KR20180122277A - 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

The present invention relates to heat transfer devices (9a, 9b) for coolant circuits (2′, 2″) in automotive air conditioning systems (1′, 1″), particularly to a coolant-air-heat transfer device which operates as a vaporizer. To this end, the heat transfer device includes an inlet (54) and an outlet (55) for the coolant, first collection tubes (50a, 50b) and second collection tubes (50a, 50b), as well as tube members (52-1, 52-2) extending between the collection tubes (50a, 50b), and arranged in parallel with each other. Devices (57a, 57b) for deposition of a gaseous coolant from a liquid coolant are integrally formed in the heat transfer devices (9a, 9b). In this case, the heat transfer devices (9a, 9b) comprise vaporization zones (64a, 64b) only for the action of the liquid coolant, and superheated zones (65a, 65b) only for the action of the gaseous coolant. The present invention also relates to an automotive air conditioning systems (1′, 1″) having a cooling water circuit (30) and the coolant circuits (2′, 2″), herein the coolant circuits (2′, 2″) include the heat transfer devices (9a, 9b).

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a heat transfer device for a coolant circuit of an automotive air conditioning system, and an air conditioning system including the device. BACKGROUND OF THE INVENTION 1. Field of the Invention [0001]

The present invention relates to a heat transfer device for a coolant circuit of an air conditioning system of an automobile, and more particularly to a coolant-air-heat exchanger which operates as a vaporizer. The apparatus includes an inlet and an outlet for the coolant, a first collection tube and a second collection tube, as well as tube members extending between the collection tubes and arranged in parallel alignment with respect to each other.

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

In the case of a vehicle known in the prior art, the waste heat of the engine is used to heat the supply air for the passenger space. The waste heat is transferred to the air conditioning equipment by the cooling water circulating in the engine cooling water circuit, and is then transferred to the air flowing into the passenger space through the heater heat exchanger. A known device having a cooling water-air-heat exchanger relating to heating performance from the cooling water circuit of an efficient combustion engine of a vehicle drive part is required for a comfortable warming of the passenger compartment to meet the overall heating requirement of the passenger space when the ambient temperature is low Level. The same applies to automobiles using hybrid drives, that is to say, electric motor-driven as well as air-conditioning in automobiles using combustion engine-driven drives.

If the overall heating demand of the passenger space can not be met by heating from the cooling water circuit of the engine, for example, an electrical resistance heater or a fuel heater, referred to in the English language as PTC ("Positive Temperature Coefficient-Thermistor" A heating action of the heater is required. The same applies to an air conditioner in a vehicle or a fuel cell vehicle driven purely by an electric motor. A more efficient possible 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 not only the only heating means but is also used as an additional heating measure.

An air conditioning system downstream of an electrical resistance heater can be manufactured cost-effectively on the one hand and can be used in any automobile, but it involves a very large demand for electrical energy because, in the overflow of the vaporizer of the coolant circuit, Is first cooled / cooled or dehumidified, and then heated by electrical resistance, which transfers heat directly to the feed air or coolant circuit.

Although the operation of a conventional air conditioning system operating as a heat pump is actually efficient, it requires a very large structural space for positioning the interior of the vehicle without any structural space for the air conditioning system. In particular, not only does the cost of manufacturing and maintenance rise, but also the need for a large structural space is also hindered.

An air-air-heating pump belonging to the prior art, which is formed for the combined cooling plant mode and the heating pump mode, i.e. for the subsequent heating mode, also referred to as reheating-operation as well as heating mode, Absorbed. Thus, ambient air is used as a heat source for vaporizing the coolant. A conventional air-air-heating pump includes a heat exchanger for heat transfer between the coolant and the surroundings, a heat exchanger for supplying heat to the coolant to regulate air in the passenger space, and heat to the conditioned air for the passenger space from the coolant And a heat exchanger for transferring the heat. Performance is transferred between the coolant and air, respectively.

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

DE 10 2012 111 672 A1 describes the coolant circuit of the air conditioning system for controlling 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 heating pump mode and for the subsequent heating mode and includes a compressor, a heat exchanger for transferring heat between the coolant and the surroundings, a first inflator, A heat exchanger for supplying the heat of the air to be supplied to the coolant, a heat exchanger for transferring heat from the coolant to the air to be conditioned for the passenger space, and a second expander in the flow direction of the coolant.

DE 10 2011 100 301 A1 describes a vehicle air conditioning system with a coolant circuit that can operate as a heating pump. The coolant circuit includes a compressor, a valve body disposed between the inlet side and the inner space condenser of the external heat exchanger under the influence of air, an inflator for expansion of the coolant, a three-way valve, as well as an internal vaporizer.

The coolant circuits include a respective one branched system consisting of connection lines that are not easy to integrate into existing structural space. In addition, additional valves and coolant reservoirs arranged at a low pressure level, each designed with a large volume, each require a large structural space. In addition, the valve includes a very high internal density resulting in increased system cost.

In this case, a heat exchanger for transferring heat between the ambient air of the air-air-heating pump and the coolant, also referred to as an external heat exchanger or ambient heat exchanger under the influence of air, In particular, outside the air conditioner, and is particularly affected by the air through the wind.

During operation of the coolant circuit in the cooling plant mode, the ambient heat exchanger is operated as a condenser / gas cooler to provide heat to the ambient air from the coolant, and during operation of the coolant circuit in the heat pump mode the heat is absorbed Lt; / RTI > Thus, although the surrounding heat exchanger is designed to operate with two functions, the result is that this design is not designed optimally for either function, so a trade-off must be found.

For these different functions, some contradictory design criteria are derived for the heat exchanger. The heat exchanger, which operates as a condenser / gas cooler, must be designed, for example, for high coolant pressures, at which time the wall thickness must be set very large with respect to the flow cross section, so that the flow cross section for the condenser / Is provided substantially smaller than the flow cross-section of the heat exchanger operating as a vaporizer at a lower coolant pressure level. The small flow cross section of the surrounding heat exchanger causes high pressure loss when the heat exchanger operates as a vaporizer and this pressure loss seriously degrades the overall performance and efficiency of the air conditioning system as an important design criterion.

Also, during operation of the coolant circuit in the heat pump mode, the coolant flows into the surrounding heat exchanger with a vapor content in the range of 20% to 60%. The vapor content of the coolant is included only to the extent that it is not critical to transfer heat from the ambient air to the coolant, but it is critical to the pressure loss during the perfusion of the surrounding heat exchanger.

The pressure loss of the coolant during operation of the peripheral heat exchanger as a vaporizer results in a temperature drop of the coolant and consequently the coolant at the inlet to the ambient heat exchanger has a higher temperature than at the outlet. To prevent the risk of freezing of the surrounding heat exchanger, the maximum temperature difference between the temperature of the air entering the surrounding heat exchanger and the temperature of the coolant is particularly limited to the range of 2 K to 10 K. At this time, the maximum allowable temperature difference is related to the temperature of the air entering the peripheral heat exchanger and the temperature of the coolant at the outlet, which is the lowest temperature in the vaporizer. Thus, the greatest temperature difference occurs between the air entering the surrounding heat exchanger and the temperature of the coolant at the outlet of the coolant from the vaporizer. The possible overheating of the coolant is not considered. In this case, the inflow portion of the coolant flowing into the surrounding heat exchanger is provided with a temperature difference smaller than the allowable temperature difference. The larger the pressure loss on the coolant side, the smaller the temperature difference at the inlet where the coolant enters the surrounding heat exchanger, and then the heat used to heat passenger space can be less absorbed from the ambient air.

In systems known in the prior art, the coolant, at least partially in gaseous form, is introduced into the surrounding heat exchanger, resulting in undesired pressure losses, and as a result, the heat that can be maximally transferred from ambient air by the coolant is limited, For example up to 3 kW.

At a temperature in the range of 0 ° C and at a temperature of less than 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. When the dew point temperature is lowered, the water vapor present in the air is condensed and deposited as water on the heat transfer surface. In this case, the water condensed from the air at the heat transfer surface adheres to ice when the surface temperature is below 0 ° C and 0 ° C. As the ice layer increases, the heat transfer on the air side and on the air side is reduced, resulting in a reduction in the heat transfer between the air and the vaporized coolant.

US 6 457 325 B1 discloses an air conditioning system having a compressor, a peripheral thermocouple capable of operating as a gas cooler / condenser, an inflator, a device for the deposition of a gaseous coolant, as well as a vaporizer capable of regulating the air to be supplied to the passenger space . A device disposed between the gas cooler / condenser and the vaporizer and for depositing the gaseous coolant includes a chamber having an inlet connected to the gas cooler / condenser, a vapor outlet connected to the vaporizer via the bypass line, . By forming a device for the deposition of a gaseous coolant from a liquid coolant, it is ensured that only the liquid coolant is directed towards the vaporizer.

By using an apparatus for the deposition of a gaseous coolant from a liquid coolant, which is disposed before the vaporizer in the flow direction of the coolant, only the liquid coolant is guided in the vaporizer, and as a result the coolant circuit can be operated efficiently. On the other hand, a coolant circuit having an apparatus for such 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 And these components can also impart a high mass to the vehicle and occupy a large seat within the very limited structural space of the vehicle. In addition, an additional regulator is needed with an expander disposed in the bypass line, which further increases the complexity of the system and, in addition, makes it difficult to match the regulatory strategy.

It is therefore an object of the present invention to provide a peripheral heat exchanger which can only operate as a vaporizer, such that the peripheral heat exchanger is capable of operating at a minimum pressure loss on the coolant side during operation and, therefore, . The peripheral heat exchanger as a heat exchanger for absorbing heat from ambient air must be optimally designed.

The surrounding heat exchanger must be able to be integrated into the air conditioning system for the vehicle, which, if necessary, absorbs heat from the surroundings through the surrounding heat exchanger and releases heat to the surroundings through components other than the surrounding heat exchanger. The air conditioning system can be operated not only in the cooling equipment mode and the heating pump mode but also in the subsequent heating mode. In this case, the ambient air should be used not only as a heat source, but also as a heat sink, for example during operation in the cooling plant mode, depending on the respective operating mode, for example in operation in the heat pump mode. In addition, the air conditioning system must be compact and efficient to operate, minimizing the risk of freezing the vaporizer of the coolant circuit, e.g., for heat transfer by air.

In this case, the coolant circuit of the air conditioning system must be structurally simple in order to include minimal structural space as well as causing minimal operating cost, manufacturing cost, and maintenance cost, and at least include the required number of components Should be.

These problems are solved by objects or methods having the features of the independent claims of the claims. Further improvement examples are described in the dependent claims.

The above problem is solved by a heat transfer device for a coolant circuit of an automotive air conditioning system, in particular by a coolant-air-heat exchanger operating as a vaporizer. The apparatus includes an inlet and an outlet for a coolant, a first collection tube and a second collection tube, as well as tube members extending between the collection tubes and arranged in parallel alignment with respect to each other.

According to the inventive concept, an apparatus for the deposition of a gaseous coolant from a liquid coolant is formed integrally within an apparatus for heat transfer. To this end, the device for heat transfer comprises exclusively a vaporization zone for the action of the liquid coolant and a superfluid zone for the action of the gaseous coolant only.

Preferably, a discharge portion for the coolant is formed in the second collection tube.

According to a first alternative embodiment of the present invention, the collection tubes are arranged in vertical alignment and are connected to one another through tube members arranged in a horizontal direction parallel to each other.

According to one improvement of the invention, an apparatus for the deposition of a gaseous coolant from a liquid coolant is incorporated in a first collection tube.

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

Also preferably, the deposition apparatus comprises a separation member arranged in a vertically aligned arrangement, the separation member dividing the internal volume of the first collection tube into a liquid region and a gas region.

A further advantage of the present invention is that the tube member connecting the liquid region of the first collection tube with the second collection tube forms a vaporization zone and the tube member connecting the gas region of the first collection tube with the second collection tube And the like. In this case, the tube member forming the vaporizing region and the tube member forming the swirling region are formed differently / arranged or arranged differently from each other.

According to a second alternative embodiment of the present invention, the collection tubes are aligned in a horizontal direction and are connected to one another through tube members arranged in a vertical direction parallel to each other.

According to one improvement of the invention, a device for the deposition of a gaseous coolant from a liquid coolant is arranged to interconnect the collection tubes between a first collection tube and a second collection tube.

Preferably, the inlet for the coolant is formed in a device for deposition of a gaseous coolant from a liquid coolant.

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

According to a preferred embodiment of the present invention, an apparatus for depositing a gaseous coolant from a 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 zone, and the second collection tube forms an overflow zone.

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

- minimal coolant side pressure loss,

- maximum heat absorption from ambient air, and

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

It is a further object of the present invention to provide a method for controlling air in the passenger compartment of a vehicle having a coolant circuit and a coolant circuit in order to operate in a heating mode as well as a subsequent heating mode, It is solved by the air conditioning system.

According to the inventive concept, a coolant circuit is formed with a heat transfer device having the above-mentioned characteristics.

According to an improvement of the invention, the coolant circuit comprises a compressor in the flow direction of the coolant, a coolant-coolant-heat exchanger which can operate as a condenser / gas cooler for heat transfer between the coolant of the coolant circuit and the coolant, a first expander But includes a first coolant-air-heat exchanger for air conditioning of the feed air for passenger space. The cooling water circuit is formed by a conveying device for circulating cooling water, a first cooling water-air-heat exchanger for heating the supply air for the passenger space, a second cooling water-air-heat exchanger as well as a coolant-cooling water-heat exchanger do.

The coolant circuit also includes a device for heat transfer as a second coolant-air-heat exchanger that can only operate as a vaporizer. In this case, a second inflator is located upstream of the second coolant-air-heat exchanger in the flow direction of the coolant. The second cooler-air-heat exchanger as well as the second expander are communicated in the first flow path.

The cooling plant mode is used primarily for cooling, the heat pump mode is used for heating, and the subsequent heating mode is used for subsequent heating of the feed air of the passenger space to be controlled. In the case of the subsequent heating mode, the feed air was cooled / cooled or dehumidified prior to subsequent heating.

The heat exchanger is referred to as a condenser, for example, during operation below critical of the coolant circuit, such as using coolant R134a, or when the coolant is liquid in certain ambient conditions with carbon dioxide. Part of the heat transfer occurs at a constant temperature. In the event of an operation exceeding a critical value in the heat exchanger or a heat transfer exceeding a critical value, the temperature of the coolant continuously decreases. In this case, the heat exchanger is also referred to as a gas cooler. Exceeding the threshold may occur with certain ambient conditions or the use of carbon dioxide coolant, for example, in the way the coolant circuit operates.

The second coolant-air-heat exchanger of the cooling water circuit and the second coolant-air-heat exchanger of the coolant circuit are advantageously arranged in the interior of the facility module and in the order of the air flow direction, .

According to one improvement of the present invention, in particular, a facility module disposed in a front area of an automobile can be perfused by air discharged from a passenger space, or ambient air, or mixed air consisting of air discharged from a passenger space and ambient air .

According to a first alternative embodiment of the invention, the first coolant-air-heat exchanger and the second coolant-air-heat exchanger are arranged in a refrigerant circuit so as to be flowable in series with respect to each other.

Advantageously, the coolant circuit comprises a second flow path with a valve. In this case, the first flow path extends with a second refrigerant-air-heat exchanger as well as a second inflator, and the second flow path each extend from the branching position to the merging position, And is formed as a bypass parallel to the path.

According to a second alternative embodiment of the present invention, the first coolant-air-heat exchanger and the second coolant-air-heat exchanger are arranged in a refrigerant circuit so as to be capable of being perfluent in parallel with respect to each other.

A further advantage of the present invention is that the first flow path with the second inflator and the second coolant-air-heat exchanger extends from the branching position to the confluence position. In this case, a first inflator, a first coolant-air-heat exchanger, and a third inflator are formed in the second flow path. The third inflator is disposed downstream of the coolant-air-heat exchanger. The second flow path is likewise formed so as to extend from the branching position to the merging position.

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

- regulating, especially cooling, dehumidifying and / or heating the supply air of the passenger space using minimum energy by using a loss heat flow for the heating of the passenger space,

A coolant-air-heat exchanger specially designed for operation as a vaporizer, for use in operating in the heat pump mode to absorb heat from the environment, especially at low external temperatures, is used, where a higher external temperature and cooling are required The heat is dissipated to the environment through components that are different from the coolant-air-heat exchanger,

- Not only increases performance, efficiency and service life,

- It provides ample comfort inside the passenger space,

It uses a structurally simple coolant circuit that can be integrated for use in the known structure of existing automobiles and the available structural space, and includes minimal structural space, minimum weight and minimum component count,

- Minimum operating costs, manufacturing costs and maintenance costs.

Other and further details, features and advantages of embodiments of the present invention will be apparent from the following description of an embodiment with reference to the drawings.

Figures 1 and 2 show a cooling circuit comprising a first and a second coolant-air-heat exchanger as well as an internal heat exchanger, a cooling water circuit comprising first and second cooling water-air-heat exchangers, Cooling-water heat exchanger that thermally couples the circuit,
Figure 1 shows a coolant-air-heat exchanger arranged in series with respect to each other,
Figure 2 shows a coolant-air-heat exchanger arranged in parallel with respect to one another,
Figures 3 and 4 each illustrate a heat transfer device, particularly a coolant-air-heat exchanger, having an overflow region and a vaporization region for a gaseous coolant, as well as an integrated device for the deposition of a gaseous coolant from a liquid coolant,
Figure 3 shows the deposition apparatus being formed inside the collection tube,
Figure 4 shows that a deposition apparatus is formed and disposed between two collection tubes.

1 shows an air conditioning system 1 'provided with a coolant circuit 2' and a cooling water circuit 30. The coolant circuit 2 'comprises a compressor 3 in the flow direction of the coolant, a coolant-coolant-heat exchanger 4, which can operate as a condenser / gas cooler, a first inflator 5, Air-heat exchanger (6) for the control of the temperature. In addition, the coolant circuit 2 'is formed with a second coolant-air-heat exchanger 9a, 9b that acts as a vaporizer to transfer the heat of the air to the coolant, and the second coolant- A second inflator 8 is located upstream of the second inflator 8. The first coolant-air-heat exchanger 6 and the second coolant-air-heat exchanger 9a, 9b are arranged in series or in sequence with respect to each other. A second coolant-air-heat exchanger 9a, 9b and a second inflator 8 assigned thereto are formed in the first flow path 12. Advantageously, the second coolant-air-heat exchanger 9a, 9b comprises a structural space of a conventional coolant-air-heat exchanger which acts as a condenser / gas cooler under the action of air.

A collector 11 is arranged between the second coolant-air-heat exchanger 9a, 9b and the compressor 3. [ Collector 11, located in front of compressor 3 in the direction of flow of coolant and therefore on the low pressure side, is also referred to as an accumulator and is used for the deposition and collection of coolant liquid. The compressor (3) sucks the gaseous coolant from the collector (11). The coolant circuit 2 'is closed. According to an alternative embodiment, which is not shown, the collector is incorporated in the coolant-coolant-to-heat exchanger 4 as a coolant reservoir, thereby placing it at the high pressure level of the coolant. In this case, the collector 11 disposed at the low pressure level can be omitted. The coolant-coolant-to-heat exchanger 4 may also be provided 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 and the second flow path extends from the branching position 14 to the confluence position 15, respectively. A second flow path 13 formed in parallel to the first flow path 12 and in particular to the second coolant-air-heat exchanger 9a, 9b comprises a valve 16, in particular a shut-off valve 16 And to bypass the second coolant-air-heat exchanger 9a, 9b to guide the mass flow of the coolant.

In the first flow path 12, a check valve 10, in particular a check valve, is arranged between the second coolant-air-heat exchanger 9a, 9b and the confluence position 15. The countercurrent blocking member 10 bypasses the coolant-air-heat exchangers 9a and 9b through the second flow path 13 and the guided coolant mass flow returns to the coolant-air-heat exchangers 9a and 9b Thereby preventing flow.

The coolant circuit 2 'is also formed with an internal heat exchanger 7 which is connected to the coolant-coolant-to-heat exchanger 4 and the first coolant-air-heat exchanger 6 Is formed between the merging position 15 and the collector 11 or the compressor 3, as well as between the first expander 5 and the low-pressure side. In this case, the internal heat exchanger 7 is used for heat transfer between the coolant at the high pressure and the coolant at the low pressure, where on the one hand the liquid coolant exiting the heat exchanger 4, which acts as a condenser / gas cooler, And the coolant discharged from the heat exchanger (6, 9a, 9b), which on the other hand acts as a vaporizer, is superheated before the vaporizer (3) as an intake gas.

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

The cooling water circuit 30 includes a transfer device 31 for circulating the cooling water in the flow direction of the cooling water, in particular a pump, as well as a heating heat exchanger (not shown) as a first cooling water- 32). The heating heat exchanger 32 is also connected to the coolant-coolant-heat exchanger 4. The cooling water circuit 30 is closed. As a result, the coolant-coolant-heat exchanger 4, which acts as a condenser / gas cooler on the coolant side, is cooled by cooling water.

The connecting line formed between the heating heat exchanger 32 and the coolant-cooling water-heat exchanger 4 is provided with a three-way valve 33 as well as a joining position 34 as a branching position, Air-heat exchanger 36 as well as the first flow path 35 having the second cooling water-air-heat exchanger 36 for transferring the heat to the cooling water- 37 are formed.

The heat exchanger as the first coolant-air-heat exchanger 32 and the second coolant-air-heat exchanger 36 are arranged so as to be perfusable by cooling water in series with respect to each other.

The second coolant-air-heat exchanger 9a, 9b, which acts as a vaporizer for the second coolant-air-heat exchanger 36 of the coolant circuit 30 and the coolant circuit 2 ' But also in the existing structural space of the vehicle and in the direction of flow 43 of air. In this case, the facility module 42 disposed in the front area of the automobile can be perfused by the air discharged from the passenger space, the surrounding air, or the mixed air of the air discharged from the passenger space and the surrounding air. As a result, the air conditioning system 1 'uses the potential heat of the air discharged from the passenger space, as well as the heat from the surroundings, as a heat source.

In this case, the air is first guided via the coolant-air-heat exchanger 36 and then through the coolant-air-heat exchangers 9a and 9b so that the arrangement of these heat exchangers 9a, 9b, - reducing the risk of freezing the heat transfer surface of the air-to-heat exchanger (9a, 9b).

Air to be introduced into the cooling water-air-heat exchanger 36 is also used to flow into the coolant-air-heat exchanger 9a, 9b.

The coolant-air-heat exchanger 6 of the coolant circuit 2 'and the heating heat exchanger 32 of the coolant circuit 30 are arranged inside the air conditioner 40 and are arranged in the flow direction 41 of the supply air of the passenger space, As shown in FIG. Thereby, the supply air for the passenger space, which is cooled and / or dehumidified in the overflow of the vaporizer 6, can be heated in the superheat of the heat heat exchanger 32 if necessary. First, the conditioned air introduced into the heating heat exchanger 32 during the superheating of the coolant-air-heat exchanger 6 can be controlled by a temperature valve (not shown).

The coolant-coolant-to-heat exchanger 4 is used to thermally couple the coolant circuit 2 'with the coolant circuit 30. In this case, the heat of the coolant is transferred to the cooling water.

The air conditioning system 1 'is particularly suited for use as a refrigerant-air-conditioning system that operates as a vaporizer during operation by circulating air, that is, even when the outside air temperature value is less than 0 ° C during operation by air discharged from the passenger space as a heat source, The heat exchanger surfaces of the heat exchangers 9a and 9b can be operated without risk of freezing.

To ensure this operation, the coolant-air-heat exchanger 6 disposed in the air conditioning system 40 is operated by the coolant at the intermediate pressure level and operated as a vaporizer. In this case, the potential heat discharged from the air during the dehumidification of the air entering the vaporizer is used in conjunction with the capability of being supplied to the refrigerant 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 exchanger 4 cooled by the coolant, and the coolant transfers the absorbed heat to the supply air in the flow of the heat- Release.

When operating in the cooling plant mode or in a subsequent heating mode for dehumidification of the feed air, the 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, Air-heat exchanger 36, also referred to as the cryogenic cooler, in the front region of the vehicle. The cooling water circulates irrespective of the operating mode and is heated during the flow of the coolant-coolant-heat exchanger (4).

When the air conditioning system 1 'is operating in the heating pump mode or the subsequent heating mode, the heat that can be transferred to the supply air of the passenger space in the heat exchanger 32 reaches a sufficient temperature of the supply air for the passenger space Air-heat exchanger 9a, 9b operating as a vaporizer, or in the first coolant-air-heat exchanger 6 acting as a vaporizer, or from the energy delivered to the coolant in the compressor 3, , Which energy is transferred to the coolant as a total in the coolant-coolant-heat exchanger (4).

In this case, the coolant-air-heat exchanger 9a, 9b, which is designed solely for the absorption of heat and thus as a vaporizer, is subjected to the action of coolant at low pressure levels.

The heat provided for the heating of the supply air of the passenger space in the coolant circuit 2 'is sufficient for the operation in the subsequent heating mode, as required, so that it is added in the second coolant-air-heat exchanger 9a, 9b The second coolant-air-heat exchanger 9a, 9b may be disconnected from the coolant circuit 2 'and bypassed via the second flow path 13 at bypass if no heat absorption of the second coolant-air-heat exchanger 9a, 9b is needed at all. The valve 16 is opened while the inflator 8, which is formed as an expansion valve, is closed.

When the air conditioning system 1 'is operating in the heating pump mode, the inflator 8, located upstream of the second refrigerant-air-heat exchanger 9a, 9b, Lt; RTI ID = 0.0 > low < / RTI > The coolant vaporizes at the temperature corresponding to the low pressure level.

In this case, the first coolant-air-heat exchanger 6, which acts as a condenser / gas cooler, is capable of receiving the action of coolant at intermediate pressure levels and preheating the air for the passenger compartment entering the air conditioning system 40, have. The feed air is further heated during the superheat of the heat transfer converter 32, which is operated by the cooling water.

The two-stage heating of the feed air results in an increase in the operating efficiency of the air conditioning system 1 'by means of an increase in the possible enthalpy deviation of the coolant, prior to expansion and subsequent evaporation in the second coolant-air-heat exchanger 9a, 9b .

2 shows an air conditioning system 1 " having a coolant circuit 2 " and a cooling water circuit 30. In Fig. The air conditioning system 1 "is distinguished from the air conditioning system 1 'of FIG. 1 only in the configuration of the coolant circuits 2', 2".

The coolant circuit 2 " comprises a compressor 3 in the flow direction of the coolant, a coolant-coolant-heat exchanger 4 acting as a condenser / gas cooler, a first inflator 5, Air-heat exchanger 6. A third inflator 20, in particular an expansion valve, is arranged downstream of the coolant-air-heat exchanger 6. The first inflator 5, The combination of the first coolant-air-heat exchanger 6 and the third inflator 20 is arranged in the second flow path 17 extending from the branching position 18 to the confluence position 19.

In addition, the coolant circuit 2 " is formed with a second coolant-air-heat exchanger 9a, 9b which acts as a vaporizer to transfer the heat of the air to the coolant, Air-heat exchanger 6 and the second coolant-air-heat exchanger 9a, 9b are arranged in parallel with respect to one another. The second coolant-air-heat exchanger 6 9a and 9b and the second inflator 8 assigned thereto are formed in the first flow path 12 extending from the branching position 18 to the merging position 19 as the second flow path 17. The first flow path 12 and the second flow path 17, which include the check valve 10, in particular the check valve, between the coolant-air-heat exchangers 9a, 9b and the merging position 19, Advantageously, the second coolant-air-heat exchanger 9a, 9b is a conventional coolant-air-heat exchanger 9a, 9b under the influence of air and operating as a condenser / It includes a structure area of the transmitters.

A collector 11 is disposed again between the merging position 19 and the compressor 3. According to an alternative embodiment, which is not shown, the collector is integrated as a coolant reservoir inside the coolant-coolant-to-heat exchanger 4 and is thereby located at the high pressure level of the coolant, . The coolant-coolant-to-heat exchanger 4 may also be provided with a device for drying the coolant.

If the air conditioning system 1 " operates in a subsequent heating mode, the heat provided to heat the supply air of the passenger compartment in the coolant circuit 2 " The second coolant-air-heat exchanger 9a, 9b can be disconnected from the coolant circuit 2 ", if no additional heat absorption is required at the first coolant-outlets 9a, 9b. (8) is closed, such as when the air conditioning system (1 ') is operating in a refrigeration facility mode.

If the air conditioning system 1 " operates in the heat pump mode, the first inflator 5 can be closed when the second inflator 8 is opened. In this case, the first refrigerant- Is not subjected to the action of the coolant. The overall coolant mass flow is guided through the second coolant-air-heat exchanger 9a, 9b to absorb heat.

An unillustrated embodiment of the coolant circuit relates to the arrangement of the first coolant-air-heat exchanger and the second coolant-air-heat exchanger in combination with the arrangement of the diverging positions formed as three-way valves.

Here, a three-way valve is provided in the connection line formed between the transfer device and the heat exchanger, while the confluence position is formed between the heat exchanger and the coolant-coolant-heat exchanger. The second cooling water-air-heat exchanger is formed in the first flow path and the heat transfer coupler is formed in the second flow path, each extending from the branching position to the merging position. Thus, the heat exchanger as the first coolant-air-heat exchanger and the second coolant-air-heat exchanger are arranged to be perfusable by the coolant water in parallel with respect to each other.

The coolant circuit and modes of operation may be used for each coolant that undergoes a phase transition from liquid to gaseous form at the low pressure side. On the high pressure side, the medium provides absorbed heat to the heat sink 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, chemical materials such as R134a, R152a and HFO-1234yf as well as mixtures of various coolants can be used.

Figures 3 and 4 illustrate the heat transfer with the overflow areas 65a and 65b and the vaporization areas 64a and 64b for the gaseous coolant as well as the integrated devices 57a and 57b for deposition of the gaseous coolant from the liquid coolant, Apparatus, particularly a coolant-air-heat exchanger or ambient heat exchanger, operating as a vaporizer. Apparatus 57a, 57b for deposition of gaseous coolant from a liquid coolant, also referred to as a deposition separator or phase separator, is formed integrally within the coolant-air-heat exchanger 9a, 9b.

Before the coolant flows through the heat transfer section of the coolant-air-heat exchanger 9a, 9b, the deposition devices 57a, 57b separate the liquid phase of the coolant from the gas phase. In this case, the heat transfer portion of the coolant-air-heat exchanger 9a, 9b is divided into two regions, namely active regions 64a, 64b, also referred to as vaporization regions, Regions 65a and 65b.

The active areas 64a, 64b can be subjected to air action in a cross-flow relative to the coolant, wherein the heat of the air can be transferred to the coolant. Since the inactive regions 65a and 65b are preferably not affected by the air, heat is not transferred at all in the inactive regions 65a and 65b.

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

Since only the liquid coolant flows through the heat-conducting active areas 64a, 64b of the coolant-air-heat exchangers 9a, 9b, the coolant-air- heat exchangers 9a, The overall refrigerant side pressure loss is much less than the pressure loss during perfusion through a conventional coolant-air-heat exchanger operating as a vaporizer in the heat pump mode. In addition, since the gaseous coolant is guided bypassing the inactive regions 65a, 65b and thus the active regions 64a, 64b of the coolant-air-heat exchangers 9a, 9b, the active regions 64a, 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-heat exchanger known in the prior art if the performance requirements for the heat to deliver are the same, As a result, this leads to lower cost of manufacture and lower weight.

In addition, the coolant-air-heat exchangers 9a, 9b do not contain any additional components formed separately, such as, for example, an inflator or an original device for deposition, as well as no coolant lines connecting these components, This likewise reduces the cost and complexity of the coolant circuit.

3 shows an integrated device 57a for deposition of a gaseous coolant from a liquid coolant as well as a vaporization zone 64a as an active zone 64a and an overflow zone 65a for a gaseous coolant as an inactive zone 65a A heat transfer device 9a is shown. A device 57a for depositing a gaseous coolant from a liquid coolant is disposed within the first collection tube 50a or the distribution tube or coolant inlet distributor.

The heat transfer device 9a comprises a first collection tube 50a which is connected to each other by tube members 52-1 and 52-2 formed in parallel to each other and in the horizontal direction x, And a second collection tube 51a. The internal volumes of the collection tubes 50a, 51a are summed in a common volume by the tube members 52-1, 52-2.

The device 9a includes 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 the outlet 55. [

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

A mixture of gas and liquid coolant introduced into the first collection tube 50a in the flow direction 56, particularly aligned in the horizontal direction x, is separated from the separating member 57a of the device 57a for deposition of gaseous coolant from the liquid coolant, (60), which is preferably arranged in a vertical direction (y) to function as a baffle plate. After flowing into the heat transfer device 9a, the coolant collides against the front side of the separating member 60 formed as the separating wall. Due to the different inertial forces of the liquid coolant and the gaseous coolant, which are followed by the two phases whose directions are varied by sudden fluctuations in flow velocity and flow direction, different phases of the coolant are separated from each other.

The liquid coolant flows downward into the liquid region 58a formed in the first collection tube 50a in the flow direction 61, particularly aligned in the vertical direction (y), because the density of the liquid coolant is greater, while the gas coolant has a density Is guided upwardly into the gas region 59a formed in the first collecting tube 50a in the flow direction 62, particularly 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 only 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 an active vaporization region 64a and is configured to define an active vaporization region 64a, A rib 53 is provided for enlarging 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 is passed through the tube member 52-1 of the vaporization zone 64a, where heat is transferred to the coolant to vaporize the coolant. For example, the air flows through the ribs 53 in a cross-relative flow. After being fully vaporized, the gaseous coolant is discharged in the flow direction 63 in the direction of the discharge portion 55 inside the second collection tube 51a.

The tube member 52-2 extending between the first collecting tube 50a and the second collecting tube 51a in the gas region 59a of the first collecting tube 50a is a tube member 52-2 extending from the liquid collecting tube 50a for the deposition of gas coolant Forms an inert superfluous region 65a for the gaseous coolant that has been separated from the apparatus 57a and does not contain any ribs as opposed to the tube member 52-1 which forms the vaporization region 64a. Further, the tube member 52-2 of the superheating region 65a may also be formed of a flat tube disposed so as to be in contact with each other. The compact arrangement of the tube member 52-2 results in a very compact structural space of the heat exchanger 9a.

The gaseous coolant is guided through the tube member 52-2 of the superflow region 65a. In this case, no heat is transferred to the coolant. The gaseous coolant that is perfused through the supernatant region 65a is mixed with the gaseous coolant produced during vaporization inside the second collection tube 51a and the gaseous coolant is passed through the outlet 55 in the flow direction 56 And is discharged from the heat exchanger 9a.

The mass flow of the gaseous coolant and the liquid coolant is guided through different regions of the heat exchanger 9a that are eventually separated from each other, using the vaporization region 64a and the superfluous region 65a. These regions are set to different sizes, in which the vaporization region 64a is designed to be larger than the swirling region 65a.

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

According to one alternative embodiment, which is not shown, the tube member of the vaporization zone and the tube member of the super-flow zone are arranged on two sides, respectively aligned parallel to each other. In this case, the air may flow sequentially in the heat transfer surface of the preferential vaporization zone, and then the heat transfer surface of the superfluid zone, or vice versa, depending on the direction of each flow.

4 shows a heat transfer device 9b with an integrated device 57b for the deposition of a gaseous coolant from a liquid coolant as well as a vaporization zone 64b for the liquid coolant and an overflow zone 65b for the gaseous coolant, - air-heat exchanger is shown. A device 57b for depositing a gaseous coolant from the liquid coolant is disposed between the first collection tube 50b and the second collection tube 51b to connect the collection tubes 50b and 51b to each other.

The first collecting tube 50b and the second collecting tube 51b are arranged in parallel and in the vertical direction y with respect to the device 57b as well as with respect to each other, Respectively. The internal volumes of the collection tubes 50b, 51b are summed in common volume by the tube members 52-1 and the deposition apparatus 57b.

The coolant-air-heat exchanger 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 gaseous coolant from the liquid coolant while the second collection tube 51b comprises the outlet 55. [

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

The mixture consisting of a gas and a liquid coolant is introduced into a device 57b arranged to be aligned in a vertical direction y for the deposition of a gaseous coolant from a liquid coolant in a flow direction 56, Lt; / RTI > Due to the different inertial forces of the liquid coolant and the gaseous coolant, which are caused by the sudden variation of the flow velocity and the direction of flow while bombarding the wall of the device 57b, the two phases whose directions are varied differently are different phases, Separated.

The liquid coolant flows downward into the liquid region 58b formed in the device 57b in the direction of flow 61, especially aligned in the vertical direction (y), because the density of the liquid coolant is greater, while the gas coolant is less dense In particular in the direction of flow 62 aligned in the vertical direction y, into the gas region 59b formed in the device 57b as well.

The liquid region 58b is connected to the first collection tube 50b while the gas region 59b is hydraulically coupled to 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 ribs 53 for enlarging the heat transfer surface with respect to the outer side, that is, specifically with respect to the air side.

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

The second collection tube 51b forms an inert fluid region 65b for the gaseous coolant separated from the device 57b for deposition of gaseous coolant from the liquid coolant. The gaseous coolant is guided through the second collecting tube 51b in the flow direction 63 to be admixed with the gaseous coolant generated during vaporization and to be discharged as gaseous coolant in the flow direction 56 in the discharge direction 55 Through heat exchanger 9b.

Because only the liquid coolant flows through the active areas 64a, 64b, the overall vaporization enthalpy of the two-phase region of the coolant is used for heat absorption, respectively. The reduced coolant mass flow combined with the increased vaporization enthalpy causes much less coolant side pressure loss inside the active vaporization zones 64a, 64b, so that the coolant-air-heat exchanger as compared to the coolant- Resulting in a much lower temperature deviation of the coolant between the portion 54 and the discharge portion 55. Therefore, much more heat can be absorbed from the surroundings.

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

4, the heat exchanger 9b of FIG. 4 has a larger number of tubular members 52-1 in the same structural space and is perfused in parallel with a shorter length than the heat exchanger 9a of FIG. Whereby the refrigerant side pressure loss of the heat exchanger 9b can be further reduced.

A gaseous coolant flows through the second collecting tube 51b within the inert fluidized region 65b, which free flow section is formed such that only a small coolant side pressure loss occurs during the perfusion in the gaseous coolant.

Integrated devices 57a and 57b for the deposition of gaseous coolant from the liquid coolant are designed to allow the mass flow of the completely liquid coolant to always flow through the active vaporization areas 64a and 64b even when the fill heights of the liquid coolant are different Respectively. 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 "coolant circuit
3 compressor
4 Heat exchanger, coolant - coolant - heat exchanger
5 First expander
6 heat exchanger, first coolant-air-heat exchanger
7 Internal heat exchanger
8 Second expander
9a, 9b heat transfer device, heat exchanger, second coolant-air-heat exchanger
10 backflow preventing member
11 collector
12 first flow path
13 second flow path
14th quarter location
15 Joining position
16 valves, shutoff valve
17 second flow path
Quarter 18 Location
19 Joining position
20 third expander
30 Cooling water circuit
31 Feeding device
32 1st coolant-air-heat exchanger, heat exchanger
33 branch position, 3 way valve
34 Joining position
35 first flow path
36 2nd cooling water - air - heat exchanger
37 second flow path
40 Air conditioner
41 Direction of air flow in passenger space
42 Equipment module
43 Direction of air flow
50a, 50b first collecting tube
51a, 51b second collection tube
52-1, 52-2.
53 rib
54 coolant inlet
55 coolant discharge portion
56 Coolant flow direction
57a, 57b A device for depositing a gaseous coolant from a liquid coolant
58a, 58b,
59a, 59b gas region
60 separating 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
65a and 65b, the superfluid region of the gaseous coolant,
x horizontal direction
y vertical direction

Claims (19)

A heat exchanger (9a, 9b) for a coolant circuit (2 ', 2 ") of an automotive air conditioning system (1', 1"), in particular as a coolant- 54b and the collecting tubes 51a, 51b as well as the collecting tubes 51a, 51b and the collecting tubes 51a, 51b as well as the collecting tubes 55a, 54 and the collecting tubes 55a, 50b and the collecting tubes 51a, In a heat transfer device comprising disposed tube members 52-1, 52-2,
Devices 57a and 57b for depositing a gaseous coolant from a liquid coolant are integrally formed in the devices 9a and 9b for heat transfer and the heat transfer devices 9a and 9b are provided with a vaporizing area 64a , 64b) and an overflow region (65a, 65b) for the action of a gaseous coolant. 2. The apparatus according to claim 1, wherein the collection tubes (50a, 51a) are arranged in a vertical direction (y) and arranged in parallel with each other and in the horizontal direction (x) 2). ≪ / RTI > The heat transfer device (9a) according to claim 2, characterized in that the device (57a) for the deposition of a gaseous coolant from the liquid coolant is formed integrally in the first collection tube (50a). The heat transfer device (9a) according to claim 2, characterized in that said inlet (54) is formed in a first collection tube (50a). The apparatus according to claim 3, wherein the deposition apparatus (57a) comprises a separation member (60) arranged in a vertical direction (y) and the separation member is arranged to divide the internal volume of the first collection tube (50a) (58a) and the gas region (59a). 6. The method of claim 5, wherein a tube member (52-1) connecting the liquid region (58a) of the first collection tube (50a) to the second collection tube (51a) forms a vaporization region (64a) Characterized in that the tube member (52-2) connecting the gas region (59a) of the second collecting tube (50a) to the second collecting tube (51a) forms an overflow region (65a). 2. The apparatus according to claim 1, wherein the collection tubes (50b, 51b) are arranged in a horizontal direction (x) and arranged through the tube members (52-1) arranged parallel to each other and in the vertical direction Are connected to each other. A device according to claim 7, wherein the device for the deposition of gaseous coolant from the liquid coolant is arranged to connect the collection tubes (50b, 51b) between the first collection tube (50b) and the second collection tube (51b) (9b). ≪ / RTI > A device according to claim 8, characterized in that the device (57b) for the deposition of gaseous coolant from the liquid coolant is arranged in the vertical direction (y) and parallel to the tube members (52-1) ). 9. The heat transfer apparatus according to claim 8, characterized in that the inlet (54) is formed in a device (57b) for the deposition of a gaseous coolant from a liquid coolant. A device according to claim 8, wherein the device for the deposition of a gaseous coolant from a liquid coolant comprises a liquid region (58b) and a gas region (59b), wherein the liquid region (58b) , And the gas region (59b) is configured to be connected to the second collection tube (51b). 8. The apparatus according to claim 7, wherein the tube members (52-1) connecting the first collection tube (50b) to the second collection tube (51b) as well as the first collection tube (50b) form a vaporization region , And the second collection tube (51b) forms an overflow region (65b). An air conditioning system (1 ', 1') of an automobile having a coolant circuit (2 ', 2 ") and a coolant circuit (30) comprising a heat transfer device (9a, 9b) according to any one of the claims 1-11 "). 14. The method of claim 13,
- coolant circuit (2 ', 2 ") comprises a compressor (3), a coolant-coolant-heat exchanger (4) capable of operating as a condenser / gas cooler for the transfer of heat between the coolant of the coolant circuit (30) Air heat exchanger (6) for air conditioning of the supply air for the passenger space, as well as the first inflator (1)
The cooling water circuit 30 comprises a transfer device 31, a first cooling water-air-heat exchanger 32 for heating the supply air for the passenger compartment, a second cooling water-air-heat exchanger 36, - a cooling water-heat exchanger (4)
The heat transfer devices 9a and 9b are formed as second refrigerant-air-heat exchangers 9a and 9b which can only act as a vaporizer and are connected to the second coolant-air-heat exchangers 9a and 9b in the flow direction of the coolant, Characterized in that a second inflator (8) is located upstream of the second inflator and in that the second inflator (8) as well as the second coolant-air-heat exchanger (9a, 9b) (1 ', 1 "). The system according to claim 14, characterized in that the second coolant-air-heat exchanger (9a, 9b) of the second coolant-air-heat exchanger (36) and the coolant circuit (2 ' (1 ', 1 ") arranged in the interior of the air conditioning system (42) and arranged in order to act in the air flow direction (43). 16. The facility module (42) according to claim 15, characterized in that the facility module (42) is formed so as to be able to be perfused by air discharged from a passenger space, or ambient air, or mixed air consisting of air discharged from a passenger space and ambient air. Air conditioning system (1 ', 1 "). 15. A system according to claim 14, characterized in that the first coolant-air-heat exchanger (6) and the second coolant-air-heat exchanger (9a, 9b) are arranged in a refrigerant circuit (1 '). 15. A system according to claim 14, characterized in that the first coolant-air-heat exchanger (6) and the second coolant-air-heat exchanger (9a, 9b) are arranged in a refrigerant circuit (1 "). 19. The method of claim 18,
A first flow path 12 with a second inflator 8 and a second coolant-air-heat exchanger 9a, 9b is formed to extend from the branching position 18 to the converging position 19,
A first inflator 5, a first coolant-air-heat exchanger 6 and a third inflator 20 are formed in a second flow path 17, wherein the third inflator 20 is a coolant- Characterized in that the first flow path (17) is arranged downstream of the heat exchanger (6) and the second flow path (17) is formed to extend from the branching position (18) to the converging position (19).

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