flow path 17. Between the coolant-air-heat transferers 9a and 9b and the confluence position 19, the first flow path 12 and the second flow path 17 which comprise a backflow preventing member 10, in particular a check valve, are consequently consequently Proceeds in parallel Advantageously, the second coolant-air-heat transferr 9a, 9b is a conventional coolant-air-operated by air and acts as a condenser / gas cooler. It includes a structure area of the transmitters.

The collector 11 is again arranged between the confluence position 19 and the compressor 3. According to an alternative embodiment not shown, the collector is integrated into the coolant-coolant-heat transferr 4 as a coolant reservoir and is thus arranged at the high pressure level of the coolant, with the collector 11 disposed at the low pressure level omitted. Can be. In addition, the coolant-coolant-heat transfer machine 4 may be formed with a device for drying the coolant.

If the air conditioning system 1 "is operated in the subsequent heating mode, the second coolant-air-heat transfer machine may have sufficient heat provided to heat the supply air of the passenger space in the coolant circuit 2" as needed. If no additional heat absorption at all is required at 9a, 9b, the second coolant-air-heat transferr 9a, 9b may be disconnected from the coolant circuit 2 ". Second inflator formed as an expansion valve 8 is closed, such as when the air conditioning system 1 'operates in the cooling installation mode.

When the air conditioning system 1 "is operating in the heat pump mode, the first expander 5 can be closed when the second expander 8 is opened. In this case, the first coolant-air-heat transferer 6 Is not affected by coolant The overall coolant mass flow is guided through second coolant-air-heat transferers 9a and 9b to absorb heat.

An unillustrated embodiment of the coolant circuit relates to the arrangement of the first coolant-air-heat transferr and the second coolant-air-heat transferr combined with the arrangement of branch positions formed as three-way valves.

Here, the three-way valve is provided in a connection line formed between the transfer device and the heat transfer heat, while the confluence position is formed between the heat transfer heat and the coolant-coolant-heat transfer heat. The second coolant-air-heat transfer unit is formed in the first flow path and the heat transfer heat transfer unit is formed in the second flow path, each of which flows from the branch position to the confluence position. Thus, the heating heat transferer and the second cooling water-air-heat transferer as the first cooling water-air-heat transferer are arranged to be perfused by the cooling water in parallel with each other.

Coolant circuits and modes of operation can be used for each coolant that undergoes a phase transition from liquid to gaseous form on the low pressure side. On the high pressure side, the medium provides the heat sink with heat absorbed through gas cooling / condensation and subcooling. As the coolant, for example, natural materials such as R744, R717 and the like, combustible materials such as R290, R600, R600a and the like, and chemical materials such as R134a, R152a, HFO-1234yf, as well as mixtures of various coolants can be used.

3 and 4 respectively show heat transfer with integrated devices 57a and 57b for the deposition of gas coolant from liquid coolant, as well as convection zones 65a and 65b and vaporization areas 64a and 64b for gas coolant. A coolant-air-heat transfer or ambient heat transferer is shown which is operated as a device, in particular as a vaporizer. Apparatus 57a, 57b for the deposition of gaseous coolant from liquid coolant, also referred to as sedimentation separator or phase separator, are formed integrated inside coolant-air-heat transferr 9a, 9b.

Before the coolant flows through the section of heat transfer in the coolant-air-heat transferers 9a and 9b, the immersion apparatus 57a and 57b respectively separate the liquid phase of the coolant from the gas phase. In this case, the heat transfer section of the coolant-air-heat transferer 9a, 9b is divided into two zones, that is, the active zone 64a, 64b, also referred to as the vaporization zone, and the inactive zone, also called the overflow zone. Regions 65a and 65b are it.

Active regions 64a and 64b may be subjected to the action of air in cross relative flow to the coolant, where heat of air may be transferred to the coolant. Since the inactive regions 65a and 65b are preferably not subjected to the action of air, no heat is transferred at all inside the inactive regions 65a and 65b.

On the coolant side, the liquid coolant separated in the devices 57a and 57b for the deposition of the gas coolant from the liquid coolant flows through the active regions 64a and 64b of the coolant-air-heat transferers 9a and 9b to absorb heat. Vaporizes. The separated gas coolant is guided through the inactive regions 65a, 65b of the coolant-air-heat transferers 9a, 9b and flows through the coolant-air-heat transferers 9a, 9b without absorbing heat.

Since only liquid coolant flows through the active zones 64a, 64b that transfer heat in the coolant-air-heat transferers 9a, 9b, The overall pressure loss on the coolant side is much less than the pressure loss during the perfusing of a conventional coolant-air-heat transferr operating as a vaporizer in the heat pump mode. In addition, since the gas coolant is guided through the inactive regions 65a, 65b and thus bypasses the active regions 64a, 64b of the coolant-air-heat transferers 9a, 9b, the active regions 64a, 64b. Is operated with less coolant mass flow.

Due to the reduced coolant mass flow as well as the reduced pressure loss on the coolant side, the component size can be reduced compared to the coolant-air-heaters known in the art, if the performance requirements for the heat to be transferred are the same, This in turn leads to lower manufacturing costs and smaller weights.

In addition, the coolant-air-heat transferers 9a and 9b do not include any additional components formed separately, such as, for example, an inflator or the original device for erosion, as well as a coolant line connecting them. This likewise reduces the cost and complexity of the coolant circuit.

3 has an integrated deposition device 57a for the deposition of gaseous coolant from the liquid coolant as well as a vaporization zone 64a as the active zone 64a and a convection zone 65a for the gas coolant as the inactive zone 65a. One heat transfer device 9a is shown. The deposition apparatus 57a for the deposition of the gaseous coolant from the liquid coolant is disposed inside the first collection tube 50a or the distribution tube or coolant inlet distributor.

The heat transfer device 9a is connected to each other by means of tube members 52-1 and 52-2 formed in parallel and in the horizontal direction x, in particular in a straight line with respect to each other. And a second collection tube 51a. The interior volumes of the collection tubes 50a, 51a are summed up to a common volume by the tube members 52-1, 52-2.

The device 9a comprises an inlet 54 and an outlet 55 for the coolant. The inlet 54 is formed in the first collection tube 50a, while the second collection tube 51a comprises an outlet 55.

The two phases of the coolant are mechanically separated from each other by the immersion deposition apparatus 57a. In this case, mechanical separation is based on inertial forces as the action force, which requires a sufficiently large difference in density between the two phases of the coolant.

In particular, the mixture consisting of the coolant of the gas and the liquid entering the first collection tube 50a in the flow direction 56 aligned in the horizontal direction x separates the deposition apparatus 57a for the deposition of the gas coolant from the liquid coolant. Guided against the member 60, the separating member is preferably arranged to align in the vertical direction y and functions as a baffle plate. After entering the heat transfer apparatus 9a, the coolant impinges on the front side of the separating member 60 formed as a separating wall. Due to the different inertia forces of the liquid coolant and the gas coolant, the two phases of which change in direction due to sudden fluctuations in the flow rate and the flow direction follow, the different phases of the coolant are separated from each other.

Since the liquid coolant has a higher density, it flows downward into the liquid region 58a formed in the first collection tube 50a, in particular in the flow direction 61 aligned in the vertical direction y, while the gas coolant has a lower density. Since it is lower, it is guided upward into the gas region 59a, which is likewise formed in the first collection tube 50a, in particular in the flow direction 62 aligned in the vertical direction y.

In addition, the separating member 60 functions as a means for separating the liquid region 58a from the gas region 59a to form two chambers. These chambers are only connected to each other in the liquid region 58a so that the liquid coolant can flow between the two chambers.

The tube member 52-1 connecting the liquid region 58a of the first collection tube 50a with the second collection tube 51a forms the active vaporization region 64a and, on the outside side, in other words A rib 53 is provided for the expansion of the heat transfer surface with respect to the air side. The tube member 52-1 is formed, for example, as a flat tube.

The liquid coolant flows through the tube member 52-1 in the vaporization region 64a, where heat is transferred to the coolant to vaporize the coolant. For example, air flows through ribs 53 in a cross relative flow. After completely vaporized, the gas coolant is discharged in the flow direction 63 in the direction of the discharge part 55 inside the second collection tube 51a.

A tube member 52-2 extending between the first collection tube 50a and the second collection tube 51a in the gas region 59a of the first collection tube 50a is used for the deposition of the gas coolant from the liquid coolant. In contrast to the tube member 52-1 forming the inert overflow region 65a for the gas coolant separated in the deposition apparatus 57a and forming the vaporization region 64a, no ribs are included at all. In addition, the tube members 52-2 of the overflow area 65a may also be formed of flat tubes disposed to be in contact with each other. The compact arrangement of the tube members 52-2 results in a very compact structural space of the heat transferr 9a.

The gas coolant is guided to flow through the tube member 52-2 in the overflow region 65a. In this case, no heat is transferred to the coolant. The gas coolant flowing through the overflow zone 65a is mixed with the gas coolant generated during vaporization inside the second collection tube 51a and moves the outlet 55 in the flow direction 56 as a co-mass flow of the gas coolant. Through the heat transferer 9a.

The mass flow of the gaseous coolant and the liquid coolant is guided through the different zones formed to separate from one another in the heat transferer 9a, eventually using the vaporization zone 64a and the overflow zone 65a. These regions are set to different sizes, where the vaporization region 64a is designed to be larger than the overflow region 65a.

According to the first alternative embodiment, the tube member 52-1 of the vaporization region 64 a and the tube member 52-2 of the overflow region 65 a are disposed on one common surface. In this case, air can overflow the tube members 52-1, 52-2 in parallel.

According to an alternative embodiment, not shown, the tube member of the vaporization region and the tube member of the overflow region are each arranged on two sides aligned parallel to each other. In this case, the air may flow sequentially in accordance with the respective flow direction first through the heat transfer surface of the vaporization region and then through the heat transfer surface of the overflow region, or vice versa.

4 shows a heat transfer device 9b, in particular a coolant, having an integrated device 57b for the deposition of the gaseous coolant from the liquid coolant as well as a vaporization zone 64b for the liquid coolant and a convection zone 65b for the gaseous coolant. Air-heat transfer is shown. An apparatus 57b for the deposition of the gas coolant from the liquid coolant is arranged between the first collection tube 50b and the second collection tube 51b to connect the collection tubes 50b and 51b to each other.

In addition, the first collection tube 50b and the second collection tube 51b are formed in parallel and in the vertical direction y, in particular in a straight line, with respect to each other as well as the device 57b. Are connected to each other by The internal volumes of the collection tubes 50b and 51b are summed in a common volume by the tube members 52-1 and the immersion apparatus 57b.

The coolant-air-heat transferer 9b includes an inlet 54 and an outlet 55 for the coolant. The inlet 54 is formed in the device 57b for the deposition of the gas coolant from the liquid coolant, while the second collection tube 51b includes the outlet 55.

The two phases of coolant are mechanically separated from each other by the deposition apparatus 57b. In this case, mechanical separation is based on inertial forces as the action force, which requires a sufficiently large difference in density between the two phases of the coolant.

The mixture consisting of a coolant of gas and liquid is arranged in a vertical direction (y) for the deposition of gas coolant from the liquid coolant, in particular in the flow direction 56 aligned in the horizontal direction (x). Flows into. Due to the sudden fluctuations in flow velocity and direction of flow as it impinges on the wall of the device 57b, the different phases of the coolant are separated from each other due to the different inertial forces of the liquid and gaseous coolant, which are followed by two different directions. Are separated.

Since the liquid coolant flows downward into the liquid region 58b formed in the device 57b, in particular in the direction of flow 61 aligned in the vertical direction y, while the gaseous coolant has a lower density, , In particular in the direction of flow 62 aligned in the vertical direction y, is likewise directed upward into the gas region 59b formed in the device 57b.

The liquid region 58b is connected with the first collection tube 50b, while the gas region 59b is hydraulically coupled with the second collection tube 51b.

The first collection tube 50b and the tube member 52-1 connecting the first collection tube 50b with the second collection tube 51b form an active vaporization region 64b. For example, the tube member 52-1 formed as a flat tube is provided with a rib 53 for enlargement of the heat transfer surface with respect to the outer side, that is to say specifically the air side.

The liquid coolant flows through the tube member 52-1 of the vaporization region 64b, where heat is transferred to the coolant to vaporize the coolant. For example, air flows through ribs 53 in a cross relative flow. After fully vaporized, the gas coolant is introduced into the second collection tube 51b.

The second collection tube 51b forms an inert overflow region 65b for the gas coolant separated in the device 57b for the deposition of the gas coolant from the liquid coolant. The gas coolant is guided to flow through the second collection tube 51b in the flow direction 63, where it is not only mixed with the gas coolant produced during vaporization, but also discharge 55 in the flow direction 56 as a co-mass flow. Through heat transfer 9b.

Since only liquid coolant flows through the active zones 64a and 64b, the overall vaporization enthalpy of the two phase-zone of the coolant is used for heat absorption, respectively. The reduced coolant mass flow combined with the elevated vaporization enthalpy results in much less coolant side pressure loss inside the active vaporization zones 64a and 64b, so that the coolant inflow as compared to the coolant-air-heaters known in the art. It causes a much smaller temperature deviation of the coolant between the part 54 and the outlet part 55. Thus, it can absorb much more heat from the surroundings.

The pressure loss on the coolant side can be further reduced, in particular by using a coolant tube formed for vaporization as the tube member 52-1.

Compared to the heat transferr 9a of FIG. 3, the heat transferr 9b of FIG. 4 is perfused in parallel with a larger number of tube members 52-1 in the same construction space. This may further reduce the coolant side pressure loss of the heat transferr 9b.

Inside the inert overflow region 65b a gas coolant flows through the second collection tube 51b, the free flowing cross section of the collection tube being formed such that only a small coolant side pressure loss occurs during perfusion in the gas coolant.

The integrated device 57a, 57b for the deposition of gaseous coolant from the liquid coolant is such that the mass flow of completely liquid coolant always flows through the active vaporization regions 64a, 64b even when the filling height of the liquid coolant is different. Formed and disposed. The state of charge of the liquid coolant is set corresponding to the pressure difference between the coolant at the inlet 54 and the outlet 55.

1 ', 1 "air conditioning system
2 ', 2' refrigerant circuit
3 compressor
4 Heat Transfer, Coolant-Coolant-Heat Transfer
5 first inflator
6 Heat transfer, first coolant-air-heat transfer
7 Internal Heat Transfer
8 second inflator
9a, 9b Heat Transfer, Heat Transfer, Second Coolant-Air-Heat Transfer
10 backflow prevention member
11 collector
12 First flow path
13 Second flow path
14 quarter position
15 confluence positions
16 valves, shut-off valve
17 Second flow path
18 branch positions
19 confluence
20 third inflator
30 coolant circuit
31 Feeding device
32 1st Coolant-Air-Heat Transfer, Heat Transfer
33 branch position, 3-way valve
34 confluence
35 first flow path
36 Second coolant-air-heat transfer
37 Second Flow Path
40 air conditioning system
41 Direction of flow of passenger space supply air
42 fixtures modules
43 Flow direction of air
50a, 50b first collection tube
51a, 51b second collection tube
52-1, 52-2 tube member
53 ribs
54 Coolant inlet
55 Coolant outlet
56 Refrigerant Flow Direction
Deposition apparatus for gaseous coolant from 57a, 57b liquid coolant
58a, 58b liquid zone
59a, 59b gas zones
60 separation member
61 Flow direction of liquid coolant
62 Flow direction of gas coolant
63 Flow direction of gas coolant
64a, 64b vaporization zone, active zone
Overflow zone, inactive zone of 65a, 65b gas coolant
x horizontal direction
y vertical direction

Claims (19)

Heat transfer devices 9a, 9b for coolant circuits 2 ', 2 "of an air conditioning system 1', 1" of an automobile, inlet 54 and outlet 55 for coolant, first collection In addition to the tubes 50a and 50b and the second collection tubes 51a and 51b, the tube members 52-1 and 52- extend between the collection tubes 51a and 51b and are arranged in parallel alignment with each other. In the heat transfer apparatus comprising 2),
The heat transfer devices 9a and 9b are formed by integrating the deposition devices 57a and 57b for the deposition of the gas coolant from the liquid coolant, and the heat transfer devices 9a and 9b form the vaporization regions 64a, 64b) and overflow zones 65a and 65b for the action of the gas coolant,
Heat transfer device (9a, 9b), characterized in that no heat transfer occurs between the air passing through the heat transfer device and the gas coolant in the overflow region. The tube members (52-1, 52-) according to claim 1, wherein the collecting tubes (50a, 51a) are arranged aligned in a vertical direction (y) and arranged parallel to each other and in a horizontal direction (x). Heat transfer device 9a, which is connected to each other via 2). 3. Heat transfer device (9a) according to claim 2, characterized in that the deposition device (57a) for the deposition of the gaseous coolant from the liquid coolant is formed integrally in the first collection tube (50a). 3. Heat transfer device (9a) according to claim 2, characterized in that the inlet (54) is formed in the first collection tube (50a). The method of claim 3, wherein the immersion apparatus 57a includes a separating member 60 arranged and arranged in a vertical direction y, which separates the interior volume of the first collection tube 50a from the liquid region (5). 58a) and gas region 59a, characterized in that the heat transfer device 9a. 6. The tube member 52-1 connecting the liquid region 58a of the first collection tube 50a with the second collection tube 51a forms a vaporization region 64a and the first collection tube. The heat transfer device (9a), characterized in that the tube member (52-2) connecting the gas region (59a) of the (50a) to the second collection tube (51a) forms a overflow region (65a). 2. The collecting tubes 50b, 51b are arranged in a horizontal direction x, arranged through tube members 52-1 arranged parallel to each other and in a vertical direction y. Heat transfer device 9b, characterized in that connected to each other. 8. The deposition apparatus 57b for the deposition of the gaseous coolant from the liquid coolant is adapted to connect the collection tubes 50b, 51b to each other between the first collection tube 50b and the second collection tube 51b. Heat transfer device (9b), characterized in that it is arranged. The heat transfer apparatus according to claim 8, characterized in that the deposition apparatus 57b for the deposition of the gaseous coolant from the liquid coolant is disposed in the vertical direction y and parallel to the tube members 52-1. 9b). 9. Heat transfer device (9b) according to claim 8, characterized in that the inlet (54) is formed in the deposition device (57b) for the deposition of the gas coolant from the liquid coolant. 9. The deposition apparatus 57b for the deposition of the gaseous coolant from the liquid coolant comprises a liquid region 58b and a gas region 59b, wherein the liquid region 58b comprises a first collection tube 50b. A heat transfer device (9b), characterized in that it is formed to be connected to the gas region (59b). 8. The tube members 52-1 connecting the first collection tube 50b with the second collection tube 51b, as well as the first collection tube 50b, form the vaporization region 64b. And the second collection tube (51b) forms a overflow region (65b). An air conditioning system (1 ', 1) having a coolant circuit (2', 2 ") comprising a heat transfer device (9a, 9b) according to any one of claims 1 to 11 and a coolant circuit (30). "). The method of claim 13,
The coolant circuits 2 ′, 2 ″, coolant-coolant-heat transferr 4, which may act as a condenser / gas cooler for heat transfer between the coolant and coolant of the compressor 3, the coolant circuit 30, A first coolant-air-heat transferer 6 for air conditioning of the supply air for the passenger space, as well as an inflator 5,
The coolant circuit 30 comprises a coolant as well as a transfer device 31, a first coolant-air-heat transferr 32, a second coolant-air-heat transferr 36 for heating the supply air for the passenger space. A coolant-heat transferr (4),
The heat transfer devices 9a, 9b are formed as second coolant-air-heat transferrs 9a, 9b which can only act as vaporizers, and the second coolant-air-heat transferers 9a, 9b in the flow direction of the coolant. Upstream of the second expander 8 is located, wherein the second expander 8 as well as the second coolant-air-heat transferers 9a, 9b are jointly arranged in the first flow path 12. Air conditioning system 1 ', 1 ". 15. The system of claim 14, wherein the second coolant-air-heat transferr 36 of the coolant circuit 30 and the second coolant-air-heat transferr 9a, 9b of the coolant circuits 2 ', 2 "are installed in an installation module. An air conditioning system (1 ', 1 "), characterized in that it is arranged inside the (42) and arranged to be acted in turn in the direction of flow of air (43). The method according to claim 15, characterized in that the facility module 42 is formed to be perfused by air discharged from the passenger space, or ambient air, or mixed air consisting of air and ambient air discharged from the passenger space, Air conditioning system (1 ', 1 "). A coolant-air-heat transferer (6) and a second coolant-air-heat transferer (9a, 9b) are disposed in a coolant circuit (2 ') so as to flow through in series with each other. Air conditioning system 1 'characterized in that. A coolant-air-heat transferer (6) and a second coolant-air-heat transferer (9a, 9b) are disposed in a coolant circuit (2 ") in a flow-through manner in parallel to each other. Air conditioning system 1 ". The method of claim 18,
The first flow path 12 with the second inflator 8 and the second coolant-air-heat transferers 9a, 9b is formed to extend from the branching position 18 to the joining position 19,
A first expander 5, a first coolant-air-heat transferer 6, and a third expander 20 are formed in the second flow path 17, wherein the third expander 20 is a coolant-air An air conditioning system (1 ″), characterized in that it is arranged downstream of the heat transfer (6) and the second flow path (17) is formed to extend from the branch position (18) to the joining position (19).

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