EP1926619A1

EP1926619A1 - Stationary automotive air-conditioning system and method

Info

Publication number: EP1926619A1
Application number: EP06805647A
Authority: EP
Inventors: Ralf Manski; Bernd Schäfer
Original assignee: Behr GmbH and Co KG
Current assignee: Mahle Behr GmbH and Co KG
Priority date: 2005-09-12
Filing date: 2006-09-01
Publication date: 2008-06-04
Also published as: WO2007031204A1; DE102006041286A1

Abstract

The invention relates to a system for providing the stationary air-conditioning of a motor vehicle, especially of a utility vehicle. Said system comprises a refrigeration cycle (2) in which at least one compressor (3) and at least one heat-exchanger (1) are arranged and in which a refrigerant flows, and a secondary refrigeration cycle (11) in which at least one pump (12) at least one heat exchanger (1) and at least one cold accumulator (13) are arranged and in which a secondary refrigerant flows, the heat exchanger (1) of the refrigeration cycle (2) and the heat exchanger (1) of the secondary refrigeration cycle (11) being configured as an integrated heat exchanger (1). The invention also relates to a method for operating said system.

Description

SYSTEM AND METHOD FOR THE LIFE-LIMITATION OF A VEHICLE

The invention relates to a system for auxiliary air conditioning of a motor vehicle, in particular a commercial vehicle, with cold storage according to the preamble of claim 1, and a method for operating such a system.

From DE 102 56 665 A1 a system for heating and cooling an interior of a vehicle is known, with a first air conditioning unit, which is intended to heat or cool a front portion of the interior, and a second air conditioner, which is provided for this purpose to heat or cool a rear portion of the interior, wherein the first air conditioner, a first connectable to a refrigerant circuit evaporator and the second air conditioner is associated with a second connectable to the refrigerant circuit evaporator. In this case, the second evaporator is arranged in a latent storage in order to charge it with cold. Further, in the second air conditioner, a first heat exchanger is arranged, which is designed to be discharged via a heat or refrigerant circuit from the latent memory cooling to cool the rear region of the Interior to transfer an air stream. For example, in commercial vehicles, the system allows the sleeper to cool both while driving and while stationary. Such a system still leaves something to be desired.

Based on this prior art, it is an object of the invention to provide an improved system. This object is achieved by a system having the features of claim 1. Advantageous embodiments are the subject of the dependent claims.

According to the invention, a system for stationary air conditioning of a motor vehicle, in particular a commercial vehicle, with a refrigerant circuit, in which at least one compressor and at least one heat exchanger are arranged and in which a refrigerant flows, as well as a refrigerant carrier circuit is provided, in which at least one Pump, at least one heat exchanger and at least one cold storage are arranged and in which a refrigerant medium flows, wherein the heat exchanger of the refrigerant circuit and the heat exchanger of the refrigerant circuit integrated are formed as a heat exchanger. In this case, the heat exchanger is preferably provided for cooling the sleeping cabin, ie the rear area. The integrated design reduces the overall space for the air conditioning of the rear area. Furthermore, simplifies the circuit of the system for stationary air conditioning. The heat exchanger, which serves as an evaporator in normal operation, may be connected in parallel or in series with a second evaporator, in particular the evaporator of the front region. In this case, an expansion element is preferably provided before each evaporator, but in particular before the first evaporator after the condenser. In the case of a series connection, the expansion element between the two evaporators can be omitted. The heat exchanger used in the inventive system for stationary air conditioning is preferably a heat exchanger having a plurality of juxtaposed, the refrigerant leading tubes and at least one brine area in which the refrigerant medium is provided, wherein at least one heat transfer area forming element, which is part of the brine area is, on a pipe carrying the refrigerant rests on at least two sides, but in particular surrounds the refrigerant pipe leading on at least three sides, at least in partial areas. In this case, the tube carrying the refrigerant can also be arranged completely within the element forming a heat transfer region. The arrangement of at least a portion of the refrigerant pipe leading in a heat transfer region forming element results in a very good heat transfer. The heat exchanger may in this case also be designed in several parts, it also being possible for control elements, for example an expansion valve, to be arranged between the individual regions of the heat exchanger through which the refrigerant flows and / or optionally also the regions through which the refrigerant flows. The element forming a heat transfer region can also have a region, for example a connection region or one or more connecting webs, in which no coolant medium is located, and which is arranged between two or more regions carrying the coolant medium. The region may preferably lie flat on the pipe carrying the refrigerant, in particular of its narrow end face, but it may also be arranged at least partially spaced from the pipe carrying the refrigerant.

In the case of an arrangement of the pipe carrying the refrigerant in the element forming a heat transfer region, it may be inserted into the element which leads to the coolant medium and forms a heat transfer region, or it may be formed directly therein, the coolant carrier Preferably, the medium surrounds the refrigerant from all sides, wherein in particular a tube-in-tube arrangement is provided.

Likewise, the element forming a heat transfer region can be formed by a tube with a U-shaped cross section, in particular with a plurality of chambers, which can also be subdivided into channels (for example multi-chambered tubes). In this case, the inner dimensions of the element forming a heat transfer region preferably correspond to the outer dimensions of the pipe carrying the refrigerant in the corresponding region, so that the tubes lie flat against one another. Also, a one-piece design, for example. Formed by a corresponding extruded tube with at least two channels is possible.

The pipe carrying the refrigerant and the refrigerant carrying pipe is preferably formed as a double-walled flat tube in the case of an arrangement completely within the heat transfer region forming member, wherein the refrigerant is in the central region and the refrigerant medium in the outer region. According to a further preferred embodiment, the double-walled flat tube webs, which connect the outer with the inner flat tube. The fact that the brine area has direct air contact, results in a very good dynamics in the heat transfer, so that, if necessary, the cooling capacity is available quickly.

The pipe carrying the refrigerant medium need not completely surround the pipe carrying the refrigerant. In this case, preferably exactly three sides of the pipe carrying the refrigerant are surrounded by the pipe carrying the refrigerant medium. The tube carrying the coolant medium may in this case be formed with a U-shaped cross-section and the tube carrying the refrigerant, which is preferably a flat tube, partially, ie over a part of its circumference, surrounded, wherein zugt the largest part of the refrigerant pipe leading inside the refrigerant carrying pipe is arranged.

The pipe carrying the refrigerant or the channels of the pipe carrying the refrigerant preferably end in a collector. In this case, both a separately formed heat exchanger can be arranged with a brine area in addition to a conventional heat exchanger, whereby two expansion elements can be provided as well as the brine area be integrated directly into the heat exchanger.

The tubes or channels leading to the coolant medium preferably end in a coolant medium collecting container formed separately from the collector.

Flat tube rows of the evaporator and the elements forming a heat transfer area are preferably aligned with one another, so that the air flow resistance is as low as possible. However, the rows of flat tubes may also be staggered, or the elements forming a heat transfer region with the tubes carrying the refrigerant therein may be twisted relative to the other flat tubes of the evaporator. A mehrflutige embodiment of the tubes in which the heat transfer region forming elements are integrated, i. several rows with the refrigerant medium pipes leading, is also possible, as their deflections in width and / or depth.

The coolant region is preferably made of aluminum, in particular internally and / or externally coated aluminum (aluminum being understood as meaning an aluminum alloy), optionally also copper, a copper-zinc alloy, synthetic resin or plastic. An aluminum container has the advantage that it can be easily soldered to the other parts of the evaporator. This is preferably a extruded flat tube having a plurality of channels, wherein a part of the channels containing the refrigerant and the other part of the channels containing the refrigerant. However, the configuration can also be multi-part.

In the storage medium provided in the cold storage, which is cooled by the refrigerant and, if necessary, the cold is returned to the refrigerant, it is preferably a PCM material (phase change material), the preferred congruent melting media, in particular decanol, tetra- , Penta- or hexadecane, LiCIO ₃ 3H ₂ O, aqueous salt solutions or organic hydrates, or is formed therefrom. Nucleating agents which accelerate crystal formation can also be provided in the storage medium. The phase transition temperature of the storage medium is preferably in a range of -5 ° C to 30 ^c C, preferably from 1 ⁰ C to 20 ⁰ C, in particular from 2 ° C to 15 ° C, particularly preferably from 4 ⁰ C to 12 ⁰ C, or from -5 ⁰ C to 5 ⁰ C. Inside the cold storage deposits, such as ribbed plates, preferably made of aluminum, but other metals or plastics are suitable, or other turbulence inserts, such as nonwovens or knits, for example. Plastic or metal, or Foams, for example. Metal foams or plastic foams, be provided. The inserts serve to improve the heat transport and to increase the internal surface to accelerate the crystallization of the latent medium. As a particularly favorable storage medium and water can be provided.

The heat exchanger preferably has the following dimensions (with regard to the dimensions, reference is made to FIGS. 9, 10 and 14):

The total depth B of the heat exchanger is preferably 10 to 90 mm, in particular 30 to 80 mm or 10 to 40, particularly preferably 60 +/- 10 mm or 20 +/- 10 mm. The width B2 of the flat tubes of the first flat tube row is preferably approximately the sum of the widths B3 and B4 of the flat tubes of the second flat tube row and thus preferably a maximum of 0.5 × total depth B of the heat exchanger. However, according to an alternative embodiment in which as many identical components as possible are used, the width B2 can also be equal to the width B3, so that the same flat tubes can be used for the first flat tube row and the thicker portion of the second flat tube row.

The thickness b2 of the flat tubes of the first flat tube row is preferably 1.2 to 3.5 mm, in particular 2.0 +/- 0.5 mm.

The thickness b3 of the flat tubes of the second row of flat tubes preferably corresponds to the thickness b2 of the flat tubes of the first row of flat tubes, that is to say preferably 1.2 to 3.5 mm, in particular 2.0 ± 0.5 mm.

The width B4 of the thinner flat tubes of the second flat tube row or of the thinner area thereof preferably corresponds to the width B3 of the thinner flat tubes of the second flat tube row or to the width of the thicker region of the second flat tube row.

The thickness b4 of the thinner flat tubes of the second flat tube row and of the thinner region of the second flat tube row is preferably smaller than the thickness b3 of the thicker flat tubes of the second flat tube row or of the thicker region of the second flat tube row. It is preferably 0.8 to 2.5 mm, in particular 1, 2 to 2.0 mm.

The width B6 of the elements forming a heat transfer region is preferably from 5 to 40 mm, with particular preference being given to the latter

Width B4 is equivalent, so that the thinner flat tubes of the second flat tube row or the thinner area of the same as far as possible inside the U-shaped heat transfer area forming elements can be added, resulting in a large heat transfer surface, which results in a fast loading and also, if necessary, a good heat absorption.

The thickness b6 of the elements forming a heat transfer region preferably corresponds to the thickness b3, but may also be larger, so that the elements forming a heat transfer region and the thinner flat tubes of the second flat tube row or their thinner region are traversed by a sufficient amount of refrigerant medium and refrigerant. The dimensions are preferably 2.5 to 8.0 mm, in particular 3.5 to 7.0 mm.

The distance h2 of the flat tubes of the first row of flat tubes is preferably 4 to 12 mm, in particular 8 +/- 2 mm.

The distance h6 of the elements forming a heat transfer region is preferably 3 to 8 mm, particularly preferably 4 to 7 mm.

The transverse dimension q of the heat exchanger is preferably 5 to 15 mm, in particular 10 +/- 3 mm.

The height H1 of the refrigerant medium collecting container is preferably 3 to 25 mm, in particular 3 to 15 mm, but is preferably as small as possible in order to save installation space and to keep the cross-section through which air can flow as large as possible.

The heat exchanger, which is arranged in a system according to the invention for stationary air conditioning, preferably both refrigerant and refrigerant medium is flowed through in the loading operation, but the Fan is switched off so that it is not traversed by air. In a further variant, replacement or additionally a flap can be provided which can block or open the airway. In the evaporator operation, the heat exchanger preferably flows through both air and refrigerant, and during operation of the auxiliary air conditioning, the heat exchanger preferably flows through both air and the refrigerant medium.

The invention will be explained in more detail below with reference to two exemplary embodiments of systems according to the invention and two exemplary embodiments of heat exchangers with variants used in these systems, with particular reference to the drawing. Show it:

1 is a schematic view of a system for stationary air conditioning according to the first embodiment,

FIG. 2 is a schematic view of a stationary air conditioning system according to the second embodiment; FIG.

3 is a perspective view of an exploded heat exchanger with collector and expansion valve according to the first embodiment of a heat exchanger, as it can be used in a system according to the invention,

4 is a detail view of the upper, right portion of FIG. 3,

5 is a detail view of the lower, right portion of FIG. 3,

6 shows the heat exchanger of FIG. 3 in a perspective view, FIG. 7 is a plan view of a first variant of the first embodiment in exploded view to illustrate the assembly,

8 a section corresponding to FIG. 7 in the region of the flat tubes, FIG.

9 is a section of Fig. 8,

10 shows the detail view of FIG. 9 in the assembled state, FIG.

11 is an exploded view of the heat exchanger of Fig. 7 to illustrate the further assembly,

12 is a longitudinal section through a heat exchanger according to the first embodiment,

13 is a detail view of the left upper portion of FIG. 12 in a non-sectional view,

14 is a detail view of the right upper portion of FIG. 12;

15 is a detail view of a section across the heat exchanger according to the first embodiment,

16 is a side view of the heat exchanger according to the first embodiment of a heat exchanger, 17 is a detailed perspective view of a heat exchanger according to a second variant of the first embodiment of a heat exchanger without upper header,

18 is a perspective view of the heat exchanger according to the second variant of the first embodiment without upper and lower collecting tank showing the flow of the refrigerant through the heat exchanger,

19 is a perspective view of the heat exchanger according to the second embodiment,

FIG. 20 shows a section across the heat exchanger of FIG. 19, FIG.

21 is a detail view of the lower portion of FIG. 20;

22 is a section along line XXII-XXII of Fig. 20,

FIG. 23 shows a section in the longitudinal direction of the heat exchanger of FIG.

17 in the upper area,

24 shows a section through a heat exchanger according to a fifth variant of the first embodiment,

25 is a section through a heat exchanger according to a sixth variant of the first embodiment,

26 shows a section through a heat exchanger according to a seventh variant of the first exemplary embodiment, 27 shows a section through a heat exchanger according to an eighth variant of the first embodiment,

28 is a longitudinal section through a heat exchanger according to a third embodiment,

Fig. 29 is a detail view of a section across the heat exchanger according to the third embodiment and

30 is a perspective view of a heat exchanger according to the third embodiment,

A system for auxiliary air conditioning, in particular for a commercial vehicle with a sleeping compartment to be cooled if necessary by means of a heat exchanger 1, according to the first embodiment is shown in Fig. 1. The system comprises a refrigerant circuit 2, shown in dotted lines in Fig. 1, with a front branch 2 'and a rear branch 2 ", in the common part of the circuit 2 a compressor 3 and a condenser 4 are arranged. before the circuit 2 branches.

In the front branch 2 ', a first expansion element 5 and a first, conventional evaporator 6 is arranged, which is part of a front air conditioner 7. Downstream of the evaporator 6 may optionally be provided a further expansion element 8, hereinafter referred to as downstream expansion element 8, as shown in Fig. 1, before the front branch 2 'is merged again with the rear branch 2 "and then to the compressor 3. This further, downstream expansion element 8 serves to increase the pressure in the area of the evaporator 6, as a result of which the temperature of the refrigerant is correspondingly increased and thereby icing of the evaporator 6 can be safely avoided. tion, the downstream expansion element 8 may also be omitted.

A second expansion element 9 and said heat exchanger 1 are arranged in the rear branch 2 "The heat exchanger 1, like a conventional heat exchanger (cf., for example, DE 102 56 665 A1), flows through cooling air and is part of the cooling air Rear air conditioning system 10, which is arranged in the sleeping cabin, but the heat exchanger 1 differs by its construction of conventional heat exchangers explained in detail later on with reference to various exemplary embodiments with variants.

The heat exchanger 1 through which refrigerant flows from the refrigerant circuit 2 is also part of a refrigerant medium circuit 11, shown in FIG. 1 by solid lines, and is also flowed through by a brine medium flowing in it, in the present case brine. The coolant medium circuit 11 has, in addition to the heat exchanger 1, a pump 12 arranged in front of it, a cold storage 13 arranged after the heat exchanger 1, and a shut-off valve 14 arranged after the cold storage 13.

In the present case, the heat exchanger 1 in the rear branch 2 "has a smaller power than the evaporator 6 in the parallel front branch 2 'of the refrigerant circuit 2.

The function of the air conditioning system shown in Fig. 1 is as follows:

In the loading operation of the cold accumulator 13 flows, circulated by the compressor 3, refrigerant in the refrigerant circuit 2. This is due to the

Compressing heated refrigerant cooled in the condenser 4. In the front Branch it is expanded in the expansion element 5 and cooled down before it passes to the air flow, located in the vehicle interior front evaporator 6, where it extracts heat from the same air flowing through and thus cools them. In the downstream expansion element 8, the refrigerant is further expanded. In the rear branch 2 ", the refrigerant which has been heated as a result of the compression and slightly cooled in the condenser 4 is expanded in the expansion element 9 and cooled further before it reaches the heat exchanger 1. The heat exchanger 1 is not air-flowed in the loading operation, but the heat exchanger 1 becomes in this operating state flows through both refrigerant and the refrigerant medium, whereby the refrigerant medium from the expanded, cold refrigerant is cooled to below ^{0 0} C. The air-side barrier of the heat exchanger 1 prevents icing of the same due to the accumulating and icing in an air flow condensate out The refrigerant circulating in the refrigerant circuit 11 cools, after it has exited the heat exchanger 1 and comes to the cold storage 13, the cold storage medium containing cold storage 13, which undergoes a phase change and stores the cold.

In normal operation, i. During operation of the evaporator 6, the refrigerant flow in the present case takes place parallel to one another through the two branches 2 'and 2 ", so that refrigerant flows through the heat exchanger 1 in addition to the evaporator 6. However, the pump 12 of the refrigerant medium circuit 11 and 11 is located there The valve 14 is closed, so that the refrigerant medium in the heat exchanger 1 does not circulate, but stands.

In an air-conditioning of the sleeping cabin, the evaporator 6 is shut off on the air side, ie the assigned to him, in this case driven by the vehicle engine fan is off. In addition, the compressor 3, which is also driven by the motor vehicle engine, is present, so that the refrigerant does not circulate in the refrigerant circuit 2 either. The valve 14 is in this open operating state and the electrically driven pump 12 circulates the refrigerant medium, so that it absorbs heat in the heat exchanger 1 and emits in the cold storage 13. In this case, the heat exchanger 1 is traversed by air, driven by an electrically operated fan, so that the air flowing through the heat exchanger 1, the sleeping cabin supplied air is cooled by the cold refrigerant medium.

Before discussing the design of the heat exchanger 1 in detail, a second exemplary embodiment of a system for auxiliary air conditioning is described below with reference to FIG. 2, in which a corresponding heat exchanger 1 is arranged.

The system according to the second embodiment, wherein the same and equivalent components are provided with the same reference numerals as in the first embodiment, has substantially the same elements, but instead of a parallel connection of the front and rear air conditioners 7 and 10 is a series circuit The same is provided in the cooling operation, so that in principle the rear branch 2 "is connected behind the front branch 2. The optional expansion element 8 of the front branch 2" is omitted, the expansion element 9 becomes optional, ie it can be omitted with appropriate design. The refrigerant medium circuit 11 is constructed the same as in the first embodiment.

The function of the air conditioning system shown in FIG. 2 is as follows:

In the loading operation of the cold accumulator 13 flows, circulated by the compressor 3, refrigerant in the refrigerant circuit 2. In this case, the heated in consequence of the compression refrigerant in the condenser 4 is cooled. In the front branch, it is expanded in the expansion element 5 and cooled down further, before it flows to the air flowing through the vehicle interior. Evaporator 6 passes where it extracts heat from the same air flowing through it and thus cools it. In the downstream expansion element 8, the refrigerant is further expanded. In the rear branch 2 ", the refrigerant which has been heated as a result of the compression and slightly cooled in the condenser 4 is expanded in the expansion element 9 and cooled further before it reaches the heat exchanger 1. The heat exchanger 1 is not air-flowed in the loading operation, but the heat exchanger 1 becomes in this operating state flows through both refrigerant and the refrigerant medium, whereby the refrigerant medium from the expanded, cold refrigerant is cooled to below ^{0 0} C. The air-side barrier of the heat exchanger 1 prevents icing of the same due to the accumulating and icing in an air flow condensate out The refrigerant circulating in the refrigerant circuit 11 cools after it has left the heat exchanger 1 and comes to the cold storage 13, the cold storage medium contained in the cold storage 13, which undergoes a phase change and stores the cold.

In normal operation, i. during operation of the evaporator 6 and the heat exchanger 1 is flowed through by refrigerant. Here, however, the pump 12 of the refrigerant circuit 11 and the valve 14 is closed, so that the refrigerant in the heat exchanger 1 does not circulate, but is and thus no significant heat absorption takes place on the part of the refrigerant.

In an air-conditioning of the sleeping cabin, the evaporator 6 is shut off on the air side, ie the assigned to him, in this case driven by the vehicle engine fan is off. Furthermore, in the present case also driven by the motor vehicle engine compressor 3, so that the refrigerant does not circulate in the refrigerant circuit 2, which is why no significant heat absorption takes place in the evaporator 6 side of the refrigerant. The valve 14 of the refrigerant circuit 11 is opened in this operating state and the electrically driven pump 12 circulates the refrigerant medium so that it absorbs heat in the heat exchanger 1 and discharges in the cold storage tank 13. In this case, the heat exchanger 1 is traversed by air, driven by an electrically operated fan, so that the air flowing through the heat exchanger 1, the sleeping cabin supplied air is cooled by the cold refrigerant medium.

In the following, three exemplary embodiments of possible heat exchangers with variants are explained in more detail, which are suitable in particular suitable for a system according to the invention for stationary air conditioning.

According to the first embodiment of a heat exchanger 1, as it is used in a system according to the invention, in particular in one of the two systems described above, a double-row evaporator 101 is provided. The area of the heat exchanger 1, in the following referred to as the cold carrier area 104, through which the coolant medium flows and which can be flowed through in the air-permeable area, is integrated directly into the evaporator 101.

The first row of flat tubes is formed by a series of conventional, multi-chamber, extruded flat tubes 107, each of which ends with their ends into a collector 103 (cf., for example, FIG. The structure of the first row corresponds to the conventional heat exchanger. In the present case, 103 partition walls 112 for specifying a flow path of the refrigerant (in the present case R134a, but can, for example. Also CO ₂ are used) provided by the heat exchanger 101, so that the heat exchanger 101 in cross-counterflow operation with two deflections in width is flowed through (see Fig. 18, wherein the flow direction of the refrigerant in a heat exchanger 101 according to a second embodiment of the second embodiment described in more detail later and the flow direction of the air is shown by arrows). There are, however other flows possible, but preferably first the side of the heat exchanger 101 is flowed through, in which the refrigerant carrier portion 104 is arranged. Likewise, heat exchangers with more than two rows can also be provided, wherein in this case the cold carrier area 104 is preferably arranged outside on the row arranged downstream of the airflow, which is preferably first flowed through by the refrigerant.

In the present case, the second row of flat tubes is formed by two flat tubes 107 'and 106 arranged directly next to one another, the flat tubes 107' being arranged upstream of the air and having a thickness corresponding to the flat tubes 107 of the first row of flat tubes, but only approximately half as long in cross section. The air outlet downstream arranged the flat tubes 106 are in the present case almost as long as the flat tubes 107 'but significantly thinner and are on three sides surrounded by U-shaped tubes in their cross section (U-tubes, in the present case with multiple channels), which is is the heat transfer region forming elements 105 that form the brine region 104 in conjunction with upper and lower refrigerant storage tanks 110. The inner dimensions of the elements forming a heat transfer region 105 correspond to the outer dimensions of the flat tubes 106, so that they rest tightly against one another.

The heat transfer region forming elements 105 are slightly shorter than the flat tubes 106, 107 and 107 'is formed so that the flat tubes 106, 107 and 107' extend beyond these discs and into the collector 103, while the in their cross section as a U-shaped Tubes formed a heat transfer area forming elements 105 only into the loading boxes protrude, hereinafter referred to as refrigerant tank sump 110, which are arranged below or above the collector 103 downstream of the heat exchanger 101. For the connection of the cold carrier region 104 to a coolant medium circuit in which the coolant medium, in the present case brine flows, are presently arranged on opposite sides of the refrigerant storage tank 110 nozzle 113. Further, a partition wall is centrally provided in the upper refrigerant header tank 110, so that the refrigerant medium flows downward on one side through the heat transfer region forming members 105 and on the other side upward, ie, is deflected once. Any other flow patterns are possible. In the present case, the brine area is flowed through in the opposite direction directly to the adjacent refrigerant flow, that is, from left to right when referring to FIG. 18, while the refrigerant flow in the corresponding area extends from right to left. In principle, a double-row arrangement of the heat transfer region forming elements 105 is also possible, so that a deflection in the depth can be done.

For the production of the heat exchanger 101 in the present case all components are assembled and soldered together in a known manner.

According to a first variant of the production (see Figures 10 and 11) is carried out a separate pre-assembly of heat exchanger (without brine area) and brine area. The two assemblies are pushed into each other after pre-assembly, as shown in the drawing, and then soldered together. Alternatively, the two assemblies can be soldered separately and then pushed into each other. Also mechanically joined heat exchangers are possible.

The flat tubes 106, 107, 107 'as well as the tubes forming the heat transfer region forming elements 105 are extruded tubes according to the present embodiment. In addition to extruded flat tubes, in particular also welded or disc-folded flat tubes are possible. According to the present embodiment, the heat exchanger 101 has the following dimensions (with regard to the dimensions, reference is made to FIGS. 9, 10 and 14):

Total depth B of the heat exchanger 101: 65 mm

Width B2 of the flat tubes 107 of the first flat tube row: 30 mm thickness b2 of the flat tubes 107 of the first flat tube row: 3 mm width B3 of the flat tubes 107 'of the second flat tube row: 15 mm thickness b3 of the flat tubes 107' of the second flat tube row: 3 mm width B4 of the flat tubes 106 of the second flat tube row: 14 mm thickness b4 of the flat tubes 106 of the second flat tube row: 1, 5 mm width B6 of the elements 105: 14 mm thickness b6 of the elements 105: 5 mm distance h2 of the flat tubes 107 of the first flat tube row: 6 mm distance h6 of FIG Elements 105: 4 mm

Transverse division q of the heat exchanger 101: 10 mm

Height H1 of the refrigerant storage tank 110: 4 mm

In accordance with a second variant of the exemplary embodiment, flat-section tubes 106 and 107 'formed in one piece and presently again extruded are provided with different thicknesses instead of separately formed flat tubes 106 and 107'. In this case, according to the first variant of the second embodiment, the brine area is pushed laterally onto the thinner area of the flat tubes, wherein the soldering can take place before or after the pushing on. In the present case, the thicker regions of the second row of flat tubes have a width which corresponds to the width of the flat tubes of the first row of flat tubes. The thinner region is in the present case somewhat narrower than the thicker region.

According to another, not shown in the drawing third variant of the embodiment, instead of the collectors forming Sammler provided milk boxes each with a U-shaped cross-section of plates collector.

According to a fourth variant of the embodiment, the flat tubes of the heat exchanger as well as the heat transfer region forming elements are bent in a U-shape in their longitudinal direction, so that the lower reservoir omitted. The upper header tanks each have a plurality of partitions in order to ensure a flow through the flat tubes of the heat exchanger and the elements forming a heat transfer region.

According to the second embodiment of a heat exchanger, as it can be used in a system according to the invention are provided in the same or equivalent components with reference numerals higher by 100 with respect to the first embodiment, a construction with respect to the collector 203 two-row evaporator 201 is provided at a cold carrier region 204 is structurally integrated into the evaporator 201.

The second row of flat tubes is represented by flat tubes 207 'which correspond in their thickness to the flat tubes 207 of the first row of flat tubes arranged on the air upstream side, but their width is reduced by approximately 50%, so that in the present case only four instead of eight chambers are used in the corresponding multi-chamber rows. Flat tubes are provided.

As seen in the direction of air flow behind the flat tubes 207 ', the cold carrier region 204 is arranged with a further series of flat tubes 206 which open into the same collectors 203 as the adjacent flat tubes 207'. The flat tubes 206 are thinner and narrower than the flat tubes 207 '. On the outside, they are surrounded in the heat transfer region by a heat transfer region-forming element 205 on all sides, wherein the heat transfer region-forming element 205 is also formed as a flat tube, but with a slightly larger thickness and a slightly smaller width than the adjacent flat tubes 207 '. The flat tubes, which form the elements 205 forming a heat transfer region, end in coolant medium collecting containers 210 arranged below or above the collectors 203, through which the flat tubes 206 protrude and terminate in the collectors 203 (see FIG. 22).

As shown in FIG. 23, the flat tubes 206 and the flat tubes forming the element 205 are formed separately, with the flat tubes 206 inserted into the flat tubes and centered by means of ribs that are perpendicular to the air flow direction. According to a variant, the corresponding arrangement can also be formed by double-walled tubes, so that the flat tubes 206 and the flat tubes forming the element 205 are formed integrally with one another. The one-piece design offers advantages in the assembly, but the cutting to length of the flat tubes is much more complex.

In the present case, the flat tubes 207 ', 206 and the flat tubes forming the element 205 end in a flattened manner as seen in the air flow direction, while they are rounded off in the direction of air flow. In this case, the ends of the flat tubes can also be designed differently, in particular both ends can be rounded.

For the production of the evaporator 201, the cold storage area together with the refrigerant storage tank 210 is preassembled and installed as an assembly in the evaporator 201 in the same step as the flat tubes 207 and 207 '. The entire evaporator 201 is then soldered in a single work step. In principle, the previously mentioned module can also be pre-soldered, but this makes the production more expensive and therefore only makes sense in special cases, in particular if no secure prefixing of the individual components of the assembly is possible, so that the tightness of the brine region 204 can not be guaranteed.

The connection of the brine area 204 is carried out after soldering in a known manner, so that via the one side provided on the upper refrigerant reservoir 210 side nozzle 213 refrigerant medium in the heat exchanger and over the other provided on the other side nozzle 213 comes out of this again, wherein it is deflected by a partition which is arranged in the upper refrigerant storage tank 210.

In the following, with reference to Figures 24 to 27, the description of the fifth to ninth variant of the above described first embodiment of a heat exchanger 101, as it can be used in a system according to the invention for stationary air conditioning. The structure of the heat exchanger corresponds in this case to the heat exchanger of the second exemplary embodiment, but in each case the heat transfer region-forming elements 105, which are integrated herein, differ.

According to the fifth variant of the first embodiment, the heat transfer region forming member 105 is formed such that the middle refrigerant medium channel 109 'is opened on a side later disposed on the side of the flat tube 106. In this case, the flat tube forming the element 105 is U-shaped bent around the region of the opened, central channel 109 ', wherein the closed channels 109 form the legs which are spaced from one another and receive the flat tube 106 between them. The element 105 thus has a plurality, in the present case two times three channels 109, on the side surfaces of the flat tube 106th lie, while the opened, central channel 109 'forms a connecting web 109 "between the two halves of the element 105.

According to the sixth variant of the first exemplary embodiment, the element 105 forming a heat transfer region is embodied such that-with the central coolant medium channel 109 'once again opened-the connecting web 109 "is designed to rest against the flat tube 106.

In the seventh variant of the first exemplary embodiment, the walls of the central coolant medium channel 109 'are compressed approximately centrally and thus free of the coolant medium. Together they form a connecting web 109 "between the two halves of the heat transfer region-forming element 105 filled with the coolant medium.

According to the eighth variant of the first exemplary embodiment, the connecting web completely disappears between the two halves of the element forming a heat transfer region over at least a substantial portion of the length of the flat tube 106. The element 105 forming a heat transfer region lies in each case flat on mutually opposite side surfaces of the flat tube 106 at.

According to a ninth variant of the first exemplary embodiment, which corresponds in its representation to FIG. 27, the connecting webs 109 "are completely omitted, ie the element 105 forming a heat transfer region is formed in two parts, wherein the two halves formed separately in each case lie flat on opposite side surfaces of the flat tube 106 abut. The heat exchanger used in the system according to the invention for stationary air conditioning is preferably a heat exchanger having a plurality of juxtaposed, the refrigerant-carrying tubes and at least one brine area, in which the refrigerant medium is provided, wherein at least one heat transfer area forming element which part the refrigerant carrier region is applied to a pipe carrying the refrigerant at least two sides, but in particular surrounds the pipe carrying the refrigerant at least in three sub-areas on at least three sides. In this case, the pipe carrying the refrigerant may also be arranged completely within the element forming a heat transfer region.

According to the third embodiment of a heat exchanger 301, as used in a system following the invention, a single-row evaporator is provided. In the arrangement of the flat tube 306 guiding the refrigerant in the heat transfer region forming member 305 shown in FIG. 28, the tube 306 is integrated into, or formed in, the refrigerant carrying member, a heat transfer region forming member 305. The heat transfer region forming member 305 is in the form of a flat tube. In a variant, the refrigerant pipe 306 may also be inserted into the flat tube 305. The coolant medium or the brine surrounds the refrigerant-carrying pipe 306 from all sides, in the present case in the form of a pipe-in-pipe arrangement. Between the heat transfer region forming elements 305 ribs 316, in particular corrugated fins are provided for a more effective heat transfer to the air flowing through or to be cooled. FIG. 29 shows, for the third embodiment, that the heat transfer region forming elements 305 are formed slightly shorter than the flat tubes 306, so that the flat tubes 306 extend beyond them the collectors 303 protrude, while the flat-tube formed a heat transfer region forming elements 305 only up to the refrigerant carrier sump 310, the lower or above the collector 303 are arranged in the heat exchanger 301. For the connection of the cold carrier region to a coolant medium circuit in which the coolant medium, in the present case brine, flows, in the present case, nozzles 313 are arranged on opposite sides of the coolant medium collecting container 310. In the present case, the brine area is directly flowed through in the same direction to the adjacent refrigerant flow, that is to say from left to right when reference is made to FIG. 30, while the refrigerant flow also runs from right to left in the corresponding area. An opposite flow of refrigerant and refrigerant is also conceivable. The nozzle 317 on the heat exchanger 301 serve to supply and discharge of the refrigerant.

By the tube-in-tube arrangement, the depth B can be kept low, since it is essentially determined by the depth of the heat transfer region forming elements 305. Preferably, the overall depth B is 10 to 40 mm, in this case about 20 mm.

Claims

Patent claims

1. A system for stationary air conditioning of a motor vehicle, in particular a commercial vehicle, with a refrigerant circuit (2), in which at least one compressor (3) and at least one heat exchanger (1) are arranged and in which a refrigerant flows, and a refrigerant circuit (11), in which at least one pump (12), at least one heat exchanger (1) and at least one cold storage (13) are arranged and in which a refrigerant medium flows, characterized in that the heat exchanger (1) of the refrigerant circuit (2) and the heat exchanger (1) of the refrigerant circuit (11) integrated as a heat exchanger (1) are formed.

2. System according to claim 1, characterized in that, the heat exchanger (1) is at least partially traversed by both the refrigerant and the refrigerant medium, wherein the flow channels in which the refrigerant and refrigerant flow, at least partially by a common wall or two flat adjoining walls are separated.

3. System according to claim 1 or 2, characterized in that the

System has exactly one compressor (3), which contains the refrigerant in the

Refrigerant circuit (2) circulates, wherein the refrigerant circuit (2) is branched and an evaporator (6) in a branch (2 ') and the heat exchanger (1) acting as an evaporator in normal operation is arranged in the other branch (2 ").

4. System according to claim 1 or 2, characterized in that the system has exactly one compressor (3), the refrigerant in the

Refrigerant circuit (2) circulated, wherein in the refrigerant circuit (2) a

Evaporator (6) is arranged in series with an acting as an evaporator in normal operation heat exchanger (1).

5. System according to any one of the preceding claims, characterized by a heat exchanger (1), which serves for cooling air to be conditioned for the motor vehicle interior, with a plurality of juxtaposed arranged, the refrigerant leading tubes and at least one cold carrier region (104 204, 304) in which a coolant medium is provided, wherein at least one heat transfer region-forming element (105; 205; 305) in which a coolant medium can flow is a pipe of the evaporator (101) which guides the coolant and is to be conditioned ; 201; 301) on at least two sides.

6. System according to claim 5, characterized in that at least one element (105, 205, 305) forming a heat transfer region surrounds a pipe of the evaporator (101, 201, 301) which guides the refrigerant and is arranged in the air stream to be conditioned on at least three sides.

7. System according to claim 5 or 6, characterized in that in at least one heat transfer region forming element (205; 306) at least one pipe carrying the refrigerant is arranged.

8. System according to one of claims 5 to 7, characterized in that the refrigerant leading and / or the refrigerant carrying pipe is a double-walled flat tube, wherein the refrigerant in the central region and the refrigerant medium is in the outer area.

9. System according to any one of claims 5 to 8, characterized in that the refrigerant leading and the refrigerant carrying pipe is formed by two separately formed tubes which are pushed into each other.

10. System according to one of claims 5 to 9, characterized in that the refrigerant leading and the refrigerant carrying pipe are integrally formed.

11. System according to any one of claims 5 to 10, characterized in that the cold carrier region (106) does not completely surround one or more tubes carrying the refrigerant.

12. System according to any one of claims 5 to 11, characterized in that the refrigerant carrier region (106) surrounds one or more tubes carrying the refrigerant at exactly three sides.

13. System according to any one of claims 5 to 12, characterized in that the coolant carrier region (106) covers one or more pipes carrying the refrigerant only partially on at least one, in particular on two sides.

14. System according to any one of claims 5 to 13, characterized in that the refrigerant carrying the tube is formed by a tube having a U-shaped cross-section.

15. The system according to any one of claims 5 to 14, characterized in that the refrigerant carrying pipe in a collector (103, 203, 303) ends.

16. System according to any one of claims 5 to 15, characterized in that the tubes or channels carrying the refrigerant medium in a refrigerant storage tank (110, 210, 310) end.

17. System according to one of claims 5 to 16, characterized in that the one or more elements forming a heat transfer region (105, 205, 305) with the pipe (s) guiding the refrigerant and with the collector (103, 203, 303 ) are soldered.

18. System according to any one of claims 5 to 17, characterized in that the cold carrier region (104) consists of aluminum, in particular coated aluminum.

19. System according to any one of the preceding claims, characterized in that the refrigerant medium is formed by brine.

20. System according to any one of the preceding claims, characterized in that the storage medium in the cold storage (13) which is cooled by the refrigerant and, if necessary, the cold returns to the refrigerant medium, a PCM material (phase change material), in particular Water is

21. A method for operating a system according to one of claims 1 to 19, characterized in that in the loading operation, both refrigerant and the refrigerant medium flow through the heat exchanger (1). men that in the evaporator operation both air and refrigerant flow through the heat exchanger (1) and that flow during operation of the stationary air conditioning both air and refrigerant the heat exchanger (1).