DE102017109313B4 - Device for heat transfer for a refrigerant circuit of an air conditioning system of a motor vehicle and air conditioning system with the device - Google Patents

Abstract

Device (9a) for heat transfer for a refrigerant circuit (2 ', 2 ") of an air conditioning system (1', 1") of a motor vehicle, having an inlet (54) and an outlet (55) for the refrigerant, a first manifold (50a) and a second collecting pipe (51a) and pipe elements (52-1, 52-2) extending between the collecting pipes (50a, 51a) and arranged parallel to one another, wherein a device (57a) for separating gaseous refrigerant from liquid refrigerant in the device (9a) is designed to be integrated and the device (9a) has an evaporation area (64a) exclusively for the application of liquid refrigerant and an overflow area (65a) exclusively for the application of gaseous refrigerant, characterized in that the header pipes (50a) in the vertical direction ( y) arranged in an aligned manner and connected to one another via pipe elements (52-1, 52-2) arranged parallel to one another and in the horizontal direction (x) ind, and that the device (57a) for separating the gaseous refrigerant from the liquid refrigerant is integrated within the first collecting pipe (50a), the device (57a) having a separating element (60) which is arranged in the vertical direction (y) and which an inner volume of the first header tube (50a) is divided into a liquid region (58a) and a gas region (59a).

Description

The invention relates to a device for heat transfer, in particular a refrigerant-air heat exchanger operated as an evaporator, for a refrigerant circuit of an air conditioning system of a motor vehicle. The device has an inlet and an outlet for the refrigerant, a first manifold and a second manifold, as well as pipe elements extending between the manifolds and arranged parallel to one another.
The invention also relates to an air conditioning system for conditioning the air of a passenger compartment of a motor vehicle with a refrigerant circuit and a coolant circuit. The refrigerant circuit is designed with the device for heat transfer.

In motor vehicles known from the prior art, the waste heat from the engine is used to heat the supply air for the passenger compartment. The waste heat is transported to the air conditioning system by means of the coolant circulated in the engine coolant circuit, where it is transferred to the air flowing into the passenger compartment via the heating heat exchanger. Known systems with coolant-air heat exchangers, which draw the heating power from the coolant circuit of an efficient internal combustion engine of the vehicle drive, no longer achieve the level required for comfortable heating of the passenger compartment at low ambient temperatures in order to cover the total heat demand of the passenger compartment. The same applies to systems in motor vehicles with hybrid drives, that is to say motor vehicles with both an electric motor and an internal combustion engine drive.

If the overall heat requirement of the passenger compartment cannot be covered by the heat from the engine coolant circuit, additional heating measures, such as electrical resistance heating, or PTC resistance for “Positive Temperature Coefficient - Thermistor”, or fuel heaters, are required. The same applies to systems in motor vehicles or fuel cell vehicles driven purely by electric motors. A more efficient way of heating the air for the passenger compartment is a heat pump with air as the heat source, in which the refrigerant circuit serves both as the sole heating element and as an additional heating measure.

An air conditioning system with downstream electrical resistance heating is inexpensive to manufacture and can be used in any motor vehicle, but it has a very high demand for electrical energy, since the supply air for the passenger compartment is initially cooled and / or dehumidified when it flows over an evaporator of a refrigerant circuit and then is heated by means of the electrical resistance heater, which transfers the heat directly to the supply air or a coolant circuit.
The operation of a conventional air conditioning system to be operated as a heat pump is efficient, but requires a great deal of installation space, even at positions within the motor vehicle that do not have any installation space provision for the air conditioning. The increased costs, in particular the production and maintenance, as well as the large space requirement are a hindrance.

Air-to-air heat pumps belonging to the state of the art, which are designed for the combined refrigeration system mode and heat pump mode, i.e. for a heating mode and for a reheating mode, also referred to as reheat mode, absorb the heat from the ambient air. The ambient air consequently serves as a heat source for the evaporation of the refrigerant. The conventional air-to-air heat pumps have a heat exchanger for transferring heat between the refrigerant and the environment, a heat exchanger for supplying heat from the air to be conditioned in the passenger compartment to the refrigerant, and a heat exchanger for transferring heat from the refrigerant to the air to be conditioned for the passenger compartment. The services are transferred between the refrigerant and air.
In the so-called “reheat” mode, the air to be supplied to the passenger compartment is cooled, dehumidified and then slightly heated again. In this operating mode, the required post-heating capacity is less than the required cooling capacity for cooling and dehumidifying the air.

From the DE 10 2012 111 672 A1 shows a refrigerant circuit of an air conditioning system for conditioning the air of a passenger compartment of a motor vehicle. The refrigerant circuit is designed for combined operation in refrigeration system mode and heat pump mode and for post-heating mode and has a compressor, a heat exchanger for heat transfer between the refrigerant and the environment, a first expansion element and a heat exchanger for supplying heat from the air in the passenger compartment to be conditioned to the refrigerant , a heat exchanger for transferring heat from the refrigerant to the air to be conditioned for the passenger compartment and a second expansion element connected to it in the flow direction of the refrigerant.

In the DE 10 2011 100 301 A1 describes a vehicle air conditioning system with a refrigerant circuit that can be operated as a heat pump. The refrigerant circuit has a compressor, a valve body, which between an inlet side of a air-acted external heat exchanger and an indoor condenser is arranged, a relaxation element for relaxing the refrigerant, a three-way valve and an internal evaporator.

The refrigerant circuits each have a branched system of connecting lines which are difficult to integrate into the existing installation space. Furthermore, the additional valves and the large-volume refrigerant reservoir, which is arranged at a low pressure level, each require a large amount of installation space. The valves must also have a very high internal tightness, which also leads to increased system costs.

The heat exchanger for heat transfer between the refrigerant and the ambient air of the air-to-air heat pump, also referred to as an air-loaded external heat exchanger or as an ambient heat exchanger, is arranged outside the housing of the air conditioning systems, specifically outside the air conditioning units, on the front of the motor vehicle and is in particular provided by the Airstream is charged with air.
When the refrigerant circuit is operated in refrigeration system mode, the ambient heat exchanger is operated as a condenser / gas cooler to transfer heat from the refrigerant to the ambient air, and when the refrigerant circuit is operated in heat pump mode as an evaporator to absorb heat from the refrigerant from the ambient air. The ambient heat exchanger is thus designed for operation in both functions, so that the design is not optimal for either of the two functions and a compromise has to be found.
For the different functions, there are partially contradicting design criteria for the heat exchanger. The heat exchanger operated as a condenser / gas cooler is designed for high refrigerant pressures, for example, with the wall thicknesses being very large in relation to the flow cross-section, so that the flow cross-sections for a condenser / gas cooler are significantly smaller than for a heat exchanger operated as an evaporator at a lower refrigerant pressure level. When the heat exchanger is operated as an evaporator, the small flow cross-sections of the ambient heat exchanger lead to high pressure losses, which greatly reduce the overall performance and the efficiency of the air conditioning system as an important design criterion.

In addition, when the refrigerant circuit is operated in heat pump mode, the refrigerant enters the ambient heat exchanger with a vapor content in the range between 20% and 60%. The vapor portion of the refrigerant only insignificantly contributes to the transfer of heat from the ambient air to the refrigerant, but it causes the pressure loss when flowing through the ambient heat exchanger.

The pressure loss of the refrigerant during operation of the ambient heat exchanger as an evaporator causes a reduction in the temperature of the refrigerant, so that the refrigerant has a higher temperature at the inlet to the ambient heat exchanger than at the outlet. In order to avoid the risk of the ambient heat exchanger icing up, the maximum difference between the temperature of the air flowing into the ambient heat exchanger and the temperature of the refrigerant is limited, in particular to a range between 2 K and 10 K. The maximum permitted temperature difference relates to the temperature of the air flowing into the ambient heat exchanger and the temperature of the refrigerant in the evaporator at the point with the lowest temperature, that is to say at the outlet. The greatest temperature difference thus occurs between the air flowing into the ambient heat exchanger and the refrigerant at the outlet of the refrigerant from the evaporator. Possible overheating of the refrigerant is not taken into account. There is a lower than the permitted temperature difference at the entry of the refrigerant into the ambient heat exchanger. The greater the pressure loss on the refrigerant side, the smaller the temperature difference at the inlet of the refrigerant into the ambient heat exchanger and the less heat can be absorbed from the ambient air, which is then available for heating the passenger compartment.

In the systems known from the prior art, the at least partially gaseous refrigerant flowing into the ambient heat exchanger results in an undesirable pressure loss, so that the maximum heat transferable by the refrigerant from the ambient air is limited and is, for example, a maximum of 3 kW.

At air temperatures in the range of 0 ° C and below 0 ° C, the heat transfer surface of the evaporator can ice up. As a result of the absorption of heat from the air, the relative humidity of the cooled air increases. When the temperature falls below the dew point, the water vapor present in the air is condensed out and deposited as water on the heat transfer surface. The water condensed out of the air on the heat transfer surface will solidify to ice at surface temperatures in the range of 0 ° C and below 0 ° C. The increasing layer of ice reduces the air-side heat transfer surface and the air-side heat transfer and thus the heat transfer between the air and the evaporating refrigerant.

the U.S. 6,457,325 B1 discloses a refrigerant circuit with a compressor, an ambient heat exchanger operated as a gas cooler / condenser, an expansion element, a device for separating gaseous refrigerant and an evaporator with which the supply air to be supplied to the passenger compartment can be conditioned. The device arranged between the gas cooler / condenser and the evaporator for separating gaseous refrigerant has a chamber with an inlet connected to the gas cooler / condenser, a vapor outlet connected to the compressor via a bypass line and an outlet for liquid refrigerant connected to the evaporator. The design of the device for separating gaseous refrigerant from liquid refrigerant ensures that only liquid refrigerant is passed to the evaporator.
With the device for separating gaseous refrigerant from the liquid refrigerant, which is arranged upstream of the evaporator in the direction of flow of the refrigerant, only liquid refrigerant is fed into the evaporator, so that the refrigerant circuit can be operated efficiently. However, the refrigerant circuit with the device for separating, the bypass line with an expansion valve arranged therein, the evaporator and a connecting line arranged between the device for separating and the evaporator has a large number of separately designed components, which also represent a high mass to be absorbed by the vehicle and take up a large space in the already very limited space of the motor vehicle. In addition, with the expansion valve arranged in the bypass line, an additional control element is required, which further increases the complexity of the system and thus makes it more difficult to coordinate the control strategy. The state of the art also includes WO 2009/152 015 A2 , the JP H06-117728 A , the EP 1 106 952 A2 as well as the JP H08-5 195 A .

The object of the invention is now to provide an ambient heat exchanger that can be operated exclusively as an evaporator, which during operation has a minimal pressure loss on the refrigerant side and thus a maximum heat that can be transferred from the ambient air to the refrigerant. The ambient heat exchanger as a heat exchanger for absorbing heat from the ambient air should be optimally designed.

The ambient heat exchanger should be able to be integrated in an air conditioning system for a motor vehicle which, as required, absorbs heat from the environment via the ambient heat exchanger and emits heat to the environment via a component that differs from the ambient heat exchanger. The air conditioning system should be able to be operated in refrigeration mode, in heat pump mode as well as in post-heating mode. Depending on the operating mode, the ambient air should serve both as a heat source, for example when operating in heat pump mode, and as a heat sink, for example when operating in refrigeration system mode. The air conditioning system should also be able to be operated efficiently, for example with a minimal risk of icing of the evaporator of the refrigerant circuit for heat transfer with air, and be designed to be compact.

The refrigerant circuit of the air conditioning system should have a simple design and have a minimum number of components in order to cause only minimal operating costs, manufacturing costs and maintenance costs and to have a minimal space requirement.

The object is achieved by the objects with the features of the independent patent claims. Further developments are given in the dependent claims.

The object is achieved by a device, in particular a refrigerant-air heat exchanger operated as an evaporator, for a refrigerant circuit of an air conditioning system of a motor vehicle. The device has an inlet and an outlet for the refrigerant, a first manifold and a second manifold, as well as pipe elements extending between the manifolds and arranged parallel to one another.

According to the conception of the invention, a device for separating gaseous refrigerant from liquid refrigerant is integrated in the device for heat transfer. In addition, the device for heat transfer has an evaporation area exclusively for the application of liquid refrigerant and an overflow area exclusively for the application of gaseous refrigerant.
The outlet for the refrigerant is preferably formed on the second manifold.

According to the invention, the header pipes are arranged aligned in the vertical direction and connected to one another via pipe elements arranged parallel to one another and in the horizontal direction.

According to the invention, the device for separating the gaseous refrigerant from the liquid refrigerant is integrated within the first collecting pipe.

The inlet for the refrigerant is advantageously formed on the first manifold.

According to the invention, the device also has a separating element which is arranged aligned in the vertical direction and which divides an inner volume of the first collecting tube into a liquid area and a gas area.

Another advantage of the invention is that the pipe elements connecting the liquid area of the first manifold to the second manifold form the evaporation area and the pipe elements connecting the gas area of the first manifold to the second manifold form the overflow area. The pipe elements forming the evaporation area and the pipe elements forming the overflow area are configured differently and / or are arranged differently from one another.

According to an alternative embodiment of the invention, the collecting pipes are aligned in the horizontal direction and connected to one another via pipe elements arranged parallel to one another and in the vertical direction.

According to a development of the invention, the device for separating the gaseous refrigerant from the liquid refrigerant is arranged between the first manifold and the second manifold, connecting the manifolds to one another.
The inlet for the refrigerant is preferably formed on the device for separating the gaseous refrigerant from the liquid refrigerant.

The device for separating the gaseous refrigerant from the liquid refrigerant is advantageously arranged in the vertical direction and parallel to the pipe elements.

According to a preferred embodiment of the invention, the device for separating the gaseous refrigerant from the liquid refrigerant has a liquid area and a gas area. The liquid area is connected to the first collecting tube and the gas area is connected to the second collecting tube.

The first manifold and the pipe elements connecting the first manifold to the second manifold advantageously form the evaporation area and the second manifold forms the overflow area.

• - minimaler kältemittelseitiger Druckverlust,
• - maximale Wärmeaufnahme aus der Umgebungsluft sowie
• - minimales Risiko der Vereisung der umgebungsluftseitigen Wärmeübertragerfläche durch Einhalten erforderlicher Temperaturdifferenzen.

The device according to the invention for heat transfer of a refrigerant circuit, in particular an air conditioning system of a motor vehicle, has various advantages in summary:

• - minimal pressure loss on the refrigerant side,
• - maximum heat absorption from the ambient air as well
• - Minimal risk of icing up of the heat exchanger surface on the ambient air side by maintaining the required temperature differences.

The object is also achieved by an air conditioning system according to the invention for conditioning the air of a passenger compartment of a motor vehicle, in particular for operation in a refrigeration system mode, in a heat pump mode and in a post-heating mode, with a refrigerant circuit and a coolant circuit.
According to the concept of the invention, the refrigerant circuit is designed with a device for heat transfer with the aforementioned features.

According to a further development of the invention, the refrigerant circuit has a compressor in the flow direction of the refrigerant, a refrigerant-coolant heat exchanger that can be operated as a condenser / gas cooler for heat transfer between the refrigerant and the coolant of the coolant circuit, a first expansion element and a first refrigerant-air heat exchanger for conditioning the supply air for the passenger compartment. The coolant circuit is designed with a conveying device for circulating the coolant, a first coolant-air heat exchanger for heating the supply air for the passenger compartment, a second coolant-air heat exchanger and the refrigerant-coolant heat exchanger.

The refrigerant circuit also has the device according to the invention for heat transfer as a second refrigerant-air heat exchanger that can be operated exclusively as an evaporator. A second expansion element is upstream of the second refrigerant-air heat exchanger in the flow direction of the refrigerant. The second expansion element and the second refrigerant-air heat exchanger are arranged together within a first flow path.

The refrigeration system mode is primarily used for cooling, the heat pump mode for heating and the post-heating mode for post-heating the supply air to be conditioned in the passenger compartment. In post-heating mode, the supply air was cooled down and / or dehumidified before post-heating.

If the refrigerant is liquefied during subcritical operation of the refrigerant circuit, for example with the refrigerant R134a or with carbon dioxide under certain ambient conditions, the heat exchanger is referred to as a condenser. Part of the heat transfer takes place at a constant temperature. In supercritical operation or in the case of supercritical heat dissipation in the heat exchanger, the temperature of the refrigerant steadily decreases. In this case, the heat exchanger is also referred to as a gas cooler. Supercritical operation can occur under certain ambient conditions or operating modes of the refrigerant circuit, for example with the refrigerant carbon dioxide.

The second coolant-air heat exchanger of the coolant circuit and the second coolant-air heat exchanger of the coolant circuit are advantageously arranged so that they can be acted upon one after the other within a system module and in the air flow direction.
According to a further development of the invention, the system module arranged in particular in a front area of the motor vehicle can be flown through with air discharged from the passenger compartment or with ambient air or with a mixture of air discharged from the passenger compartment and ambient air.

According to a first alternative embodiment of the invention, the first refrigerant-air heat exchanger and the second refrigerant-air heat exchanger are arranged within the refrigerant circuit so that they can flow through each other in series.
The refrigerant circuit advantageously has a second flow path with a valve. The first flow path with the second expansion element and the second refrigerant-air heat exchanger and the second flow path each extend from a branch point to an opening point, so that the second flow path is designed as a bypass parallel to the first flow path.

According to a second alternative embodiment of the invention, the first refrigerant-air heat exchanger and the second refrigerant-air heat exchanger are arranged within the refrigerant circuit so that they can flow through parallel to one another.
Another advantage of the invention is that the first flow path with the second expansion element and the second refrigerant-air heat exchanger extends from a branch point to an opening point. The first expansion element, the first refrigerant-air heat exchanger and a third expansion element are formed within a second flow path. The third expansion element is arranged downstream of the refrigerant-air heat exchanger. The second flow path is also designed to extend from the branch point to the opening point.

• - Klimatisieren, insbesondere Kühlen, Entfeuchten und/oder Heizen der Zuluft des Fahrgastraums mit minimalem Energieeinsatz, auch durch Nutzen von Verlustwärmeströmen zur Beheizung des Fahrgastraums,
• - Verwenden des speziell für den Betrieb als Verdampfer ausgebildeten Kältemittel-Luft-Wärmeübertragers zum Einsatz beim Betrieb im Wärmepumpenmodus, um insbesondere bei geringen Außentemperaturen Wärme aus der Umgebung aufzunehmen, wobei bei höheren Außentemperaturen und Kühlbedarf Wärme über eine vom Kältemittel-Luft-Wärmeübertrager abweichende Komponente an die Umgebung abgegeben wird,
• - erhöhte Leistungsfähigkeit, Effizienz und Lebensdauer sowie
• - Bereitstellen eines ausreichenden Komforts innerhalb des Fahrgastraums mit
• - konstruktiv einfachem Kältemittelkreislauf, welcher zum Einsatz in bekannten Schemata und vorhandenen Bauräumen bestehender Kraftfahrzeuge integrierbar ist und einen minimalen Bauraum, ein minimales Gewicht sowie eine minimale Anzahl an Komponenten aufweist, dadurch
• - minimale Betriebskosten, Herstellungskosten und Wartungskosten.

The air conditioning system according to the invention with the device according to the concept for heat transfer has in summary various advantages:

• - Air conditioning, in particular cooling, dehumidifying and / or heating the supply air to the passenger compartment with minimal use of energy, also by using waste heat flows to heat the passenger compartment,
• - Use of the refrigerant-air heat exchanger, specially designed for operation as an evaporator, for use in operation in heat pump mode, in order to absorb heat from the environment, especially at low outside temperatures, with heat from a component that differs from the refrigerant-air heat exchanger at higher outside temperatures and cooling requirements is released into the environment,
• - increased performance, efficiency and service life as well
• - Providing sufficient comfort within the passenger compartment
• - structurally simple refrigerant circuit, which can be integrated for use in known schemes and existing installation spaces of existing motor vehicles and has a minimal installation space, a minimal weight and a minimal number of components, thereby
• - minimal operating costs, manufacturing costs and maintenance costs.

• 1 und 2: jeweils ein Klimatisierungssystem mit einem Kältemittelkreislauf, aufweisend einen ersten und einen zweiten Kältemittel-Luft-Wärmeübertrager sowie einen inneren Wärmeübertrager, mit einem Kühlmittelkreislauf, aufweisend einen ersten und einen zweiten Kühlmittel-Luft-Wärmeübertrager, sowie mit einem den Kältemittelkreislauf und den Kühlmittelkreislauf thermisch verbindenden Kältemittel-Kühlmittel-Wärmeübertrager,
• 1: mit in Reihe zueinander angeordneten Kältemittel-Luft-Wärmeübertragern,
• 2: mit parallel zueinander angeordneten Kältemittel-Luft-Wärmeübertragern,
• 3 und 4: jeweils eine Vorrichtung zur Wärmeübertragung, insbesondere einen Kältemittel-Luft-Wärmeübertrager, mit integrierter Vorrichtung zum Abscheiden gasförmigen Kältemittels von flüssigem Kältemittel sowie einem Verdampfungsbereich und einem Überströmbereich für gasförmiges Kältemittel
• 3: mit der Ausbildung der Vorrichtung zum Abscheiden innerhalb eines Sammelrohres und
• 4: mit der Ausbildung und Anordnung der Vorrichtung zum Abscheiden zwischen zwei Sammelrohren.

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

• 1 and 2 : each an air conditioning system with a refrigerant circuit, having a first and a second refrigerant-air heat exchanger and an internal heat exchanger, with a coolant circuit, having a first and a second coolant-air heat exchanger, and with a thermally connecting the refrigerant circuit and the coolant circuit Refrigerant-coolant heat exchanger,
• 1 : with refrigerant-air heat exchangers arranged in series,
• 2 : with refrigerant-air heat exchangers arranged parallel to one another,
• 3 and 4th : in each case a device for heat transfer, in particular a refrigerant-air heat exchanger, with an integrated device for separating gaseous refrigerant from liquid refrigerant and a Evaporation area and an overflow area for gaseous refrigerant
• 3 : with the formation of the device for separation within a collecting tube and
• 4th : with the design and arrangement of the device for separating between two collecting pipes.

In 1 is an air conditioning system 1' with a refrigerant circuit 2 ' and a coolant circuit 30th shown. The refrigerant circuit 2 ' has a compressor in the direction of flow of the refrigerant 3 , a refrigerant-coolant heat exchanger operated as a condenser / gas cooler 4th , a first expansion organ 5 and a first refrigerant-air heat exchanger 6th for conditioning the supply air for the passenger compartment. The refrigerant circuit 2 ' is also equipped with a second refrigerant-air heat exchanger operated as an evaporator 9a , 9b designed to transfer heat from air to the refrigerant, which has a second expansion element 8th is upstream. The first refrigerant-air heat exchanger 6th and the second refrigerant-air heat exchanger 9a , 9b are arranged in series or in series with one another. The second refrigerant-air heat exchanger 9a , 9b and the associated second expansion element 8th are within a first flow path 12th educated. The second refrigerant-air heat exchanger 9a , 9b advantageously has the installation space of a conventional air-charged refrigerant-air heat exchanger operated as a condenser / gas cooler.

Between the second refrigerant-air heat exchanger 9a , 9b and the compressor 3 is a collector 11 arranged. The one upstream of the compressor in the direction of flow of the refrigerant 3 and thus collectors arranged on the low pressure side 11 , also known as an accumulator, is used to separate and collect refrigerant liquid. The compressor 3 sucks gaseous refrigerant out of the receiver 11 at. The refrigerant circuit 1' is closed. According to an alternative embodiment, not shown, the collector is a refrigerant storage device within the refrigerant-coolant heat exchanger 4th integrated and thus arranged at the high pressure level of the refrigerant. The collector arranged at the low pressure level can thereby 11 omitted. The refrigerant-coolant heat exchanger 4th can also be designed with a device for drying the refrigerant.

The refrigerant circuit 2 ' points next to the first flow path 12th also a second flow path 13th which are each from a junction 14th up to an outlet point 15th extend. The one parallel to the first flow path 12th , especially for the second refrigerant-air heat exchanger 9a , 9b , formed second flow path 13th has a valve 16 , especially a shut-off valve 16 , and serves as a bypass for guiding a refrigerant mass flow around the second refrigerant-air heat exchanger 9a , 9b hereabouts.
Within the first flow path 12th is between the refrigerant-air heat exchanger 9a , 9b and the muzzle 15th a non-return element 10 , in particular a check valve, arranged. The kickback element 10 prevents backflow of the through the second flow path 13th and thus around the refrigerant-air heat exchanger 9a , 9b refrigerant mass flow passed around in the refrigerant-air heat exchanger 9a , 9b .

The refrigerant circuit 2 ' is also equipped with an internal heat exchanger 7th formed, which on the high-pressure side between the refrigerant-coolant heat exchanger 4th and the first expansion device 5 of the first refrigerant-air heat exchanger 6th as well as on the low pressure side between the orifice 15th and the collector 11 or the compressor 3 is trained. The internal heat exchanger 7th serves to transfer heat between the refrigerant at high pressure and the refrigerant at low pressure, with the heat exchanger operated as a condenser / gas cooler on the one hand 4th outflowing liquid refrigerant is further cooled and on the other hand that from the heat exchanger operated as an evaporator 6th , 9a , 9b escaping refrigerant as suction gas upstream of the compressor 3 becomes overheated. In addition to protecting the compressor 3 before liquid hammers can operate the refrigerant circuit 2 ' with internal heat exchanger 7th the specific compressor capacity and at the same time the specific cooling capacity and thus the efficiency of the operation of the air conditioning system 1' increase.

The coolant circuit 30th has a delivery device in the flow direction of the coolant 31 for circulating the coolant, in particular a pump and a heat exchanger 32 as the first coolant-air heat exchanger to heat the supply air for the passenger compartment. The heat exchanger 32 is also with the refrigerant-coolant heat exchanger 4th tied together. The coolant circuit 30th is closed. The refrigerant-coolant heat exchanger operated on the refrigerant side as a condenser / gas cooler 4th is therefore coolant-cooled.

In between the heat exchanger 32 and the refrigerant-coolant heat exchanger 4th formed connecting line are also a three-way valve 33 as a branch point as well as an outlet point 34 provided, between each of which there is a first flow path 35 with a second coolant-air heat exchanger 36 for transferring heat to air as well as a second flow path 37 as a bypass around the coolant-air heat exchanger 36 are trained.

The heating heat exchanger as the first coolant-air heat exchanger 32 and the second coolant-air heat exchanger 36 are thus arranged in series one after the other so that the coolant can flow through them.

The second coolant-air heat exchanger 36 of the coolant circuit 30th and the second refrigerant-air heat exchanger operated as an evaporator 9a , 9b of the refrigerant circuit 2 ' are within a system module 42 as well as in the existing installation space of the motor vehicle and in the direction of flow 43 the air arranged one after the other can be acted upon. The system module arranged in the front area of the motor vehicle can 42 with air discharged from the passenger compartment, with ambient air or a mixture of air discharged from the passenger compartment and ambient air. The air conditioning system 1' can consequently use the latent heat of the air discharged from the passenger compartment and also heat from the surroundings as a heat source.
The air is first passed through the coolant-air heat exchanger 36 and then via the refrigerant-air heat exchanger 9a , 9b guided so that the arrangement of the heat exchanger 9a , 9b , 36 the risk of the heat exchanger surface of the refrigerant-air heat exchanger icing up 9a , 9b reduced.
In addition, a fan can flow onto the coolant-air heat exchanger 36 also for flow to the refrigerant-air heat exchanger 9a , 9b be used.

The refrigerant-air heat exchanger 6th of the refrigerant circuit 2 ' and the heat exchanger 32 of the coolant circuit 30th are inside an air conditioner 40 as well as in the direction of flow 41 the supply air of the passenger compartment arranged to be acted upon one after the other. This can be used when overflowing the evaporator 6th cooled and / or dehumidified supply air for the passenger compartment as required when flowing over the heat exchanger 32 be heated. The flow to the heat exchanger 32 with before when overflowing the refrigerant-air heat exchanger 6th conditioned air can be regulated by means of a temperature flap (not shown).

The refrigerant-coolant heat exchanger 4th serves to thermally connect the refrigerant circuit 2 ' with the coolant circuit 30th . The heat is transferred from the refrigerant to the coolant.

The air conditioning system 1' can, especially when operating with circulating air, i.e. with air extracted from the passenger compartment as a heat source, even at outside air temperatures with values below 0 ° C, without the risk of the heat exchanger surface of the refrigerant-air heat exchanger operated as an evaporator icing up 9a , 9b , operate.

To ensure this operation, the in the air conditioner 40 arranged refrigerant-air heat exchanger 6th charged with refrigerant at a medium pressure level and operated as an evaporator. The latent heat to be removed from the air when the air entering the evaporator is dehumidified, together with that of the refrigerant during compression in the compressor 3 The power supplied is used to heat the supply air for the passenger compartment to a desired outlet temperature. The heat absorbed by the refrigerant is transferred to the coolant-cooled refrigerant-coolant heat exchanger 4th transferred to the coolant, which absorbs the heat as it flows through the heat exchanger 32 to the supply air.

When operating in the refrigeration system mode or in the post-heating mode for dehumidifying the supply air, the excess heat absorbed by the refrigerant and transferred to the coolant is passed through the first flow path 35 of the coolant circuit 30th and in the second coolant-air heat exchanger 36 , also referred to as low-temperature cooler, released into air in the front area of the motor vehicle. The coolant is circulated regardless of the operating mode and when flowing through the refrigerant-coolant heat exchanger 4th warmed up.

When operating the climate system 1' in heat pump mode or in post-heating mode, a 32 Heat transferable to the supply air of the passenger compartment from the first refrigerant-air heat exchanger operated as an evaporator 6th or in the second refrigerant-air heat exchanger operated as an evaporator 9a , 9b and in the compressor 3 Energy transferred to the refrigerant, which is the sum in the refrigerant-coolant heat exchanger 4th to be transferred to the coolant, put together in order to achieve a sufficient temperature of the supply air for the passenger compartment.

The one configured exclusively for the absorption of heat and thus for operation as an evaporator Refrigerant-air heat exchanger 9a , 9b is acted upon with refrigerant at a low pressure level.

Depending on requirements, that is, when in the refrigerant circuit 2 ' sufficient heat provided to heat the air supply to the passenger compartment when operating in post-heating mode and in the second refrigerant-air heat exchanger 9a , 9b no additional heat absorption is necessary, the second refrigerant-air heat exchanger can 9a , 9b from the refrigerant circuit 2 ' shut off and in bypass through the second flow path 13th be bypassed. The valve 16 is opened while the expansion element designed as an expansion valve 8th is closed.

When operating the climate system 1' in heat pump mode, this can be done by the second refrigerant-air heat exchanger 9a , 9b upstream expansion device 8th be regulated in such a way as to relax the refrigerant to a low pressure level at which the inlet temperature of the refrigerant is only slightly below the temperature of the air, in particular the ambient air. The refrigerant is evaporated at the temperature associated with the low pressure level.

The first refrigerant-air heat exchanger operated as a condenser / gas cooler 6th is pressurized with refrigerant at a medium pressure level and can, if necessary, be fed into the air conditioning unit 40 Preheat incoming air for the passenger compartment. When overflowing the heat exchanger charged with coolant 32 the supply air is heated further.

The two-stage heating of the supply air increases by increasing the possible enthalpy difference of the refrigerant before the expansion and thus the evaporation in the second refrigerant-air heat exchanger 9a , 9b the efficiency of the operation of the air conditioning system 1' .

the end 2 goes an air conditioning system 1'' with a refrigerant circuit 2 '' and the coolant circuit 30th emerged. The air conditioning system 1'' differs from the air conditioning system 1' the end 1 only in the formation of the refrigerant circuits 2 ' , 2 '' .

The refrigerant circuit 2 '' points the compressor in the direction of flow of the refrigerant 3 , the refrigerant-coolant heat exchanger operated as a condenser / gas cooler 4th , the first expansion organ 5 as well as the first refrigerant-air heat exchanger 6th for conditioning the supply air for the passenger compartment. The refrigerant-air heat exchanger 6th is a third expansion organ 20th , in particular an expansion valve, downstream. The combination of the first expansion element 5 , the first refrigerant-air heat exchanger 6th and third expansion device 20th is within a second flow path 17th arranged, which is from a junction 18th up to an outlet point 19th extends.

The refrigerant circuit 2 '' is also connected to the second refrigerant-air heat exchanger operated as an evaporator 9a , 9b designed to transfer heat from air to the refrigerant, which the second expansion element 8th is upstream. The first refrigerant-air heat exchanger 6th and the second refrigerant-air heat exchanger 9a , 9b are arranged parallel to each other. The second refrigerant-air heat exchanger 9a , 9b and the associated second expansion element 8th are within the first flow path 12th formed, which, like the second flow path 17th , from the junction 18th up to the muzzle 19th extends. The first flow path 12th , which is between the refrigerant-air heat exchanger 9a , 9b and the muzzle 19th a non-return element 10 , in particular a check valve, and the second flow path 17th thus run parallel. The second refrigerant-air heat exchanger 9a , 9b advantageously has the installation space of a conventional air-charged refrigerant-air heat exchanger operated as a condenser / gas cooler.

Between the muzzle 19th and the compressor 3 is again a collector 11 arranged. According to an alternative embodiment, not shown, the collector is a refrigerant storage device within the refrigerant-coolant heat exchanger 4th integrated and thus arranged at the high pressure level of the refrigerant, the collector arranged at the low pressure level 11 can be omitted. The refrigerant-coolant heat exchanger 4th can also be designed with a device for drying the refrigerant.

When operating the climate system 1'' in post-heating mode, depending on requirements, i.e. when the refrigerant circuit 2 '' Sufficient heat provided to heat the supply air to the passenger compartment and in the second refrigerant-air heat exchanger 9a , 9b no additional heat absorption is necessary, the second refrigerant-air heat exchanger 9a , 9b from the refrigerant circuit 2 '' be locked. The second expansion element designed as an expansion valve 8th as when operating the air conditioning system 1' in refrigeration mode, closed.

When operating the climate system 1'' in the heat pump mode, the first expansion element 5 with the second expansion element open 8th getting closed. This is the first refrigerant-air heat exchanger 6th not charged with refrigerant. The entire refrigerant mass flow is used to absorb heat by the second refrigerant-air heat exchanger 9a , 9b directed.

An embodiment of the coolant circuit, not shown, 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 branch point designed as a three-way valve.
The three-way valve is provided in the connecting line formed between the conveying device and the heating heat exchanger, while the opening point is formed between the heating heat exchanger and the refrigerant-coolant heat exchanger. The second coolant-air heat exchanger is formed within a first flow path and the heating heat exchanger is formed within a second flow path, each of which extends from the branch point to the point of opening. The heating heat exchanger as the first coolant-air heat exchanger and the second coolant-air heat exchanger are thus arranged parallel to one another so that the coolant can flow through them.

The refrigerant circuit and the operating modes can be used for any refrigerant which undergoes a phase transition from liquid to gaseous on the low-pressure side. On the high pressure side, the medium releases the absorbed heat to a heat sink through gas cooling / condensation and subcooling. Natural substances such as R744, R717 and similar, flammable substances such as R290, R600, R600a and similar chemical substances such as R134a, R152a, HFO-1234yf, as well as various refrigerant mixtures can be used as refrigerants.

the 3 and 4th each show a device 9a , 9b for heat transfer, in particular a refrigerant-air heat exchanger or ambient heat exchanger operated as an evaporator, with an integrated device 57a , 57b for separating gaseous refrigerant from liquid refrigerant as well as an evaporation area 64a , 64b for liquid refrigerant and an overflow area 65a , 65b for gaseous refrigerant. The device 57a , 57b for separating the gaseous refrigerant from the liquid refrigerant, also referred to as a separator, phase separator or phase separator, is inside the refrigerant-air heat exchanger 9a , 9b integrated trained.

The device 57a , 57b separates the liquid phase from the gaseous phase of the refrigerant before the refrigerant passes through a heat-transferring section of the refrigerant-air heat exchanger 9a , 9b flows through. The heat transferring section of the refrigerant-air heat exchanger 9a , 9b is divided into two areas: an active area 64a , 64b , also known as the evaporation area, and the inactive area 65a , 65b , also known as the overflow area.
The active area 64a , 64b can be acted upon with air in cross-countercurrent to the refrigerant, whereby heat can be transferred from the air to the refrigerant. The inactive area 65a , 65b is preferably not exposed to air, so within the inactive area 65a , 65b no heat is transferred.
This flows into the device on the refrigerant side 57a , 57b liquid refrigerant separated from the liquid refrigerant by the active area to separate the gaseous refrigerant 64a , 64b of the refrigerant-air heat exchanger 9a , 9b and is evaporated while absorbing heat. The separated gaseous refrigerant is passed through the inactive area 65a , 65b of the refrigerant-air heat exchanger 9a , 9b and thus flows through the refrigerant-air heat exchanger without absorbing heat 9a , 9b through.

Since only liquid refrigerant through the active area 64a , 64b of the heat transferring section of the refrigerant-air heat exchanger 9a , 9b flows, is the total refrigerant-side pressure loss of the refrigerant when flowing through the refrigerant-air heat exchanger 9a , 9b significantly lower than the pressure loss when flowing through a conventional refrigerant-air heat exchanger operated in heat pump mode as an evaporator. In addition, the gaseous refrigerant through the inactive area 65a , 65b and thus around the active area 64a , 64b of the refrigerant-air heat exchanger 9a , 9b is routed around it becomes the active area 64a , 64b acted upon with a lower refrigerant mass flow.

As a result of the reduced pressure loss on the refrigerant side and the lower refrigerant mass flow, the component size can be reduced compared to a refrigerant-air heat exchanger known from the prior art, with the same performance requirements for the heat to be transferred, which leads to lower manufacturing costs and lower weight leads.
In addition, the refrigerant-air heat exchanger 9a , 9b no additional separately formed components, such as an expansion element or an independent device for separating as well as refrigerant lines connecting the components, which also reduces the costs and the complexity of the refrigerant circuit.

the end 3 goes a device 9a for heat transfer with integrated device 57a for separating gaseous refrigerant from liquid refrigerant as well as an evaporation area 64a as an active area 64a and an overflow area 65a for gaseous refrigerant as an inactive area 65a emerged. The device 57a for separating the gaseous refrigerant from the liquid refrigerant is inside a first manifold 50a or distribution pipe or refrigerant inlet manifold arranged.

The device 9a has the first manifold 50a and a second manifold 51a on which about parallel to each other and in a horizontal direction x arranged, in particular rectilinear tubular elements 52-1 , 52-2 are connected to each other. The internal volumes of the manifolds 50a , 51a are about the pipe elements 52-1 , 52-2 combined to form a common volume.

The device 9a has an inlet 54 and an outlet 55 for the refrigerant. The inlet 54 is on the first manifold 50a formed while the second manifold 51a the outlet 55 having.

The two phases of the refrigerant are by means of the device 57a mechanically separated from each other. The mechanical separation is based on the inertial force as the driving force, which requires a sufficiently large difference in density between the phases of the refrigerant.

That in particular in the horizontal direction x aligned flow direction 56 into the first manifold 50a The inflowing mixture of gaseous and liquid refrigerant is counteracted, preferably in a vertical direction y Aligned separating element serving as a baffle plate 60 the device 57a to separate the gaseous refrigerant from the liquid refrigerant. After flowing into the device 9a the refrigerant strikes a front side of the separating element designed as a partition 60 . Due to the abrupt changes in the flow velocity and the flow direction, the different phases of the refrigerant are separated from one another due to the different inertial forces of the liquid refrigerant and the gaseous refrigerant, with which the two phases follow the change in direction differently.

Due to the greater density, the liquid refrigerant flows in the, in particular, in the vertical direction y aligned flow direction 61 down into one in the first manifold 50a formed fluid area 58a , while the gaseous refrigerant due to the lower density in the particular in the vertical direction y aligned flow direction 62 up into one also in the first manifold 50a trained gas area 59a is directed.

The separator 60 also serves as a means for separating the liquid area 58a from the gas area 59a and thus to the formation of two chambers. The chambers are only in the liquid area 58a interconnected to allow liquid refrigerant to flow over between the chambers.

The the fluid area 58a of the first manifold 50a with the second manifold 51a connecting pipe elements 52-1 form the active evaporation area 64a and are designed with ribs to enlarge the heat exchanger surface on the outside, i.e. especially the air side 53 Mistake. The pipe elements 52-1 are designed, for example, as flat tubes.

The liquid refrigerant is passed through the pipe elements 52-1 the evaporation area 64a passed through, heat is transferred to the refrigerant and the refrigerant evaporates. For example, the air flows in a cross-countercurrent over the ribs 53 . After complete evaporation, the gaseous refrigerant is inside the second manifold 51a in the direction of flow 63 towards the outlet 55 directed.

Which are in the gas area 59a of the first manifold 50a between the first manifold 50a and the second manifold 51a extending pipe elements 52-2 form the inactive overflow area 65a for that in the device 57a for separating the gaseous refrigerant separated from the liquid refrigerant and have the evaporation area in comparison to the 64a forming pipe elements 52-1 no ribs on. Also the pipe elements 52-2 of the overflow area 65a can be designed as flat tubes, which are arranged adjacent to one another. The compact arrangement of the pipe elements 52-2 results in a very compact installation space for the heat exchanger 9a .

The gaseous refrigerant gets through the pipe elements 52-2 of the overflow area 65a passed through. No heat is transferred to the refrigerant. That through the overflow area 65a Gaseous refrigerant passed through is inside the second manifold 51a mixed with the gaseous refrigerant generated during evaporation and as a common mass flow of gaseous refrigerant in the direction of flow 56 through the outlet 55 from the heat exchanger 9a derived.

The mass flows of the gaseous and liquid refrigerant are consequently associated with the evaporation area 64a and the overflow area 65a through different, separately designed areas of the heat exchanger 9a directed. The areas have different dimensions, with the evaporation area 64a is dimensioned larger than the overflow area 65a .

According to a first alternative embodiment, the tubular elements 52-1 the evaporation area 64a and the pipe elements 52-2 of the overflow area 65a arranged in a common plane. In doing so, the air can hit the pipe elements 52-1 , 52-2 overflow in parallel.

According to an alternative embodiment, not shown, the tube elements of the evaporation area and the tube elements of the overflow area are each arranged in two planes aligned parallel to one another. Here, depending on the direction of flow, the air can flow one after the other over the heat transfer surface of the evaporation area and then over the heat transfer surface of the overflow area or vice versa.

In 4th is a device 9b for heat transfer, in particular a refrigerant-air heat exchanger, with an integrated device 57b for separating gaseous refrigerant from liquid refrigerant as well as an evaporation area 64b for liquid refrigerant and an overflow area 65b shown for gaseous refrigerant. The device 57b to separate the gaseous refrigerant from the liquid refrigerant is between a first manifold 50b and a second manifold 51b who have favourited manifolds 50b , 51b arranged connected to one another.

The first manifold 50b and the second manifold 51b are also about parallel to each other and to the device 57b and in the vertical direction y arranged, in particular rectilinear tubular elements 52-1 connected with each other. The internal volumes of the manifolds 50b , 51b are about the pipe elements 52-1 and the device 57b combined to form a common volume.

The refrigerant-air heat exchanger 9b has an inlet 54 and an outlet 55 for the refrigerant. The inlet 54 is on the device 57b designed to separate the gaseous refrigerant from the liquid refrigerant, while the second manifold 51b the outlet 55 having.

The two phases of the refrigerant are by means of the device 57b mechanically separated from each other. The mechanical separation is based in turn on the inertial force as the driving force, which requires a sufficiently large difference in density between the phases of the refrigerant. The mixture of gaseous and liquid refrigerant flows in particular in the horizontal direction x aligned flow direction 56 in the vertical direction y aligned device 57b to separate the gaseous refrigerant from the liquid refrigerant. Due to the abrupt changes in the flow velocity and the flow direction when it hits the wall of the device 57b Due to the different inertial forces of the liquid refrigerant and the gaseous refrigerant, with which the two phases follow the change of direction differently, the different phases of the refrigerant are separated from one another.

Due to the greater density, the liquid refrigerant flows in the, in particular, in the vertical direction y aligned flow direction 61 down into one in the device 57b formed fluid area 58b , while the gaseous refrigerant due to the lower density in the particular in the vertical direction y aligned flow direction 62 up in one also in the device 57b trained gas area 59b is directed.

The fluid area 58b is with the first manifold 50b connected while the gas area 59b with the second manifold 51b is hydraulically coupled.

The first manifold 50b and the first manifold 50b with the second manifold 51b connecting pipe elements 52-1 form the active evaporation area 64b the end. The tubular elements, for example, designed as flat tubes 52-1 are designed with ribs to enlarge the heat exchanger surface on the outside, i.e. especially on the air side 53 Mistake.

The liquid refrigerant is passed through the pipe elements 52-1 the evaporation area 64b passed through, heat is transferred to the refrigerant and the refrigerant evaporates. For example, the air flows in a cross-countercurrent over the ribs 53 . After complete evaporation, the gaseous refrigerant enters the second manifold 51b initiated.

The second manifold 51b forms the inactive overflow area 65b for that in the device 57b for separating the gaseous refrigerant separated from the liquid refrigerant. The gaseous refrigerant is in the direction of flow 63 through the second manifold 51b passed through and mixed with the gaseous refrigerant generated during evaporation and as a common mass flow in the direction of flow 56 through the outlet 55 from the heat exchanger 9b derived.

As only liquid refrigerant through the active evaporation area 64a , 64b flows through, the entire enthalpy of vaporization of the two-phase region of the refrigerant is available for heat absorption. The reduced one In combination with the increased enthalpy of evaporation, the refrigerant mass flow results in a significantly lower pressure loss on the refrigerant side within the active evaporation area 64a , 64b and thus leads to a significantly lower temperature spread of the refrigerant between the inlet 54 and the outlet 55 of the refrigerant compared to a refrigerant-air heat exchanger known from the prior art. This means that significantly more heat can be absorbed from the environment. The pressure loss on the refrigerant side can be further reduced by using refrigerant pipes specially designed for evaporation as pipe elements 52-1 be used.

Compared to the heat exchanger 9a the end 3 becomes at the heat exchanger 9b the end 4th a larger number of tubular elements with the same installation space 52-1 flows through parallel, which also have a shorter length. This can reduce the pressure loss on the refrigerant side of the heat exchanger 9b can be further reduced.

Within the inactive overflow area 65b the gaseous refrigerant flows through the second manifold 51b whose free flow cross-section is designed in such a way that only a slight pressure loss on the refrigerant side occurs in the gaseous refrigerant while it is flowing through.

The integrated device 57a , 57b for separating the gaseous refrigerant from the liquid refrigerant is designed and arranged in such a way that a mass flow of completely liquid refrigerant through the active evaporation area always occurs even with different fill levels of the liquid refrigerant 64a , 64b flows through. The level of the liquid refrigerant is set according to the pressure difference between the refrigerant at the inlet 54 and at the outlet 55 a.

List of reference symbols

1 ', 1' '

Air conditioning system

2 ', 2' '

Refrigerant circulation

3rd

compressor

4th

Heat exchanger, refrigerant-coolant heat exchanger

5

first expansion device

6th

Heat exchanger, first refrigerant-air heat exchanger

7th

internal heat exchanger

8th

second expansion device

9a, 9b

Device for heat transfer, heat exchanger, second refrigerant-air heat exchanger

10

Non-return element

11

Collector

12th

first flow path

13th

second flow path

14th

Branch point

15th

Mouth point

16

Valve, shut-off valve

17th

second flow path

18th

Branch point

19th

Mouth point

20th

third expansion organ

30th

Coolant circuit

31

Conveyor

32

first coolant-air heat exchanger, heating heat exchanger

33

Junction point, three-way valve

34

Mouth point

35

first flow path

36

second coolant-air heat exchanger

37

second flow path

40

Air conditioner

41

Direction of flow in the passenger compartment supply air

42

Plant module

43

Direction of air flow

50a, 50b

first manifold

51a, 51b

second manifold

52-1, 52-2

Tubular element

53

rib

54

Inlet refrigerant

55

Refrigerant outlet

56

Direction of flow refrigerant

57a, 57b

Device for separating gaseous refrigerant from liquid refrigerant

58a, 58b

Liquid area

59a, 59b

Gas range

60

Separator

61

Direction of flow refrigerant liquid

62

Direction of flow of gaseous refrigerant

63

Direction of flow of gaseous refrigerant

64a, 64b

Evaporation area, active area

65a, 65b

Overflow area for gaseous refrigerant, inactive area

x

horizontal direction

y

vertical direction

Claims (17)

Device (9a) for heat transfer for a refrigerant circuit (2 ', 2 ") of an air conditioning system (1', 1") of a motor vehicle, having an inlet (54) and an outlet (55) for the refrigerant, a first manifold (50a) and a second collecting pipe (51a) and pipe elements (52-1, 52-2) extending between the collecting pipes (50a, 51a) and arranged parallel to one another, wherein a device (57a) for separating gaseous refrigerant from liquid refrigerant in the device (9a) is designed to be integrated and the device (9a) has an evaporation area (64a) exclusively for the application of liquid refrigerant and an overflow area (65a) exclusively for the application of gaseous refrigerant, characterized in that the manifolds (50a) in the vertical direction ( y) arranged in an aligned manner and connected to one another via pipe elements (52-1, 52-2) arranged parallel to one another and in the horizontal direction (x) are, and that the device (57a) for separating the gaseous refrigerant from the liquid refrigerant is integrated within the first collecting pipe (50a), the device (57a) having a separating element (60) which is arranged in the vertical direction (y) and which an inner volume of the first collecting tube (50a) is divided into a liquid region (58a) and a gas region (59a). Device (9a) according to Claim 1 , characterized in that the inlet (54) is formed on the first manifold (50a). Device (9a) according to Claim 1 or 2 , characterized in that the pipe elements (52-1) connecting the liquid region (58a) of the first collecting pipe (50a) to the second collecting pipe (51a) with the evaporation region (64a) and the gas region (59a) of the first collecting pipe (50a) the pipe elements (52-2) connecting the second collecting pipe (51a) form the overflow area (65a). Air conditioning system (1 ', 1 ") of a motor vehicle with a coolant circuit (30) and a refrigerant circuit (2', 2"), having a device (9a) for heat transfer according to one of the Claims 1 until 3 . Air conditioning system (1 ', 1 ") of a motor vehicle with a coolant circuit (30) and a refrigerant circuit (2', 2"), comprising a device (9b) for heat transfer for the refrigerant circuit (2 ', 2 ") with a Inlet (54) and an outlet (55) for the refrigerant, a first manifold (50b) and a second manifold (51b) and pipe elements (52-1) extending between the manifolds (50b, 51b) and arranged parallel to one another, characterized in that a device (57b) for separating gaseous refrigerant from liquid refrigerant is integrated into the device (9b) and the device (9b) has an evaporation area (64b) exclusively for the application of liquid refrigerant and an overflow area (65b) exclusively for Has loading with gaseous refrigerant. Climate system (1 ', 1'') Claim 5 , characterized in that the collecting pipes (50b, 51b) of the device (9b) are arranged aligned in the horizontal direction (x) and are connected to one another via pipe elements (52-1) arranged parallel to one another and in the vertical direction (y). Climate system (1 ', 1'') Claim 6 , characterized in that the device (57b) for separating the gaseous refrigerant from the liquid refrigerant is arranged between the first manifold (50b) and the second manifold (51b) connecting the manifolds (50b, 51b) to one another. Climate system (1 ', 1'') Claim 7 , characterized in that the device (57b) for separating the gaseous refrigerant from the liquid refrigerant is arranged in the vertical direction (y) and parallel to the pipe elements (52-1). Climate system (1 ', 1'') Claim 7 or 8th , characterized in that the inlet (54) is formed on the device (57b) for separating the gaseous refrigerant from the liquid refrigerant. Air conditioning system (1 ', 1'') according to one of the Claims 7 until 9 , characterized in that the device (57b) for separating the gaseous refrigerant from the liquid refrigerant has a liquid area (58b) and a gas area (59b), the liquid area (58b) with the first collecting tube (50b) and the gas area (59b) are formed connected to the second manifold (51b). Air conditioning system (1 ', 1'') according to one of the Claims 6 until 10 , characterized in that the first manifold (50b) and the pipe elements (52-1) connecting the first manifold (50b) to the second manifold (51b) the evaporation area (64b) and the second manifold (51b) the overflow area (65b) form. Air conditioning system (1 ', 1'') according to one of the Claims 4 until 11 , characterized in that - the refrigerant circuit (2 ', 2'') has a compressor (3), a refrigerant-coolant heat exchanger (4) that can be operated as a condenser / gas cooler for heat transfer between the refrigerant and the coolant of the coolant circuit (30), has a first expansion element (5) and a first coolant-air heat exchanger (6) for conditioning the supply air for the passenger compartment, - the coolant circuit (30) has a conveying device (31), a first coolant-air heat exchanger (32) for heating the supply air for the passenger compartment, a second coolant-air heat exchanger (36) and the refrigerant-coolant heat exchanger (4), the device (9a, 9b) for heat transfer as a second coolant-air heat exchanger that can be operated exclusively as an evaporator (9a, 9b) and the refrigerant-air heat exchanger (9a, 9b) in the flow direction of the refrigerant is upstream of a second expansion element (8), w whether the second expansion element (8) and the second refrigerant-air heat exchanger (9a, 9b) are arranged within a first flow path (12). Climate system (1 ', 1 ") according to Claim 12 , characterized in that the second coolant-air heat exchanger (36) of the coolant circuit (30) and the second coolant-air heat exchanger (9a, 9b) of the refrigerant circuit (2 ', 2 ") within a system module (42) and in Direction of flow (43) of the air are arranged to be acted upon one after the other. Climate system (1 ', 1'') Claim 13 , characterized in that the system module (42) can be flown through with air discharged from the passenger compartment or with ambient air or with a mixture of air discharged from the passenger compartment and ambient air. Air conditioning system (1 ') according to one of the Claims 12 until 14th , characterized in that the first refrigerant-air heat exchanger (6) and the second refrigerant-air heat exchanger (9a, 9b) are arranged in series within the refrigerant circuit (2 ') so that there can be flow through one another. Air conditioning system (1 '') according to one of the Claims 12 until 14th , characterized in that the first refrigerant-air heat exchanger (6) and the second refrigerant-air heat exchanger (9a, 9b) are arranged within the refrigerant circuit (2 ″) so that they can flow through parallel to one another. Climate system (1 '') Claim 16 , characterized in that - the first flow path (12) with the second expansion element (8) and the second refrigerant-air heat exchanger (9a, 9b) is designed to extend from a branch point (18) to an opening point (19) and - The first expansion element (5), the first refrigerant-air heat exchanger (6) and a third expansion element (20) are formed within a second flow path (17), the third expansion element (20) being the refrigerant-air heat exchanger (6 ) is arranged downstream and the second flow path (17) is designed to extend from the branch point (18) to the opening point (19).

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