DE202017105468U1 - Heat exchange device - Google Patents

Abstract

Heat exchange apparatus for exchanging heat energy between a first gas mass flow (10) and a second gas mass flow (12) comprising a high efficiency heat exchanger (14) with a minimum efficiency of 75%, one upstream of the heat exchanger (14) in the flow direction of the second gas mass flow (12) Pressure change device (18) which is adapted to change the pressure of the second gas mass flow (12), wherein the pressure difference between the first (10) and the second gas mass flow (12) in the heat exchanger (14) is at most 0.5 bar.

Description

The invention relates to a heat exchange device for exchanging heat energy between a first gas mass flow and a second gas mass flow.

Heat exchangers are basically known and are used for example in ventilation systems. In this case, the temperature of a first gas mass flow, which is also called the primary flow, is changed, in particular lowered and / or increased, by means of a second gas mass flow, which is also called secondary flow.

So far, however, occur energy losses, which must be compensated by other measures.

Also known is the so-called Brayton cycle, which is also called Joule cycle. The ideal Brayton cycle involves four stages: isentropic compression of a gas that heats up, an isobaric exchange of heat energy, an isentropic release of the gas, and an isobaric release of heat to the surrounding atmosphere.

Under real conditions, the four stages are as follows: an adiabatic process for compression, an isobaric process for heat exchange, an adiabatic process for relaxation, and an isobaric process for heat release.

This process was originally used for piston engines, but only made its breakthrough with the development of turbojet engines. This process is also used in pressurized cabins for airplanes, whereby a turbine is used for air conditioning of the cabs by utilizing the cabin pressure and so-called bleed air is used. There, however, occur in the heat exchanger high pressure differences between the gas mass flows, which deteriorates the efficiency due to the resulting robust construction.

It is therefore an object of the invention to provide a heat exchange device for exchanging heat energy between a first gas mass flow and a second gas mass flow having a high efficiency.

The solution to this problem is achieved by the subject matter of claim 1.

According to the invention, heat energy is exchanged between a first gas mass flow and a second gas mass flow. In particular, the heat energy is transferred from the second gas mass flow to the first gas mass flow. However, a heat exchange in the opposite direction is conceivable.

Both gas mass flows are preferably the same gas, preferably air.

Before the pressure changing device, the pressure of the first and / or second gas mass flow may correspond to the ambient pressure. The gas mass flows may in particular have the same pressure at the beginning. In particular, the gas mass flows are thus not previously compressed or decompressed, as is the case for example with engine air.

The heat exchange device includes a high efficiency heat exchanger with a minimum efficiency of 75%. Older heat exchangers have a significantly lower efficiency, so that according to the invention recourse is had to modern heat exchangers, preferably air-to-air heat exchangers.

In particular, the minimum efficiency of the heat exchanger may be 80%, 85%, 90% or 95%. The higher the minimum efficiency of the heat exchanger, the higher the overall efficiency of the heat exchange device.

In the flow direction of the second gas mass flow, a pressure change device is arranged in front of the heat exchanger, which is designed to change the pressure of the second gas mass flow, in particular to decrease or increase.

In order to lower the pressure, the pressure-changing device can be designed as a pressure-release device or comprise a pressure-release device. The gas can be expanded, for example, to a larger volume.

The expander may be e.g. around a filter, a valve, a throttle, a divergence tube, a Venturi suction in the inlet, e.g. tangentially operating turbine wheel, a radial turbine and / or an axial turbine act.

To increase the pressure, the pressure changing device may be formed as a compressor or comprise a compressor. The gas can be compressed in it, for example, to a smaller volume.

The compressor may be, for example, a (simple) ramjet inlet, a (specially designed) ramjet scoop, a convergence tube, an axial compressor, a centrifugal compressor and / or a centrifugal compressor.

The pressure difference between the first and the second gas mass flow in the heat exchanger is a maximum of 0.5 bar. It was surprising that such low pressure differences are possible in modern, highly efficient heat exchangers. In particular, the efficiency of the heat exchanger depends on whether small differential pressures between the primary and secondary currents are sufficient to overcome losses in efficiency. Therefore, highly efficient components are used according to the invention. The heat exchanger may preferably comprise fins. The slats are comparatively thin.

In particular, the maximum pressure difference is 0.45 bar, 0.4 bar, 0.35 bar, 0.33 bar, 0.3 bar, 0.25 bar, 0.2 bar, 0.15 bar or 0.1 bar. Preferably, the pressure difference is at least 0.01 bar, 0.02 bar, 0.03 bar 0.04 bar, 0.05 bar, 0.06 bar, 0.07 bar, 0.08 bar, 0.09 bar or 0 , 1 bar.

Characterized in that the pressure of at least one gas mass flow is varied before entering the heat exchanger, the efficiency of the heat exchange device compared to conventional heat exchangers without a pressure change device is significantly increased.

According to the invention, the ideal Brayton process is used to extract energy from a gas mass flow and to transfer it to another gas mass flow, preferably without the expense of additional energy, ie at least substantially without energy loss.

The ideal Brayton cycle is getting as close as possible. For this purpose, highly efficient components are used, namely a heat exchanger and at least one pressure changing device. Preferably, two pressure-changing devices are used, in particular a compressor and a pressure-release device.

Preferably, the energy is transferred exclusively through the heat exchanger. Energy is transferred from a hot, compressed or a cold, relaxed secondary stream gas to the primary stream using a high efficiency heat exchanger.

By using the high efficiency heat exchanger, a small differential pressure is sufficient for the process to raise the energy content of the secondary flow above the level of the initial environment or to lower it to below the level of the environment at the exit of the heat exchanger during cooling. The higher the efficiency of the heat exchanger, the lower differential pressures are necessary.

In particular, by a slight manipulation of the pressure in the secondary flow, the temperature is adjusted so that the temperature can be raised by the heat exchange within a high-efficiency heat exchanger on the prevailing at the output of the primary flow - and thus the secondary current - level for heating or lowered for cooling ,

The invention enables the transfer of thermal energy from one gas mass flow to another gas mass flow beyond the original capability of a heat exchanger.

The heat exchange device can be used in particular for temperature control, in particular cooling and / or heating, of battery compartments. Also in automobiles, especially in electric cars, the heat exchange device can be used.

In particular, by combining a high efficiency heat exchanger with a low pressure compressor, an increase in the temperature level beyond the loss of efficiency of the heat exchanger may occur.

Further developments of the invention can be found in the dependent claims, the description and the accompanying drawings.

According to one embodiment, a further pressure changing device is arranged after the heat exchanger, which is adapted to change the pressure of the second gas mass flow to ambient pressure, preferably to increase or decrease.

In particular, the pressure change after the heat exchanger is opposite to the pressure change before the heat exchanger. Thus, a previously compressed gas mass flow, for example, after the heat exchanger by the further pressure changing device is relaxed. If the gas mass flow before the heat exchanger, however, relaxed, he is back-compressed by the further pressure-changing device after the heat exchanger.

The pressure change is thus in particular temporary. Efficiency losses in the heat exchanger can thereby be absorbed and the supply air can be lifted beyond the heat exchanger beyond the level of the atmosphere prevailing there.

In accordance with a further embodiment, one pressure-changing device is designed as a compressor, in particular a compressor, and the other pressure-changing device as a pressure-release device, in particular a turbine. Thus, a gas mass flow can be compressed or expanded before entering the heat exchanger. After the heat exchanger, the gas mass flow can be correspondingly relaxed again or recompressed.

According to a further embodiment, a pressure variation device arranged in the flow direction of the first gas mass flow upstream and / or downstream of the heat exchanger is provided, which is designed to change the pressure of the first gas mass flow. In this way, the pressure of the first gas mass flow can be changed.

Preferably, a pressure change device before the heat exchanger and a further pressure change device are provided after the heat exchanger for the first gas mass flow. A pressure changing device arranged after the heat exchanger can change the pressure of the first gas mass flow in particular to ambient pressure.

In particular, the first gas mass flow can be compressed or expanded before it enters the heat exchanger. After the heat exchanger, the first gas mass flow can be correspondingly relaxed again or recompressed.

In particular, for the manipulation of the physical states of two dependent or independent gas mass flows, a slight compression or decompression of one or both gas mass flows can take place from the ambient atmosphere before they flow into a highly efficient heat exchanger. Subsequently, a gas mass flow or both gas mass flows can be relaxed or compressed after leaving the heat exchanger back to ambient pressure, while in the heat exchanger, the heat of the warmer stream is transferred to the heat of the colder stream with very high efficiency. This has the purpose of controlling the physical states of one or both streams.

For example, the temperatures of the gas mass flows may be affected by heating the primary flow, either by compression of the secondary flow or by decompression of the primary flow. It is also conceivable that the primary stream is cooled, either by decompression of the secondary stream or by compression of the primary stream.

According to a further embodiment, one, in particular the further, pressure-changing device is coupled to the other pressure-changing device of the second gas mass flow and can drive it in particular. For example, a decompressor, in particular a turbine, can be exploited even better.

Alternatively or additionally, one, in particular the further, pressure-varying device can be coupled to a drive device of the first gas mass flow and / or a pressure change device of the first gas mass flow arranged before or after the heat exchanger and drive it in particular. Preferably, this can save an additional motor for the primary current. For example, a propeller of the drive device of the primary flow can be driven by the turbine of the secondary flow.

It is conceivable, for example, a firm connection of both devices on a shaft, so that the energy absorption of the turbine can be returned to the propeller. In particular, via a belt and the propeller for the other power could be driven with.

Alternatively, the further pressure-changing device can also run free and, for example, drive a generator.

According to a further embodiment, a dehumidifying device for dehumidifying the first and / or second gas mass flow is provided. A gas mass flow can be dried in this way. The heat exchange device can thus also be used as a dehumidifier.

In particular, during the expansion of a gas stream within the heat exchanger, condensed liquid can be rinsed off via at least one siphon and / or at least one valve. Also, when relaxing after leaving the heat exchanger auskondensierende liquid fail to open.

According to a further embodiment, a moistening device is provided for moistening the first and / or second gas mass flow. A gas mass flow can be moistened in this way. The heat exchange device can thus also be used as a humidifier.

In particular, when compressing a gas stream within the heat exchanger, liquid can be injected via nozzles. Also, when recompressed after leaving the heat exchanger liquid can be injected via nozzles.

In particular, the temperatures of the gas mass flows can be influenced in such a way that the proportion of solids within the gas streams is influenced, in particular in the sense of a sublimation and / or resublimation. To resublimate when relaxing a gas stream within the heat exchanger particles or when relaxing after leaving the heat exchanger resublimierende particles fall open. Furthermore, it is possible that sublimate particles in the compression of a gas stream within the heat exchanger or that sublimate when recompressed after leaving the heat exchanger particles.

In particular, the temperatures of the gas mass flows can be influenced in such a way that icing of the gas mass flows takes place or is prevented. For this purpose, the primary stream is compressed during cooling and thus the secondary stream is heated in the direction of exhaust air. Furthermore, it is possible that during heating, the secondary flow is compressed and thus the primary flow in the Außenluftansaugung heated early. In addition, the secondary stream can be evacuated to form ice in the primary stream or can be evacuated to form ice in the secondary stream, the primary stream.

The applications may preferably be combined in any form and / or order. Thus, the state of the gas mass flows can be manipulated in particular simultaneously for several applications.

In particular, both streams can be compressed and / or decompressed in parallel in the heat exchanger in parallel and / or simultaneously, as long as the pressure difference in both flows in the heat exchanger is sufficiently low. The pressure difference amounts to a fraction of the atmospheric pressure. The state of the gas mass flows can thereby be manipulated simultaneously for several applications.

Preferably, the method may follow a placement, e.g. between two confined spaces, exchanging a same gas between the rooms or recirculating one or two different gases or in an open atmosphere, so that both sides of the process are open and have the same gas. Also, a placement between an open atmosphere and a closed space, either as an exchange of gas masses or as circulation of the gas in a closed space is possible.

In particular, the structure of the method in exchanging and / or recirculating gas streams compressing and / or expanding in the primary flow and / or secondary flow or both work. The method or the components of the heat exchange device can be combined as desired in parallel, serial, loop-shaped or any other conceivable arrangement.

According to a further embodiment, the heat exchanger is designed as a countercurrent heat exchanger. The first gas mass flow is passed in parallel in the heat exchanger, but in the opposite direction to the second gas mass flow. The route on which the heat exchange takes place is thus comparatively long. In this way, the efficiency increases compared to rectangularly oriented gas mass flows.

According to a further embodiment, the heat exchanger is designed as a countercurrent-channel heat exchanger. The heat exchanger thus comprises at least two adjacent channels. In this case, the first gas mass flow is guided in one channel while the second gas mass flow is conducted in the other channel.

Preferably, a plurality of channels are provided, in which parts of the first and parts of the second gas mass flow are alternately guided. The channels may preferably be formed lamellar.

In particular, the channels can also be arranged one above the other in different planes or layers. Thus, a sandwich structure may result from multiple levels of parallel channels.

This cross-sectional geometry results in a high efficiency of the heat exchanger.

The invention also relates to a method for exchanging heat energy between a first gas mass flow and a second gas mass flow, in particular by means of a heat exchanger device according to the invention.

The pressure of a second gas mass flow is changed. Subsequently, the second gas mass flow is fed to a high efficiency heat exchanger with a minimum efficiency of 75%.

In the heat exchanger, heat energy is exchanged with the first gas mass flow, wherein the pressure difference between the first and the second gas mass flow is at most 0.5 bar.

Thermal energy can be transferred from one gas mass flow to the other gas mass flow, specifically beyond the energy level of the original gas mass flow. This is realized by compressing and heating a secondary gas mass flow before entering the heat exchanger. In the heat exchanger it can, at least almost, give off its entire temperature difference to the oncoming primary stream. Upon exiting the temperature during the relaxation falls to the ambient pressure below the level of the ambient temperature.

Conversely, the method allows thermal energy to escape from a gas mass flow, and in particular below the level of the incoming energy state, by decompressing the secondary stream prior to entry into the heat exchanger and thus being subcooled. In the flow through the heat exchanger, the secondary flow absorbs the sensitive enthalpy of the oncoming primary flow and cools it below the level of the inlet state. After leaving the heat exchanger, the secondary flow is compressed back to ambient pressure. The resulting extra heat is released to the environment as the heat taken from the primary flow.

The pressure of the primary stream can remain in particular at ambient pressure.

Both methods, ie compression and decompression, can be used for both heating and cooling, depending on which power is to be used.

For heating, the temperature of the first gas mass flow is in particular raised above the ambient temperature at the outlet. For cooling, the temperature of the first gas mass flow is preferably lowered below the ambient temperature at the outlet.

According to one embodiment, the pressure of the second gas mass flow is changed to ambient pressure after leaving the heat exchanger.

For controlling the temperature of the gaseous primary stream, the gaseous secondary stream can be heated in particular by means of compression or cooled by means of decompression. Subsequently, heat is exchanged between the two streams in a high efficiency air-to-air heat exchanger. Subsequently, the secondary flow is expanded or recompressed to ambient pressure.

In this case, the method can also be applied so that both streams are compressed or expanded for the course in the heat exchanger, the differential pressure, however, allows additional heat transfer and still small enough to avoid mechanical changes in the heat exchanger.

According to a further embodiment, the heat energy between the first gas mass flow and the second gas mass flow is exchanged exclusively by the heat exchanger. Additional energy is therefore not supplied to the system, resulting in a high efficiency.

Furthermore, in particular only the Brayton cycle is used. Another cycle, especially a composite cycle system, as used for example in heat pumps use, is not provided.

Furthermore, according to the invention, no storage is provided for the first gas mass flow and / or the second gas mass flow.

All of the embodiments and components of the device described herein are particularly adapted, e.g. by means of a control device to be operated according to the method described herein. Furthermore, all embodiments of the device described here and all embodiments of the method described here can each be combined with each other, in particular also detached from the specific embodiment, in the context of which they are mentioned.

The invention will now be described by way of example with reference to the drawings. Show it:

1 a schematic representation of an embodiment of a heat exchange device according to the invention,

2 a schematic representation of another embodiment of a heat exchange device according to the invention,

3 a graph showing the dependence of the pressure difference on the temperature,

4 a schematic representation of various dependencies,

5 a schematic representation of another embodiment of a heat exchange device according to the invention,

6 a schematic representation of another embodiment of a heat exchange device according to the invention,

7 a schematic representation of various dependencies,

8th a schematic representation of another embodiment of a heat exchange device according to the invention,

9 a schematic representation of another embodiment of a heat exchange device according to the invention, and

10 a schematic representation of another embodiment of a heat exchange device according to the invention.

First, it should be noted that the illustrated embodiments are merely exemplary in nature. The features of one embodiment may also be arbitrarily combined with features of another embodiment.

If a figure contains a reference numeral which is not explained in the directly associated descriptive text, reference is made to the corresponding preceding or following statements in the description of the figures. Thus, the same reference numerals are used for the same or comparable components in the figures and these are not explained again.

1 shows a heat exchange device for exchanging heat energy between a first gas mass flow 10 and a second gas mass flow 12 ,

The heat exchange device comprises a high efficiency heat exchanger 14 and a drive device 16 , which is adapted to the first gas mass flow 10 drive.

In the drive device 16 it may be a device capable of producing a gas mass flow 10 to transport.

Furthermore, the heat exchange device comprises a first pressure change device 18 which the second gas mass flow 12 drives and changes its pressure.

For compaction, any method and / or device can be used which is able to compress a gas mass flow or to put in overpressure, in particular also taking advantage of different static and dynamic pressures.

For example, the pressure change device 18 be designed as a compressor and the second gas mass flow 12 compress. In particular, a compressor wheel can be used as a device for compression.

A second pressure changing device 20 For example, it can be designed as a decompressor and the second gas mass flow 12 relax back to the ambient state.

In particular, an overpressure can be built up between the compressing device and the relaxing device or the negative pressure can be established between the relaxing device and the compressing device, which can amount to less than half, in particular one third, of the atmospheric pressure.

The pressure difference between the primary stream 10 and the secondary current 12 can be less than half, in particular one third, of the atmospheric pressure, independent of the total pressure versus the atmosphere in the two flow channels 10 . 12 ,

For relaxation, any method and / or device can be used which is able to relax a gas mass flow or put it into negative pressure or partial vacuum. For example, a turbine wheel can be used as a device for relaxation.

In particular, the device for relaxation can be used as a turbine wheel in combination with a device for compaction, e.g. as a coupled compressor-turbine combination.

For example, the device for transporting the gas mass flows 10 . 12 coupled to a turbine and / or the compressor or a compressor-turbine combination.

A propeller may be provided for transporting an open flow or a turbine wheel for relaxing the flow or the compressor wheel for compressing the flow. A combination of two or three rotors can also have adjustable propeller blades in order to be able to generate different pressures, in particular negative pressure and / or overpressure, at different volume flows.

Preferably, the propeller, the turbine wheel and / or the compressor wheel have adjustable propeller blades, around the flow direction of the two mass flows 10 . 12 reverse.

In particular, the setting angle of the compressor wheel can be coupled to the setting angle of the turbine wheel.

The pitch angle of the propeller may be e.g. be coupled to the setting angle of the compressor wheel and / or to the setting angle of the turbine wheel.

Following the second law of thermodynamics, the heat energy goes inside the heat exchanger 14 uniform from the warm side to the cold side. The efficiency of the heat exchanger 14 is influenced by many factors. One of them is the heat capacity of the gas mass flows 10 . 12 , These should be secondary 12 and primary current 10 be aligned as well as possible, ie for the same gases, the mass flows should 10 . 12 be identical.

But other factors also play a role, such as the ability of partitions to transfer heat. The partitions between the gas mass flows 10 . 12 in the heat exchanger 14 should be as thin as possible. This enables high efficiency and thus high efficiency.

The heat exchanger 14 may preferably comprise fins.

Since the partitions are relatively sensitive, no large pressure differences between the two streams 10 . 12 occur. Large differences in pressure could in particular lead to leaks and / or deformations, but ultimately to a balancing of the pressures.

The efficiency or the efficiency η of the heat exchanger 14 is defined by the relation between the transferred heat to the heat difference between the two sides a and b of the heat exchanger 14 , without manipulation of the pressure, ie on both sides a and b there is atmospheric external pressure.

The following formula stands for the efficiency η (ZuL) on the supply air (ZuL) side b of the primary flow 10 , The secondary current 12 could under the same conditions have a different efficiency η (FoL) in the exhaust air (FoL): η (CaR) = (T _10b - _10a T) / (T _b - T _a).

It is also possible a state in which in both streams 10 . 12 the same pressure prevails, ie no pressure is manipulated in the short term if this is necessary for the application of the method, for example when switching from overpressure to underpressure.

2 shows a heat exchange device under normal atmospheric conditions. A second pressure changing device 20 is not intended.

Under ideal conditions, the efficiency of a heat exchanger would be 100%, ie both temperatures on the outside a and inside b will be in the streams 10 . 12 completely transferred. According to the invention, the temperature level of the primary stream is also here 10 when heating above the level raised at the output or lowered when cooling below the appropriate level.

Technologically feasible are air-to-air countercurrent channel heat exchangers 14 Efficiencies of up to approx. 95%. The loss in the thermal transfer adds aerodynamic friction resistance, the so-called pressure loss. This can be reduced by enlarging the heat exchanger 14 or reduction of the mass flow. Technologically feasible is in particular a pressure loss performance of about 1% of the heat transfer capacity.

Further losses are caused by the drive device 16 and the pressure changing device 18 caused. The efficiency of these components must therefore also be taken into account.

The secondary current 12 can with the help of the pressure change device 18 be compressed or expanded on the exhaust side b to assume a short-term higher or lower temperature than the environment on the exhaust side b, with the aim of the temperature in the primary stream 10 to manipulate accordingly.

An optional relaxer 20 , which may be configured as a throttle, may serve to increase the pressure within the heat exchanger 14 to maintain.

wobei der Isentropenexponent κ verschiedene Konstanten für bestimmte Gase annimmt. Für Luft beträgt κ ungefähr 1,4 und bei idealen Gasen steigt der Isentropenexponentexponent maximal auf 1,66. Je höher der Exponent, desto leichter kann durch Kompression die Temperatur gesteigert werden. The temperature as a function of pressure is described by the formula of Poisson. It defines the relationships between two temperatures and corresponding pressures of a gas:

wherein the isentropic exponent κ assumes different constants for certain gases. For air, κ is about 1.4, and for ideal gases, the isentropic exponent increases to a maximum of 1.66. The higher the exponent, the easier the compression of the temperature.

The International Standard Atmosphere [ISA] is defined by the following values: p _ISA = 101325 Pa, T _ISA = 15 ° C = 288 K, ρ _ISA = 1.225 kg / m ³ .

muss ein Druck von 102.562 Pa erzeugt werden, um die Umgebungstemperatur um 1°C zu erhöhen, d.h. der Umgebungsdruck müsste um 1.237 Pa für 1°C erhöht werden. According to the formula

it is necessary to generate a pressure of 102.562 Pa to increase the ambient temperature by 1 ° C, ie the ambient pressure should be increased by 1.237 Pa for 1 ° C.

The higher the ambient temperature, the lower pressure increases are necessary. Since an object of the invention is the cooling and heating of human environments, the ambient temperature is placed in the comfort zone of 21 ° C (294 K). To heat air from 21 ° C by 1 ° C, now only 1,211 Pa are needed.

3 shows the change in temperature (in ° C) when the pressure changes (in Pa) graphically in a curve.

Now the pressure in the secondary flow 12 changed according to the formula, its temperature is mitverändert and supplies the heat exchange device with a corresponding additional enthalpy.

If the absolute difference Δ of the temperature is higher than the thermal efficiency loss (1 - η) in the heat exchanger 14 . | .DELTA.T | > η · (T _{b -Ta} ), then the supply air in the primary stream 10 be raised above the level on the exhaust side for heating, or be brought under the condition of the exhaust air side b for cooling under vacuum condition.

As gas, air can be used. In principle, however, other suitable gases and / or gas mixtures are also conceivable.

With the heat exchange device according to the invention, for example, a building on the side b with the help of the outside air from the side a can be heated.

For example, set a temperature of 20 ° C inside, outside a temperature of 0 ° C is assumed and the heat exchanger 14 has an efficiency of 90%, so would the heat exchanger 14 already provide the building with 18 ° C warm air. To close the missing gap of 2 K and prevent the building from cooling down, the secondary current becomes 12 According to the invention applied with 3.677 Pa. This is the pressure that is needed to control the secondary flow 12 in addition to heat up to 3K. At 90% now 20.7 K to the primary stream 10 passed, ie it is heated. When the secondary current 12 on the outside of a relaxed again to ambient pressure, he loses again the 3 K, so that the exhaust air falls below 0 ° C.

Thus, the problem of icing can occur. According to the invention, the water contained in the air can be manipulated. This refers to the physical conditions such as icing and defrosting, humidification and dehumidification, sublimation and resublimation.

Another example concerns dry air. In summer, for example, the outside temperature should be 30 ° C and it should be introduced at 20 ° C in the supply air. The heat exchanger 14 Without the procedure, it would already supply the building with 21 ° C. To overcome the 1 K gap, the process would have to be in secondary current 12 build a negative pressure of -1,206 Pa to cool both streams accordingly. In subsequent recompression, the exhaust air will increase to about 30 ° C.

The building could also be cooled by replacing decompression of the secondary flow 12 a compression of the primary stream 10 he follows. First, the outside air, ie the primary flow on the side a, would then be compressed by 1 K in the heat exchanger 14 from the non-manipulated exhaust air, so the secondary flow 12 cooled on the side b, and fall by another Kelvin at the final relaxation.

Thus, the process of the present invention can cool or heat in both directions with both compression and decompression.

Since the relative humidity changes with temperature, the absolute humidity as a constant mass flow within the heat exchanger 14 but remains the same, the compression and decompression method also allows the humidity to be influenced beyond the condensation limits of the environment.

During compression, in particular additional moisture can be absorbed by evaporation. In a decompression in particular additional water can be deposited in a condensate formation. For this, states from the Mollier diagram can be approached accordingly.

By absorbing additional water in the gas phase, the air cools adiabatically as it releases energy to the water. Conversely, the formation of condensate causes the air to adiabatically heat up, absorbing energy from the water. Taking advantage of these effects, the method can be used in particular additionally for adiabatic cooling and / or reheating.

Heating, cooling, humidifying, dehumidifying, sublimating, resublimating, icing and / or deicing constitute various applications of the invention.

Placement is the manner in which the method can be used in relation to its environment. In particular, there are three ways of placing the method:
First, an energy transfer between two streams in a completely open environment. Second, an energy transfer between two streams, both coming from a closed environment and flowing into the closed environment. Third, an energy transfer between two streams, with one side closed and the other side representing the open environment.

Various dependencies between applications ANW, placements PLA and superstructures AUF are in 4 shown.

For the applications ANW, e.g. to heat HE, cool KÜ, humidify BF, dehumidify EF, freeze VE, defrost EE, resublimation RE and / or sublimation SU act.

In the placement PLA, there are e.g. the variants open / open o / o, closed / closed g / g and / or closed / open g / o.

When set to UP, exchange air OFF and / or circulating air UML can be provided. The primary stream 10 and / or the secondary current 12 can experience compression KO and / or expansion EX.

Due to the PLA placement, it is possible to operate the method according to the invention either in circulating air UML or in exchange AUS. These alternative possibilities are referred to as the construction UP of the method.

In recirculation UML, the two atmospheres are through the walls of the heat exchanger 14 separated from each other, the streams 10 . 12 feed themselves. When replacing OFF, both atmospheres can pass through the heat exchanger 14 through, both currents 10 . 12 feed the opposite atmosphere.

The energy transfer between two streams 10 . 12 can take place in different environments. For example, the environment can be completely open.

When the method is applied in an open environment on both sides, the same atmosphere and state is on both sides a, b. When one stream is heated by the process and the other is cooled, both streams become 10 . 12 shortly after leaving the process again assume the atmospheric state.

In principle, there are two possibilities for setting up the method with this PLA placement, which is open on both sides:
First, the expansion of the secondary current leads 12 to a temperature increase in the exhaust air, so the secondary flow 12 on page a, and a temperature drop in the supply air, ie the primary flow 10 on page b.

Second, the compression of the secondary current leads 12 to a temperature drop in the exhaust air, so the secondary flow 12 on page a and a temperature rise in the supply air, ie the primary flow on page b.

For example, a heat exchanger 14 used in an open environment, an open primary stream 10 to heat or cool without having to subject it to pressure or other manipulation, eg to avoid danger or contamination. Possible applications are similar to a hot air gun, a hair dryer, a cooling fan, eg for brakes, a humidifier, eg in cellulose production, a drying device eg in the household, a snow gun, an ice-producing device eg in the food industry, dry ice extraction in the pharmaceutical industry and / or a device for extracting particles in the gas phase.

5 shows a heat exchange device in which an energy transfer between two streams 10 . 12 Both come from a closed environment and flow into a closed environment.

The heat exchange device can thus be placed in a closed on both sides environment. In particular, in this case only the secondary current 12 manipulated.

With circulating air UML, both environments work separately. In particular, different gases can be used here. With exchange air OFF, one closed environment operates the other. This results in four options for a structure:
First, with replacement air OFF, expansion EX of the secondary flow will occur 12 to a temperature increase in the exhaust air, so the secondary flow 12 on page a, and a temperature drop in the supply air, ie the primary flow 10 on page b.

Secondly, with exchange air OFF, the compression KO of the secondary flow 12 to a temperature drop in the exhaust air, so the secondary flow 12 on page a, and a temperature increase in the supply air, ie the primary flow 10 on page b.

Third, in recirculating air UML, the expansion EX of the secondary current leads 12 to a rise in temperature in the vicinity of the exhaust air, so the secondary flow 12 on page a, and a temperature drop in the vicinity of the supply air, ie the primary stream 10 on page b.

Fourth, with recirculation UML, the compression KO of the secondary flow 12 to a temperature drop in the environment of the exhaust air, so the secondary flow 12 on page a, and a temperature rise in the vicinity of the supply air, ie the primary stream 10 on page b.

The last two cases with setup UP in circulating air UML only reach the temperature difference due to the pressure difference. Because the streams 10 . 12 in the heat exchanger 14 bring each other back to their level, makes the process with heat exchanger 14 no sense. It would be simpler to directly manipulate the pressure within the closed environment.

This is due to the fact that PLA placement with the AUF structure in recirculating air UML can not exceed the physical limits of the enthalpy exchange with the countercurrent plus the temperature difference generated by the pressure difference. For example, if the pressurization produces 10 K of temperature, then both environments will differ only by 10K. The disadvantage is that a real system will permanently bring energy into the closed system, which would lead to overheating.

Unlike the situation of construction looks up in exchange air OFF. As the currents 10 . 12 in the heat exchanger 14 Heat or cool down at their own countercurrent, the temperatures go further and further apart by the process. The physical limit of the method in such a construction is ON at a point where the temperature difference is from the power loss of the heat exchanger 14 reached the temperature difference from the pressure manipulation.

Or a state of liquefaction by cold is achieved. This is also possible with the heat exchange device according to the invention.

Assumed in both closed environments is an initial state of 20 ° C, the efficiency of the heat exchanger is 90% and the method can be in secondary flow 12 establish a ΔT of 10 K (Δp = 12.629 Pa), then the temperatures diverge until the heat exchanger 14 the 10 K can not overcome. In this case, however, this would be a temperature difference of 100 K. With an efficiency of 95%, the distance would be 200 K. If an ideal gas is used - after all, PLA is a closed environment - with κ = 1.66 , eg at 20 ° C, a heat exchanger 14 Efficiency of 90% and a Δp of 10% of the atmosphere, the limit of the distance would be 113 K, ie on one side would prevail -36 ° C and on the other side 76 ° C.

The heat exchange device thus allows the generation of extreme temperatures without much energy. The only energy that the process needs is the drives 16 . 18 to transport the currents 10 . 12 , Maybe the drive can 16 for the primary stream 10 omitted, because the system here anyway on the primary stream 10 comes to a pressure equalization. The AUF structure therefore enables the production of cold gases.

A construction UP with exchanging flow is in 6 shown. This can be used to transport dissolved liquids in a gas and then to extract RE by condensation or resublimation. For example, water can be sprayed on the warm side. This condenses on the cold side and is removed there again. Also, for the extraction of water from the air, the process can be used without much energy, for example, with the help of greenhouses.

In particular, a cold and a warm environment can be generated at the same time. For example, data centers need to be cooled for better computer performance, while surrounding spaces for people and / or plants should be better heated. In this setup, heat can be extracted from the data center and released into a habitable room without much energy expenditure.

Since plants need CO2 for better growth, in particular a build-up AUF can first take place in recirculating air UML and later, when oxygen is needed, switch to an exchange air OFF. The advantage of a construction AUF in a two-sided closed placement PLA is therefore also that gases separated from the environment can be used.

In a construction AUF in exchange air OFF with PLA closed on both sides and an application as energy storage is conceivable. This allows the process to pump large volumes of heat energy from one side to the other.

Through the heat exchange device can also be an energy transfer between two streams 10 . 12 take place with one side closed and the other side representing the open environment.

Particularly advantageous is the heat exchange device, which is placed such that one side works in an open environment and the other side works with a closed environment. The open environment can be formed, for example, by the near-Earth atmosphere.

Placement PLA open / closed o / g allows setup UP of the process with different possibilities in combination of power, pressure and circuit, which are each different applications possible. Here is the primary stream 10 and / or the secondary current 12 be manipulated, in overpressure or negative pressure, with circulating air UML or exchange air OFF.

With a placement PLA between open and closed environment, there are thus eight possibilities for a construction AUF:
First, with replacement air OFF, expansion EX of the secondary flow will occur 12 to a temperature drop in the supply air, ie the primary stream 10 on page b, and a temperature rise in the exhaust air, so the secondary flow 12 on page a.

Secondly, with exchange air OFF, the compression KO of the secondary flow 12 to a temperature rise in the supply air, ie the primary stream 10 on page b, and a temperature drop in the exhaust air, so the secondary flow 12 on page a.

Third, in recirculating air UML, the expansion EX of the secondary current leads 12 to a temperature drop in the closed environment of the supply air, ie the primary stream 10 on page b, and a rise in temperature in the open environment of the exhaust air, so the secondary flow 12 on page a.

Fourth, with recirculation UML, the compression KO of the secondary flow 12 to a temperature increase in the closed environment of the supply air, ie the primary stream 10 on page b, and a temperature drop in the open environment of the exhaust air, so the secondary flow 12 on page a.

Fifth, with replacement air OFF, expansion EX of the primary flow will result 10 to a temperature rise in the supply air, ie the primary stream 10 on page b, and a temperature drop in the exhaust air, so the secondary flow 12 on page a.

Sixth, when exchange air OFF, the compression KO of the primary flow 10 to a temperature drop in the supply air, ie the primary stream 10 on page b, and a temperature rise in the exhaust air, so the secondary flow 12 on page a.

Seventh, with circulating air UML, the expansion EX of the primary flow leads 10 to a temperature increase in the closed environment of the supply air, ie the primary stream 10 on page b, and a temperature drop in the open environment of the exhaust air, so the secondary flow 12 on page a.

Eighth leads in compression UML the compression KO of the primary flow 10 to a temperature drop in the closed environment of the supply air, ie the primary stream 10 on page b, and a rise in temperature in the open environment of the exhaust air, so the secondary flow 12 on page a.

Below are examples of all eight setup options. The explanations are limited to atmospheric air as an exemplary gas mixture.

The order does not match the list above.

In exchange air OFF, the compression KO of the secondary flow leads 12 an increase in the temperature of the supply air and a drop in the temperature of the exhaust air, where b represents closed, warm rooms and a the cold outside atmosphere.

This structure is typical for example for an application for the heating of premises. The outgoing exhaust air is in front of the heat exchanger 14 compresses and transfers the additive heat in the heat exchanger 14 to the colder outside air passing to the heating supply air. Behind the heat exchanger 14 relaxes the exhaust air and cools down under outdoor air.

An advantage of this design is that the cold, dry outside air in the warmer part of the supply air can be enriched with moisture.

In exchange air OFF, the expansion EX, ie decompression of the primary current leads 10 an increase in the temperature of the supply air and a drop in the temperature of the exhaust air, where b represents closed, warm rooms and a the cold outside atmosphere.

This structure also allows the heating of the premises. The outside air is in front of the heat exchanger 14 relaxed, for example by means of a filter, and thereby cooled again, then warms up inside the heat exchanger 14 at the oncoming secondary flow 12 and additionally heats up beyond the room level during recompression.

An advantage of this construction is that the relaxation of the outside air is additionally cooled and in this way moisture can be deposited as soon as the temperature falls below the condensation limit. Drying is not desirable in buildings in winter. In vehicles, however, a dry warm air for quick removal of fog can be used very positively.

Also in this structure, the device for compressing the air lies on the inside of the closed space. For the application that the structure is operated here only with ram air, a negative pressure in the primary stream 10 be generated for example by means of a Venturi arrangement.

In exchange air OFF, the expansion EX leads, ie decompression of the secondary flow 12 to a temperature drop in the supply air and a temperature increase in the exhaust air, where b is closed cool premises and a the hot outside atmosphere.

Such a construction allows the cooling of closed rooms with warmer fresh air from the outside. The room air or exhaust air is in front of the entrance to the heat exchanger 14 Relaxed and thus falls in the temperature below the level of indoor air. The warm countercurrent cools down accordingly and reaches the room as a cold supply air. The exhaust air falls behind the compressor back to atmospheric external pressure and heats up.

As more energy is used for cooling worldwide than for heating, this design is a very useful application.

The compressor is preferably arranged on the outside of the structure.

However, moisture can occur. Moist, warm outside air may contain more gaseous water than the cold indoor air can carry. If the relative humidity during cooling in the heat exchanger 14 If the condensation limit of 100% humidity is reached, the enthalpy transferred is henceforth wasted for the formation of the condensate. By contrast, the sensitive temperature barely drops. When the water condenses, it releases its energy from the gas phase to the surrounding air and heats the air back.

The heat exchanger device according to the invention makes it possible to find optimal structures for the various purposes.

7 shows a phase diagram. Different applications are shown depending on the phases solid fe, liquid fl and gas ga. The big arrow represents the energy E.

Whenever a substance is part of a gas phase and is dissolved in an atmosphere, such as water in the air, the corresponding substance exchanges its energy E with the surrounding atmosphere. Lose that Water at energy E and migrates in a lower energy phase, then it releases energy E to the air and heats it and vice versa.

In recirculation UML, expansion EX leads, ie decompression of the secondary flow 12 to a temperature drop in the closed environment of the supply air and a temperature increase in the open environment of the exhaust air.

This construction circumvents the problem of condensate formation when cooling closed rooms to a certain extent. The warm outside air is at the beginning of the heat exchanger 14 as far as possible decompressed and cooled. The cooling must be brought by decompression below the level of indoor air. In the heat exchanger 14 takes the primary air 10 then the corresponding temperature.

The air in the primary stream 10 can be considered as a separate gas. For example, this eliminates the disadvantage of moist outside air.

Another advantage is that the compressor and the expander are located on the outside.

This structure is particularly suitable for use in vehicles and / or missiles when a high back pressure is available. The dynamic pressure would have to be calculated according to Bernoulli's equation p _stat = p _a - p _dyn be converted into negative pressure, for example by means of a Venturi device. This allows cooling without atmospheric compensation, since circulating air.

In recirculation UML the compression KO of the primary flow leads 10 to a temperature drop in the closed environment of the supply air and a temperature increase in the open environment of the exhaust air.

This structure results in a cooling of the closed environment. The air heated by the compression KO is cooled in the outside air and then further cooled by the decompression. This method depends on the temperature of the outside air. Inside, the temperature can not fall below the outside air minus the heat of compression. Nevertheless, this design offers advantages that are optimal in certain applications.

The fact that the components for compression and relaxation are inside the closed space, they can be protected against environmental influences. Furthermore, it is also possible to build up a unique atmosphere inside or to use a foreign gas.

This structure is therefore suitable e.g. for the cooling of closed electronic housings, control cabinets and / or brake housings.

The manipulation within the closed space allows further applications, such as humidification BF, resublimation RE or icing VE, ie applications for energy loss by relaxing in the primary stream 10 ,

In exchange air OFF performs the compression of the primary flow 10 to a temperature drop in the supply air and a temperature increase in the exhaust air.

A compressed stream cools when released from the overpressure. Thus, this structure is also suitable for cooling. Warm outside air becomes the entrance to the heat exchanger 14 compressed and additionally heated. The relative humidity drops. In the heat exchanger 14 cools the primary stream 10 now on the secondary stream 12 from. After leaving the heat exchanger 14 the cool supply air is released and additionally cooled.

An advantage of this method over decompression of the secondary flow 12 it is that the problem of condensate formation is shifted to the part of the expansion in the process by lowering the relative humidity.

As a result, lower temperatures can be generated with the same absolute differential pressure. The process is moved away from the condensation boundary. The condensation is quasi delayed by this structure.

Another implementation of this design is the ability to pure back pressure for the compression KO of the primary stream 10 to use.

If, for example, a heat exchanger 14 used with an efficiency of 95%, then a temperature difference ΔT of 1 K would produce a maximum temperature range of 20 K. This is sufficient to air-condition a vehicle from 40 ° C to 20 ° C inside air. The following equation calculates the dynamic pressure:

For the production of 1 K, a pressure increase of 1,211 Pa at 20 ° C is required. This back pressure results in a speed v of 44.5 m / s (160 km / h). Since the speed is quadratic, at 300 km / h already a ΔT of about 3.5 K is reached, which gives a range of 35 K at η = 90%. Thus, with an outside temperature of 55 ° C a fresh air of 20 ° C is possible and that without energy consumption.

A device for receiving the dynamic pressure can in particular be designed as a specially designed aerodynamic air inlet.

In particular, missiles with even higher speeds could cool the electronics and / or sensors in this way.

In recirculation UML, the expansion EX, that is, the decompression of the primary current 10 to a temperature increase in the closed environment of the supply air and a temperature drop in the open environment of the exhaust air.

The drive energy receiving part of the structure is within the heated, closed environment. It is the device for relaxing the exhaust air or room air in the primary stream 10 , For example, a turbine, a device for driving the secondary current 12 eg a fan and mainly a compressor for recompression of the primary flow 10 in the supply air, for example, an axial compressor, the same time the primary current 10 drives.

Despite this additional energy, the process with this construction does not exceed the recompression temperature, since the room air at the heat exchanger 14 is cooled. Nevertheless, the structure is suitable for heating closed rooms when it is achieved to use energy-saving and efficient drive components.

In particular, the method is suitable for dehumidification EF, sublimation SU and / or de-icing EE in critical systems. It is advantageous that the drive components can be in the closed space, e.g. to encapsulate the sound.

In recirculation leads the compression of the secondary flow 12 to a temperature increase in the closed environment of the supply air and a temperature drop in the open environment of the exhaust air.

When the secondary current 12 It is compressed in circulating air, so it is with the help of the heat exchanger 14 the resulting heat to the primary stream 10 pass, in this case heat. The secondary current 12 is fed with ambient air UML but again and again from the outside temperature. The primary stream 10 So it can not grow beyond the outside temperature plus the temperature of the pressure increase. Thus, the process is limited to a slight manipulation of the temperature. However, such a structure can be used to maintain or heat closed environments that do not require fresh air or that do not produce gas, since little energy is needed for the heating process.

According to one embodiment, the components of the heat exchange device can also be combined with one another in different forms.

As already mentioned, it is possible to combine several applications. Furthermore, it is possible to combine the structure, for example by the method of Umluft UML is switched to exchange air OFF. Also, it is possible that the procedure applies to both streams 10 . 12 is applied. Alternatively or additionally, a switching within a current between compression KO and decompression can take place.

For the latter case, in particular a compressor-expander combination of positive pressure can be reversed to a decompressor-compressor combination with negative pressure. Such a solution is relatively easy to accomplish, for example by means of axial rotors with adjustable wings. At the same speed, the compressor has a higher angle of attack than the subsequent wheel, which can act as a turbine with a lower angle of attack.

For decompression, the front rotor has a lower angle of attack and decelerates the flow, while the rear rotor with higher angle of attack accomplishes both vacuum and transport of the flow. It is also conceivable a firm connection of both devices on a shaft, so that the energy absorption of the turbine can be returned to the propeller.

In particular, via a belt or other forms of transmission and the propeller for the other power could be driven with.

However, rotors with adjustable setting angle also have another important influence on the heat exchange device and the method. This requires from the drives both a mass flow, as well as a pressure difference. So while the mass flow can be varied with the speed of the rotors, the setting angle allows control of the pressure difference in the heat exchanger 14 and thus influencing the temperature.

Certain temperatures can thus be approached directly. It can be heated or cooled immediately and desired temperatures can be targeted. A lead time is not required. Unnecessary energy is not wasted.

Combinations of different constructions, on the other hand, allow the process to satisfy different applications simultaneously with the same gas mass flow. Thus, e.g. cool a build while dehumidifying another build.

It is also possible to combine UML recirculation constructions in connection with 8th to be discribed. The task of the construction is the tempering of a closed electronic room or a control cabinet. The room should be hermetically sealed off from weather conditions. Desired application is cooling and / or heating. The best solution is a placement PLA closed / open g / o with build-up in convection UML.

A combination of structures allows in particular two approaches. On the one hand, as described, a rotor combination with adjustable wings can be used on the inside of the method. For heating, the combination decompresses inside the heat exchanger 14 and for cooling it compresses.

A second, cost-effective solution without adjustable rotors is a compression on both sides of the heat exchanger 14 , depending on the application. For example, an electronics room 22 to heat, is the lying in the open atmosphere secondary flow 12 compressed, the primary stream 10 remains at its atmospheric pressure and is only at the heat exchanger 14 heated and by the drive device 16 transported.

For cooling, the secondary current is reversed 12 left under atmospheric pressure and merely transported. The second pressure change device 20 serves only as a drive.

Now the primary current 10 with the aid of the first primary pressure changing device 16 and the second primary pressure changing device 17 compressed, in the heat exchanger 14 cooled in the outside air and loses after the relaxation further to temperature.

The cooling capacity in the heat exchanger 14 must be in the electronics room 22 corresponding heat output correspond. This results from the specific heat capacity multiplied by the mass flow, the heat capacity in turn being determined by the temperature difference.

With the increase of the mass flow, therefore, the heat output can be increased, but also with the temperature difference. Is the temperature difference and thus the pressure difference in the heat exchanger 14 small, then this can be compensated by a large mass flow. An optimum here would be the minimal loss of energy.

The method in this example is particularly suitable for very large applications such as e.g. Greenhouses and data centers, but also for very small electronic devices such as Phones or portable computers.

A parallel combination with exchange air OFF is also possible. However, the situation is more complex in atmospheres that are consumed by living things or machines and that need to be changed, ie ventilated. Humans must be guaranteed a habitable environment, the maintenance of which is considered critical. While the proportion of certain gases must be kept, the habitable temperature has its limits. Another factor is the moisture, ie the gas phase of certain liquids.

In the external environment on earth no direct influence on the factors can be taken. Within e.g. However, a building or greenhouse must have a positive influence on the temperature, humidity and / or gas content.

Desired applications are heating HE, humidifying BF and deicing iron EE in cold weather as well as cooling KÜ with dehumidifying EF in warm weather.

This is done by placing PLA closed / open g / o with build UP in exchange air OFF.

During the winter, room air dries quickly and leads to the spread of viruses. Heating by means of decompression of the primary stream 10 is therefore only an insufficient solution, since the cold outside air may be further dehumidified, which is not desirable. Therefore, it is advantageous to use the secondary flow 12 to compress. This simultaneously counteracts icing VE in the outside air.

During the summer, the atmosphere carries a lot of water due to its energy content. This does not even mean high humidity, but when entering a refrigerated building this can lead to very high humidity. If the cooled air falls below the condensation limit, it may fog in the building on surfaces such as e.g. Furniture, walls and / or plants are coming. This easily leads to spores that can endanger the health of humans and plants. If the air has been cooled down accordingly, it can often reach the room with 100% humidity in the supply air.

The formation of condensate during the flow through the heat exchanger 14 brings the problem of rewarming through the energy delivery to the primary stream 10 with himself. The condensation essentially consumes the enthalpy that would otherwise be taken from the temperature. This problem of atmospheric cooling is also referred to as wet adiabatic temperature change.

If a gas which does not contain a condensing out liquid is cooled according to the method according to the invention, it is possible to cool it down to the temperature range of ΔT / (1-η). However, as soon as condensate which has formed is prevented by reheating, the process can come under the starting point in the exhaust air with the aid of the manipulation of the pressure with the supply air, progressive cooling is no longer possible. In that case, the pressure manipulation produces a certain enthalpy, around which the primary flow 10 can be cooled. A support by a cooling exhaust air, however, is no longer.

This double problem can be solved in particular by cooling the air by decompression to such an extent that it carries an absolute humidity which corresponds to a relative humidity of e.g. 50% in the comfort area corresponds. This would be e.g. at about 10 ° C and 100% relative humidity of the case.

However, such a negative pressure would already correspond to almost half the atmospheric pressure and each heat exchanger 14 to fail, as the differential pressure between the two streams 10 . 12 is too big.

A parallel, simultaneously relaxing procedure can solve this problem. The process will be parallel in both streams 10 . 12 applied. In this way, the differential pressure can still be kept minimal or even zero.

9 branches off a parallel decompression with exchange air OFF.

With such a parallel, simultaneously decompressed structure AUF in exchange air OFF and open / closed placement PLA, three applications can be simultaneously controlled. The volume flow is controlled by the pressure difference between the outside and inside b. Dehumidification EF is via the pressure difference in the heat exchanger 14 in the primary stream 10 controlled and the temperature is above the pressure difference in the heat exchanger 14 in the secondary current 12 controlled.

The precipitating liquid behind the expander must still before the heat exchanger 14 be removed by, for example, at least one siphon and / or valve. The negative pressure in the heat exchanger 14 should be kept upright.

For example, icing in the secondary stream 12 To avoid this, it should only be decompressed to a minimum of 0 ° C, ie about 20,000 Pa at 20 ° C.

To the pressure difference to the primary flow 10 to be kept low, say 10,000 Pa, the primary flow in this case would have to be evacuated between 10,000 Pa and 30,000 Pa.

It should be remembered that the primary stream 10 to increase the recompressed pressure in temperature again. It is therefore to seek a compromise between desired humidity and temperature. The external conditions also have a certain influence on this.

Furthermore, a serial combination in exchange air OFF is possible, as exemplified in 10 is shown.

Accordingly, a heat exchange device may be provided in which the moisture is first degraded in a first structure and then the temperature is lowered in a second structure. Different components are therefore combined serially. Such a construction is also referred to as a serial, simultaneously relaxing process.

For example, the outside air can be used for cooling, since there is enough available.

Suppose the environmental situation a consists of tropical weather with hot humid air. Just before tropical rain, the air may e.g. do not absorb any more moisture. Cooling in this case would waste almost all enthalpy on the formation of raindrops.

In order to prevent this, in a first construction, the primary current 10 compressed to get away from the condensate limit. When walking through the heat exchanger 14 becomes the primary stream 10 on the outside air a in a third gas mass flow 13 , which is also called tertiary flow, cooled again to outside air level.

During the subsequent expansion, the primary stream cools 10 then off and excretes condensate in a first step. Now to continue cooling, the primary current 10 then passed to a second setup, where it is at a decompressed secondary flow 12 continues to cool, but not as strong as desired due to the now safe condensation. Therefore, the secondary current should 12 be relaxed to the maximum, ie as much as the heat exchanger 14 withstand pressure difference. The secondary current 12 condenses after recompression to hot exhaust air, so the secondary flow 12 on page a (in the middle).

With this method in a simultaneously relaxing structure, for example, 26 ° C at 100% humidity can be achieved. It should be remembered that the process extracts about 100 kJ per m ^{3 of} air, ie cooling energy.

It is also conceivable a combined combination of above structures in exchange air OFF and recirculation UML.

The procedures in Umluft UML are subject to the limitations of pressure manipulation. On the other hand, they are good ways to move within the given limits.

For example, in the home ventilation, the comfort range is between 20 ° C and 26 ° C. The process can operate in circulating air between 10 ° C and 36 ° C outside air, if the defined pressure difference, for example, allows up to 10 K heat transfer.

For a healthy indoor air, a minimum amount of fresh air must also be guaranteed through replacement. However, this can be reduced to the required oxygen consumption. If, however, the outside atmosphere also deviates in temperature, the proportion of replacement air must also be increased in order to absorb the temperature losses.

A combination between exchange desire AUS and circulating air UML is called unified combination of superstructures.

In order to use the method for several applications at the same time, combinations in parallel, serial and / or loop-shaped construction can be provided. In addition to heating HE, cooling KÜ, humidifying BF, dehumidifying EF, sublimation SU, resublimation RE, icing VE and deicing EE can also be multiple applications.

Through an appropriate combination, the highest possible transfer of energy can be obtained.

LIST OF REFERENCE NUMBERS

10

first gas mass flow, primary flow

12

second gas mass flow, secondary flow

13

third gas mass flow, tertiary flow

14

heat exchangers

16

Drive device, first primary pressure change device

17

second primary pressure changing device

18

first pressure changing device, compressor

20

second pressure change device, expander

21

third pressure-changing device

22

electronics compartment

a

outside

b

Inside, exhaust side

ANW

application

PLA

placement

ON

construction

HE

Heat

CT

Cool

BF

moisten

EF

dehumidify

VE

ice up

EE

de-ice

RE

resublimation

SU

sublimation

o / o

Open / Open

g / g

closed / closed

g / o

closed open

OUT

replacement air

UML

circulating air

KO

compression

EX

expansion

fe

firmly

fl

liquid

ga

gaseous

e

energy

Claims (9)

Heat exchange device for exchanging heat energy between a first gas mass flow ( 10 ) and a second gas mass flow ( 12 ) comprising a high efficiency heat exchanger ( 14 ) with a minimum efficiency of 75%, one in the flow direction of the second gas mass flow ( 12 ) in front of the heat exchanger ( 14 ) arranged pressure change device ( 18 ), which is adapted to the pressure of the second gas mass flow ( 12 ), whereby the pressure difference between the first ( 10 ) and the second gas mass flow ( 12 ) in the heat exchanger ( 14 ) is a maximum of 0.5 bar. Heat exchange device according to claim 1, characterized in that after the heat exchanger ( 14 ) a further pressure change device ( 20 ) is arranged, which is adapted to the pressure of the second gas mass flow ( 12 ) to change to ambient pressure. Heat exchange device according to claim 2, characterized in that the one pressure change device ( 18 . 20 ) as the compressor, in particular compressor, and the other pressure-changing device ( 20 . 18 ) is designed as a decompressor, in particular turbine. Heat exchange device according to one of the preceding claims, characterized in that a flow direction of the first gas mass flow ( 10 ) before and / or after the heat exchanger ( 14 ) arranged pressure change device ( 16 . 17 ) is provided, which is adapted to the pressure of the first gas mass flow ( 10 ) to change. Heat exchange device according to one of the preceding claims, characterized in that a pressure change device ( 20 ) of the second gas mass flow ( 12 ) with the other pressure changing device ( 18 ) of the second gas mass flow ( 12 ), a drive device ( 16 ) of the first gas mass flow ( 10 ) and / or one before or after the heat exchanger ( 14 ) arranged pressure change device ( 16 . 17 ) of the first gas mass flow ( 10 ) is coupled. Heat exchange device according to one of the preceding claims, characterized in that a dehumidifying device for dehumidifying the first ( 10 ) and / or second gas mass flow ( 12 ) is provided. Heat exchange device according to one of the preceding claims, characterized in that a moistening device for moistening the first ( 10 ) and / or second gas mass flow ( 12 ) is provided. Heat exchange device according to one of the preceding claims, characterized in that the heat exchanger ( 14 ) is designed as a counterflow heat exchanger. Heat exchange device according to one of the preceding claims, characterized in that the heat exchanger ( 14 ) is designed as a countercurrent channel heat exchanger.

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