DE102004056814B4 - air conditioning - Google Patents

Abstract

Air conditioning system (1) for air conditioning a motor vehicle interior with a mixing chamber (14), which is set up to control at least one warmer and a cooler conditioned air stream (24 , 25), characterized in that in the mixing chamber (14) a. An outlet (40) for the warmer, conditioned air stream (25) is arranged opposite the inlet opening of the warm partial air stream (20), so that there is a substantially rectilinear flow path (70) between the inlet opening and the outlet (40), and b. Flow-guiding means which influence the flow path (72) between the inlet opening (74) and the outlet (38) are arranged between the inlet opening (74) of the cold partial air flow (22) and the outlet (38) of the colder conditioned air flow (24) that i. the flow paths (70, 72) of the warm partial air flow (20) and the cold partial air flow (22) intersect in the mixing chamber (14), the mixing zone (66) forming at the crossing point of the warm and cold partial air flow (20, 22) , and ii. the warm and the cold partial air flow (20, 22) in the mixing zone (66) are conducted in counterflow.

Description

The subject of the present invention is an air conditioning system.

Air conditioning systems for the automotive sector are set up to at least one according to the wishes of the user conditionable, d. H. to generate freely adjustable air flow in its strength or its temperature.

In order to generate such an air flow, ambient air is sucked in via a fan and, after passing through a filter, fed into the conditioning unit of the air conditioning system. There, the sucked ambient air is cooled by a heat exchanger in which a liquefied refrigerant is evaporated to a defined starting temperature. This starting temperature is typically below 10 ° C, often in the range of 4 ° C. With the cooling of the sucked air is accompanied by a dehumidification. In this way, a cold air flow is generated with a defined outlet temperature and defined outlet humidity.

A partial flow thereof is passed through another heat exchanger in which a heated medium, for. B. the coolant of the drive unit of the motor vehicle, circulates. Since the temperature of the coolant during operation of the motor vehicle is substantially constant, a warm partial air flow with a substantially constant temperature is generated in this way. The cold partial air flow thus available and the warm partial air flow are then fed to a mixing chamber in a mixing ratio to be controlled by suitable adjusting elements.

The mixing chambers of prior air conditioners are based on a controlled mixing of the mixing chamber supplied hot and cold partial air streams. This mixing takes place in such a way that a mixing zone with a shear layer is formed within the mixing chamber, in which a stable temperature profile is present along an axis. Characteristic of these mixing chambers is that the flow paths of the supplied warm or cold partial air streams do not pass straight through the mixing chamber. To put it clearly, a warmer conditioned air flow generally does not exit the mixing chamber on the side opposite the entry point of the warm partial air flow. Rather, the warmer air stream generated in the mixing chamber usually exits the mixing chamber at an angle of approximately 90 ° with respect to the flow direction of the incoming warm partial air flow. If, under the flow path of the warmer partial air flow in the mixing chamber, one understands the flow path which extends from the entry point of the warm partial air flow to the exit point of the warmer conditioned air flow, then the flow path of the warm partial air flow through the mixing chamber is not rectilinear but angled. The same applies to the flow path of the cold partial air flow. In a conventional mixing chamber, the incoming warm and cold partial air streams encounter one another such that they collide at an angle and are deflected to their respective exit locations to form a shear layer intermediate the deflected partial air streams. The temperature of the component streams emerging from the mixing chamber is essentially determined by the arrangement of the outlet openings, since it is determined via the arrangement of the outlet opening which spatial area of the shear layer is fed to the outlet opening.

In this way it is possible, by selecting the spatial length of an outlet along this axis, to set the temperature of the conditioned air stream flowing out of the outlet. In particular, it is possible to provide different outlets from the mixing chamber, which are arranged at different locations along said axis. Thus, it is possible to produce a plurality of conditioned air streams having different temperatures without changing the mixing ratio of the supplied cold and warm air streams. As a rule, the temperature difference between the air streams or the ratio of the temperature of the air streams is predetermined by the selection of the outlet locations from the mixing chamber.

If the mixing ratio of the inflowing warm and cold partial air flows is changed by actuation of the corresponding adjusting elements, then the temperature of all the conditioned air streams emerging from the mixing chamber changes simultaneously. This means that the individual generated air flows are not individually conditionable, but they are jointly conditionable. Nevertheless, the generation of non-individually conditionable air streams for the air conditioning of a motor vehicle interior can be advantageous because the physiological requirements are different, for example, to the temperature of the injected into the motor vehicle interior airflows for different parts of the human body. Thus, the lower extremities, especially the feet, are particularly sensitive to cold, so that the blowing of warmer air than in the area of the dashboard / console brings physiological advantages and is perceived by the user of the motor vehicle as pleasant.

The DE 100 52 135 A1 describes an air duct housing, in particular for a motor vehicle heating, air conditioning and / or ventilation system, in which at least one air treatment device, at least an air path extending through the air treatment device and at least one air path bypassing the air treatment device are provided. Furthermore, at least two exit paths are provided, which open in a space in such a way that in each case one exit path of one of the other paths is substantially opposite. In the said space, a device movable about an axis is arranged, which has a channel-like air guide element and in each case provides a virtually pressure loss-free passage of air between two opposite paths and a loss of pressure air passage between other opposing paths.

The US Pat. No. 6,311,763 B1 describes an air conditioner for a vehicle that allows independent air conditioning of a front and a rear area of the vehicle. For this purpose, the air conditioner has two mixing chambers arranged in a common housing, to each of which a cold and a heated air flow are supplied in a variable ratio. From the mixing chambers conditioned air streams are each supplied to a panel and a Fußraumauslass.

The WO 01/62530 A1 also concerns a car air conditioner. It discloses a device comprising a first conduit disposed in a housing for transmitting a cold air flow. Furthermore, the device comprises a second line for transmitting a warm air flow, wherein a heat exchanger is arranged in the second line. The conduits extend between a fresh air inlet and a mixing zone that provides mixed air. The device comprises a system for dividing the warm and the cold air stream, which is arranged downstream of the heat exchanger. This system comprises a plurality of transversely alternating hot and cold air passages, respectively. These passages open into two separate mixing chambers.

Another car air conditioner is out of the box EP 0 756 955 A2 known. It also includes a mixing chamber to which a cold and a warm airflow are supplied in a variable ratio. The mixing chamber has two outputs for a panel and footwell outlet.

From the DE 101 27 339 A1 a comparably constructed automotive air conditioning system is known, in which further a channel-like element is provided, which provides a bypass chamber bypassing the bypass pipe from the heat exchanger to a Defrostauslass.

Also the EP 0 749 857 A1 discloses an automotive air conditioning system comprising a mixing chamber to which a cold and a warm airflow are supplied in a variable ratio. The mixing chamber has two outputs for a panel and footwell outlet. Furthermore, the air conditioning system has a pivotable air distribution element which allows the optional addition of cold air to the conditioned air supplied to the panel outlet or to the footwell outlet.

A disadvantage of the "layer mixer concept" described above, which is realized in all air conditioning systems of the aforementioned documents, however, is that in order to achieve the mentioned static temperature profile, the blowing of the hot and cold partial air streams usually takes place starting from one end of the mixing chamber. This results in a strong geometric restriction for the choice of the flow paths of the mixing chamber supplied hot and cold partial air flows, which brings a limitation of the structural design options with it.

Object of the present invention is therefore to provide an air conditioner for a motor vehicle, which has a mixing chamber, which allows an alternative supply of the mixed warm and cold partial air flows.

This object is achieved by an air conditioner with the features of claim 1 or claim 2.

The present invention is based on the use of a mixing chamber for the air conditioning system according to the invention, which does not make use of the "layer mixer" concept previously known from the prior art. Rather, in the present case, a novel mixer concept is proposed, which is referred to in the context of the present invention as a "cross mixer".

As before, a mixing chamber is provided in the air conditioning system to produce at least one warmer and one colder communally conditionable air stream. As in the past, a warm and a cold partial air flow are mixed in this mixing chamber in a ratio which can be selected by means of suitable adjusting elements. However, in deviation from the hitherto realized layer mixer concept, it is not essentially intended to form a shear layer for thorough mixing of the warm and cold partial air streams blown into the mixing chamber.

According to the invention, this general concept is implemented by supplying the mixing chamber with a cold and a warm partial air flow in such a way that the forming flow paths of the hot and cold partial air flow in the mixing chamber intersect.

This novel concept of the "cross-mixer" can be specifically improved by the thus formed in the mixing chamber mixing zone by appropriate means is dimensioned so that mix the warm and cold partial air flow in the mixing zone only incompletely. This incomplete mixing can be promoted by arranging flow dividers in the flow paths of the cold and / or warm partial air flow, which only supply a certain proportion of the partial air streams to the mixing zone and lead the remainder part to an outlet with only slight contact of the other partial air stream.

Illustratively speaking, in a preferred embodiment, a certain proportion is diverted to the warm partial air flow entering the mixing chamber. The remaining (warm) portion of the warm partial air flow passes through the mixing chamber on a substantially rectilinear first flow path and in this way arrives at a first outlet. The entering into the mixing chamber cold partial air flow is also diverted a certain part, wherein the Remaining (cold) remainder of the cold partial air flow passes through the mixing chamber on a substantially rectilinear or S-shaped second flow path to a second outlet from the mixing chamber. The respective branched warm or cold air streams are controlled mixed in the mixing chamber the respective cold or warm residual air flow.

The further proposed targeted dimensioning of the mixing zone can be done in various ways, such as by introducing suitable flow-conducting means in the mixing chamber. Furthermore, the size of the forming mixing zone can be influenced by suitable flow guidance of the hot and cold partial flow in the mixing chamber, for example by flowing the warm and cold partial air streams into the mixing chamber at suitably selected angles.

According to the invention, the hot and the cold partial air flow in the mixing zone are conducted in countercurrent. Here, countercurrent means that the vectorial variable "flow direction" of one partial air flow has a component which is directed counter to the flow direction of the other partial air flow. This means, in particular, that the flow directions of both partial air flows in the mixing zone enclose an angle of 90 ° or greater.

It has furthermore proven particularly advantageous if the expansion of the mixing zone is limited by flow-conducting means which are arranged in the mixing chamber itself. Here it has proven useful to arrange a chimney as a flow-conducting agent in the mixing chamber. Such a chimney is advantageously arranged, for example, in the flow path of the warm partial air flow, which is formed in the mixing chamber, downstream of the mixing zone. Alternatively, it is also possible, the chimney in the flow path of the cold partial air flow downstream of the mixing zone, d. h., To arrange downstream of the crossing point of the two partial air streams.

If a chimney is provided as a flow-conducting means in the mixing chamber, it is particularly advantageous if the inlet surface of the chimney has an opening cross section which is smaller than the inlet surface of the inlet opening of that partial air flow into the mixing chamber, in the flow path of the chimney is arranged. To put it clearly, this means that the chimney cuts out a smaller partial flow of the partial air flow which has passed through the mixing zone and in whose flow path it is arranged. Thus, the fireplace also acts as a flow divider.

Particular advantages also arise if the inlet opening of one of the warm or cold partial air streams is arranged opposite an outlet for a conditionable air stream. In this way results for a passing through the mixing chamber (warm or cold) partial air flow, a substantially rectilinear flow path in the mixing chamber. On the other hand, the flow path of the other warn or cold partial air flow through the mixing chamber can be deflected by introducing further flow-conducting means in the mixing chamber from its straight course, as far as z. B. is required by structural conditions. According to the invention, it is necessary that the forming flow path runs partially in the opposite direction to the rectilinear first flow path. It has proven particularly useful as a flow-conducting agent in the mixing chamber to form a baffle for the diverting partial air flow.

Further advantages and features of the "layer mixer" air conditioning system according to the invention will become apparent from the subclaims and the embodiments described below, which are not to be understood as limiting and will be explained in more detail with reference to the drawing. In the drawing show:

1 : a section through a multi-zone air conditioning system with two mixing chambers,

2 : A perspective sectional view of the mixing chamber of the rear module of the air conditioner 1 , and

3 : another perspective section through the mixing chamber 2 ,

1 shows a section through a multi-zone air conditioning 1 for the independent conditioning of two zones of a motor vehicle, in particular the first row of seats and the rear area of the motor vehicle. Here is the section in the plane of symmetry of the main climate module 2 the air conditioning 1 executed. In the installation position in the vehicle, this plane of symmetry is oriented more generally in the direction of travel and in the vertical direction.

The air conditioner 1 according to this embodiment is divided into various modules that are easily replaceable and in the ready state of the air conditioner 1 are tightly interconnected. The air conditioning has a main climate module 2 with a basic body 34 on. With the main body 34 On the inlet side is an air supply module 3 connected in which a blower 26 is arranged. The fan 26 serves for intake of ambient air. Here are the main body 34 the main climate module 2 and the air supply module 3 designed so that the air supply module 26 optionally on the right or on the left side (seen in the direction of travel of the motor vehicle) from the main climate module 2 can be arranged. The inventive multi-zone air conditioning 1 is thus suitable for installation in both right-hand drive and left-hand drive vehicles. The blower 26 into the air supply module 3 extracted ambient air is supplied via an (optional) filter located in the air supply module 32 inside the body 34 the main climate module 2 directed.

The blower 26 sucked ambient air passes through an air filter 32 into the main body 31 the main climate module 2 one. immediately after the filter 32 is the first heat exchanger 4 arranged in which a liquefied refrigerant is evaporated. The resulting cold development serves to cool the intake ambient air to a defined starting temperature, for example 4 ° C, and condense the contained air moisture.

After passing through the first heat exchanger 4 the cooled dried air is divided into several flow paths, which in 2 are indicated as dashed lines. A first flow path 29 performs a first part of the first heat exchanger 4 exiting air flow through the inside of the body 34 arranged second heat exchanger 6 and a subsequently arranged electrical heating element 26 , The second heat exchanger 5 is connected to the coolant circuit of the drive unit of the motor vehicle. The coolant circulating therein has a relatively high temperature, which is typically about 100 ° C. The downstream electric heating element 26 , which is optionally provided, can be switched on when the heat demand in the air conditioner can no longer be met by the heat loss of the drive unit of the motor vehicle. This condition can occur, for example, in the warm-up phase of the drive unit. An additional heating element 26 However, it may also be necessary at all times, provided that the drive unit of the motor vehicle used has high efficiency and thus low heat loss. Examples of this are the modern common-rail diesel engines called.

After the branched first partial air flow over the first flow path 29 through the second heat exchanger 6 as well as the optional heating element 26 he has warmed up and enters the first warm partial airflow 16 from below into the main climate module 2 arranged first mixing chamber 12 the multi-zone air conditioning system according to the invention 1 one.

On a second flow path 31 A second partial cold air stream, which at the beginning is cold, also passes through the second heat exchanger 6 as well as the optional heating element 26 , wherein this second flow path 31 through barriers from the first flow path 29 is disconnected. On the second flow path 31 becomes a second warm partial airflow 20 generated from the top into one in a separate rear module 10 arranged second mixing chamber 14 entry.

A third flow path 28 in turn, through barriers from the first flow path 29 is separated, performs a first partial cold air flow 18 from below Into the first mixing chamber 12 , The mixing ratio between first warm partial airflow 16 and first cold partial airflow 18 is by means of an angled mixing flap 58 set.

On a fourth flow path 30 Finally, a last cold partial air flow from the first heat exchanger 4 to the second mixing chamber 14 , in which he laterally as the second cold partial airflow 22 entry. The mixing ratio of second warm partial airflow 20 and second cold partial airflow 22 is by means of an adjustable mixing flap 60 set.

The multi-zone air conditioning system according to the invention with a main air conditioning module 2 and a rear module 10 is doing this by inserting the rear module 10 into the main body 34 the main climate module 2 put into the ready state, with a joint connection of both modules is made. In 2 is here at the joint surfaces lying on both surfaces forming joint 50 between the main body 34 of Main air module 2 and the rear module 10 indicated by a dash-dotted line. The connection between the main climate module 2 and rear module 10 is formed overpressure-tight. The rear module 10 is preferably after insertion into the main climate module 2 in its position by screwing with the main climate module 2 fixed. Here is the fund module 10 formed so that the above-described first flow path 29 Being in the first, in the main climate module 2 arranged mixing chamber 12 leads, is trained only when the rear module 10 at the main climate module 2 is arranged. Furthermore, the second flow path 31 that goes through the main climate module 2 and the rear module 10 extends through, formed only when the rear module 10 at the main climate module 2 is arranged.

Both the first flow path 29 as well as the second flow path 31 extend through the second heat exchanger 6 as well as the optional heating element 26 , In this way, a particularly space-saving configuration of the multi-zone air conditioning system according to the invention is realized. By rear module 10 and main climate module 2 both the second heat exchanger 6 as well as the optional heating element 26 divide and adding both the first flow path 29 leading to the first mixing chamber 12 the main climate module 2 leads, as well as the second flow path 31 leading to the second mixing chamber of the rear module 10 leads, through one and the same second heat exchanger 6 and by one and the same additional heating element 26 run, significant design features can be realized. So it is possible to another (second) heat exchanger or a second optional heating element in the rear module 10 to renounce. This allows a particularly compact design of the multi-zone air conditioning system according to the invention.

The first mixing chamber 12 , which in the main climate module 2 is formed, corresponds in its operation to the already known in many air conditioning mixing chambers. The underlying mixer concept is referred to in the context of the present invention as a "layer mixer". The first mixing chamber 12 become the first warm partial airflow 16 as well as the first cold partial airflow 18 supplied from below. In the first mixing chamber 12 become the first and second partial air flow 16 . 18 so mixed that within the first mixing chamber 12 sets in the vertical direction a shear layer with a fixed temperature profile. This means that, depending on the arrangement of an outlet from the first mixing chamber 12 a conditionable airflow 8th . 9 outlet, whose temperature depends on the exact arrangement of the outlet in the vertical direction. This design principle is regularly used in the art. It makes it possible with a mixing chamber to which a warm and a cold part air flow is supplied to produce a plurality of conditioned air streams having different temperatures. In general, however, the differently tempered air streams generated in this way will not be able to be conditioned independently of one another. Rather, there is usually a temperature difference between the generated conditioned air streams. This can be kept constant by suitable design of the air conditioner over the largest possible temperature and ventilation area.

In the case of the present multi-zone air conditioning 1 are in the area of the first mixing chamber 12 three outlets 42 . 44 and 46 intended. In the upper area of the mixing chamber 12 are a defrost outlet 42 and a front panel outlet 44 arranged. From the defrost outlet 42 as well as the front panel outlet 44 enter conditioned airflows 7 and 8th whose temperature is slightly different from each other.

In the vertical direction significantly lower at the first mixing chamber 12 arranged is a front Fußraumauslass 46 , from the much warmer air from the first mixing chamber 12 is led out. In this way, with only a first mixing chamber 12 (colder) first conditioned air streams 7 and 8th generated from the outlets 42 and 44 emerge, as well as a (warmer) second conditioned airflow 9 coming out of the footwell outlet 46 exit. The absolute and relative strength of the outlets 42 . 44 and 46 outflowing air streams 8th such as 9 is by means of the blower 26 as well as mixing flaps, which are arranged in the area of the outlets. The mixing valves are the first mixing chamber 12 and possibly the air conditioning control advantageously designed so that the strength and temperature of the outlets 42 . 44 such as 46 exiting air streams 7 . 8th and 9 only insignificant change if only a single mixing flap is adjusted.

The second mixing chamber 14 in the rear module 10 is formed, however, based on a new fluidic mixer concept, which is referred to in the context of the present invention as a "cross mixer". How out 1 can be seen, the second warm partial air flow 20 the mixing chamber 14 fed from above. On the other hand, the second partial cold air stream which is still supplied is used 22 the mixing chamber 14 supplied from the side. Therefore, the flow paths intersect 70 . 72 of warm and cold partial airflow 20 . 22 in the second mixing chamber 14 at an angle of about 135 °. In particular, here is a partial countercurrent flow of both partial air flows in the forming mixing zone 66 realized.

The entry point of the warm partial airflow 20 into the second mixing chamber 14 arranged opposite is a Fußraumauslass 40 from the mixing chamber 14 to supply the footwell of the rear area with a warmer conditioned airflow 25 is provided. Here is the footwell outlet 40 for the rear area substantially below the second mixing chamber 14 arranged. By contrast, the side of the second mixing chamber opposite to the entry point of the second partial cold air flow 22 a panel outlet 38 arranged for the fund area. From this panel outlet 38 occurs opposite the footwell outlet 40 slightly cooler second conditionable airflow 24 out. The exact temperature ratio of the conditioned air streams 24 and 25 can be adjusted by the mixing conditions in the "cross mixer". These mixing ratios are essentially due to the flow-mechanical properties of the second mixing chamber 14 certainly. Therefore, the air flows 24 and 25 can not be conditioned independently of one another with respect to temperature. By means of another angled mixing flap 64 However, the relative strength of the outlets can 38 and 40 exiting air streams 24 and 25 be varied.

2 illustrates the fluid mechanical conditions within the designed as a "cross mixer" second mixing chamber 14 the air conditioning system of the invention. Via a second flow path 31 becomes the second mixing chamber 14 a second warm partial airflow 20 fed. This enters from above into the second mixing chamber. The strength of this second warm partial airflow 20 is by means of a flap 62 regulated. Furthermore, a second cold partial airflow occurs 22 via a laterally arranged access opening into the second mixing chamber 14 a, wherein this access opening well below the inlet opening for the second warm partial air flow 20 is arranged. The in the second mixing chamber 14 occurred second warm partial air flow 20 crosses a mixing zone 66 and becomes a footwell outlet 40 led for the fund area. The in the horizontal flow direction in the second mixing chamber 14 occurred second cold partial air flow 22 meets a baffle 56 and gets up from this towards the mixing zone 66 diverted. He flows around in front of the mixing zone 66 the as a fireplace 68 into the second mixing chamber 14 protruding footwell outlet 40 for the fund area. This fireplace 68 ends only when the mixing zone is reached 66 located in the center of the second mixing chamber 14 located.

With the fireplace 68 becomes part of the second of the mixing chamber 14 supplied warm partial airflow 20 after passing through the mixing zone 66 from the second mixing chamber 14 led out. Here is the opening cross section of the upper opening of the fireplace 65 that of the mixing zone 66 facing, smaller than the cross-sectional area of the inlet opening 54 the second warm partial airflow 20 into the second mixing chamber 14 , It therefore deletes a proportion of the second warm partial air flow determined essentially by the area ratios 20 in the fireplace 68 into it. This proportion of the second warm partial airflow 20 Therefore, it is essentially without mixing with the second cold partial air flow 22 immediately after entering the mixing zone 66 again from the second mixing chamber 14 led out. A relevant mixing with the second partial cold air flow 22 did not take place here, leaving only some cooling off of the footwell outlet 40 for the rear area exiting conditioning airflow 25 opposite the incoming second warm partial airflow 20 took place.

The not of the entrance opening 52 of the fireplace 68 captured part of the second warm partial airflow 20 will be in the mixing zone 66 with the at the fireplace 68 passing second cold partial air stream 22 As a result, a significant cooling occurs. Therefore emerges from the laterally located rear panel outlet 38 a much cooler second conditioning airflow 24 out. It can be clearly seen that the flow path 70 the warm partial airflow 20 practically straight through the second mixing chamber 14 extends. It can also be seen that the flow path 72 of cold partial airflow 22 not straight through the second mixing chamber 14 extends. The flowing in the horizontal direction second cold partial airflow 22 meets after his entry into the second mixing chamber 14 on an inclined surface, which serves as a baffle 56 is trained. This baffle 56 directs the cold partial airflow 22 in the vertical direction, so that it is in the area of the mixing zone 66 in the opposite direction to the warm partial airflow 20 flows. In the mixing zone 66 form the flow paths 70 and 72 the warm and the cold partial air flow an angle α with each other, which is in the illustrated embodiment in the range of 135 °. Here are the skilled person many opportunities to adapt the supply of mixing in the "cross mixer" partial air flows within wide limits of the structural conditions of the conception of the air conditioning.

The size of the mixing zone 66 in which are the warm and cold partial air currents 20 . 22 partially mixing, in the embodiment shown is essentially determined by how far the fireplace 68 into the center of the second mixing chamber 14 protrudes. Thus, the temperature difference of the generated air streams 24 and 25 in particular by the dimensions of the fireplace 68 be determined.

3 shows a perspective partial sectional view of the second cutting chamber 14 seen from the main module towards the panel outlet 38 seen for the fund area. Clearly visible is the center in the second mixing chamber 14 arranged fireplace 68 on the three sides of the second cold partial airflow 22 is flowed around. The side right and left of the fireplace 68 passing flow paths 72 lead a substantial portion of the incoming cold partial airflow 22 Panelauslass 38 for the fund area. In this case, only a slight mixing occurs with those portions of the warm partial air flow 22 not on the opening cross-section 52 of the fireplace 68 be recorded. The on the middle running flow path 72 flowing proportion of the cold partial air flow 22 however, it comes into intensive contact with the opening cross-section 52 of the fireplace 68 captured fraction of the warm partial airflow 22 , He is intensively mixed with this and the Fußraumauslass 40 led for the fund area. Out 3 it can be seen that the fireplace 68 as a flow regulator for both the second partial cold air flow 22 as well as for the second warm partial airflow 20 acts.

Finally, it should be noted that it is readily possible to vary the supply of hot and cold partial air flows to the mixing chamber compared to the discussed embodiment for the practical realization of working according to the "cross mixer" concept mixing chamber, in particular to swap because of gravitational influences or a buoyancy in the dimensions in question of the mixing chamber of the "cross mixer" are practically negligible.

Out 3 Finally, the various outlets for conditioned air flows are visible, the rear module 10 are formed. By introducing a centrally arranged parting plane, the single-zone rear module shown 10 be further developed in a simple way to a two-zone rear module, which then two separately controllable second mixing chambers 14a and 14b formed. From the second mixing chamber 14 lead a rear panel outlet 38 and a rear footwell outlet 40 for the fund area out. From the outlet 38 flows a second (regardless of the first conditioned air flow 8th ) Conditionable cooler airflow 24 out. From the outlet 40 another warmer conditionable air stream flows 25 whose temperature is in a fixed ratio to the temperature of the second conditioned air stream 24 stands.

In addition, it should be noted that all the above-described assignments of the outlets of the air conditioning system according to the invention 1 to be understood by way of example. Of course it is possible that of the air conditioning 1 provided differently conditioned air flows freely to the various ventilation outlets of the vehicle. In particular, the specified temperature differences between Fußraumauslässen on the one hand and panel or Defrostauslässen on the other hand to understand by way of example and can be tailored to the requirements of the vehicle manufacturer.

The fluidically active actuating elements shown, such as closing and mixing flaps, can for example be mounted on shafts and actuated by means of conventional servomotors, in particular stepper motors. The control of these active control elements is preferably carried out via a central air conditioning control, which receives the commands of the user of the motor vehicle and adjusts the control elements suitable for the implementation of the user input.

LIST OF REFERENCE NUMBERS

1

Multi-zone air conditioning

2

Main climate control module

3

Air supply module

4

first heat exchanger

6

second heat exchanger

7

further front conditionable air flow first front conditionable air flow (= first conditionable air flow)

8e

first front right conditioned airflow

8b

first front left conditioned airflow

9

second front conditionable airflow

9e

second front right conditioned airflow

9b

second front left conditionable airflow

10

fond module

12

first mixing chamber

12a

first right mixing chamber

12b

first left mixing chamber

14

second mixing chamber

14a

second right mixing chamber

14b

second left mixing chamber

16

first warm partial airflow

18

first cold partial airflow

20

further warm partial airflow

22

second cold partial airflow

24

first rear conditionable airflow (= second conditioned airflow)

24a

first rear right conditioned airflow

24b

first rear left conditioned airflow

25

second rear conditionable airflow

25a

second rear right conditioned airflow

25b

second rear left conditioned airflow

26

heating element

28

third flow path

29

first flow path

30

fourth flow path

31

second flow path

32

filter

34

body

36

fan

38

Panel outlet rear

38a

right panel outlet rear

38b

left panel outlet rear

40

Footwell outlet rear

40e

right footwell outlet rear

40b

left footwell outlet rear

42

defrost outlet

42a

right defrost outlet

42b

left defrost outlet

44

front panel outlet

44a

front right panel outlet

44b

front left panel outlet

46

front footwell outlet

46a

front right footwell outlet

46b

front left footwell outlet

50

joint

52

Opening cross section of the fireplace

56

baffle

58

first angled mixing flap

60

mixing flap

62

flap

64

second angled mixing flap

66

mixing zone

68

fireplace

70

first flow path

72

second flow path

74

Inlet cold partial airflow

76a

right rear connection outlet

76b

left rear outlet outlet

Claims (10)

Air conditioning ( 1 ) for the air conditioning of a motor vehicle interior with a mixing chamber ( 14 ), which is arranged by means of controlled mixing of a hot and a cold partial air flow ( 20 . 22 ) in a mixing zone ( 66 ) at least one warmer and one colder conditioned air stream ( 24 . 25 ), characterized in that in the mixing chamber ( 14 ) a. the inlet opening of the warm partial air flow ( 20 ) opposite an outlet ( 40 ) for the warmer conditioned airflow ( 25 ) is arranged, so that a substantially rectilinear flow path ( 70 ) between the inlet opening and the outlet ( 40 ), and b. between the entrance opening ( 74 ) of the cold partial air flow ( 22 ) and the outlet ( 38 ) of the colder conditioned air stream ( 24 ) flow-conducting means are arranged, which the flow path ( 72 ) between the inlet ( 74 ) and the outlet ( 38 ) so that i. the flow paths ( 70 . 72 ) of the warm partial air flow ( 20 ) and the cold partial air flow ( 22 ) in the mixing chamber ( 14 ), where at the crossing point of the hot and cold partial air flows ( 20 . 22 ) the mixing zone ( 66 ), and ii. the warm and the cold partial airflow ( 20 . 22 ) in the mixing zone ( 66 ) are conducted in countercurrent. Air conditioning ( 1 ) for the air conditioning of a motor vehicle interior with a mixing chamber ( 14 ), which is arranged by means of controlled mixing of a hot and a cold partial air flow ( 20 . 22 ) in a mixing zone ( 66 ) at least one warmer and one colder conditioned air stream ( 24 . 25 ), characterized in that in the mixing chamber ( 14 ) a. the entrance opening ( 74 ) of the cold partial air flow ( 22 ) opposite an outlet ( 38 ) for the colder conditioned airflow ( 24 ) is arranged, so that a substantially rectilinear flow path ( 72 ) between the inlet ( 74 ) and the outlet ( 38 ), and b. between the inlet opening of the warm partial airflow ( 20 ) and the outlet ( 40 ) of the warmer conditioned air stream ( 25 ) flow-conducting means are arranged, which the flow path ( 70 ) between the inlet opening and the outlet ( 40 ) so that i. the flow paths ( 70 . 72 ) of the warm partial air flow ( 20 ) and the cold partial air flow ( 22 ) in the mixing chamber ( 14 ), where at the crossing point of the hot and cold partial air flows ( 20 . 22 ) the mixing zone ( 66 ), and ii. the warm and the cold partial airflow ( 20 . 22 ) in the mixing zone ( 66 ) are conducted in countercurrent. Air conditioning ( 1 ) for the air conditioning of a motor vehicle interior according to claim 1 or 2, characterized in that the mixing zone ( 66 ) is dimensioned so that the warm and the cold partial air flow ( 20 . 22 ) in the mixing zone ( 66 ) mix only incompletely. Air conditioning ( 1 ) for the air conditioning of a motor vehicle interior according to claim 1 or 2, characterized in that to limit the extent of the mixing zone ( 66 ) flow-conducting means in the mixing chamber ( 14 ) are provided. Air conditioning ( 1 ) for the air conditioning of a motor vehicle interior according to claim 4, characterized in that as a flow-conducting means a chimney ( 68 ) in the mixing chamber ( 14 ) is arranged. Air conditioning ( 1 ) for the air conditioning of a motor vehicle interior according to claim 5, characterized in that the chimney ( 68 ) in the flow path of the warm partial air flow ( 20 ) in the mixing chamber ( 14 ) downstream of the mixing zone ( 66 ) is arranged. Air conditioning ( 1 ) for the air conditioning of a motor vehicle interior according to claim 6, characterized in that the chimney ( 68 ) an opening cross-section ( 52 ), which is smaller than the cross-sectional area of the inlet opening of the warm partial air flow ( 20 ) into the mixing chamber ( 14 ). Air conditioning ( 1 ) for the air conditioning of a motor vehicle interior according to claim 5, characterized in that the chimney ( 68 ) in the flow path of the cold partial air flow ( 22 ) in the mixing chamber ( 14 ) downstream of the mixing zone ( 66 ) is arranged. Air conditioning ( 1 ) for the air conditioning of a motor vehicle interior according to claim 8, characterized in that the chimney ( 68 ) an opening cross-section ( 52 ), which is smaller than the cross-sectional area of the inlet opening ( 74 ) of the cold partial air flow ( 22 ) into the mixing chamber ( 14 ). Air conditioning ( 1 ) for the air conditioning of a motor vehicle interior according to claim 1 or 2, characterized in that as a flow-conducting means an impact surface ( 56 ) is trained.

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