DE102009057095A1 - Waste heat supplied heat utilization device - Google Patents

Abstract

A heat utilization device WNV is described, which achieves a high overall efficiency of 0.45 <η _{PM + WNV} <0.69 using the cooling and / or exhaust heat of a primary machine PM in a resource BM cycle.
As a PM are used an internal combustion engine VM, stationary or installed in a (power) vehicle, a gas / steam turbine power plant, a combined heat and power plant or a (biogas) burner, and BM as a superheated steam or a mixture of a supercritical high pressure steam plus the superheated steam and / or plus parts of the exhaust gas to obtain enthalpy of mixing.
Furthermore, a use of WNV is provided as an air or exhaust gas compressor under storage, as a mechanical supercharger PM, which, as well as the WNV, using the stored compressed air / des-exhaust gas can be operated as a compressed air / exhaust engine or as a booster and then gives a total combined PM + WNV combined ratio of 1.6 <P _{PM + WNV} / P _PM <2.3.

Description

introduction

The aim of the invention is to obtain as efficiently as possible all the waste heat from the cooling and / or the exhaust gas of a primary source / machine (PM),
I. a burner, II. A gas + steam turbine (GT + DT) or III. a rotary or rotary piston (DK) internal combustion engine (VM) using a heat utilization device (WNV) in a single resource supply circuit to use.

The WNV consists of a / the operating medium (BM) promoting and compressing compression device, a compressor or a heat pump (WP), and a subsequent expansion device, a steam / gas engine (DM).

The function of the conveyor / compression / heat pump WP for the steam or gaseous BM or that of a high-pressure pump for the initially liquid BM is essential for the high effective efficiency η _{PM + WNZ of} the conversion of the primary machine PM with WNZ system:
0.41 <η _{PM + WNZ} <0.69
even at a speed of U = 3000 / min (1500 / min) for a VM up to η _{VM + WNZ} = 0.5 and for a GT + DT system as PM η _{(GT + DT) + WNZ} = 0.7.

The WNV delivery / compression device consumes practically nothing up to a maximum of 30% (as heat pump WP) of the total additional power P _{WNZ of} the WNZ system, while z. B. the turbine compressor of a GT about 40% of the P _GT power needed.

The serious disadvantage of a DT is that it requires a large mass flow rate at high pressure. The high pressure can be built up energetically favorable only in the liquid state of the BM, and thus in the BM circulation after a DT chain a liquefaction of the entire BM is necessary. This is usually done by external cooling and performs the high condensation as useless or less few waste heat.

The PM, VM, GT or burner (BR) waste heat must provide its heat of vaporization prior to heating the BM, ie before each cycle, which is about the same as that used to heat the BM from e.g. B. T ₀ = 30 ° C to T ₂ = 530 ° C must be applied.!

For the WNV, here z. B. is designed as a rotary piston engine (DKM), must be, depending on the BM mixture, only a quarter to the whole of the BM liquid state, which is then acted upon by a high-pressure pump with the high, supercritical pressure, while the non-condensed BM directly as Steam is recirculated back to the circuit and then mixed with the high pressure steam in two of the four BM versions provided in the first component of the WNV.

The advantage of high-pressure / superheated steam (exhaust gas) BM mixtures is that a BM state with low entropy (high-pressure steam) is mixed with a high entropy (hot steam or exhaust gas), which increases the usable exergy.

The heat energy saved in this way of about 30% to 50% can be used to heat the BM to higher temperatures or to prepare a larger batch BM. Since both, the molar amount of BM and its temperature increase approximately in proportion to the available heat energy - but compete with each other -, the recoverable WNV additional power P _{WNV will increase} approximately linearly with the introduced heat energy.

This and the advantageous use of the DKM, which already achieves comparable work with significantly lower pressure and volume flow, is the explanation for the achievable, high values of the additional power P _WNV and the high efficiency η _{WNZ of} the WNV, see below.

The DKM is equipped here with two inlets and outlets per DKM disc and then delivers three cylinder chamber volumes full of BM per one revolution of the respective rotary piston.

The presented here WNZ plant then contributes in a cycle system, alone taking advantage of the waste heat of a PM, z. For example, for a VM or a (GT + DT) plant, a relative additional power to the PM at
17% <P _WNZ / P _{VM (GT + DT)} <61%,
already for a speed of U = 3000 / min (1500 / min), z. B. the DKM as WNV.

In particular for a WNV behind a VM as PM, the advantage for operating with a BM steam is that in one circulatory system the waste heat of the cooling water in the low temperature range (NT) is used to evaporate the BM, and the entire exhaust heat of the VM to the other Heating the BM to higher temperatures is available.

The conversion of (waste) heat into mechanical energy of combined heat and power plants behind a VM thus equals that of a modern gas and steam (combined cycle) power plant and clearly outperforms it behind a GT + DT turbine.

The respective additional services P _WNZ with a VM or a GT + DT system or the increase in efficiency with a burner can, taking into account and including several relevant, realistic loss factors η _x between
0.75 <η _x <0.95, see below,
achieve comparable or even higher values, especially with the introduction of the planned additional functions of the WNV.

• 1. als mechanischer Luftverdichter (LV) durch Umkehrung der Beschickungsrichtung – in der Aufwärmphase des VM, bei niedrigen Drehzahlen und bei hoher Leistungsanforderung zur Aufladung des VM und der GT plus deren Feuerungsstelle, sowie
• 2. als LV und Abgasverdichter (AV) zur Rekuperation von Bewegungsenergie bei Schub- und Bremsvorgängen des VM betriebenen KFZ, bzw. im Unterlastbetrieb eines stationären VM, eines Brenners oder einer GT + DT Anlage – unter Abspeicherung der erzeugten Druckluft/des Druckabgases in einem Druckluftspeicher (DLS) und/oder einem Druckabgasspeicher (DAS) und – anschließendem kraftstofflosen/-armen Betrieb des VM bzw. der GT mit der abgespeicherten Druckluft/dem Druckabgas, sowie
• 3. als Booster unter Beschickung der WNV Anlage selbst mit der abgespeicherten Druckluft/dem Druckabgas über einen Druckminderer für starke Beschleunigungsvorgänge im VM betriebenen KFZ und zur Abdeckung von Spitzenlast bei einem stationären VM und bei einer GT + DT Anlage, unter gleichzeitiger Beschickung des VM bzw. der GT und deren Feuerungsstelle. Die Leistungsabgabe des WNV Booster kann dann die maximale Leistung der Primärmaschine PM in etwa erreichen oder sogar übertreffen, im kurzfristigen Betrieb z. B. des VM in einem KFZ oder längerfristig bei der DT + GT und der stationären VM Anlage, abhängig von der Menge (und dem Druck) der/des gespeicherten Druckluft/-abgases.

In addition, the WNV should and can be used in principle three other functions:

• 1. as a mechanical air compressor (LV) by reversing the feeding direction - in the warm-up phase of the VM, at low speeds and high power requirement for charging the VM and the GT plus their Feuerungsstelle, as well
• 2. as LV and exhaust gas compressor (AV) for recuperation of kinetic energy during thrust and braking operations of the VM operated vehicle, or under load operation of a stationary VM, a burner or a GT + DT system - under storage of the generated compressed air / the pressure exhaust gas in one Compressed air storage (DLS) and / or a pressure exhaust gas storage (DAS) and - subsequent non-fuel / low-power operation of the VM or the GT with the stored compressed air / the pressure exhaust gas, and
• 3. as a booster with the WNV system itself with the stored compressed air / pressure exhaust via a pressure reducer for strong acceleration operations in the VM operated vehicle and to cover peak load in a stationary VM and GT + DT system, while feeding the VM or the GT and its firing point. The power output of the WNV booster can then reach or even exceed the maximum power of the primary machine PM in about, in short-term operation z. B. the VM in a car or longer term in the DT + GT and the stationary VM plant, depending on the amount (and pressure) of the stored compressed air / -abgas.

Due to the / in the energy storage DLS / DAS stored compressed air / -abgas with 100 l to 300 l capacity, z. As in a car, which are comparable in their energy storage capacity with the battery storage of today's "Mild Hyprid" cars, all suitable auxiliary equipment in the car's converted to compressed air, such. B. brake booster, power steering and starter, etc.

This allows the VM in the car safely shut off while driving, z. B. when rolling up to red traffic lights and on gentle slopes.

Without including these uses, the combined heat and power plant can achieve an effective efficiency of:
η _{VM + WNZ} > 0.5 or η _{GT + DT + WNZ} > 0.70.

Taking advantage of the WNV booster function can be for the VM in the car under charging with the stored compressed air for a short time, z. Eg for a few minutes, the maximum power of the combined plant, P _{VM + WNV, max} , the maximum rated power of the VM, P _{VM, max} , can be more than doubled P _{VM + WNV, max} > 2.3 P _{VM, max} , see below.

Due to the savings effect of unneeded, multiple intermediate evaporation performance in case II, a GT + DT (GuD) plant, see below, and by operating the WNV plant with a 1: 1 BM mixture of high pressure and superheated steam, eg. B. of H ₂ O, there is an increased additional power of
P _WNV = 34 MW,
see description to 5a , to the assumed basic performances of the combined cycle power plant, of P _DT = 67 MW and P _GuD = 200 MW.

So then assuming for the GT + DT plant
P _{GT + DT} = 3 P _DT with P _GT = 2 P _DT and
P _{DT + WNV} = 1.51 P _DT
At least P _{GT + DT + WNV} = 3.51 P _DT results, ie an increase of 17%, (without counting the booster function of the WNV), which the efficiency η _{GuD + WNV} to values close to or above η _{GuD + WNV} > 70% brings.

For a gas and steam turbine plant can continue under charging the GT with the stored compressed air, which was generated with the LV function of the WNV and then stored, then with the elimination of the turbine compressor and the above assumptions,
P _{GuD + WNVBoost} > 5 P _DT , ie an increase by a factor of 1.61,
For use in peak load periods over a long period of time, depending on the stored quantity of the compressed air / compressed exhaust gas, see description to 5 ,

This is for a combined cycle power plant, the other great advantage of the combined WNV plant that they both as a heat-using device WNV and LV can be operated by storing the generated compressed air, with the possibilities described above, and no additional compressor is needed.

With the storage of the pressure exhaust gas and its subsequent use with the WNV as a booster and the VM as a pressure (air) exhaust gas engine residual heat content of the exhaust gas is also still widely used.

• – mit einem Biogas-Brenner in kleineren lokalen Anlagen, dessen Brenngas nicht als Brennstoff für einen VM oder eine GT genutzt werden kann, oder
• – mit einem stationären VM Aggregat, wie z. B. in Kraft-Wärme-Kopplungsanlagen (KWK) für Schulen, Schwimmbäder und Krankenhäuser, aber auch schon für Ein- und Mehrfamilienhäuser,
• – präferentiell mit einem Benzin oder Gas betriebenen Otto VM oder einer Drehkolbenmaschine (DKM), einem Wankel Motor, welcher schon bei niedrigen Drehzahlen eine hohe Abgastemperatur aufweist, und die dann als Kombianlage, stationär oder in einem KFZ betrieben, den Gesamtwirkungsgrad eines vergleichbaren Diesel VM deutlich übertrifft,
• – mit einem aufgeladenen Diesel VM für PKW, LKW oder Schiffe,
• – sowie mit einer mittleren GuD Anlage mit einer Leistung von bis zu 300 MW. – Auch ein kompakter Nachrüstsatz, z. B. für ältere PKW oder GuD Anlagen, mit einer eigenen Steuerung ist möglich.

The WNV plant can be used behind and with the following primary aggregates:

• - with a biogas burner in smaller local plants, whose fuel gas can not be used as fuel for a VM or a GT, or
• - With a stationary VM unit, such. B. in combined heat and power plants (CHP) for schools, swimming pools and hospitals, but also for single and multi-family homes,
• - Preferably with a petrol or gas operated Otto VM or a rotary piston engine (DKM), a Wankel engine, which has a high exhaust gas temperature even at low speeds, and then operated as a combined plant, stationary or in a car, the overall efficiency of a comparable diesel VM clearly surpasses,
• - with a charged diesel VM for cars, trucks or ships,
• - as well as with a medium-sized combined cycle power plant with an output of up to 300 MW. - Also a compact retrofit kit, z. B. for older cars or CCG systems, with its own control is possible.

With the combination of biogas burners or stationary VM aggregate plus WNV plant, their runtime can be significantly increased even in the summer, as more power is available for power generation and possibly network feed-in to the grid, and then lower residual heat, but on if necessary, elevated temperature level, see below, can continue to be used for hot water heating or as process heat.

In addition to gasoline and diesel, the VM in a motor vehicle or in a stationary unit can also preferably be operated with (natural) gas, the pressure vessels of which can then be used as DLS after the partial consumption of the gas.

It can be a one-component liquid / vaporous BM 11 '' . 11 or a mixture of high pressure steam 11 ' , z. B. H ₂ O _Hd , and superheated steam 11 , H ₂ O _d , and / or variable proportions of the exhaust gas 13 , whose temperature is still (far) in the high temperature range, can be used.

• – wobei der H₂O_Hd Dampf vorher durch hohe Druckbeaufschlagung mit p ~ p_krit, dem kritischen Druck des flüssigen BM 11'', z. B. H₂O_fl, und Erwärmung in WT’s durch die Kühlabwärme und durch das Abgas, z. B. des VM’s, auf Temperaturen T_fl,d > T_krit präpariert wurde, und
• – anschließend in der ersten Komponente der WNV, z. B. einer DKM, die Gemischbildung des H₂O_Hd mit dem H₂O_d und/oder dem Abgas stattfindet, unter Gewinnung von Mischenthalpie, und
• – die nachfolgende Entspannung unter weiterer Arbeitsleistung in den anderen WNV Komponenten, z. B. den (drei) restlichen Zylinderkammern der Zweischeiben DKM bis an die Taulinie oder in das Zweiphasengebiet des H₂O_d Naßdampfes erfolgt.

The highest values for the additional power of the WNV arise when the superheated, high-pressure BM steam 11 ' , H ₂ O _Hd , low entropy is mixed with either H ₂ O _d vapor 11 and / or with the (or parts of) the exhaust gas (es) 13 higher entropy, to the mixture BM 11 ' + 11 (+ 13 ) respectively. 11 ' + 13 .

• - wherein the H ₂ O _Hd vapor previously by high pressurization with p ~ p _crit , the critical pressure of the liquid BM 11 '' , z. B. H ₂ O _fl , and heating in WT's by the cooling waste heat and by the exhaust gas, z. B. of the VM, to temperatures T _{fl, d} > T _{crit was} prepared, and
• - Then in the first component of the WNV, z. B. a DKM, the mixture formation of H ₂ O _{Hd takes place} with the H ₂ O _d and / or the exhaust, with the production of mixing enthalpy, and
• - The subsequent relaxation under further work in the other WNV components, eg. B. the (three) remaining cylinder chambers of the two-disc DKM up to the tau line or in the two-phase region of the H ₂ O _d wet steam.

In general, it turns out that about a 1: 3-4 by mass mixture for the VM and a 1: 1-2 mixture for the GT + DT plant of high-pressure steam H ₂ O _Hd and superheated steam H ₂ O _d and / or Exhaust gas gives the best results for the additional power of the WNV plant, and thus the high values for
η _WNV and P _WNZ / P _{VM (GT + DT) are} achieved,
See the values given above and the values listed in Tab. 1 and 2.

Heat exchangers (WT) are required for all these WNV systems.

Particularly in the case of the VM units but also in the case of the biogas burner, possibly also in the case of a GT, a WT in the high-temperature region of the exhaust gas stream can simultaneously be used as a catalyst (CAT) by appropriate dimensioning and exhaust gas-side coating with catalyst noble metals, and if necessary a second, likewise exhaust-side coated WT as an oxidation catalyst with controlled air supply, in particular for a diesel engine as PM.

This reduces the reaction of the heat exchangers WT on the VM in a similar order of magnitude as in a modern VM with controlled catalysts, see 4 ,

State of the art

The good old steam engine (H ₂ O _d ) operated steam engine is in the smell of low efficiency. Thus, the DM's, which were developed for steam locomotives until 1957, at a maximum boiler pressure of H ₂ O _d of about 25 bar corresponding to a temperature of T = 225 ° C, a maximum mechanical efficiency of 13%, since the H ₂ O _d Steam at a temperature of about T = 100 ° C was blown through the chimney.

Before that has the exhaust steam flue gas by a negative pressure effect, z. B. with Giesl ejectors, and thus sucked more fresh air into the boiler, for more complete combustion of the heating coal. The efficiency of a corresponding, reversible, ideal Carnot machine, η _C = (T ₂ -T ₁ ) / T ₂ , (1) between the corresponding temperature reservoirs with T ₂ = 500 K and T ₁ = 373 K would be, without the Abdampfverluste, η _C = 0.25.

The charging of gasoline and diesel engines by an exhaust gas turbocharger (ATL) or a mechanical compressor and the operation of reciprocating engines with compressed air are known, as well as the turbine air compressor in front of a GT.

In the patent application DE 102 59 488 A1 "Heat engine" is a VM using the waste heat in two separate, closed equipment (BM) circuits, a low-temperature and a separate high-temperature circuit, each with a relaxation device, an improvement in the efficiency of a VM of 5% to 6% reached. It is assumed in each case from an initially liquid BM, which is conveyed by a pump and brought to operating pressure, evaporated in heat exchangers and heated.

In the present application, however, a single closed or a partially open circulation system is used for the BM, which is evaporated and / or preheated via evaporator VD and heat exchanger WT in a low-temperature (NT) range, the cooling of the VM or the End regions of the exhaust gas of the burner BR9 or the GT, and further heated by WT's in the high-temperature region of the exhaust gas of all PM's. The equipment consists of either BM steam or a mixture of high-pressure steam plus steam and / or exhaust gas and is pumped in separate stages of the WNV, compressed and / or relaxed under work, with a component for the BM mixtures is used as a clocked mixing chamber.

The use of WNV in the other, above and below described in more detail functions is inherently planned, given and claimed.

In the filed on 16.09.2008, but then withdrawn utility model application DE 102 59 488 A1 have been the basic idea of this application in approaches developed.

Today, combined gas / steam (combined cycle) power plants are used for the large-scale production of electrical energy and electricity, since a gas turbine GT alone has a comparatively low efficiency of η _GT ≲ 45%, because of the high power requirement (around 40% of the total power) of the turbine compressor and despite the very high inlet temperatures of 1200 ° C to 1400 ° C.

Because of the high outlet temperature of the exhaust gas of T _a = 550 to 650 ° C of GT, at an outlet pressure only slightly above atmospheric pressure, it makes sense to use the exhaust heat by means of heat exchangers to heat a vapor, usually H ₂ O _d , to operate with several DT stages. The disadvantage of the DT's is that they must be operated largely in the H ₂ O _d single-phase area, otherwise the turbine blades are removed by droplet formation.

A solution to this is to reheat the H ₂ O _d and use one or more medium pressure (MD) DTs as the second stage and use low pressure (ND) DTs as the third stage (s).

The ND DT is successful in this application also for larger units with a
GT + DT Total power of P _GuD ≲ 300 MW
replaced by a WNV plant, which then much further into the two-phase area, H ₂ O _d plus water H ₂ O _fl , can be operated into.

In the case of the WNVs described here, the delivery and the compression, z. B. the H ₂ O _Hd high-pressure steam or the H ₂ O _D vapor, in the above BM versions for the high pressure pump a fraction and for the WP to almost a third of the total WNV power.

characters

1 : Schematic diagram of a waste heat fed WNV heat utilization device, for three uses: I. behind an internal combustion engine VM, II. Behind a GT + DT system and III. behind a burner.

2a to c: TS diagrams for waste heat fed WNV cycle cycles for a VM (a) to (c) and a GT + DT plant (d) with the resource BM versions (1), (3) and ((4)) the start and end points) with m = mixture by thin arrows → indicated and na = not adiabatic correction ->:
(a) (1): H ₂ O _d + (b) (3): H ₂ O _Hd + H ₂ O _d X (c) ((4)): H ₂ O _Hd + H ₂ O _d + exhaust gas ⊗ 2 (d) : for a GT + DT system with the BM version (3): H ₂ O _Hd + H ₂ O _d ⊙

3a : Diagram of an internal combustion engine VM2 plus heat utilization device WNV plant, here a two-disc rotary piston machine (DKM), used as conveyor (DM0) and / or compression (WP5) and expansion device (DM1, DM2,3) operated with the BM mixtures
(3): H ₂ O _Hd high pressure steam + H ₂ O _d steam and
((4)): H ₂ O _Hd high-pressure steam + H ₂ O _d vapor plus exhaust gas, fed by the waste heat of a VM2, and used as air and exhaust gas compressor (LV / AV) or as WNV booster 3b : dito operated with the BM version (1): pure superheated steam H ₂ O _d

4a and b: Longitudinal and cross section through a high-temperature heat exchanger / catalyst WT2 / KAT in the exhaust stream of the VM2 with a flutter check valve

5 : Diagram of a WNV plant as a DKM behind a gas plus steam turbine combined cycle plant, with heat exchangers

figure description

• I. hinter einem VM2, eingebaut in einem KFZ 60 oder in einem stationären Aggregat, zum Leistungserhöhten Betrieb eines KFZ 60 plus Nebenaggregaten bzw. eines Generators G51 plus Heizung 42'.
• II. hinter einer GT4 + DT3‚3' Anlage zum Betrieb eines Generators G51 und zur Fern-/Prozessheizung 42,
• III. hinter einem (Biogas-)Brenner BR9 zum Betrieb eines Generators G51 und einer Gebäude-/Brauchwasserheizung 42'.

In the diagram of the 1 schematically the three principal uses of the waste heat-charged heat utilization device WNV, shown here as at least two-disc DKM:

• I. behind a VM2, installed in a car 60 or in a stationary unit, for increased power operation of a motor vehicle 60 plus ancillary units or a generator G51 plus heating 42 ' ,
• II. Behind a GT4 + DT3.3 'system for the operation of a G51 generator and for remote / process heating 42 .
• III. behind a (biogas) burner BR9 for the operation of a generator G51 and a building / hot water heating 42 ' ,

With this possible use III of the WNV can advantageously be used inferior landfill or biogas for local power generation in smaller units coupled with heating / process heat generation.

Further use of the WNV system as an air / (exhaust) compressor LV / (AV) with the storage and / or charging of the VM2, the charging of the GT4 plus its combustion point 54 or the burner BR9, and use of the stored compressed air 10 ' (the pressure exhaust gas 13 ' ) in a DLS 20 (THE 50 , please refer 3 ) for non-fuel / low-power operation of the VM2, the GT4 or the WNV plant itself as a booster, is in 3 and 5 described in detail.

The initially liquid, then vapor present resource BM 11 '' . 11 enthalpy is supplied via evaporator / heat exchanger VD / WT, in the cooling circuit of the VM2 / DKM or at the end in the hot exhaust gas flow 13 of the burner BR9, the GT4 and the VM2 are used:
WT0 and VD / WT0 ', VD / WT0''in the low temperature (NT) range (75 ° C <T <130 ° C to 250 ° C) for evaporating / preheating the BM, and
WT1 to WT4 in the high temperature (HT) range (250 ° C <T _a <770 ° C to 900 ° C) of the exhaust gas 13 to reheat the BM.

In case I of the VM2, the low temperature (90 ° C-130 ° C) reservoir of the cooling water of the VM2 and / or the DKM via WT0 or VD / WT0 'for evaporation and preheating the then present in BM BM 11 used.

In the case where only a one-component, vaporous operating medium is used, it is advantageous to use the H ₂ O coolant of the VM2 directly as BM 11 '' . 11 ' . 11 to use in a closed loop system for the WNV plant.

The antifreeze can be released by a simultaneous antifreeze lubricating the DKM.

One-third to two-thirds of the cooling of the VM2 and the DM0 / WP5 is due to the evaporation / preheating of the BM 11 discharged, so a mixture of water and steam cooling for the VM2 and the DKM used.

For application I, the VM2, the heated cooling water of the VM2 is pumped 27 ' through hollow cone or ultrasonic nozzles 24 sprayed into fine about ∅ = 20 to 70 microns droplets and with cooling of the VM2 and the DM0 / WP5 and possibly the DM1, evaporated and heated to a temperature T ₁ > 115 ° C to 130 ° C.

In Application II, the H ₂ O _d superheated steam is determined either by the medium pressure MD steam turbine DT3 ', see 5 , or, as shown here, at a center tap 56 the DT3 'with the appropriate temperature T ₁ and the pressure p ₁ diverted. The exhaust steam of DT3 'and the last WNV component DM2,3 ends in an advantageously externally cooled ( 42 ) Condensation cooler 41 ,

For more details of the WNV combined systems, see 3 and 5 ,

To build z. As the heat exchanger / catalyst WT2 / KAT, see 4 ,

For the case I, the VM2, a 0.6 l to 1 l Otto (or rotary piston) engine with z. B. used two to four cylinders, each with four valves per cylinder, with an average consumption per hour of 2.6 l / h corresponding to 2 kg / h gasoline (gas), including the WNV additional power. As rated power of the VM2 will be
P _{VM, max} = 50 kW assumed.

Because of the higher exhaust gas temperatures required for the WNV plant, operation of the VM2 without exhaust gas turbocharger is ATL 15 or prefer a DKM as VM2.

The 2 kg / h of gasoline consumption correspond to a calorific value per hour, h / h = 84,000 kJ / h, of which about 33%, ie Δh / h = 27,000 kJ / h, usually by the cooling and the exhaust gas 13 the VM2 gets lost to the environment.

Only about one-third of the calorific value flows into the engine and the auxiliary units, whose power consumption has already been significantly reduced by means of the changeover to compressed air, so that with the average consumption of 2 kg / h of gasoline (gas) about 0.3 h / h = 25,500 kJ / h, according to a performance of
P _VM = 7.1 kW
for the propulsion of the vehicle (without WNV) are available.

Taking into account the WNV additional capacity of
P _WNV = 3.2 kW will be the total power of VM2 + WNV
P _{VM + WNV} = 10.3 kW = 14 hp,
and thus a smaller vehicle can be operated in 5th gear at a speed of about 120 km / h in the plane.

In 3a and b is schematically shown a combination plant VM2 plus WNV for the two BM versions (3) and (2), and it is also the routing for the operation of the WNV as LV / AV with compressed air DLS20 and DAS50 gas tanks, respectively, as LV for the VM2 and as a booster drawn.

• (1) ein einkomponentiger H₂O_a Dampf (11),
• ((2)) ein Gemisch aus H₂O_Hd Hochdruckdampf (11') plus Anteilen des (Abgases 13),
• (3) ein Gemisch aus H₂O_Hd Hochdruckdampf (11') plus H₂O_a Heißdampf (11) und
• ((4)) dito plus Zugabe von Anteilen des (Abgases 13) in einer der letzten Entspannungsstufe(n) der WNV, hier der DM3.

For WNV, four versions can be used to advantage with water as BM:

• (1) a one-component H ₂ O _a vapor ( 11 )
• ((2)) a mixture of H ₂ O _Hd high pressure steam ( 11 ' ) plus shares of (exhaust 13 )
• (3) a mixture of H ₂ O _Hd high pressure steam ( 11 ' ) plus H ₂ O _a superheated steam ( 11 ) and
• ((4)) dito plus addition of portions of (exhaust gas 13 ) in one of the last relaxation stage (s) of the WNV, here the DM3.

For the BM versions ((2)), (3) and ((4)) after the heat exchangers WT0 and WT0 ', see 1 , initially preheated, liquid BM 11 '' , here z. B. H ₂ O _fl , by a high pressure (gear or piezo) pump 27 subjected to a pressure p ~ 190 bar and through the WT2 in the exhaust stream 13 the PM / VM2 heated to T = 400 ° C> T _crit = 374 ° C (for H ₂ O). This superheated H ₂ O _Hd vapor is then in the DM0, the first stage of WNV, in the sucked superheated steam H ₂ O _d (or the exhaust gas 13 ), and the mixture of high-pressure steam H ₂ O _Hd + superheated steam H ₂ O _d and / or (+ exhaust gas 13 ) is then advantageously two (three) stages of the relaxation device of the WNV, DM1, DM2 (and the DM3), relaxed under work.

In the last component of the WNV and subsequently in a condensation cooler 41 Then just the part of the H ₂ O _D vapor is condensed, which is used for the preparation of BM 11 ' H ₂ O _Hd content through the high pressure pump 27 needed and the rest of BM 11 , H ₂ O _d superheated steam, if necessary after cleaning, directly as H ₂ O _d superheated steam by suction with the DM0 is supplied by the WT1 again.

In the resulting saving of the heat of vaporization and thus the heat energy, which is mainly from the cooling water / cooling the H ₂ O _{fl, Hd} supply, is the advantage of the (mechanical) WNV system, and the second advantage in the use of WNV as LV / AV and as a booster.

In the following, the BM mixture version (3) is calculated in detail, whereby the calculations for the other BM versions (1), ((2)) and ((4)) can be carried out analogously, and the results also in the Tab. 1 are registered.

As WNV compression and expansion device advantageously a two-rotor rotary piston engine (DKM) is used, the DK have no piston recesses, and refined the cylinder surfaces, z. B. are chrome plated.

This DKM works as a nearly perfect "two-stroke" without valves and allows a very good separation of suction and compression processes. Both the lower and the upper cylinder chamber of the DKM, which are formed alternately with each 120 ° rotation of the rotary piston, can be used to different functions, each with two separate inputs ( 18 to 18 ' ) and outlets ( 19 to 19 ''' ) are used. This DKM can achieve compression factors of κ> 23: 1 without a piston recess and are capable of high speeds of U> 18,000 / min.

The chamber volume of the DKM was 80 cm ³ (90 cm ³ for the BM version (1)) with a transport volume of
V _T = 72 (81) cm ³ and a compression ratio of κ = 22: 1.

This corresponds to the dimensioning of the DKM in 3 for both discs a cylinder chamber height of A = 130 mm and for the first disc 1 a - wide of
B = 24 (28) mm and for the second disc 1' from 2B.

The delivered H ₂ O _d volume V _d per hour is then added to V _d / h = V _T × U / min × 60 min × 1.5 = 19.4 (22) m ³ / h (2) at a speed of U = 3000 / min DKM. The factor 1.5 comes about as per one revolution of the rotary pistons 25 . 25 ' the lower and the upper cylinder chamber 22 . 22 ' occur 1.5 times each.

With a density of H ₂ O _d of ρ = 1.5 kg / m ³ at a temperature of T ₁ = 130 ° C, the mass H ₂ O _d vapor per hour, m _d / h, promoted
m _d / h = 29.2 (32.6) kg / h corresponding to ν _d = (1250 + 350) = 1600 (1800) mol / h H ₂ O _d

• – maximale Abwärmenutzung aus beiden, dem NT und vornehmlich dem HT Reservoir der PM’s, hier des VM2,
• – bei den BM Versionen ((2)), (3) und ((4)) wird die H₂O_Hd Menge soweit beschränkt, dass diese auf eine Temperatur T₂ >> T_krit 374°C in den WT’s im Abgasstrom 13 erhitzt wird; daher der kleine Anteil von ν_d = 350 mol/h H₂O_Hd, siehe unten,
• – der maximale Druck in den Rohrleitungen p_max < 250 bar, in der DKM p_max < 120 bar, die maximale Temperatur < 530°C nicht überschritten wird, und
• – die Erfüllung obiger Kriterien bei möglichst kleiner Dimensionierung der DKM als WNV Zusatzaggregat.

In the calculation examples described below, the following criteria are taken into account in the given order:

• Maximum use of waste heat from both the NT and especially the HT reservoir of the PM's, here the VM2,
• - In the BM versions ((2)), (3) and ((4)), the H ₂ O _Hd amount is limited so that they to a temperature T ₂ >> T _crit 374 ° C in the WT's in the exhaust stream 13 is heated; hence the small fraction of ν _d = 350 mol / h H ₂ O _Hd , see below,
• - the maximum pressure in the piping p _max <250 bar, in the DKM p _max <120 bar, the maximum temperature <530 ° C is not exceeded, and
• - compliance with the above criteria with the smallest possible dimensioning of the DKM as a WNV additional unit.

With larger dimensioning of the DKM and thus higher delivery volume V _d / h and lower starting temperature of the BM / BM mixture before the WNV expansion components, the final component continues into the wet steam zone H ₂ O _d + H ₂ O _fl , cf. 2a to c.

In principle, however, this is only slightly in the results listed in Tab. 1, since the conveyed BM amount and its maximum achievable temperature T2 are complementary and, in a first approximation, both depend linearly on the introduced waste heat energy.

From the heat supply ΔQ from the coolant or the exhaust gas 13 the PM, here the VM2, with the temperature T _a , to the BM 11 . 11 ' ( 11 '' ) in the WT's are calculated using the formula, Eq. 3, which calculates the resulting BM temperatures T _x : T _x = (η _W ν _a C _{p, a} T _a + ν _{d / Hd} C _v T _x-1 ) / (η _WÜ v _a C _{p, a} + ν _{d / Hd} C _{v, d / Hd} ), 3) where T _{x is} the temperature of the BM ( 11 '' . 11 ' . 11 ) and T _x-1, which stands before the respective WTx.

The only partial heat transfer by convection of the PM exhaust gas 13 to the BM (s) used 11 . 11 ' ( 11 '' ) is taken into account by μ _WÜ = 0.8,
with ν _a = 1180 mol, the number of moles of exhaust gas 13 , for 2 kg of gasoline and stoichiometric combustion, composed of: 75% N ₂ , 14% H ₂ O superheated steam and 11% CO ₂ and CO, with a temperature of the VM2 exhaust gas 13 With
T _a = 350 (to 520 ° C) and 770 ° C in front of the heat exchangers WT1 and WT2, which latter is located directly behind the exhaust manifold of the VM2,
with the average molar heat of the exhaust gas 13 at constant pressure and constant volume C _{p, a} = 32.3 J / (mol / K) for a mean temperature of T = 580 ° C and
C _{v, a} = 21.5 J / (mol / K) for T = 350 ° C, see below,
ν _d = 1250 mol and ν _Hd = 350 mol, the molar numbers for the H ₂ O _d vapor and the H ₂ O _Hd high-pressure steam,
and the molar heat of H ₂ O _d at constant volume for an average temperature of
T = 300 ° C, for calculating the mixing temperature of the BM mixture, of H ₂ O _Hd + H ₂ O _d ,
C _{v, d} = 30.8 J / (mol / K), and the average molar heat of H ₂ O _Hd
C _{v, Hd} = 124 J / (mol / K)! for T = 130 to 530 ° C.

The relaxation in the WNV components DM0, DM1 and DM2 (DM3) is calculated isentropically (adiabatically), with isochoric, non-adiabatic correction _factors η _n.ad together with the overflow correction _factors η _Str , the effective change in enthalpy then becomes
ΔH _eff = η _n.ad η _Str ΔH,
With ΔH = (+/-) ν _d C _{v, d (a)} (T _{3 (2)} - T _{2 (1)} ), (4) in each case for the compression (with sign) and the relaxation process (with + sign), with η _n.ad = 0.8 and η _Str = 0.9 to 0.95.

In the first stage of the WNV, the DM0 as the lower cylinder chamber 22 the first DKM disc 1 , In this case, the heated in the WT1 to T ₁ = 270 ° C H ₂ O _d vapor with the reciprocal density 1 / ρ _d = 0.65 m ³ / kg sucked.

After closing the inlet 18 by rotation of the rotary piston (DK) 25 , which thus provides the function of a check valve, the superheated high-pressure steam, H ₂ O _Hd ( 11 ' ) with p ~ 190 bar and here heated to a temperature of P ₂ = 400 ° C in the heat exchanger WT2, via a controllable metering valve 7 ' if necessary via a hollow cone, ultrasonic or supersonic nozzle, see 1 , mixed and remains in vapor form.

The mixture temperature T _m is isentropic (for the whole system) according to Eq. 3, and because of the lossless mixture of the two gases with η _WÜ = 1, calculated to T _m = 350 ° C.

The mixture density ρ _m is governed by the law of Amagat 1 / ρ _m = (w _d / ρ _d + w _Hd / ρ _Hd ), (5) with w _d = 0.78 and w _Hd = 0.22, the molar mass fractions of the H ₂ O _d vapor or the high pressure steam H ₂ O _Hd , so that with 1 / ρ _Hd = 0.012 m ³ / kg for the BM ( 11 . 11 ' ) Mixture gives 1 / ρ _m = 0.51 m ³ / kg.

With the enthalpy value H = 3170 kJ / kg as starting point 2, the highest point in the TS diagrams for the mixture, H ₂ O _d plus H ₂ O _Hd , of the now common BM 11 , with now ν _d = 1600 mol H ₂ O _d vapor reached, see 2 B ,

After opening the outlet 19 is about a volume short, short connection 34 the upper chamber of the first DKM disc 1 as the first expansion stage with a ratio of 1: 2, filled as DM1, whereby the reciprocal density of
1 / ρ = 0.51 increased to 0.87 m ³ / kg,
where losses through interconnections ( 34 ) and by overflowing with a compression loss factor of η _KV = 0.85.

By introducing the H ₂ O _d BM 11 parallel in the two cylinder chambers 22 and 22 ' the second DKM disc 1' The H ₂ O _d vapor relaxes under working performance and partial condensation in a ratio of 1: 4.5 on
1 / ρ = 3.33 m ³ / kg,
before he gets in the cooler 41 further just so far partially condensed that for the high-pressure pump 27 required liquid H ₂ O _fl BM 11 '' Proportion and the remaining in vapor form H ₂ O _d BM 11 Part of the BM circuit to be fed separately, see 3a ,

In the BM version ((4)), see Tab. 1, the two chambers become 22 . 22 ' the second DKM disc separated as DM2 and DM3 and fed one after the other. After the DM2, 2/3 to 3/4 of the H ₂ O _d vapor with approx. T = 140 ° C is returned to the BM circuit, the WT1, and only then the exhaust gas 13 in the upper chamber 22 ' , the third WNV relaxation stage DM3, the remaining H ₂ O _d steam admixed, this BM wiring in 3 is not shown.

The early recycling of the H ₂ O _D vapor has the disadvantage that the expansion is not extended to (far) in the wet steam range, but has the comparatively much greater savings effect that only necessary for the H ₂ O _Hd H ₂ O _fl Part condensed and must be evaporated again. This also applies to a similar extent for the BM version (3).

The saving in heat energy ΔQ to be supplied is then approximately one order of magnitude higher than the lost residual energy.

In the return of the H ₂ O _d directly in the vapor phase into the BM cycle without prior condensation is one of the reasons for the high efficiencies for all three BM versions ((2)), (3) and ((4)), which Mixture H ₂ O _Hd + H ₂ O _d (+ exhaust 13 ) use.

The exhaust 13 in the BM version ((4)) after the WT1 still has a pressure p ₄ ~ 1.6 bar and a temperature of T ₄ = 350 ° C and heats the remaining H ₂ O _d BM steam ( 11 ) then from T = 140 ° C back to a mixing temperature of T = 290 ° C.

So it finds a Zwischenerhitzung the BM 11 H ₂ O _d steam instead, similar to that in a multi-stage HD, MD (and LP) steam turbine DT3, 3 'system, see 5 ,

The prerequisite for this is that the pressure of the exhaust gas p _a ~ 1.6 bar> p _d , ~ 1.2 bar, the pressure of H ₂ O _d vapor in the cylinder chambers 22 ' , the DM3, at the time of exhaust ( 13 ) Feed, ie the H ₂ O _d BM steam 11 has already relaxed so far.

The new BM mixture ( 11 . 13 ) continues to relax under working power to p _a ~ 1 bar for the exhaust gas 13 and the temperatures from T ≈ 210 ° C to T = 100 ° C and the corresponding vapor pressures for H ₂ O _d and is the condensation condenser 41 supplied in which the remaining H ₂ O _d plus the 14% H ₂ O _d vapor content of the exhaust gas 13 continue to condense at T <100 ° C and in the BM circuit as H ₂ O _fl via the high-pressure pump 27 be recycled, and the exhaust 13 after the additional wash cleaning is released to the atmosphere. This 14% H ₂ O _d vapor content of the exhaust gas 13 Fill up in about the H ₂ O _d vapor losses in the open river system again. Tab. 1: Values for circular cycles of the WNV with four different operating resources BM versions with advantages and disadvantages BM versions eff. (1) steam ((2)) HD steam + Exhaust (3) HD steam + Steam / ((4)) + Exhaust H ₂ O _d H ₂ O _Hd + Exhaust H ₂ O _Hd + H ₂ O _d / + Exhaust enthalpy ΔH _eff ΔH _eff / ΔH _m ΔH _eff ΔH _eff / ΔH _m ΔH _eff / ΔH _m WNZ comp. unit WP5 / DM0 -133 + 29 * + 28 * + 28 * kJ / kg DM1 +151 +177 +99 +133 +133 kJ / kg DM2 +325 +297 +62 +246 +139 + 71 + 16 kJ / kg total 343 × 32.6 kg / h 503 × 9.3 kg / h + 190 × 29.2 kg / h 407 × 29.2 kg / h 387 × 29.2 kg / h kJ / h .DELTA.W / h 11180 9380 11,900 11,300 kJ / h P _WNV 3.1 2.6 3.3 - 0.1 = 3.2 3.15 - 0.1 = 3.05 kW P _WNV / P _VM 0.44 0.37 0.45 0.43 η _{VM + WNV} 0.47 0.45 0.48 0.47 .DELTA.K / K -29% -27% -31% - 30% .DELTA.Q / h 25,000 24,000 25,700 27,500 kJ / h η _WNV = ΔQ / ΔW 0.45 0.39 0.46 0.41 advantages A BM additional emission control Highest additional services Simple construction pump 27 small power pump 27 small power Low pressure system Further control parameters Further control parameters Additional exhaust KAT Additional exhaust KAT disadvantage Lowest additional power Two BM Two BM / Three BM Highest start temperature Contaminated BM Contaminated BM WP5 performance minus Part high-pressure system Part high-pressure system partially open river system partially open river system small volume WT2 Exchange of the BM necessary Exchange of the BM

The ΔH _m values marked with a * in Table 1 result from the volume work according to Eq. 6 through the mixture, ie the entry of H ₂ O _Hd high pressure in the H ₂ O _d superheated steam: Δ _Hm = ∫∫Δp × Δ (1 / ρ) = (5.8-3.8) 10 ⁵ Pa (0.65-0.51) m ³ / kg = 28 kJ / kg, (6) as an example for the BM versions (3) and ((4)) in the WNV component DM0.

For the implicit increase of the enthalpy values for the mixture H ₂ O _d + H ₂ O _Hd , see the arrows in the TS diagrams in 2 B and c (d).

For the BM mixtures according to the versions (1) to ((4)), the values in Table 1 now result: ΔH _eff (ΔH _m ) the effective enthalpy difference,
ΔW / h, P _WNV , the additional power of the WNV, all in the specified units, and
P _WNV / P _VM , the power ratio of WNV to VM2,
η _{VM + WNV} = η _VM (1 + P _WNV / P _VM ) of the effective efficiency of the VM2 plus the WNV system in normal operation, whereby here a value of η _VM = 0.33 is used, which is compatible with modern (charged) gas / Petrol-powered petrol or DK engines and is achievable, with a clever reduction in consumption of ancillaries, z. B. by compressed air (exhaust) from the DLS (DAS), and .DELTA.K / K, the relative fuel economy.

For the discussed BM version (3): H ₂ O _Hd + H ₂ O _d , results as relative additional power of the WNV plant
P _WNV / P _VM = (3.3 - 0.1) kW / 7.1 kW = 0.45,
the power consumption of the high-pressure pump 27 was deducted from 0.1 kW.

For the implicit increase of the output enthalpy values for the cycle of the mixture H ₂ O _d + H ₂ O _Hd , see the TS diagrams in 2 B and c.

The relative fuel economy ΔK / K then becomes ΔK / K = - (1 - 1 / (1 + P _WNV / P _VM )) / K = -31%. (7) with the effective efficiency of the VM2 plus the combined WNV system
η _{VM + WNV} = η _VM (1 + P _WNV / P _VM ) = 0.48 around 50%,
So that at U = 3000 / min it comes close to the efficiencies of today's combined cycle plants, so that the question is allowed whether the use of electric vehicles in everyday use still makes sense?

In the mixed mode of operation according to the NEDC (New European Driving Cycle), the planned recuperation of braking and thrust energy is expected to produce further, low, double-digit percentage profits, so that an actual, relative fuel saving with the combined system VM + WNV of approx.
ΔK / K ~ -36%.

• – ein thermischer Wirkungsgrad η_WNZ der WNZ Anlage mit der BM Version (3) (nach einem angenäherten, irreversiblen Clausius-Rankine Prozess) zu η_WNZ = ΔW/ΔQ = 0,60, (8) der als letzter Wert in der Tab. 1 eingetragen ist, wobei die jeweils insgesamt im BM Kreiszyklus zugeführten Wärmemengen pro Stunde, ΔQ/h, auf- oder abgerundet, verwendet wurden, aber Effekte der Mischung(senthalpie) der BM Gemische nicht berücksichtigt werden. Der reversible Carnotprozess hätte bei der oberen T = 1043 K und der unteren Temperatur T = 347 K einen Wirkungsgrad nach Gl. 1 von η_C = (1043 – 347)/1043 = 0,68, wobei hier die Mischungen mit dem H₂O_Hd Dampf nicht berücksichtigt sind.

As a sample is calculated

• - A thermal efficiency η _{WNZ of} the WNZ plant with the BM version (3) (after an approximate, irreversible Clausius-Rankine process) too η _WNZ = ΔW / ΔQ = 0.60, (8) is entered as the last value in Tab. 1, wherein the total amount of heat supplied per hour in the BM cycle cycle, ΔQ / h, rounded up or were used, but effects of the mixture (senthalpy) of the BM mixtures are not taken into account. The reversible Carnot process would have an efficiency according to Eq. 1043 K and the lower temperature T = 347 K according to Eq. 1 of η _C = (1043 - 347) / 1043 = 0.68, where the mixtures with the H ₂ O _Hd vapor are not taken into account.

In 2a to c, the circular cycles of the BM versions (1), (3) and ((4)) are plotted as TS diagrams, for the WNV system with the VM2 and in 2d with the GT4 + DT3,3 '.

The advantage of the BM mixture versions ((2)), (3) and ((4)) is that a BM state with low entropy (H ₂ O _Hd ) is mixed with such a high entropy (H ₂ O _d or exhaust 13 ), which increases the usable exergy.

• 1. Die Summe beider (der drei) Massen geht linear in die Zusatzleistung P_WNZ ein, und auch der Wärmeinhalt und die restliche Volumenarbeit des Abgases 13 wird in der Version ((2)) und ((4)) noch zum Teil ausgenutzt. Die gemeinsame Dichte ρ_m und Temperatur T_m des BM Gemisches liegt so weit im H₂O_d Dampfbereich, dass die Entspannung in den drei Stufen der WNV noch nicht oder nur knapp in den Nassdampfbereich des H₂O_d,fl führt.
• 2. Die Druckaufladung des H₂O_Hd Dampfes erfolgt mit einer Hochdruck-Flüssigkeitspumpe 27 und benötigt viel weniger Leistung als z. B. die Wärmepumpe WP5 oder ein Turbinenverdichter 52 für den H₂O_d Dampf bzw. ein Gas, z. B. Luft.
• 3. Weiterhin hat das H₂O_Hd BM 11' den Vorteil, dass es im unteren Temperaturbereich bis T_krit = 374°C flüssig vorliegt und darüber in überkritischer Dampfform, und das für beide die Wärmeleitfähigkeit höher ist als für den H₂O_d Dampf. Dadurch kann die zu übertragende Wärmeenergie pro Zeiteinheit, ΔQ/Δt, leichter, d. h. mit kleinerem ΔT- und relativen Δp/p-Verlusten vom Abgas auf diesen Teil des BM 11' übertragen werden, resultierend in einer höheren Endtemperatur T₂ des H₂O_Hd, siehe die Berechnungen zu 4, oder es kann eine größere Menge H₂O_Hd präpariert werden.
• 4. Im Falle der BM Version ((2)) und ((4)), der Beimischung des Abgases 13 zu dem als H₂O_d vorliegenden BM 11 wird wieder die letzte Komponente der WNV aufgeteilt in die DM2 und DM3, hier die untere und obere Zylinderkammer 22, 22' der zweiten Scheibe 1' der DKM. Nach der DM2 werden z. B. zwei Drittel des H₂O_d abgezweigt und in den BM Kreislauf zurückgeführt, und nur ein Drittel des H₂O_d BM 11, der für die Hochdruckpumpe 27 in flüssiger Form, als H₂O_fl, vorliegen muss, in dem Kondensationskühler 41 (41') verflüssigt, während der verbleibende H₂O_d Dampf direkt in den BM Kreiszyklus zurückgeführt wird. Dies bedeutet eine Ersparnis der entsprechenden Verdampfungswärmen, die sich auf mindestens ein Drittel der gesamten einzusetzenden Wärmeenergie beläuft. In einer normalen DT Anlage wird im Verhältnis zur geleisteten Arbeit etwa die gleiche Wärmeenergie in Form von Kondensationswärme durch den Kondensationskühler 41' abgeführt und geht verloren, bzw. wird als minderwertige Heizenergie genutzt, und muss dann als Verdampfungswärme im Kreiszyklus aus z. B. dem GT4 Abgas wieder aufgebracht werden. Dies hat den weiteren Vorteil, dass die Mischung aus restlichem H₂O_d und dem Abgas 13 auf der Isobaren p = 1 bar im T-S Diagramm nach links auf den Siedepunkt T_S = 100°C des H₂O_d bei Atmosphärendruck entspannt und dann im Kühler 41 weiter auskondensiert und als H₂O_fl der Hochdruckpumpe 27 wieder zugeführt wird.
• 5. Schon die erste Stufe DM0 der WNV leistet durch die H₂O_Hd Mischungszugabe Volumenarbeit (ΔH_m Werte mit * in Tab. 1) bzw. verbraucht keine, während bei der BM Version (1) die Wärmepumpe WP5, die als erste Stufe für das Ansaugen, den Transport und die Kompression des reinen H₂O_d Dampf eingesetzt wird, ein knappes Drittel der gesamten WNV Zusatzleistung verbraucht. Das wird dadurch kompensiert, dass bei der BM Version (1) der Hauptteil des H₂O_d ohne Verflüssigung in den BM Kreislauf zurückgeführt wird, und dass hier etwas größere H₂O_d Molmenge mit höherer Ausgangstemperatur zur Verfügung gestellt werden können. Die benötigte Verdampfungswärme für die kleine Menge verflüssigtes H₂O_fl von dem VM2 bzw. DKM Kühlwasser im NT Bereich aufgebracht und geht somit nicht negativ in die Energiebilanz des HT Abgas 13 Bereichs ein. Es fehlen hier Beiträge der Mischungsenthalpie. Die BM Version (1) hat aber den Vorteil des einfachsten Aufbaus der WNV.
• 6. Durch den Leistungszuwachs zum VM2, zu der GT4 + DT3 Anlage mit der WNV Kombianlage steigt der Gesamtwirkungsgrad auch für den Brenner BR9 auf optimal rund 50% bzw. 70%, vergleiche Tab. 1 und 2. Die BM Versionen (3) und ((4)) ergeben die höchste Zusatzleistungen P_WNV, siehe Diskussion oben, vornehmlich wegen des großen Beitrags der impliziten Mischungsenthalpie H_m und der direkten ΔH_m Beiträge, Werte mit * in Tab. 1 und 2, durch die Volumenarbeit. Der Primärquelle/-maschine PM wird bei den BM Versionen ((2)) und ((4)) die größte Wärmeenergiemenge ΔQ/h entzogen, sowohl dem NT Bereich durch Verdampfen des flüssigen BM 11'' und Vorerhitzen des gasförmigen BM 11 bzw. des flüssigen BM 11'' für den H₂O_Hd, als auch dem HT Bereich, dem Abgas 13 der PM, hier dem VM2, aber auch im Falle der GT4 oder dem Brenner BR9.
• 7. Durch eine Extremwertaufgabe kann in jedem Betriebszustand das optimale Mischungsverhältnis H₂O_Hd zu H₂O_d durch den Steuerungscomputer berechnet werden, in Abhängigkeit von der Umdrehungszahl U/min, der angebotenen Temperaturen des VM2 Kühlwassers, der DM0/WP5 und auch der DM1, sowie insbesondere von der Temperatur des Abgases 13, um dann über das Dosierventil 7' und/oder die H₂O_fl,Hd Fördermenge der Hochdruckpumpe 27 eingestellt zu werden.
• 8. Der Wasserdampf H₂O_d reinigt in der Version ((2)) und ((4)) das Abgas weiter nach dem Abgas Katalysator, hier in der Kombination WT2/KAT, weiter von SO_x, NO_x, und anderen Schadstoffen, und diese können am Ende des Zyklus im dann kondensierten H₂O_fl, vor der Rückführung in den BM Kreiszyklus, durch Filter und/oder mit Chemikalien, z. B. mit Calciumhydroxid, CaOH, als Gips, ausgefällt werden, ähnlich der Auswaschreinigung in Kühltürmen bei GuD Kraftwerken. Das BM H₂O wird nach einer festzulegenden Zahl von Zyklen, abhängig von der Effektivität der eingebauten Filter, ausgetauscht. Mit den BM Versionen ((2)) und ((4)) wird auch die Abgasreinigung einer Drehkolbenmaschine DKM deutlich einfacher.

The advantages of the WMV combination plant behind the VM2 and the GT4 + Dt3,3 ', see 5 , for the BM version (1) or the BM mixtures ((2)) to ((4)) are:

• 1. The sum of both (three) masses is linear in the additional power P _WNZ , and also the heat content and the residual volume work of the exhaust gas 13 is partially exploited in the version ((2)) and ((4)). The common density ρ _m and temperature T _{m of} the BM mixture is so far in the H ₂ O _d steam range that the relaxation in the three stages of the WNV does not or only slightly in the wet steam range of H ₂ O _{d, fl} leads.
• 2. The H ₂ O _Hd vapor is charged with a high-pressure liquid pump 27 and needs much less power than z. As the heat pump WP5 or a turbine compressor 52 for the H ₂ O _d vapor or a gas, for. For example, air.
• 3. Furthermore, the H ₂ O _Hd BM 11 ' the advantage that it is liquid in the lower temperature range to T _crit = 374 ° C and above it in supercritical vapor form, and that for both the thermal conductivity is higher than for the H ₂ O _d vapor. As a result, the heat energy to be transmitted per unit time, ΔQ / Δt, lighter, ie with smaller ΔT and relative Δp / p losses of the exhaust gas on this part of the BM 11 ' transferred, resulting in a higher end temperature T ₂ of H ₂ O _Hd , see the calculations 4 , or it can be prepared a larger amount of H ₂ O _Hd .
• 4. In the case of the BM version ((2)) and ((4)), the admixture of the exhaust gas 13 to the BM present as H ₂ O _d 11 again the last component of the WNV is divided into the DM2 and DM3, here the lower and upper cylinder chamber 22 . 22 ' the second disc 1' the DKM. After the DM2 z. B. Two-thirds of H ₂ O _d branched off and returned to the BM cycle, and only a third of H ₂ O _d BM 11 , who for the high pressure pump 27 in liquid form, as H ₂ O _fl , must be present in the condensation cooler 41 ( 41 ' ), while the remaining H ₂ O _d vapor is returned directly to the BM cycle. This means a saving of the corresponding heat of evaporation, which amounts to at least one third of the total thermal energy to be used. In a normal DT system, the heat energy in the form of heat of condensation through the condensation cooler will be approximately equal to the work done 41 ' dissipated and lost, or is used as inferior heating energy, and then as heat of vaporization in the cycle from z. B. the GT4 exhaust are reapplied. This has the further advantage that the mixture of residual H ₂ O _d and the exhaust gas 13 on the isobaric p = 1 bar in the TS diagram, left to the boiling point T _S = 100 ° C of the H ₂ O _d at atmospheric pressure and then in the condenser 41 condensed further and as H ₂ O _{fl of} the high-pressure pump 27 is fed again.
• 5. Even the first stage DM0 of the WNV makes volume work (ΔH _m values with * in Tab. 1) due to the H ₂ O _Hd mixing addition, or does not consume them, while in the BM version (1) the heat pump WP5, the As a first stage for the suction, transport and compression of pure H ₂ O _D steam is used, nearly one-third of the total WNV consumed power. This is compensated by the fact that in the BM version (1) the main part of the H ₂ O _{d is returned} without liquefaction in the BM cycle, and that here a little larger H ₂ O _d molar amount can be provided with higher starting temperature. The required heat of vaporization for the small amount of liquefied H ₂ O _{fl applied} by the VM2 or DKM cooling water in the NT range and thus does not negatively impact the energy balance of the HT exhaust gas 13 Area. There are no contributions of the enthalpy of mixing. The BM version (1) has the advantage of the simplest construction of the WNV.
• 6. Due to the increase in performance to the VM2, to the GT4 + DT3 system with the WNV combination system, the overall efficiency also increases for the burner BR9 to optimally around 50% or 70%, compare Tab. 1 and 2. The BM versions (3) and ((4)) give the highest additional benefits P _WNV , see discussion above, mainly because of the large contribution of the implicit enthalpy of mixing H _m and the direct ΔH _m contributions, values with * in Tables 1 and 2, through the volume work. In the BM versions ((2)) and ((4)), the primary source / machine PM is deprived of the largest amount of thermal energy ΔQ / h, both the NT region by evaporation of the liquid BM 11 '' and preheating the gaseous BM 11 or the liquid BM 11 '' for the H ₂ O _Hd , as well as the HT range, the exhaust gas 13 the PM, here the VM2, but also in the case of the GT4 or the BR9 burner.
• 7. By an extreme value task, the optimal mixing ratio H ₂ O _Hd to H ₂ O _d can be calculated by the control computer in each operating state, depending on the number of revolutions RPM, the offered temperatures of VM2 cooling water, the DM0 / WP5 and also the DM1, and in particular the temperature of the exhaust gas 13 then to the metering valve 7 ' and / or the H ₂ O _{fl, Hd} flow rate of the high-pressure pump 27 to be adjusted.
• 8. The water vapor H ₂ O _d cleans in the version ((2)) and ((4)) the exhaust gas further to the exhaust gas catalyst, here in the combination WT2 / KAT, further from SO _x , NO _x , and other pollutants , and at the end of the cycle, they may be condensed in the H ₂ O _fl , before being returned to the BM cycle, by filters and / or with chemicals, e.g. B. with calcium hydroxide, CaOH, as a gypsum precipitated, similar to the washout in cooling towers at combined cycle power plants. The BM H ₂ O is exchanged after a number of cycles to be determined, depending on the effectiveness of the built-in filters. With the BM versions ((2)) and ((4)) also the exhaust gas cleaning of a rotary piston machine DKM becomes much easier.

The remaining pressure and the residual temperature potential of the exhaust gas 13 , also its 14% H ₂ O _d content, see above, is widely used in the versions ((2)) and ((4)). For the BM version (3), the same applies as for ((4)) except for the non-use of the remaining pressure and temperature potential of the exhaust gas 13 ,

• – eine Zwischenerhitzung des BM (11) in der DM0 bzw. DM3 Abgaszugabe-Stufe durch das restliche Wärmepotential des Abgases 13 stattfindet,
• – das teilweise abgekühlte Abgas 13 noch zur direkten Arbeitsleistung herangezogen wird,
• – das BM Gemisch (11, 13) am Ende der Entspannungs- und Abkühlungskette auf der Isobaren mit p = 1 bar im T-S Diagramm nach links bis auf die Siedetemperatur von T_S = 100°C des H₂O bei Normaldruck herunterfährt,
• – nach dem KAT/WT2 eine weitere Schadstoff Reinigung des Abgases 13 durch Auswaschung im dampfförmigen/flüssigen BM stattfindet, wie in der BM Version (2), und
• – das Spülen der WNV Anlage vor und nach Umschaltvorgängen zwischen den Funktionen der WNV wegen des teiloffenen BM Flusssystems ganz entfallen, bzw. auf zwei bis drei Umdrehungen der WNV reduziert werden kann, und in den Nachteilen von ((4)), dass
• – der komplexeste Aufbau der WNV mit drei BM Sorten in einem teiloffenen BM Kreislaufsystem verwendet wird,
• – die Endtemperatur des BM Kreiszyklus am höchsten liegt, was der Grund ist für die gegenüber (3) niedrigere Zusatzleistung,
• – eine Reinigung des zirkulierenden BM durch Filter und/oder Zugabe von Chemikalien mit Ausfällung vorzusehen ist, und
• – das BM ersetzt und recycelt werden muss nach einer festzulegenden (großen) Zahl von Stundenzyklen, und
• – in der Version ((2)) der gesamte, geringe H₂O_d Anteil, aus der H₂O_Hd Charge, vor der Rückführung zu H₂O_fl auskondensiert werden muss, was aber nicht negativ in die Energiebilanz des HT Abgas 13 Bereichs eingeht, da die Vorerwärmung des H₂O_fl aus dem Kühlwasser des VM2 und der DKM im NT Bereich effizient erfolgt.

The further difference between the BM versions ((2)), ((4)) versus (3) consists in the advantages of ((4))

• - an intermediate heating of the BM ( 11 ) in the DM0 or DM3 exhaust gas addition stage by the residual heat potential of the exhaust gas 13 takes place,
• - The partially cooled exhaust gas 13 is still used for direct work,
• - the BM mixture ( 11 . 13 ) at the end of the relaxation and cooling chain on the isobarene with p = 1 bar in the TS diagram to the left down to the boiling point of T _S = 100 ° C of H ₂ O at atmospheric pressure,
• - After the KAT / WT2 another pollutant purification of the exhaust gas 13 by leaching in the vapor / liquid BM, as in the BM version (2), and
• - The flushing of the WNV system before and after switching operations between the functions of the WNV due to the partially open BM flow system completely omitted, or can be reduced to two to three turns of the WNV, and in the disadvantages of ((4)) that
• - the most complex structure of WNV with three BM varieties in a partially open BM circulatory system is used,
• - the final temperature of the BM circuit cycle is highest, which is the reason for the (3) lower additional power,
• - cleaning the circulating BM by filtering and / or adding chemicals with precipitation, and
• - the BM must be replaced and recycled after a (large) number of hourly cycles, and
• - In the version ((2)), the entire, small H ₂ O _d portion, from the H ₂ O _Hd charge, must be condensed out before returning to H ₂ O _fl , but this does not have a negative impact on the energy balance of the HT flue gas 13 Range comes because the preheating of the H ₂ O _fl from the cooling water of the VM2 and the DKM in the NT area is efficient.

The BM versions (3) and ((4)) can be used in an analogous manner also for the cases II and III of the primary sources, the GT4 + GT3 system and the burner BR9, with similarly good results, see description to 5 and Tab. 2, and the above-mentioned advantages and, in the case of stationary installations, more easily manageable disadvantages.

All data in Tab. 1 result at U = 3000 / min of the VM2 + WNV system and without inclusion of the additional, effective and / or energy-increasing functions of the WNV system. The absolute values will increase with the power / RPM of the VM2 according to G. 8, see below.

For high performance requirements, the VM2 is also charged with the compressed air, which the VM2 can tolerate for a short time, and which adds at least 15 kW to the 50 kW.

With the booster function of the WNV system can be briefly, from a full 100 l compressed air storage DLS 20 starting, for about 2 to 3 min at least once again the maximum VM rated power retrieve, ie
P _{VM + LV, max} + P _WNVBoost = (65 + 50) kW = 115 kW.

So from a 50 kW vehicle VM2 with the combined WNV system, a sports equipment with a power of 115 kW corresponding to 156 hp, which in a small car, z. As the polo class, allows an enormous power development, the increase in torque - decisive for the acceleration - percentage even higher.

At a speed change of the VM2 and the WNV, the additional power P _{WNV is} proportional to the conveyed BM number of moles ν _d , which increases linearly with the number of revolutions per minute, see Eq. 2. The dependence of the temperature of the VM2 exhaust gas 13 VM2 RPM shows a slightly more complex behavior, but also increases with RPM. So, in a first approximation assumed dependency P _{VM + WNV} ~ U ^{1.25 ... 1.75} (8) in the range 2500 <RPM <6500, which increases more than linearly with RPM.

In 3b is another advantageous example of the combination system VM2 + WNV for the BM version (1): pure H ₂ O _d steam, with the placement of the WT2 between the WP5 and the DM1 drawn schematically.

The double disc DKM is used here as a conveying heat pump plus working steam engine, WP + DM, with the lower cylinder chamber 22 the first disc 1 the DKM functions as WP5, the upper as DM1 stage, which more than compensates for the power consumption of the upstream WP5, see Tab. 1, the entire second DKM disc 1' is used again as a DM2 level.

As equipment H ₂ O _{fl, d} BM 11 '' . 11 can the H ₂ O _fl cooling water 21 itself, as assumed here, or another, initially liquid BM 11 '' be used.

From the radiator 40 The VM2 becomes the main part of the cooling water 21 with a pump 27 ' through the cylinder head of the VM2, or through the two discs 1 . 1' the DKM (in 3 not shown) in channels or pipe snakes ( 26 ' ) circulates. This main flow of cooling water 21 can through a valve 7 '' be regulated so that the heat dissipation by the evaporation and / or preheating of the H ₂ O _{fl, d} BM 11 '' . 11 just in the VM2 / DKM cooling is compensated.

The cooling of the two (multi) discs DKM, see 1 , takes place at temperatures t ₁ > 110 ° C to 130 ° C either with water under elevated pressure or directly with H ₂ O _d steam from the BM 11 Steam cycle, under further heating of the BM 11 ,

For the evaporator / heat exchanger WT0 and VD / WT0 ', see 1 , can here in the NT area z. B. Al cast pipe blocks are used, which are in good thermal contact with the cylinder block of the VM2 and the DKM.

To improve the evaporation, the cooling water (mixed with a lubricating antifreeze) by hollow cone or ultrasonic nozzles ( 24 ) in droplets with a diameter of about ∅ = 20 to 70 microns in the channel / tube system of the VD / WTO ', see 1 , Case I, or nebulised by ultrasonicated surfaces.

In the two WT1 and WT2 / KAT in the exhaust gas flow 13 flows inside in the stainless steel tubes 26 the BM 11 and on the outside these are from the VM2 exhaust 13 flows around.

To build the WT2 / KAT as an example, see 4 ,

The A- 18 . 18 ' . 18 '' . 18 ' and outlets 19 . 19 ' . 19 '' . 19 ''' are on the DKM cylinder discs 1 . 1' arranged so that during rotation of the rotary piston 25 . 25 ' No or little overlap of the intake and exhaust stroke results.

In particular for the BM version (1) care must be taken here that the dead volumes in the WT2 at the outlet 19 and inlet 18 ' be kept as small as possible.

Behind the DKM outlet 19 is a flutter check valve 37 fitted to a backflow of the BM 11 into the lower WP5, to prevent DKM chamber.

For operation of the WNV with the BM version (1), the total internal volume of the WT2 then becomes equal to the transport volume V _{T of} a DKM chamber 22 . 22 ' chosen, see 4 , so that the compression or expansion ratio of the WP5 or the DM1 is advantageously 2: 1 or 1: 2.

For the other BM versions one is free in the choice in particular the volume dimension of the heat exchanger, and can choose an optimal design, eg. B. for the WT2 as KAT or with respect to the pressure loss .DELTA.p and the temperature difference .DELTA.T, see Eq. 9 and 10. After the WT2 / KAT follows the second DKM disc 1' double chamber width 2B as steam engine DM2 as another expansion device, which provides the main auxiliary performance. For this purpose, the H ₂ O _d BM 11 in both cylinder chambers 22 . 22 ' the second DKM disc introduced as DM2 parallel and further relaxed under work performance.

Alternatively, the DKM disc 1' also have the width B, then translated by a transmission 16 with twice the speed or by two gears (not shown) and then in reverse direction to the first DKM disc 1 run, with then exchanged one 18 and outlets 19 ,

After the DM2 (3) stage, the BM H ₂ O _d becomes a condensation condenser 41 in which it continues to condense to a small extent of (1-x) <0.2, with x = the remaining H ₂ O _d vapor content, which is returned to the BM cycle via the WT1.

The condensation cooler 41 is available for preheating in a controllable connection to the VM2 (DKM) main cooler 40 ,

The VM2 cooler 40 must for the BM 11 Version (1): H ₂ O _d , here about 1/3 to 1/2 of the VM2 (DKM) cooling arise, and for the entire VM2 (DKM) cooling below the VM2 transition speed U _Ü <2500 / min, for which the WNV works as LV for charging the VM2, and generally when operating the WNV system as LV / AV or as a booster.

For expelling the already condensed in the DM2 (3) stage of DKM H ₂ O _fl share with the main part of BM H ₂ O _d DKM can be operated lying and advantageously with side inlets.

For U _Ü <2500 / min of the VM2 then the two DKM discs through the inlet 29 In the reverse flow direction to the WNZ / DM + WP operation with atmospheric air fed and operated as a three-stage air compressor, LV1 to LV3 for the VM2, and a 1: 3 to 4 reduction of the transmission 16 selected.

To switch from WNV / DM + WP to LV / AV operation, all four three-way valves 6 who are 18 . 18 '' and behind the outlets 19 ' . 19 '' the DKM discs 1 and 1' are arranged, for. B. electro-magnetically, provided switchable. This also applies to all other valves and control units.

In the BM versions (1) and (3) the DKM chambers are 21 . 21 ' via the ventilation valves 8th flushed for about ten turns before and after each switch.

For the BM versions ((2)) and ((4)) are less revolutions, or must not be rinsed at all, since the through the port 29 sucked air 10 (the exhaust gas) in the partially open circuit system with the exhaust gas 13 is ejected, or the small amount of remaining in the WNV plant BM 11 , H ₂ O _d , when switching to LV / AV to charge the VM2 or to store the compressed air in the DLS 20 / the DAS 50 does not matter, or in the exhaust 13 Storage due to the 14% H ₂ O _d content in the exhaust gas 13 is negligible, and in the BM ( 11 '' . 11 . 11 ' . 13 ) This fraction largely replaces the H ₂ O _d lost in the partially open BM circulatory system.

• – dem VM2 über den Ansaugstutzen 38 zur mechanischen Aufladung des VM2 unter U_Ü < 2500/min und bei hoher Leistungsanforderung, oder
• – zum Betrieb des VM2 ohne Kraftstoff bei genügender Füllung des DLS 20 (DAS 50), oder
• – zum Betrieb der WNV Anlage als Booster.

During braking and pushing operations and at speeds of the VM2 below U _Ü <2500 / min, a compressed air (exhaust) storage DLS is used in LV (AV) operation 20 (THE 50 ) charged. Its compressed air 10 ' (Pressure exhaust 13 ' ) is then via adjustable pressure reducer 17 . 17 ' fed:

• - the VM2 via the intake manifold 38 for mechanical charging of the VM2 under U _Ü <2500 / min and with high power requirement, or
• - to operate the VM2 without fuel with sufficient filling of the DLS 20 (THE 50 ), or
• - to operate the WNV system as a booster.

That's enough in a DLS 20 of 100 liters of stored compressed air 10 ' with a pressure of about p ~ 100 bar and about T ~ 500 ° C to operate the VM2 without fuel for about 6 min, ie for a distance of about 12 km at a mean speed of 120 km / h.

The elevated temperature of the compressed air 10 ' (the pressure exhaust gas 13 ' ) is energetically meaningful, since with the expansive decompression the stored compressed air by means of the variable pressure reducer 17 . 17 ' , to about p ≈ 2 bar for charging the VM2 or to about a mean pressure of p _m ≈ 6 bar to operate the VM2 without fuel or the WNV as a booster, a significant cooling of the air takes place. A good thermal insulation 53 of the DLS 20 (THE 50 ) and all supply lines (not shown) is provided.

In case of cooling of the DLS 20 and especially the DAS 50 below the dew point of the stored H ₂ O, a drain tap for H ₂ O residues is provided at the lowest point of the storage tank (in 3 not shown). The DLS 20 and the 50 Containers are internally protected by a protective plastic coating or a durable metal coating against corrosion.

Since the WT2 / KAT and / or the WT1 are also in LV (AV) operation in compressed air ( 10 ' ) (- exhaust 13 ' ) Flow course, these heat exchangers are maintained at a temperature of T> 300 and> 400 ° C, so that the energy efficient switchover to WNV operation without delay and can be used in each driving condition of the car increasing performance and optimally used.

The switching times are mainly determined by the approximately ten revolutions of the WNV, the DKM, which is used to flush the cylinder chambers 22 . 22 ' and the lines in the BM version (1) and (3) are necessary, and amount to z. B. at the transition speed of U = 2500 / min to .DELTA.t = 0.2 s, which correspond approximately to a fast human reaction time. When operating the WNV with the BM versions ((2)) and ((4)) without flushing, the changeover time is less than Δt <0.1 s.

In this way, the WNV with virtually barely noticeable delay between the various functions can be switched, which is essential for the energy recuperation during braking and coasting of the car and for activating the LV function for charging the VM2 and the booster function during heavy acceleration operations ,

When operating the VM2 in uneconomic areas of the VM2 map and falling below a minimum pressure in the DLS 20 (THE 50 ), a higher power of the VM2 is demanded by downshifting to a lower gear (in the case of manual transmissions, for example, by an electrically connectable and deactivatable overdrive) and the LV / AV function and, at the same time, charging the VM2 from the DLS 20 via a variable pressure reducer 17 activated.

The shorter or longer term call, depending on the volume design of the DLS 20 , the performance of the WNV Booster can reach or exceed the maximum rated power of the VM2 or the DT3 and thus acts similar to the KERS (Kinetic Energy Recovery System) device for Formula 1 engines, only with significantly higher power delivery, see Introduction.

This compressed air motor function of the WNV saves in application II if necessary a second GT4 'for peak load times, see description for 5 ,

With these three functions of the WNV system, all processes are optimally used and controlled by an intelligent, electronic controller.

A drive belt 34 , each with a conical wheel 32 running on the crankshaft of the VM2 and on the shaft of the WNV / DKM, advantageously couples the VM2 to the WNV via a CVT transmission 16 (Continously Variable Transmission) or a planetary gear (not shown). This gear 16 can be varied by an electro-magnetic or pneumatic control advantageously continuously between reduction ratios 1: 1 to 4: 1, for optimized operation of DKM as a WNV system, as WNV booster or as LV / AV or as a mechanical loader for the VM2.

In 4a and b shows the construction of a high-temperature heat exchanger using the example of the WT2 / KAT, consisting of 12 stainless steel tubes 26 with outer diameter ∅ = 3.4 mm or 3.6 mm with a wall thickness d = 0.2 mm or 0.3 mm, with a total length of L = 850 mm. These tubes made of high-temperature resistant stainless steel withstand a test pressure of p = 160 bar or 280 bar.

Above the 18 ' and the outlet 19 the DKM 1 are four tubes each 26 in three staggered rows to a 12-piece bundle in the connecting flange 35 arranged to the DKM in a rectangle, with the external dimensions b = 30 mm and a = 13 mm.

The tubes 26 are divided into four sections with a length l = 212 mm with a fourfold deflection in a total width w = 55 mm and at one end into the connecting flange 35 and at the other end into a common deflection flange 36 soldered hard. Both flanges 35 and 36 are also made of stainless steel, and the soldering is done with a nickel solder at about 1000 ° C in a vacuum or under inert gas.

In the outlet opening 19 the DKM is in the connecting flange 35 a flutter check valve 37 used, in the rhythm of the intake and compression stroke of the DKM component WP5 the inlet to the 12 tubes 26 opens or closes.

This valve 34 is so thin-walled and smooth running that it has the maximum clock frequency of the discs 1 and 1' the DKM managed about U <9,000 / min.

Over the entire, folded tubes 26 Arrangement is a stainless steel dome 39 inverted, tight in a groove of the flange 35 is admitted. By two exhaust 13 pipe connections 33 and 33 ' , each in the lower part of the hood 39 , become the tube bundles 26 flowed across, and the exhaust flow 13 is through a midway between the tube bundles 26 arranged partition 44 then up to below the upper flange 36 and back to the outlet 33 guided.

Advantageously, the tubes are 26 outside with Pd or Pt ( 40 ), so that the heat exchanger WT2 can simultaneously take over the function of the catalytic converter KAT. The dimensioning of the WT2 / KAT is then limited except for the BM version (1) and can be optimized for the catalyst function.

The volume content of the WT2, including flutter check valve 37 then corresponds to the transport volume of V _T = 90 cm ³ for the BM version (1).

The tubes 26 In particular, in the WT2 (and the WT1) are designed so that the temperature difference .DELTA.T, which is necessary to the amount of heat .DELTA.Q / h by convection of the exhaust gas 13 to transfer the H ₂ O _d vapor (the H ₂ O _Hd high-pressure steam), only up to ΔT <30 (20) ° C, and the corresponding pressure loss in the WT's not greater than Δp <0.2 (5) bar becomes. For the total amount of heat transferred in all WTs / hour ΔQ / h, see Tab. 1.

The heat transfer in the flowing H ₂ O _d vapor and H ₂ O _Hd high pressure steam is calculated for the BM versions (1) and (3), with the data and values for H ₂ O _d without and for (H ₂ O _Hd ) are indicated in brackets.

It takes place mainly by convection in the pipe 26 bundle existing heat exchanger WT. For the heat flow per time unit applies according to Newton: dQ / dt = α _Ko AΔT, (9) with A = 2πnrL, the effective inner surface of the WT, see values for the WT2 in 4 , with the total length L = 0.85 (0.85) m of the n = 12 tubes 26 with r = 0.0015 m and
α _Ko = Nuλ / 2r, the convective heat transfer coefficient, with
λ = 0.055 (0.1) W / (mK), the thermal conductivity of the H ₂ O _d (of the H ₂ O _Hd ) averaged over the corresponding temperature range, and the
Nusselt number Nu = 0.0235 Re ^0.8 Pr ^0.48 , with the Reynolds number Re = vρ2r / η and the
Prandtl number Pr = ηc _p / λ, dimensionless characteristics, with
η = 22 (62) 10 ^-6 kg / (ms), the dynamic viscosity and
c _p = 2100 (7600) J / (kgK), the specific heat at constant pressure.

With the flow speed
v = (V _{d (Hd)} / 3600 s) / πnr ² = (19,4 (0.29) m ^3/3600 s) / 8.5 10 ^-5 m ² 63 (11) m / s according to Eq. 2, for U = 3000 / min of the DKM, the pressure loss in the tube 26 Bunch too Δp = λ '(1 / 2r) ρ / 2v ^1.75 , (10) with λ '= 0.3164 / Re ^0.25

With the density ρ = 1.54 (100) m ³ / kg, the dimensionless parameters of Re = 13,000 (53,000) and Pr = 0,84 (4,7) are obtained and used in the equations. 9 and 10 result for the H ₂ O _d (H ₂ O _Hd ) vapor pressure drop Δp and a temperature difference .DELTA.T of
Δp = 0.1 (0.46) bar and ΔT = 25 (4) ° C.

For the WT2 / KAT, the values ΔT for the WNV operated with the BM version (1) can still be reduced below higher Δp values, in particular by reducing the pipe radius r and by simultaneously increasing the total length L and possibly increasing the size n, wherein the volume content of the heat exchanger in question is kept constant.

For the other BM versions and the corresponding WT's the dimensioning is much freer to design and optimize, especially with regard to the simultaneous use of the WT2 as a catalyst KAT or the optimal utilization of the exhaust gas ( 13 ) heat for the BM mixtures ((2)), (3) and ((4)).

For the H ₂ O _Hd high-pressure steam, the conditions are completely uncritical, since both the small Δp and the ΔT are well within the given range of Δp <5 bar and ΔT <30 ° C and here in particular the high pressure of p ~ 190 bar the high-pressure liquid pump is constructed.

In 5 is as an example a P _GuD = 200 MW (without WNV) combined cycle power plant (with WNV P _{GuD + WNV} = 234 MW) with a gas turbine GT4, z. B. by a gas or oil ( 55 )burner 54 , with compressor turbine 52 shown which the exhaust gas flow 13 to operate a high-HD DT3 and a medium pressure steam turbine MD DT3 '(and without WNV with a low pressure ND DT3'') generated.

The GT4 is directly charged with the up to 1250 ° C hot exhaust gas 13 the furnace 54 and with P _GT = 133 MW provides about two-thirds of the power of the combined cycle plant, the remaining third of P _DT = 67 MW would be provided by the DT3.3 ', 3''without WNV.

To the two DT's, the HD DT3 and the MD DT3, instead of the ND DT3 '' a WNV is coupled, here as example consisting of
five large - volume two - disk rotary engines DKM, which the
Dimensions A = 1100 mm and B = 450 mm, compare 3 , at a speed of
U = 1500 / min.

Of the five DKMs, only one is schematic with DM0 / WP5, DM1 and DM2,3, as the three (four) components of WNV, in 5a located.

Each of the five DKMs delivers at a transport volume of V _T = 85 liters according to Eq. 2
Vd / s = V _T × 1500 / min / 60 × 1.5 = 3.2 m ³ / s

What with a H ₂ O _d vapor density of ρ _d = 4 kg / m ³ , a promoted H ₂ O _d mass of
m _d / s = 5 × 3.2 m ³ / s × 4 kg / m ³ = 64 kg / s
for all 5 DKM's, see below.

The use of large-volume rotary piston machines DKM up to a cylinder diameter of A> 100 cm, for the dimensioning see 3 , which is possible at the above speed, has been demonstrated by Curtis-Wright and Ingersoll Rand, and the more continuous compression and expansion processes used here can be controlled more easily than the explosive combustion processes of using a large volume DCM as a VM.

Further, heat exchangers / evaporators, WT0 '' / VD, WT1, WT2, WT3 and WT4, and a compressed air reservoir DLS 20 (a pressure exhaust gas storage DAS is not shown) with heat insulation 53 for storing the compressed air 10 ' provided for the WNV by atmospheric air 10 (or exhaust 13 ) through the port 29 over two three-way valves 6 can be operated in the reverse direction as air compressor LV1, LV2 and LV3.

In a condensation cooler 41 ' in which as foreign cooling waste heat recovery 42 , z. B. a district heating, is connected, the BM ( 11 . 11 ' ) H ₂ O _{d, Hd} completely liquefied after passing through the DT3 and DT3 'as well as the three DKM components for the BM version (3).

For the BM version (1) with the dashed cable routing in 5b only about three quarters of the H ₂ O _{d is} liquefied and the remaining quarter fed directly as H ₂ O _d steam to the circuit again, possibly by suction with a Venturi jet pump 34 in the steam flow output the DT3 to compensate for pressure differences.

Three three-way valves 6 allow the electromagnetic switching between the various functions of the WNV.

Over two pressure reducers 17 and 17 ' Both the WNV as a booster, and the firing system 54 and thus the GT4, with decoupling of the turbine compressor 52 via a clutch 57 , with the compressed air 10 ' from the DLS 20 operated or fed.

For the BM version (3), the WNV with the circuit, as in 5a drawn, operated, which also gives the GT + DT system the largest additional performance in normal mode WNV.

The special feature is that the high-pressure steam H ₂ O _Hd with p = 190 bar and T = 530 ° C, generated by a high-pressure pump 27 for H ₂ O _fl from the condensation cooler 41 ' and by heating in the first heat exchanger WT0 '' and then in the WT3, the end or the very front just behind the PM in the exhaust stream 13 in all three units, in the HD DT3, the MD DT3 'and the first WNV component DM0, at the points 14 Branched, regulated and dosed ( 7 ' ) is usually initiated with one third each.

The DT3 is operated with the first third of the H ₂ O _Hd high pressure steam alone, while the DT3 'with the second third, then a 1: 1 mixture of H ₂ O _Hd and H ₂ O _d and the WNV with the last third of the H ₂ O _Hd , so a 1: 2 mixture of H ₂ O _Hd and H ₂ O _{d are} driven by each of the resulting H ₂ O _d superheated steam is forwarded to the next stage of the chain.

This distribution can be slightly varied by the nominal values, one third each, and can be optimized by an electronic control for the respective power requirement to the combined plant.

With the BM version (3), the total expanded H ₂ O _d steam for the WNV plant at the output of MD DT3 ', with about p ~ 8 bar, corresponding to a reciprocal density of 1 / ρ = 0.25 m ³ / kg and T = 190 ° C, branched off, and instead of another low pressure ND DT3 '' stage, fed to the WNV BM circuit and sucked by the here used as an example five parallel switched DKM's, the first component of the WNV, the DM0. This high initial pressure p ~ 8 bar is necessary to ensure the high mass transport of
Δm _d / Δt = 64 kg / s H ₂ O _{d to be} achieved by the five DKM's.

The 1: 1 mixture of H ₂ O _Hd + H ₂ O _d takes place at the entrance of the DT3 'similar to a jet engine and in the first WNV component DM0 by pulsed injection into the lower chamber of the first DKM disks after closing the inlet 18 by the rotation of the rotary piston ( 25 ), which again fulfills the function of a check valve.

Injection into the DM0 can via hollow cone or ultrasonic nozzles (in 5 not drawn) for strong expansion, so that it does not come to a removal of the rotary piston by the high-pressure steam jet H ₂ O _Hd with p = 190 bar.

The advantages of using the mixture, H ₂ O _Hd + H ₂ O _d , for the two units, the DT3 'and the WNV, instead of an ND DT, have been seen in the 3a and discussed in detail in the introduction.

The second advantage is the possibility of using the WNV as an air / exhaust compressor and as a booster.

The calculation of the performance of the combined cycle plant with downstream WNV plant for the BM version (3) used here is carried out analogously to that for the internal combustion engine VM2, and the corresponding TS diagram is a cycle for the WNV, DM0, DM1 and DM2, in 2d in drawn.

The following correction factors are used:
η _n.ad = η _WÜ = 0.8, η _Str = 0.95 and η _KV = 0.85. Tab. 2: Values for the cycle cycle of a WNV with a steam turbine DT and the BM mixture (3), high-pressure steam H ₂ O _Hd plus superheated steam H ₂ O _d H ₂ O _Hd H ₂ O _d eff. enthalpy DT / WNZ comp. p / bar T / ° C p / bar T / ° C T _m / ° C ΔH _eff unit HD DT3 190 530 383 × 0.5 kJ / kg MD DT3 ' 190 530 35 447 500 502 kJ / kg 71 * kJ / kg 573 × 1 kJ / kg DM0 190 530 0.95 350 440 42 * kJ / kg DM1 15-7.5 440-300 172 kJ / kg DM2 7.5 to 1 300-100 333 kJ / kg 547 × 1.5 kJ / kg total (-12 + 1585) × 64 kg / s kJ / kg P _{DT + WNV} = 101 MW P _{DT + WNV} / P _DT 101 MW / 67 MW = 1.51 .DELTA.Q / .DELTA.t 153 MW η _{DT + WNV} = P _{DT + WNV} / (ΔQ / Δt) 0.51

The corresponding numerical values for the BM 11 . 11 ' (3): H ₂ O _d + H ₂ O _Hd are calculated from the sum of the ΔH _eff values, subtracting the power consumption of the high pressure pump HP with P _HP = 12 kJ / kg x 64 kg / s = 0.77 MW of the Power of the DT3,3 'deducted with WNV system, so that multiplied by the mass flow Δm / Δt = 64 kg / s results in a total power of P _{DT + WNV} = 101 MW for the DT + WNV, thus an increase of P _WNV = 34 MW corresponding to 51%.

The performance of the GT + DT system is being boosted by WNV
P _{GT + DT + WNV} = 234 MW, ie by 17%.

The ΔH _eff values marked with a * again result from the volume work according to Eq. 6 by the entry of the H ₂ O _Hd high pressure into the H ₂ O _d superheated steam see Tab. 1.

For the implicit increase of the enthalpy values the mixture H ₂ O _d + H ₂ O _Hd , see the thin arrows -> in the TS diagrams in 2d (b and c).

From the quotient of P _{DT + WNV} and the heat energy supplied per unit time ΔQ / Δt results in a common efficiency for the DT3,3 '+ WNV plant of
η _{DT + WNV} = 0.51.

The combined cycle power plant with WNV and the two-stage DT3,3 'thus provides an increase in the joint efficiency η _{GuD + WNV} η _{GuD + WNV} = η _GT + η _WÜ η _{DT + WNV} (1-η _GT ) = 0.45 + 0.85 × 0.51 (1 - 0.45) = 0.69 (11) that is, to almost 70%, assuming an efficiency η _GT = 0.45 for the GT4 and the heat transfer in the WTs from the exhaust gas 13 the GT4 on the BM ( 11 ' . 11 ) was _calculated with an efficiency of η _WÜ = 0.85.

This high value for η _WÜ = 0.85 is justified, since most of the BM from the supercritical H ₂ O _Hd high pressure steam 11 '' exists and the heat transfer from the exhaust stream 13 lighter than for the H ₂ O _d superheated steam, see description 4 ,

In 5b is schematically shown with the dashed wiring the circuit for operation of the WNV with the one-component BM according to version (1): H ₂ O _d dashed lines. This version is the same as for the VM2 in 3b shown and described there in more detail. In this case, the temperature T and thus the H ₂ O _d vapor pressure p _d in the condensation cooler 41 ' varies and adapted to the vapor pressure output of the DT3 '.

As a result of an analogous to the above calculation results in an efficiency of
η _{DT + WNV} = 0.47
which results in an overall efficiency of the GT + DT + WNV
η _{GuD + WNV} = 0.67.

Moreover, the DKN combined gas turbine system is not as susceptible to the formation of droplets during the expansion of H ₂ O _d as the steam turbines DT 3,3 '(3''), and therefore the relaxation of H ₂ O _d BM 11 into the two-phase range, H ₂ O _d + H ₂ O _fl (far). In a DT, an H ₂ O _fl fraction of (1 - x)> 0.12 would damage the turbine blades by erosion.

The further advantage of the WNV combination is that it can be used in low-consumption times by switching over three three-way valves 6 as a multi-stage air compressor LV (or exhaust gas compressor AV) can be used, which has an inlet 29 atmospheric air 10 (or exhaust 13 ), see 1 and compare 3 , for charging a large-volume compressed-air storage DLS 20 (Pressure exhaust gas storage DAS 50 ) the (the) with a heat insulation 53 is surrounded (are).

With the stored, heated compressed air 10 ' (the pressure exhaust gas 13 ' ) can then via a controllable pressure reducer 17 the WNV system itself and / or the GT4 are operated with or without a reduced fuel supply.

How out 5 can be seen, at least remain the exhaust 13 Heat exchanger WT1 (and possibly also the WT2) in the LV flow and are thus by the hot, compressed air 10 ' heated.

The DKM also has the three functions described above.

In peak load times, the boost function of the WMV system can be coupled with charging the GT4 with the stored compressed air 10 ' from the DLS ( 20 ) via a second pressure reducer 17 ' , Will the turbine compressor 52 the GT4 decoupled, eliminating the 40% power consumption, and under charging the fuel 55 Charged furnace 52 and the GT4 only by the compressed air 10 ' from the DLS 20 the performance of the GT4 + DT3,3 'system can even be increased by almost two thirds along with the WNV booster function for peak load times,
P _{GT + DT + WNVBoost} / P _{GT + DT} = (P _GT / 0.6 + P _{DT + WNV} ) / P _{GT + DT} > 1.61
assuming the GT4 is designed for the higher power output, and the capacity of the DLS 20 is equal to big.

The compressed air storage is already used today in areas where no water storage pumping station is possible with high efficiencies.

• – drei Ansaug-, Kompressions- und Ausstoßtakte pro Umdrehung, mit hier getrennter Nutzung der unteren und der oberen Zylinderkammer 22, 22',
• – keine Ventile, und
• – im Vergleich mit Hubkolbenmaschine höhere Drehzahlen möglich, und damit ein inhärent hohes Leistungs-/Volumenverhältnis gegeben.

The DKM has the advantages again:

• - Three intake, compression and ejection cycles per revolution, with here separate use of the lower and upper cylinder chamber 22 . 22 ' .
• - no valves, and
• - Compared with reciprocating engine higher speeds possible, and thus given an inherently high power / volume ratio.

The problem of the sealing strips should be solved with the materials, SiC, Nikosil, Ferotic, carbon-antimony, carbon-aluminum or here because of the aggressiveness of the BM's with cast sealing strips against a chrome coating of the rotary piston surfaces.

• – die WNV plus die verschiedenen Primärmaschinen (PM), mit den vorgesehenen BM Versionen allein durch die Nutzung der Abwärme der PM, Wirkungsgrade von 0,41 < η_PM+WNV > 0,59 bis 0,69 erreicht werden, für die PM, den VM2 bzw. die GT4 + DT3 oder auch den Brenner BR9, ohne Einrechung der weiteren Nutzungsmöglichkeiten der WNV
• – die Leistung eines VM2 um Faktoren 1,59 bis zu 2.3 und die einer GuD Anlage um Faktoren 1,17 bis zu 1,61 gesteigert werden können, wobei die ersten Werte unter Normaleinsatz und die zweiten unter Nutzung der WNV als Booster erreicht werden, teilweise ohne große bzw. mit konstruktiven Änderungen, die an den PM’s vorgenommen werden müssen. Eine Nachrüstung ist auch im Falle der GT + DT Anlagen denkbar.

In summary, it can be concluded that

• - the WNV plus the various primary machines (PM), with the envisaged BM versions achieved solely by the use of the waste heat of the PM, efficiencies of 0.41 <η _{PM + WNV} > 0.59 to 0.69, for the PM, the VM2 or the GT4 + DT3 or the burner BR9, without counting the other uses of the WNV
• - the performance of a VM2 can be increased by factors of 1.59 to 2.3 and that of a CCGT by factors of 1.17 to 1.61, whereby the first values are achieved under normal use and the second as boosters using the WNV, sometimes without major or constructive changes that must be made to the PM's. Retrofitting is also conceivable in the case of GT + DT systems.

QUOTES INCLUDE IN THE DESCRIPTION

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Cited patent literature

• DE 10259488 A1 [0038, 0041]

Claims (10)

Waste heat supplied heat utilization device (WNV) behind a waste heat / the exhaust gas supplying primary unit, a burner, a gas / steam turbine (GT / DT) or an internal combustion engine (VM), characterized in that a) the WNV consists of several components, which the liquid / vapor and / or partially gaseous operating medium BM (s) 11 '' . 11 ' . 11 . 13 ) and compress (DM0, WP5, 27 ) and subsequently relax (DM1, DM2, DM3) in a single closed or partially open BM ( 11 '' . 11 ' . 11 . 13 ) Flow system, and c) the following versions can be used as operating medium BM of the WNV (1) a pure superheated steam ( 11 ) or ((2)) a mixture of parts of the exhaust gas ( 13 ) and a supercritical high pressure steam ( 11 ' ) or (3) a mixture of superheated steam ( 11 ) and the high pressure steam ( 11 ' ), or ((4)) a mixture of BM steam ( 11 ) and the high pressure steam ( 11 ' ), to which mixture in the last or in one of the last WNV expansion components (DM3) still parts of the exhaust gas ( 13 ) and c) all these resources BM ( 11 '' . 11 . 11 ' . 13 ) various evaporators (VD) and / or heat exchangers (WT0, VD / WT0 ', VD / WT0'', WT1, WT2, WT3, WT4) with enthalpy and subsequently the WNV relaxation components (DM0, DM1, DM2, DM3) under working performance depending on the BM version partially ((1)), ((2, 4))) or completely ((3)) condense and the resulting BM liquid ( 11 '' ) via a high-pressure pump ( 27 ) for generating the supercritical high-pressure steam ( 11 ' ) and the remaining BM steam ( 11 ) Both are attributed to the BM cycle, and e) the WNV can be used for further performance-enhancing, energy-saving and / or recuperating functions. Waste heat-fed heat utilization device according to claim 1, characterized in that a) that the BM ( 11 ' . 11 . 13 ) is taken directly from the primary aggregate and / or the separate BM ( 11 '' . 11 ' . 11 . 13 ) by the cooling waste heat and / or the exhaust gas ( 13 ) of the VM2, the GT4 + DT3 plant or the burner (BR9) in evaporators (VD) and / or heat exchangers (WT0, VD / WT0 ', VD / WT0'', WT1, WT2, WT3, WT4) enthalpy is supplied, and c) the resource BM consists of (1) a pure vapor ( 11 ) or ((2)) a mixture of a part of the exhaust gas ( 13 ) one of the primary units and a high-pressure steam BM ( 11 ' ), which by a high-pressure pump ( 27 ) Is applied on p ≈ p _crit and (WT0 with heat exchangers, WT0 ', WT0'', WT1, WT3) was heated to a temperature T> T _crit, or (3) a mixture of steam BM ( 11 ) and the high pressure steam ( 11 ' ) prepared as in version ((2)) or ((4)) a mixture of BM steam ( 11 ) and the high pressure steam ( 11 ' ), in which or in one of the last WNV expansion components (DM3) still parts of the exhaust gas ( 13 ), after, as for the BM version ((2)) behind the previous WNV component (DM2), the main part of the BM ( 11 ) Steam already in the BM ( 11 . 11 ' . 11 '' ) Cycle was returned, and d) the respective resource BM ( 11 ' . 11 . 13 ) after aspiration, compression or mixing in the first WNV component (WP5 or DM0), the WNV expansion components (DM0, DM1, DM2, DM3) subsequently run under working power and in the last WNV components (DM2, DM3) condensed to a small extent, and e) in a condensation condenser ( 41 . 41 ' ) - condensed for the BM version (1) another part, the evaporator / heat exchanger (VD / WT0, WT0 ') as well as the remaining BM ( 11 ) Steam in the BM ( 11 . 11 ' . 11 '' ) Cycle or, for the BM version (3), the entire BM ( 11 ) Condensed steam and the high pressure pump ( 27 ) in the BM ( 11 . 11 ' . 11 '' ) Or, for the BM versions ((2)) and ((4)), the entire BM remaining in the vapor region ( 11 ) to the BM fluid ( 11 '' ) and condensed via the high-pressure pump ( 27 ) in the BM ( 11 . 11 ' . 11 '' ) Recycled cycle and the BM exhaust ( 13 ) proportion is released to the environment. Waste heat-fed heat utilization device according to claims 1 and 2, characterized in that the components of the WNV, the WP5 / DM0 and / or the relaxation devices DM1 and DM2,3 are used in the reverse direction of charging, a) as an air compressor (LV), with suction of Air ( 10 ) from the surrounding atmosphere through a port ( 29 ), for charging the VM2 in its warm-up phase, in the lower part-load operation of the VM2 up to a to be determined transition speed U _U / min and high power requirement to the VM2 or to charge the primary engine (PM), and b) as LV or exhaust gas compressor (AV), with intake of partially cooled exhaust gas ( 13 ) behind the last heat exchanger (WT1, WT0 '') during pushing and braking operation of the motor vehicle for recuperation of kinetic energy or under load operation of a stationary VM2 or a GT4 + DT3 system or a burner (BR9), storing the generated compressed air ( 10 ' ) / the pressure exhaust gas ( 13 ' ) in a compressed air storage DLS ( 20 ) or a pressure exhaust gas storage DAS ( 50 ), each of which isolates heat well ( 53 ), and then the stored compressed air ( 10 ' ) / the pressure exhaust gas ( 13 ' ) via adjustable pressure reducers ( 17 . 17 ' ) in the VM2 or the GT4 plus Feuerungsstelle ( 54 ) is used for operation with or without reduced fuel supply, or without use of the turbine compressor ( 53 ) of the GT4, or c) the WNV itself is operated as a booster, by charging with the stored compressed air ( 10 ' ) / the pressure exhaust gas ( 13 ' ) via an adjustable pressure reducer ( 17 ), and (d) the ancillary equipment of the VM2 in a vehicle, the brake booster, the power steering system, the starter and other auxiliary equipment suitable for this purpose, on compressed air ( 10 ' ) and e) before and after each switching of the WNV to LV / AV operation over several revolutions of the WNV these with air from the atmosphere ( 10 ) or with BM steam ( 11 ) from the BM circulation through flushing valves ( 8th ) is rinsed. Waste heat-fed heat utilization device according to one of claims 1 to 3, characterized in that a) as BM alone a steam ( 11 ), which preheats and vaporizes in heat exchangers WT0, WT0 'in the low temperature region of the PM and then by the first component of the WNV, which works as a heat pump WP5, sucked through heat exchangers WT0 and WT1 and behind the WP5 in another WT2, with a check valve ( 34 ) and has a total internal volume approximately equal to the transport volume VT of the first WNV component (WP5), is compressed, wherein the WT2 in the exhaust gas flow ( 13 ) is arranged directly behind the primary machine PM, and b) the thus maximum heated BM superheated steam ( 11 ) passes through the other components of the WNV (DM1 and DM2), under relaxation and work performance and thereby to a smaller part (1 - x) <0.25, with x = BM vapor content, in the last component (DM2) or in the following cooler ( 41 . 41 ' ) and the remaining BM vapor ( 11 ) Main part x with replacement of the condensed (1 - x) fraction, by evaporation of liquid BM ( 11 '' ) in evaporators (VD) the BM circuit directly or by means of a Venturi jet pump ( 57 ) and c) as operating medium BM ( 11 '' . 11 ' . 11 . 13 ) - water mixed with a lubricating and / or a self-lubricating antifreeze, or - a suitable carbon-hydrogen-oxygen compound with self-lubricating properties or mixed with a lubricant, or - a glycerine or silicone or other synthetic fluid with self-lubricating properties and suitable. Boiling points and vapor pressures. Waste heat-fed heat utilization device according to at least one of claims 1 to 4, characterized in that a) a part of the initially liquid BM ( 11 '' ), preheated by heat exchangers (WT0, WT0 ') in the cooling system of the PM and / or around the first stage of the WNV or preheated by heat exchangers (WT0'') in the exhaust gas flow ( 13 ) of the PM, by a high-pressure pump ( 27 ) _Crit brought to a pressure of p ~ p and (through a heat exchanger (WT2 or WT3) in the exhaust stream 13 ) is heated to at least one temperature T> T _crit , and b) from the first WNV component (DM0) either the other part of the BM ( 11 ) in vapor form, vaporized in the evaporator / heat exchanger (VD / WT0) and heated in the WT1 or part of the exhaust gas ( 13 ), after the partial heat release to all heat exchangers, is sucked in, and after closing the feed, the inlet ( 18 ) of the first WNV component (DM0), the supercritical high pressure BM ( 11 ' ) via a metering valve ( 7 ' ) through a port ( 28 ) is metered injected, and a 1: 1 to 1: 4 mixture of high-pressure steam / steam ( 11 ' . 11 ) or / exhaust gas ( 11 ' . 13 c) which is subsequently expanded in at least two WNV expansion devices (DM1 and DM2) under working performance, and either d) thereby and / or in a subsequent condensation cooler ( 41 . 41 ' ) just as much BM ( 11 ) Condensed out steam, in order then in liquid form, according to point a), the high-pressure pump ( 27 ) and thus to be recirculated to the BM cycle, or e) the vapor content ( 11 ) of the BM mixture ( 11 . 13 ) Steam / exhaust gas during the expansion and subsequently in the cooler ( 41 . 41 ' ) fully condensed and after cleaning the BM ( 11 '' . 11 ) Liquid circuit, as in a), is supplied again, and thereby the water content of the exhaust gas ( 13 ) Has compensated evaporation losses in the partially open BM flow system, and the remaining exhaust gas ( 13 ), that abgasseits before the WT2 / KAT before and then by the mixture with the vaporous or liquid BM ( 11 . 11 '' ) and in the cooler ( 41 ' ) was cooled down, is released to the atmosphere, and f) a cleaning of the liquid BM ( 11 '' ) is provided by filters and / or chemicals with precipitation, and after a high hourly cycle greater than 500 hours, an exchange with recycling of the BM ( 11 '' ) he follows. Waste heat-fed heat utilization device according to claim 5, characterized in that the operating medium BM ( 11 ' . 11 ) is prepared according to the points a) and b) of claim 5 and the last WNV expansion component is divided into two stages (DM2 and DM3), wherein after DM2 the steam cycle required for the periodic BM cycle ( 11 ) portion in the BM cycle is returned, and only in the last component (DM3) the entire (or parts of) the exhaust gas (es) ( 13 ) of the primary unit, the VM2, the GT4 or the burner (BR9), the remaining BM ( 11 ) Steam is added after it has reached a pressure p _d <p _a , the pressure of the exhaust gas ( 13 ), and the new mixture ( 11 . 13 ) from residual BM vapor ( 11 ) and the admixed exhaust gas ( 13 ) then go through points e) and f) of claim 5. Waste heat-fed heat utilization device according to at least one of claims 1 to 6, characterized in that a) the components of the WNV system for the compression / expansion processes are lifting, rotary or radial piston machines, or for rotary vane or vane machines are used, and b) as an internal combustion engine VM2 a gasoline engine, a rotary piston engine, a diesel or Diesottomotor find use, and c) a (compact) WNV plant (also as a retrofit kit) behind a PM, is installed behind a VM2 in any (power) vehicle or behind stationary VM2 or GT4 + DT3 systems, each with its own control, and d) the VM2 is operated with compressed (natural) gas, and the pressure vessels used for this purpose after their consumption-related emptying as compressed air DLS ( 20 ) or pressure exhaust gas storage DAS ( 50 ) be used. Waste heat-fed heat utilization device according to at least one of claims 1 to 7, characterized in that the heat utilization device WNV a) is a rotary piston machine DKM, which is used as a compression WP5 and relaxation device DM0, DM1 and DM2 and has refined cylinder surfaces and suitable sealing strips, and b ) this one multi-disc DKM is equipped with a two-pronged trochoid as a cylinder housing ( 1 . 1' ) and one piston each ( 25 . 25 ' ) in the form of an equilateral arch triangle, which in the housing ( 1 . 1' ) rotates in a planetary manner, and c) on each DKM housing disc ( 1 . 1' ) two each ( 18 to 18 ' ) and outlets ( 19 to 19 '' ) for the two each with a 2/3 turn of the rotary pistons ( 25 . 25 ' ) forming cylinder chambers ( 22 . 22 ' ) are arranged so that the intake and exhaust stroke do not overlap or hardly overlap, and d) the two cylinder chambers ( 22 . 22 ' ) are used for separate functions, for compression and / or relaxation or as a closable mixing chamber (DM0), and cooling by water ( 21 ), through the liquid and / or the vaporous BM ( 11 '' . 11 ) and e) the DKM is used on the side and each disc ( 1 . 1' ) with at least two side inputs ( 18 to 18 ' ) and outlets ( 19 to 19 ''' ), and f) the DKM as a WNV system with or without a gearbox ( 16 ) with the drive / crankshaft ( 29 ) of a VM2 or a steam turbine DT3, 3 'is coupled. Waste heat-fed heat utilization device according to at least one of claims 1 to 8, characterized in that a) the structure of the heat exchanger WT0,0 ', WT1 and in particular that of the WT2 is optimized so that the enthalpy transfer between the exhaust gas ( 13 ) and the BM to be heated ( 11 ' . 11 ) at the smallest possible temperature difference ΔT <30 (20) ° C between the two and at the same time the pressure drop Δp <0.2 bar (2 bar for the H ₂ O _Hd high-pressure steam) for use behind a VM2 or a DT3,3 'not and b) the total internal volume of the heat exchanger WT2 is selected to be approximately equal to the transport volume V _{T of} the first WNV component (WP5), and at the inlet of the WT2, the outlet ( 19 ) of the WP5 compressor, a smooth non-return valve ( 37 ) is arranged with the smallest possible volume requirement, and c) at least one heat exchanger (WT2) abgasseits coated to a part with precious metal (s) and dimensionally designed so that this at the same time as exhaust gas ( 13 ) Catalyst (KAT) is usable, and at least one heat exchanger (WT1) abgasseits prepared to a part as an oxidation catalyst and fresh air and / or as a carrier of a particulate filter is useful and dimensionally designed for d) the materials of the sewer pipes ( 26 ) are chosen so that they are resistant to aggressive BM fluids ( 11 '' ) and the BM vapors ( 11 ' . 11 ) and the exhaust gas ( 13 ) Components are inert, and their wall thicknesses (d) so thick be chosen that the channels ( 26 ) withstand the required pressures during operation of the WNV, also as air (LV) and exhaust gas compressor (AV), and e) in the heat exchangers (WT0, WT0 ') also used as evaporators (VD) hollow cone or ultrasonic nozzles ( 24 for spraying into fine droplets or ultrasonically charged surfaces for atomizing the liquid BM ( 11 '' ) and f) by an extreme value task in each operating state the optimum mixing ratio BM steam ( 11 ) to BM high-pressure steam ( 11 ' ) is calculated by the control computer, depending on the number of revolutions rpm, the offered temperatures of the VM2 cooling water, the DM0 / WP5 and possibly also the DM1, and in particular of the exhaust gas 13 Then, the flow rate of the high-pressure pump 27 and / or via the metering valve 7 ' the injection quantity of H ₂ O _{Hd is} set. Waste heat-fed heat utilization device according to at least one of claims 1 to 9, characterized in that an electronic control for the heat utilization device WNV, here z. As the DKM, which works as a compression and / or relaxation device, as a heat pump plus steam engine (WP + DM), as a booster, or as air / exhaust compressor LV / AV or exhaust gas compressor (AV) system, for the respective operating conditions the VM2 or the DT3 the following parameters are varied in such a way that the contribution to the power P _WNV and the other possible uses of the WNV system to the waste heat supplying primary machine (PM), the VM2 or the GT4 / DT3 are optimally used, a) the over- or the reduction ratio of the transmission ( 16 b) in the case of the VM2 installed in a vehicle whose performance requirement is optimized, with charging of the VM2 and / or the DLS (FIG. 2), which is switched on for coupling between the WNV and the VM2 or the DT3 (FIG. 20 ) or DAS ( 50 ) directly with LV / AV operation of the WNV, or the charging of the VM2 from the DLS ( 20 ) via the adjustable pressure reducing valve ( 17 ), and c) under compressed air ( 10 ' ) or with pressure exhaust gas ( 13 ' ) via the pressure reducer ( 17 . 17 ' ) from the DLS ( 20 ) or the DAS ( 50 ): the use of the WNV as a booster, the VM2 as a compressed air motor or the operation of the GT4 and its firing system 54 under decoupling of the turbine compressor 52 , and d) the circuit of the three-way valves ( 6 ) and the purge valves ( 8th ), when switching the DKM from WNV to LV / AV mode, and e) the adjustable pressure reducers ( 17 . 17 ' ) behind the compressed air DLS ( 20 ) and the pressure exhaust gas storage DAS ( 50 ) and the check valve ( 7 ) in the intake manifold ( 38 ) of the VM2, as well as f) the safe switching off and on again of the vehicle VM2 even while driving with the aid of the stored compressed air ( 10 ' ) or the pressure exhaust gas ( 13 ' ), which maintain the other necessary functions of the vehicle, such as steering and braking assistance, even when the VM2 is switched off, and g) the electronic control is used together with a retrofit kit for all three primary units.

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