DE102011085810A1 - Plate evaporator for subcooling an air flow and intercooler - Google Patents

Abstract

The present invention relates to a plate evaporator (200) for subcooling an airflow (112) through a charge air cooler (100) of a vehicle. The plate evaporator (200) has a fluid-tight evaporator channel (202) for evaporating refrigerant. The evaporator channel is formed between a first plate (208) and a second plate (500). Furthermore, the plate evaporator (200) has at least one rib (602) for guiding the air flow (112) and for transferring heat from the air flow to at least the first plate (208). The at least one rib (602) is thermally conductively connected to the first plate (208) on a side of the first plate (208) opposite the evaporator channel (202). Furthermore, the plate evaporator (200) has a refrigerant inlet (204) to the evaporator channel (202), and a refrigerant outlet (206) from the evaporator channel (202) transversely to a main extension plane of the first plate (208) and / or the second plate (500) is aligned and disposed at a first end of the evaporator channel (202).

Description

The present invention relates to a plate evaporator for subcooling an air flow through a charge air cooler of a vehicle and to a charge air cooler for cooling an air flow.

To achieve short pipes in a vehicle from an exhaust gas turbocharger to an intake manifold, intercoolers are operated indirectly. In this case, cooling water flows through the engine as a heat transport medium through a compact heat exchanger in the charge air duct. Due to the compact dimensions of the indirect intercooler, the intercooler can be installed close to the engine. With cooling water, charge air temperatures in the range of the cooling water temperature can be achieved.

An "HVAC" evaporator, and specifically a flat tube evaporator, are less suitable for integration into an air intake region of an engine. For example, an air flow is performed in cross flow with 90 degrees offset to the refrigerant flow. In the indirect charge air cooler, air and coolant (water) flow in the same direction in countercurrent (180 °) or in direct current (0 °), whereby integration and adaptation is complex and voluminous, because the air flow is strongly deflected. A two-tank design is not preferred because the second tank needs space and is also sealed air side. A supernatant of the collector over the network complicates the integration with a side slot, at least in the two-tank version.

It is the object of the present invention to provide an improved charge air cooler for cooling an air flow and a plate evaporator for subcooling an air flow through a charge air cooler of a vehicle.

This object is achieved by a plate evaporator for subcooling an air flow through a charge air cooler of a vehicle and a charge air cooler for cooling an air flow according to the main claims.

A CAS evaporator (batch-air subcooling evaporator) can be based on a flat-tube evaporator. In this case, a CAS evaporator can be structurally designed so that the integration of the evaporator in the air intake of the engine with respect to the fluid flows and their connection points similar to the classic indirect intercooler (coolant-air). The current arrangement has proven itself and the installation spaces are available in this respect or generally reserved for intercooling.

Advantageously, a disk-type CAS evaporator can be easily integrated and sealed in a suction pipe or air intake duct. In particular, in a configuration as a "insertion solution", a simple installation and maintenance is possible. By means of the disc design, it is possible on the number of discs to realize a gradation of performance (kit), without the new flat-tube evaporator principle as new tools are needed, which would cause high costs. In another possible embodiment as a separate component with its own housing, the CAS evaporator can be easily implemented in a slab design. By z. As sheet metal parts are soldered, which surround the plates and provide an air-side adaptation.

An evaporator disc design can be performed with little material cost in a necessary stability for a bursting pressure level of an evaporator.

The present invention provides a plate evaporator for subcooling an airflow through a charge air cooler of a vehicle, the plate evaporator having the following features:
a fluid-tight evaporator channel for evaporating refrigerant, wherein the evaporator channel is formed between a first plate and a second plate;
at least one rib for guiding the air flow and for transmitting heat from the air flow to at least the first plate, wherein the at least one rib is thermally conductively connected to the first plate on a side of the first plate opposite to the evaporator channel;
a refrigerant inlet to the evaporator channel, which is aligned transversely to a main extension plane of the first plate and / or the second plate, and disposed at a first end of the evaporator channel; and
a refrigerant outlet from the evaporator channel, which is aligned transversely to the main extension plane of the first plate and / or the second plate, and disposed at a, opposite the first end, the second end of the evaporator channel.

The vehicle may be a motor vehicle having an internal combustion engine, for example a passenger car or a lorry. An intercooler may be understood to mean a heat transfer device which is designed to cool compressed, heated fresh air for the internal combustion engine prior to filling at least one combustion chamber of the internal combustion engine with the fresh air. The density of fresh air increases during cooling. This provides more oxygen for burning in the combustion chamber. For example, the fresh air can be compressed by means of an exhaust gas turbocharger or a compressor. The heat from the compressed fresh air can be absorbed by a refrigerant. Particularly advantageously, the heat can be absorbed during a phase change of the refrigerant. In a transition from a liquid phase to a gaseous phase, the refrigerant can absorb a lot of energy and thereby generate a particularly low temperature. As long as refrigerant is present in both phases, a temperature of the refrigerant is constant. A plate heat exchanger can be understood to mean a heat exchanger which has predominantly flat surfaces for the heat transfer between a medium to be cooled and a medium to be heated. Both media are separated by a plate. The media change. Channels for the media can be arranged between the plates. An evaporator channel may be a channel for the refrigerant. A rib, for example a corrugated fin, can form one or more channels for the medium to be cooled. The rib can increase the area for heat transfer. The medium to be cooled in the intercooler can be compressed, heated air. The rib can form air channels. The evaporator channel may have side walls, for example in the form of a punched contour of another plate. The evaporator channel may be formed by embossed structures of the plates. The rib and the plates can be soldered together. The plates may have openings for guiding the refrigerant. A breakthrough may be connected as a refrigerant feed with a refrigerant source, such as a reservoir or a pressure side of a refrigerant compressor. Between the refrigerant source and the refrigerant inlet, a throttle may be arranged. The throttle may be, for example, an expansion valve. Another breakthrough can be connected as a refrigerant outlet with a refrigerant sink, such as another reservoir or a suction side of a refrigerant compressor. The refrigerant inlet and the refrigerant outlet may be aligned perpendicular to the air flow in the air channels. For example, the refrigerant feed may be disposed in an upper one of the plates. For example, the refrigerant outlet may be arranged in a lower of the plates in order to be able to dissipate residues of liquid refrigerant with gravity assistance. A flow direction in the refrigerant inlet and / or the refrigerant outlet may be aligned transversely to the air channels in the air channels.

The at least one rib may be aligned transversely to a main extension direction of the evaporator channel. By means of a transverse rib, the air flow can be conducted in a cross-flow principle to a refrigerant flow. Due to the cross flow of the plate heat exchanger can be easily performed, since the refrigerant inlet and the refrigerant outlet does not hinder the air flow, since they are arranged laterally thereto.

The at least one rib may be aligned in the main direction of extension of the evaporator channel. By aligning airflow and refrigerant flow equally, the refrigerant may be heated above the vaporization temperature after evaporation to receive additional energy from the airflow. Thus, the plate heat exchanger can be operated in the DC principle or the countercurrent principle.

The evaporator channel can be folded at least once, so that a first sub-channel of the evaporator channel is arranged next to a second sub-channel of the evaporator channel. A convolution can be understood as a reversal of the direction of the coolant flow. The evaporator channel can change its direction by 180 degrees. The first sub-channel can run parallel to the second sub-channel. By folding the evaporator channel can be at least twice as long as a length of the plate heat exchanger. As a result, the refrigerant can have a longer residence time in the evaporator channel and absorb more energy.

The evaporator channel may have at the first end and / or at the second end a bend transverse to the main extension direction of the evaporator channel. The kink may be located at the first end or the second end. Likewise, depending on a kink can be arranged at the first and the second end. The kinks can be oriented in different directions. Preferably, the kink at the first end of the evaporator channel may be aligned in the same direction as the kink at the second end of the evaporator channel. A kink can be understood as a 90 degree bend. Due to the kink, the respective end can be moved to an edge region of the plate heat exchanger. Then, the refrigerant inlet and the refrigerant outlet may cause less flow resistance in the airflow.

The plate evaporator may have an inlet region at the first end of the evaporator channel and / or a drainage region at the second end of the evaporator channel, the inlet region and / or the drainage region projecting beyond a base body of the first plate and / or the second plate, the refrigerant inlet being in the inlet region and / or the refrigerant drain are arranged in the drain region. Under an inlet area and / or a drain area, an extension of the evaporator channel over the actual plate heat exchanger also be understood. As a result, the refrigerant inlet and the refrigerant outlet can be arranged outside the air flow. Through the inlet area and / or the outlet area, a flow cross-section of the air flow over the entire plate heat exchanger can remain constant.

Plate evaporator according to one of the preceding claims, with at least one further evaporator channel for evaporating refrigerant, with a further coolant inlet and a further coolant outlet, wherein the further evaporator channel is disposed on a side of the at least one rib opposite the evaporator channel, and the further evaporator channel congruent to the Evaporator channel is aligned. The evaporator channels can be stacked on top of each other. By stacking, different sizes of plate heat exchangers can be produced on a fixed footprint without the need for different parts. Multiple evaporator channels can be connected to a plate heat exchanger stack. The evaporator channels may each be connected by means of one or more ribs in order to obtain space between the evaporator channels for the air flow.

The refrigerant outlet from the evaporator channel can open into the further refrigerant inlet of the further evaporator channel. From the refrigerant outlet can flow unevaporated, liquid refrigerant from one evaporator channel in the refrigerant inlet of the other evaporator channel. This allows the refrigerant to evaporate completely, thus absorbing the maximum possible amount of energy.

The plate evaporator may have an internal injection pipe, which is designed to supply liquid refrigerant to at least one further evaporator channel. An injection pipe can be an additional feed for refrigerants. Thus, additional refrigerant can be introduced into the further evaporator channel in order to obtain a high cooling capacity in the further evaporator channel. The injection tube may, for example, lead directly from the first end of the evaporator channel to the beginning of the further evaporator channel in order to withdraw liquid refrigerant from the first evaporator channel. The injection tube can also come directly from the throttle. The injection pipe may be arranged coaxially with the refrigerant inlet or the refrigerant outlet. Likewise, the injection pipe can be guided by their own breakthroughs in the plates of the plate heat exchanger.

The present invention further provides a charge air cooler for cooling an air flow, comprising:
a housing having an air inlet and an air outlet, and at least one opening for inserting a heat exchanger; and
a plate evaporator according to the approach presented here, which is inserted as a heat exchanger in the opening of the housing, wherein the refrigerant inlet and the refrigerant outlet are arranged outside the housing.

Under an air inlet, an air intake can be understood. The air inlet can be connected to a turbocharger, for example. An air outlet can be an air outlet. The air outlet can be connected to a suction side of an engine. The opening may have receiving means for the heat exchanger, such as guide rails or holding elements. Further, the opening may include a seal to seal on the heat exchanger. The plate evaporator can be arranged in the opening so that the air flow can flow through the air channels. The connections for the refrigerant may protrude out of the housing, in particular on one side, in order to allow a simplified production. As a result, the plate heat exchanger can be prefabricated to a high degree and quickly integrated into the intercooler. The intercooler may further have openings into which further heat exchangers can be inserted in order, for example, to pre-cool the air flow in front of the plate evaporator with cooling water in order to reduce the energy expenditure during cooling.

Advantageous embodiments of the present invention will be explained below with reference to the accompanying drawings. Show it:

1 a representation of an embodiment of a charge air cooler;

2 a representation of a plate evaporator with countercurrent principle according to an embodiment of the present invention;

3 a representation of a plate evaporator according to an embodiment of the present invention with two connection areas;

4 a representation of a plate evaporator according to an embodiment of the present invention with countercurrent principle;

5 a representation of a plate evaporator according to an embodiment of the present invention with connection areas on one side;

6 a section through the plate evaporator according to an embodiment of the present invention from 5 ;

7 a representation of a plate evaporator according to an embodiment of the present invention with a cross-flow principle and a convolution; and

8th a representation of a plate evaporator according to an embodiment of the present invention with a cross-flow principle and three convolutions.

In the following description of the preferred embodiments of the present invention, the same or similar reference numerals are used for the elements shown in the various drawings and similar, and a repeated description of these elements will be omitted.

1 shows a representation of a charge air cooler 100 for cooling compressed and heated fresh air for an internal combustion engine. The intercooler has an air inlet 102 , a diffuser 104 , a fluid-cooled heat exchanger 106 , a nozzle 108 as well as an air outlet 110 on. Hot charge air 112 flows through the air inlet 102 at high speed in the intercooler 100 , In the diffuser 104 a flow cross-section increases steadily, which increases the speed of the charge air 112 reduced. The charge air flows with the low speed 112 through the heat exchanger 106 , The heat exchanger 106 is an indirect heat exchanger that uses an intermediate medium with high heat transfer capacity to heat the charge air 112 evacuate. The heat exchanger shown here 106 has external collectors to guide the intermediate medium. The heat exchanger 106 is used in cross-flow operation. The heat exchanger 106 is slanted in the intercooler 100 built to a larger cross-sectional area for cooling the charge air 112 to have available. In the heat exchanger 106 increases the density of the charge air 112 at. After the heat exchanger 106 is the charge air in the nozzle 108 accelerated again. In the nozzle 108 The flow cross-section narrows again to the air outlet 110 , The diffuser 104 is less steep than the nozzle 108 to avoid turbulence of the charge air 112 to cause. Through the air outlet 110 leaves the cooled charge air 112 the charge air cooler again high speed and flows into the intake of the engine.

The 2 to 8th show various structural embodiments and heat transfer technologies for a charge-air subcooling subcooling evaporator that can be integrated into an air intake area of an engine.

The 2 to 6 show a flow guide in which the air flows in counter or DC flow to the refrigerant channel (disc channel). This corresponds to a 180 degree or 0 degree arrangement. A rib for guiding the air is rotated 90 degrees compared to the classic disc evaporator. In the classic disc evaporator, the air flows 90 degrees offset to the refrigerant in the cross flow. For a counter or DC flow, the collector would get in the way of the classic disc evaporator and the rib would have to be turned.

2 shows a plate evaporator 200 according to an embodiment of the present invention. The plate evaporator 200 for subcooling an airflow 112 through a charge air cooler of a vehicle is designed as a countercurrent heat exchanger. The plate evaporator 200 has an evaporator channel 202 , at least one rib, a refrigerant feed 204 as well as a refrigerant drain 206 on. The rib is through a first plate 208 obscured, which is a wall of the evaporator channel 202 forms. The evaporator channel 202 is shown for illustrative purposes without covering second plate. in ready state is the evaporator channel 202 fluid tight between the first plate 208 and the second plate and provides a space for evaporating refrigerant. The at least one rib is adapted to the air flow 112 through the plate evaporator 200 to guide and additional area for heat transfer from the airflow 112 on at least the first record 208 to provide. The at least one rib is on one of the evaporator channel 202 opposite side of the first plate 208 with the first plate 208 thermally conductive connected. The refrigerant feed 204 is with the evaporator channel 202 connected and transversely to a main extension plane of the first plate 208 and / or the second plate aligned. The refrigerant feed 204 is at a first end of the evaporator channel 202 arranged. The refrigerant drain 206 is also with the evaporator channel 202 connected and transverse to the main extension plane of the first plate 208 and / or the second plate aligned. The refrigerant drain 206 is at one, the first end of the evaporator channel 202 opposite, second end of the evaporator channel 202 arranged. Through the refrigerant feed 204 becomes liquid refrigerant in the evaporator channel 202 initiated. In the evaporator channel 202 There is a low pressure. The pressure is set so that the refrigerant starts to boil at a predetermined temperature. Because at least the first plate 208 from the airflow 112 thermal energy is supplied, the refrigerant thereon is on his Boiling heated and begins to evaporate. The refrigerant takes the thermal energy from the first plate 208 on. Because there continues to be refrigerant in the evaporator channel 202 is introduced, forms the refrigerant in the evaporator channel 202 a refrigerant flow 210 out. The refrigerant flow 210 flows to the refrigerant outlet 206 where the refrigerant is discharged. As long as liquid refrigerant is present, the boiling temperature is not exceeded. When all the refrigerant has evaporated, the temperature in the evaporator channel 202 be increased by the air flow above the boiling temperature. The refrigerant is overheated. Due to the refrigerant flow 210 Overheating can only be close to the refrigerant drain 206 occur. The refrigerant flow 210 is opposite to the airflow 112 aligned, therefore, the plate evaporator shown here 200 a countercurrent heat exchanger. In a cross-flow heat exchanger design, the plate evaporator in a charge air cooler could be as in 1 be used.

In other words shows 2 a "pure counterflow arrangement", in which the refrigerant is guided in a flow path against the air flow. Here are also several flow blocks on top of each other conceivable (counter, equal, counter -...). The collectors 204 . 206 are in this embodiment symmetrically centered to the evaporator channel 202 arranged and are bilaterally flowed around by the air, which has the additional advantage that these areas are used with and the overheating zone proportionate in the collector 206 takes place. In general, in the single flow, the overheating zone is evenly distributed over all the disks and the air is further cooled in the subsequent long flow path. However, the single flow requires the smallest possible number of slices with long, rather narrow slices in order to ensure the refrigerant distribution in two phases at the entrance can.

3 shows a plate evaporator 200 according to an embodiment of the present invention. Shown is a disc with collection areas arranged on both sides. The general structure corresponds to the plate evaporator, as in 2 is shown. In contrast to the embodiment of 2 is the evaporator channel 202 once folded in the middle. As a result, between the first plate 208 and the second plate, which is not shown again, two adjacent sections of the evaporator channel 202 arranged. The refrigerant flow 210 is deflected by the fold by 180 degrees. In addition, the evaporator channel 202 90 degrees at the first end and at the second end. The kinks are oppositely oriented. The kink in the evaporator channel 202 at the first end allows an arrangement of the refrigerant inlet 204 in an inlet area, the side over the first plate 208 and the second plate survives. The kink at the second end allows an arrangement of the refrigerant outlet 206 in a drain region, opposite to the inlet region from the first plate 208 and the second plate protrudes. Due to the protruding inlet and outlet areas, an air duct between the plates is unobstructed. The plate evaporator 200 has several levels one above the other. Between the planes, the ribs for guiding the air flow are arranged. In each case adjacent evaporator channels 202 is the refrigerant flow 210 each oriented in opposite directions. That is, the refrigerant drain 206 bridged the underlying rib area and opens as a refrigerant inlet into the underlying next evaporator channel.

4 shows a plate evaporator 200 according to an embodiment of the present invention. The plate evaporator 200 corresponds to the plate evaporator 3 , In contrast to 3 points The plate evaporator 200 only one side inlet area (collector) and one in the air flow 112 located collector 206 on. The in the air stream 112 lying refrigerant outlet 206 leads in particular in a multi-block interconnection, the refrigerant to the next block on. The refrigerant feed 204 is arranged in the inlet area. And stands over the first record 208 and the second plate over. The evaporator channel has in contrast to 3 just a kink.

5 shows a view of a plate evaporator 200 according to an embodiment of the present invention. The plate evaporator 200 corresponds essentially to the plate evaporators from the 2 . 3 and 4 , In contrast to 3 has the plate evaporator 200 the inlet area and the drainage area on the same side. The plate evaporator 200 is shown closed. The second plate 500 forms an upper end of the plate evaporator 200 and covers the evaporator channel, the first plate and the refrigerant flow in the evaporator channel. Shown is the refrigerant feed 204 with a coaxial injection tube 502 which supplies deeper evaporator channels with liquid refrigerant directly from a refrigerant source. The refrigerant flow 210 is added to the refrigerant feed 204 divided. One part flows into the uppermost evaporator channel to cover part of the airflow 112 to cool. Another part flows through the injection pipe 502 in underlying evaporator channels to other parts of the air flow 112 to cool. Through a bottom refrigerant drain 206 leaves the refrigerant flow 210 at least partially evaporates the plate evaporator 200 again. This embodiment may, like a classic disc evaporator, also be embodied in a plurality of flow blocks. However, the two pipe connections are then arranged opposite each other or it is additionally an internal injection pipe 502 in the collector.

6 shows one of the evaporator channels 202 of the plate evaporator 5 according to an embodiment of the present invention. The evaporator channel 202 is like in the 2 . 3 and 4 without the second plate shown to the coolant flow 210 to be able to represent. The evaporator channel is through raised sealing surfaces 600 between the first plate 208 and the second plate formed. The evaporator channel 202 points as in 5 an L-shape, wherein both legs of the L in each case in two directions from the refrigerant flow 210 be flowed through. Thus, the evaporator channel 202 starting from the refrigerant feed 204 in one of the plate evaporator 200 is arranged above the inlet area, a first kink. At the end of the plate 208 the evaporator channel is folded and runs parallel back to a second kink and to the refrigerant outlet, which is arranged in the laterally upstream outlet region. Below the first plate 208 are ribs 602 indicated the airflow 112 conduct and deprive him of heat when the plate evaporator 200 is in operation. Both collectors with pipe connections 204 . 206 are in the 90 degree angle to the actual heat exchanger block 200 arranged laterally, preferably on the same side. The flow 210 Thus, initially undergoes a 90 degree deflection, halfway on a 180 degree turn and the exit again a 90 degree deflection. Will the CAS evaporator 200 (Charge Air Subcooler) operated with a TXV (Thermal Expansion Valve), this flow guidance may be advantageous if the majority of the superheat zone in the 90 degree outlet flow upstream of the inlet path of the air is arranged. As a result, the higher air temperature after the overheating zone in the following flow area can compensate again. The refrigerant connections 204 . 206 or collectors are arranged on one side (single-tank) and are preferably led out of the air flow area.

7 shows a plate evaporator 200 according to an embodiment of the present invention. The classic flow through the disc evaporator 200 in the cross flow is also possible, but this requires relatively "deep" slices (deep in the air flow direction), as in 7 and 8th is shown. One advantage of this circuit, especially with more than two flow paths, is that the overheating zone in the last refrigerant block on the air side is very well compensated by the long further flow path in countercurrent.

Also in 7 are an inlet area with a refrigerant inlet 204 , which is aligned perpendicular to the plates and a drain area with a refrigerant outlet 206 which is also aligned perpendicular to the plates laterally led out of the plate evaporator. The evaporator channel 202 has a fold, so that the coolant flow 210 flows back and forth side by side. The airflow 112 is transverse to the coolant flow 210 aligned. The airflow 112 gets from ribs 602 between the evaporator channels 202 passed through to be cooled.

8th shows how 7 a plate evaporator 200 in the cross-flow according to an embodiment of the present invention. In contrast to 7 has the evaporator channel 202 three consecutive folds. By the convolutions is a length of the evaporator channel 202 effectively doubled.

In addition to all embodiments, the air flow 112 be guided by an inlet and an outlet frame and by side walls to the heat exchanger network. These components may optionally be soldered directly from aluminum and preferably made of plastic. All approaches have in common that the discs are designed significantly deeper than in today's (and earlier) disc evaporators usual. The countercurrent arrangement is very advantageous over previously known designs in the automotive application.

The described embodiments are chosen only by way of example and can be combined with each other.

LIST OF REFERENCE NUMBERS

100

Intercooler

102

air intake

104

diffuser

106

Heat exchanger

108

jet

110

air outlet

112

airflow

200

plate evaporator

202

evaporator channel

204

Refrigerant inlet

206

Refrigerant flow

208

first plate

210

Refrigerant flow

500

second plate

502

internal injection pipe

600

sealing surfaces

602

Rib (s)

Claims (10)

Plate evaporator ( 200 ) for subcooling an air stream ( 112 ) by an intercooler ( 100 ) of a vehicle, the plate evaporator ( 200 ) has the following features: a fluid-tight evaporator channel ( 202 ) for evaporating refrigerant, wherein the evaporator channel between a first plate ( 208 ) and a second plate ( 500 ) is trained; at least one rib ( 602 ) for guiding the air flow ( 112 ) and for heat transfer from the air stream to at least the first plate ( 208 ), wherein the at least one rib ( 602 ) on an evaporator channel ( 202 ) opposite side of the first plate ( 208 ) with the first plate ( 208 ) is thermally conductively connected; a refrigerant feed ( 204 ) to the evaporator channel ( 202 ) transverse to a main plane of extension of the first plate ( 208 ) and / or the second plate ( 500 ) and at a first end of the evaporator channel ( 202 ) is arranged; and a refrigerant drain ( 206 ) from the evaporator channel ( 202 ) transverse to the main plane of extension of the first plate ( 208 ) and / or the second plate ( 500 ), and at a, opposite the first end, the second end of the evaporator channel ( 202 ) is arranged. Plate evaporator ( 200 ) according to claim 1, wherein the at least one rib ( 602 ) transversely to a main direction of extension of the evaporator channel ( 202 ) is aligned. Plate evaporator ( 200 ) according to claim 1, wherein the at least one rib ( 602 ) in the main direction of extension of the evaporator channel ( 202 ) is aligned. Plate evaporator ( 200 ) according to one of the preceding claims, wherein the evaporator channel ( 202 ) is folded at least once, so that a first sub-channel of the evaporator channel ( 202 ) next to a second sub-channel of the evaporator channel ( 202 ) is arranged. Plate evaporator ( 200 ) according to one of the preceding claims, wherein the evaporator channel ( 202 ) at the first end and / or at the second end a bend transverse to the main direction of extension of the evaporator channel ( 202 ) having. Plate evaporator ( 202 ) according to one of the preceding claims, with an inlet region at the first end of the evaporator channel ( 202 ) and / or a drain region at the second end of the evaporator channel ( 202 ), wherein the inlet region and / or the drainage region via a main body of the first plate ( 208 ) and / or the second plate ( 500 ), whereby the refrigerant feed ( 204 ) in the inlet area and / or the refrigerant outlet ( 206 ) are arranged in the drainage area. Plate evaporator ( 200 ) according to one of the preceding claims, with at least one further evaporator channel ( 202 ) for vaporizing refrigerant, with a further coolant inlet ( 204 ) and another coolant outlet ( 206 ), wherein the further evaporator channel ( 202 ) on an evaporator channel ( 202 ) opposite side of the at least one rib ( 602 ), and the further evaporator channel ( 202 ) congruent with the evaporator channel ( 202 ) is aligned. Plate evaporator ( 202 ) according to claim 7, wherein the refrigerant effluent ( 206 ) from the evaporator channel ( 202 ) into the further refrigerant feed ( 204 ) of the further evaporator channel ( 202 ) opens. Plate evaporator ( 200 ) according to one of claims 7 to 8, with an internal injection pipe ( 502 ) which is designed, at least in the one further evaporator channel ( 202 ) liquid refrigerant to supply. Intercooler ( 100 ) for cooling an air stream ( 112 ), comprising: a housing having an air inlet ( 102 ) and an air outlet ( 110 ), and at least one opening for inserting a heat exchanger ( 106 ); and a plate evaporator ( 200 ) according to one of claims 1 to 9, as a heat exchanger ( 106 ) is inserted into the opening of the housing, wherein the refrigerant feed ( 204 ) and the refrigerant outlet ( 206 ) are arranged outside the housing.

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