DE19806654A1 - Air conditioning system for a motor vehicle powered by an internal combustion engine - Google Patents
Air conditioning system for a motor vehicle powered by an internal combustion engineInfo
- Publication number
- DE19806654A1 DE19806654A1 DE19806654A DE19806654A DE19806654A1 DE 19806654 A1 DE19806654 A1 DE 19806654A1 DE 19806654 A DE19806654 A DE 19806654A DE 19806654 A DE19806654 A DE 19806654A DE 19806654 A1 DE19806654 A1 DE 19806654A1
- Authority
- DE
- Germany
- Prior art keywords
- heat
- heat exchanger
- air conditioning
- combustion engine
- internal combustion
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H1/00899—Controlling the flow of liquid in a heat pump system
- B60H1/00907—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant changes and an evaporator becomes condenser
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00007—Combined heating, ventilating, or cooling devices
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H2001/00928—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising a secondary circuit
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H2001/00957—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising locations with heat exchange within the refrigerant circuit itself, e.g. cross-, counter-, or parallel heat exchange
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/16—Receivers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/05—Refrigerant levels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2501—Bypass valves
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Air-Conditioning For Vehicles (AREA)
Abstract
Description
Die Erfindung betrifft eine Klimaanlage zum Heizen und Kühlen des Fahrgastraumes eines durch eine Verbrennungskraftmaschine angetriebenen Fahrzeuges, mit einem ersten, eine Umwälzpumpe und mindestens einen Wärmetauscher aufweisenden Kanalnetz für die Zirkulation eines Wärmeträgers zur Ableitung von Wärme aus der Verbrennungskraftmaschine sowie zur Heizung des Fahr gastraumes und mit einem zweiten, einen regelbaren Kompressor, mehrere Wärmetauscher und mindestens eine Expansionsein richtung aufweisenden, eine Kreislaufströmung ermöglichenden Kanalnetz für die Zirkulation eines anderen Wärmeträgers, wo bei einer der Wärmetauscher des zweiten Kanalnetzes ein Kli matisierungswärmetauscher ist, indem dieser in einem zu dem Fahrgastraum führenden Belüftungskanal angeordnet ist.The invention relates to an air conditioning system for heating and cooling of the passenger compartment by an internal combustion engine driven vehicle, with a first, a circulation pump and at least one heat exchanger having duct network for the circulation of a heat transfer medium to dissipate heat from the internal combustion engine and for heating the vehicle and with a second, an adjustable compressor, several heat exchangers and at least one expansion directional, enabling a circulatory flow Duct network for the circulation of another heat transfer medium, where a Kli at one of the heat exchangers of the second sewer network matatisation heat exchanger is in one to the Ventilation duct leading passenger compartment is arranged.
Bei Klimaanlagen der genannten Art bildet das zweite Kanal netz in der Regel eine Zusatzausrüstung zu der in jedem Kraftfahrzeug vorhandenen, durch Kühlwasser der Verbrennungs kraftmaschine betriebenen Anlage zur Heizung des Fahrgast raumes, so daß der für die Kühlung vorgesehene Klimatisie rungswärmetauscher mit entsprechendem Raumbedarf zusätzlich zu dem grundsätzlich vorhandenen, für die Heizung vorgesehe nen Klimatisierungswärmetauscher in dem zum Fahrgastraum füh renden Belüftungskanal angeordnet ist und für beide Kanalnet ze jeweils eine Regeleinrichtung vorgesehen ist. Die Anord nung der Klimatisierungswärmetauscher in Strömungsrichtung der Belüftung hintereinander führt zu entsprechend großem Raumbedarf, folglich zu erhöhtem konstruktiven Aufwand und außerdem zu erhöhtem Strömungswiderstand des Belüftungsstro mes.In air conditioning systems of the type mentioned, the second channel forms usually an additional equipment to that in each Motor vehicle existing, through cooling water of combustion Engine operated system for heating the passenger space, so that the air conditioning intended for cooling heat exchanger with additional space requirements to the fundamentally available heating system air conditioning heat exchanger in the lead to the passenger compartment renden ventilation duct is arranged and for both duct network ze a control device is provided. The arrangement air conditioning heat exchanger in the direction of flow the ventilation in succession leads to a correspondingly large one Space requirement, consequently to increased design effort and also to increased flow resistance of the ventilation flow mes.
Die durch das erste Kanalnetz der bekannten Klimaanlage er folgende Klimatisierung durch Heizen hat den schwerwiegenden Nachteil, daß bei Kaltstart der Verbrennungskraftmaschine deren Wärme erst nach ausreichender Erwärmung des Motorkühl wassers und somit zu spät zur Verfügung steht, um vereiste Scheiben des Fahrgastraumes vor Start des Fahrzeuges abzu tauen.He through the first duct network of the known air conditioning system the following air conditioning by heating has the serious Disadvantage that when the internal combustion engine is cold started their heat only after sufficient warming of the engine cooling water and is therefore available too late to freeze Remove windows of the passenger compartment before starting the vehicle Thaw.
Der Erfindung liegt die Aufgabe zugrunde, eine Klimaanlage zum Heizen und Kühlen zu finden, die beim Heizen sofort nach dem Start der Verbrennungskraftmaschine aus kaltem Zustand eine hohe Wärmeleistung zur Verfügung stellt. Dabei soll sie mit verhältnismäßig geringem Raumbedarf und verringertem konstruktiven und regeltechnischem Aufwand verbunden sein.The invention has for its object an air conditioning system to find heating and cooling that immediately after heating the start of the internal combustion engine from a cold state provides a high thermal output. It should with relatively little space and reduced constructive and control-related effort.
Die Lösung dieser Aufgabe erfolgt erfindungsgemäß dadurch, in dem zweiten Kanalnetz mindestens ein durch eine Regelein richtung umschaltbarer Strömungsverteiler angeordnet ist, durch dessen Umschaltung jeweils der Strömungsweg für einen von zwei Betriebskreisläufen des Kanalnetzes zur wahlweisen Beheizung oder Kühlung des Fahrgastraumes gebildet wird, in welchem der Klimatisierungswärmetauscher und die mindestens eine Expansionseinrichtung angeordnet sind, wobei in Strö mungsrichtung an den Kompressor anschließend eine Verzwei gung für beide alternative Betriebskreisläufe vorgesehen ist, derart, daß in einem ersten der Betriebskreisläufe der Kli matisierungswärmetauscher in Strömungsrichtung hinter dem Kompressor folgt und in einem zweiten Betriebskreislauf der Klimatisierungswärmetauscher in Strömungsrichtung hinter ei nem Abwärmetauscher zur Abführung von Wärme an die Umgebung außerhalb des Fahrzeuges und hinter der mindestens einen Ex pansionseinrichtung angeordnet ist, wobei in dem ersten Be triebskreislauf in Strömungsrichtung hinter der mindestens einen Expansionseinrichtung ein Wärmetauscher vorgesehen ist, in dem der andere Wärmeträger in Wärmeaustausch mit einer Wärmequelle steht.According to the invention, this object is achieved by in the second channel network at least one by rule flow switchable direction is arranged, by switching the flow path for one of two operating circuits of the sewer network to choose from Heating or cooling of the passenger compartment is formed in which of the air conditioning heat exchangers and the at least an expansion device are arranged, wherein in Strö direction to the compressor then a branch is intended for both alternative operating cycles, such that in a first of the operating circuits of the Kli Matisation heat exchanger in the flow direction behind the Compressor follows and in a second operating cycle Air conditioning heat exchanger in flow direction behind egg a waste heat exchanger to dissipate heat to the environment outside the vehicle and behind the at least one Ex pansionseinrichtung is arranged, wherein in the first loading drive circuit in the direction of flow behind the minimum an expansion device a heat exchanger is provided, in which the other heat carrier in heat exchange with one Heat source stands.
Vorzugsweise dient die Verbrennungskraftmaschine bzw. deren Kühlsystem jeweils als Wärmequelle, indem beide Kanalnetze durch einen beiden gemeinsamen Wärmetauscher miteinander ge koppelt sind.The internal combustion engine or its is preferably used Cooling system each as a heat source by using both sewer networks ge by a two common heat exchanger together are coupled.
Zum besseren Verständnis der Erfindung wird diese im folgen den anhand der Zeichnungen erläutert. Es zeigtFor a better understanding of the invention, it will follow in the following the explained with reference to the drawings. It shows
Fig. 1 ein schematische Darstellung der Klimaanlage mit ih ren beiden Kanalnetzen, wobei zum Kühlen der zweite Betriebskreislauf des zweiten Kanalnetzes eingeschal tet ist, Fig. 1 is a schematic representation of the air conditioner with ih ren two channel systems, wherein for cooling the second operating circuit of the second channel network is inserted tet scarf,
Fig. 2 eine Darstellung der Klimaanlage nach Fig. 1, wobei zum Heizen der erste Betriebskreislauf des zweiten Kanalnetzes eingeschaltet ist, Fig. 2 is a diagram of the air conditioner of Fig. 1, wherein for heating the first operating circuit of the second channel network is switched on,
Fig. 3 ein Druck-Enthalpiediagramm für CO2 als Wärmeträger, mit einer Darstellung des ersten Betriebskreislaufes beim Heizen sowie mit einer Strichliniendarstellung des ersten Betriebskreislaufes bei Leerlaufregelung des Kompressors. Fig. 3 is a pressure-enthalpy diagram for CO 2 as a heat carrier, with a representation of the first operating circuit when heating and with a dashed line representation of the first operating circuit with idle control of the compressor.
Die Darstellungen der Klimaanlage in den Fig. 1 und 2 nach Art eines Fließdiagrammes zeigen in ihrem unteren Teil das erste Kanalnetz 1, das im wesentlichen dem üblichen Kühlsystem ei ner Verbrennungskraftmaschine 2 entspricht. Im oberen Teil der Darstellung ist das zweite Kanalnetz 3 zu sehen, das für die Zirkulation von phasenweise flüssigem und phasenweise gasförmigem Kohlendioxyd (CO2) vorgesehen ist.The illustrations of the air conditioning system in FIGS. 1 and 2 in the manner of a flow chart show in their lower part the first duct system 1 , which essentially corresponds to the usual cooling system of an internal combustion engine 2 . In the upper part of the illustration, the second sewer network 3 can be seen, which is provided for the circulation of phases of liquid and phases of gaseous carbon dioxide (CO 2 ).
Das zweite Kanalnetz 3 läßt sich durch die gemeinsame Um schaltung von z. B. zwei als Dreiwegeventile ausgeführten Strömungsverteilern 4 und 5 wahlweise mit einem ersten oder zweiten Betriebskreislauf 6 und 7 betreiben, die in den Fig. 1 und 2 durch die dickeren Linien gekennzeichnet sind.The second sewer network 3 can by the common order of z. B. operate as three-way flow distributors 4 and 5 optionally with a first or second operating circuit 6 and 7 , which are characterized in FIGS. 1 and 2 by the thicker lines.
Der zweite Betriebskreislauf 6 ist auf an sich bekannte Wei se (WO 90/07683) als Kühlkreislauf ausgeführt, indem in Strö mungsrichtung hintereinander ein Kompressor 8, ein Wärmetau scher 9, mindestens eine z. B. als Expansionsventil ausgeführ te Expansionseinrichtung 10, 11 und ein Klimatisierungswärme tauscher 12 angeordnet sind. Vorzugsweise ist in dem Kreis lauf 6 zusätzlich ein Zwischenwärmetauscher 13 vorgesehen, der zur Wärmeableitung aus dem im Kompressor 8 erhitzten CO2-Wärmeträger beiträgt und somit die Wirkung des Wärmetauschers 9 unterstützt. Weiterhin erfolgt die Expansion des Wärmeträ gers beispielsweise zweistufig in zwei Expansionseinrich tungen 10, 11, zwischen denen ein Flüssigkeitssammler 14 an geordnet ist. Die Regelung des Füllungsgrades dieses unter mittlerem Druck stehenden Sammlers 14 kann zur Pufferung und Regelung der Leistung dieses Betriebskreislaufes 6 dienen. Als Kompressor (8) eignet sich ein Taumelscheibenkompressor mit regelbarer Hubbewegung seiner Kolben, wie durch die Pa tentliteratur (z. B. EP 0 809 027, Audi AG, et al) bekannt ist.The second operating circuit 6 is carried out in a manner known per se (WO 90/07683) as a cooling circuit, in that a compressor 8 , a heat exchanger 9 , at least one z. B. designed as an expansion valve te expansion device 10 , 11 and a heat exchanger 12 are arranged. Preferably, an intermediate heat exchanger 13 is additionally provided in the circuit 6 , which contributes to heat dissipation from the CO 2 heat transfer medium heated in the compressor 8 and thus supports the action of the heat exchanger 9 . Furthermore, the expansion of the heat transfer medium takes place, for example, in two stages in two expansion devices 10 , 11 , between which a liquid collector 14 is arranged. The regulation of the degree of filling of this collector 14 , which is under medium pressure, can serve for buffering and regulation of the performance of this operating circuit 6 . A compressor ( 8 ) is a swash plate compressor with adjustable stroke movement of its pistons, as is known from the patent literature (e.g. EP 0 809 027, Audi AG, et al).
Die Kälteleistung des zweiten Betriebskreislaufes 6 wird am Klimatisierungswärmetauscher 12 zur Verfügung gestellt, der in Wärmeaustausch mit Luft steht, die durch ein nichtdarge stelltes Gebläse in Richtung der Pfeile 16 und damit zu dem Fahrgastraum des Kraftfahrzeuges gefördert wird. Ein z. B. in diesem Luftstrom angeordnet er Temperaturfühler 17 ist über eine durch die Strichlinie 18 angedeutete Signalleitung mit einer Regelvorrichtung 19 verbunden, die aufgrund des zusätz lichen Signales einer elektronischen Sollwertregelung u. a. die Leistung des Kompressors 8 regelt. Die Vorgabe für die Sollwertregelung erfolgt durch den Benutzer des Kraftfahr zeuges.The cooling capacity of the second operating circuit 6 is made available on the air conditioning heat exchanger 12 , which is in heat exchange with air, which is conveyed by a non-charged fan in the direction of the arrows 16 and thus to the passenger compartment of the motor vehicle. A z. B. arranged in this air flow, he temperature sensor 17 is connected via a signal line indicated by the dashed line 18 to a control device 19 , which regulates, inter alia, the output of the compressor 8 on the basis of the additional signal from an electronic setpoint control. The user of the motor vehicle specifies the setpoint control.
Aufgrund der Erfindung ermöglicht diese Temperaturregelung nicht nur eine Regelung der Kälteleistung, sondern auch eine Regelung der Heizleistung der Klimaanlage, so daß ein stufen loser Übergang zwischen Kühlen und Heizen möglich ist.Because of the invention, this enables temperature control not just a regulation of the cooling capacity, but also one Regulation of the heating power of the air conditioning system, so that a step loose transition between cooling and heating is possible.
Vorzugsweise hat der Kompressor 8 eine feste, d. h. kupplungs lose Antriebsverbindung mit der Verbrennungskraftmaschine 2, wofür seine Leistung durch Veränderung der Hubweite seiner Kolbenbewegungen bis auf Null regelbar ist. Falls bei Betrieb des zweiten Betriebskreislaufes 6 über seine Nulleistung hi naus durch die Regelvorrichtung 19 eine Heizleistung gefor dert wird, so bewirkt diese eine Umschaltung der beiden Strömungsverteiler 4, 5 aus der in Fig. 1 gezeigten Durchlaß position in die in Fig. 2 gezeigte Durchlaßposition und folg lich eine Umschaltung von dem zweiten Betriebskreislauf 6 auf den in Fig. 2 durch dickere Linien gezeigten ersten Betriebs kreislauf 7.The compressor 8 preferably has a fixed, ie clutchless, drive connection to the internal combustion engine 2 , for which its output can be regulated to zero by changing the stroke width of its piston movements. If during operation of the second operation circuit 6 via its zero power Naus hi by the control device 19 is a heating power is changed Shaped, thus causing this switching of the flow distributor 4, 5 from the position shown in Fig. 1 passage position into the position shown in Fig. 2 passage position and consequently a switchover from the second operating circuit 6 to the first operating circuit 7 shown by thick lines in FIG. 2.
Bei Umschaltung auf den ersten Betriebskreislauf 7 werden zwei zuvor unbenutzte Teile 20 und 21 des Kanalnetzes 3 zugeschal tet und statt dessen ein Teil 22 des Kanalnetzes 3 abgeschal tet. Der Netzteil 20 beginnt an der Verzweigungsstelle 23 und endet an dem Strömungsverteiler 4. Der zugehörige zweite Netzteil 21 beginnt an dem Strömungsverteiler 5 und endet vor dem Kompressor 8. Der abgeschaltete Netzteil 22 beginnt an der Verzweigungsstelle 23 und endet an dem Strömungsverteiler 5.When switching to the first operating circuit 7 , two previously unused parts 20 and 21 of the sewer network 3 are switched on and instead a part 22 of the sewer network 3 is switched off. The power supply 20 begins at the branch point 23 and ends at the flow distributor 4 . The associated second power supply unit 21 begins at the flow distributor 5 and ends before the compressor 8 . The switched-off power supply 22 begins at the branch point 23 and ends at the flow distributor 5 .
Die Umschaltung der Strömungsverteiler 4, 5 hat eine Umkehr der Strömungsrichtung durch die Expansionseinrichtungen 10, 11 und durch den Klimatisierungswärmetauscher 12 zur Folge, die einer Umschaltung auf einen Wärmepumpenkreislauf ent spricht. Somit beheizt der den Kompressor 8 verlassende, er hitzte Wärmeträger den Klimatisierungswärmetauscher 12 und folglich denselben Wärmetauscher 12, der zuvor die Kältelei stung für die Kühlung des Fahrgastraumes abgegeben hat.The switchover of the flow distributors 4 , 5 has a reversal of the flow direction through the expansion devices 10 , 11 and through the air conditioning heat exchanger 12 , which speaks ent to switchover to a heat pump circuit. Thus, the compressor 8 exiting, he heated the heat carrier heated the air conditioning heat exchanger 12 and consequently the same heat exchanger 12 , which has previously given the Kältelei stung for cooling the passenger compartment.
Da die Wärmeerzeugung durch Kompression des Wärmeträgers im Kompressor 8 nahezu trägheitslos erfolgt, steht bei Umschal tung zwischen beiden Betriebskreisläufen die Kühl- oder Heiz leistung am Klimatisierungswärmetauscher sofort bzw. inner halb weniger Sekunden zur Verfügung.Since the heat is generated by compression of the heat carrier in the compressor 8 almost without inertia, when switching between the two operating circuits, the cooling or heating power at the air conditioning heat exchanger is available immediately or within a few seconds.
Die für den Wärmepumpenbetrieb, d. h. den ersten Betriebs kreislauf 7 erforderliche Wärmezufuhr erfolgt über einen für diesen Betrieb mit dem Netzteil 21 zugeschalteten Wärmetau scher 24, der in Wärmetausch mit einer Wärmequelle steht, die in bevorzugter Ausführungsform der Erfindung durch die Ver brennungskraftmaschine 2 direkt oder deren Kühlkreislauf ge bildet ist.The heat supply required for heat pump operation, ie the first operating circuit 7 , takes place via a heat exchanger 24 connected for this operation with the power supply unit 21 , which is in heat exchange with a heat source, which in a preferred embodiment of the invention by the internal combustion engine 2 directly or the latter Cooling circuit is formed.
Das erste Kanalnetz 1 hat auf an sich bekannte Weise zwei Netzteile 25, 26, die durch ein Thermostatventil 27 miteinan der verbunden sind. In der Aufwärmphase der Verbrennungs kraftmaschine ist der den Kühler 28 aufweisende Netzteil 26 durch das Thermostatventil 27 abgesperrt, so daß die in dem Netzteil 25 vorgesehene Pumpe 29 das Kühlmedium nur durch den somit kurzgeschlossenen Netzteil 25 fördert. In diesem ist der Wärmetauscher 24 des zweiten Kanalnetzes 3 vorgesehen, um für dessen ersten Betriebskreislauf 7 die Wärmequelle zu bil den. Für die räumliche Position des Wärmetauschers 24 inner halb des Netzteiles sind in Abhängigkeit von der jeweiligen Gestaltung des Motorraumes des Kraftfahrzeuges und der Ge staltung der Verbrennungskraftmaschine zahlreiche konstrukti ve Ausführungsformen möglich, einschließlich einer direkten Einbeziehung in die Konstruktion der Verbrennungskraftmaschi ne.The first sewer network 1 has in a manner known per se two power supplies 25 , 26 which are connected to one another by a thermostatic valve 27 . In the warm-up phase of the combustion engine is of the cooler 28 having power supply shut off by the thermostat valve 27 26, so that the provided in the power supply unit 25 pump 29 pumps the cooling medium only by the thus short-circuited power supply 25th In this, the heat exchanger 24 of the second duct network 3 is provided in order to form the heat source for the first operating circuit 7 . For the spatial position of the heat exchanger 24 within the power supply, depending on the particular design of the engine compartment of the motor vehicle and the design of the internal combustion engine, numerous constructive embodiments are possible, including direct involvement in the construction of the internal combustion engine.
Für den Einsatz des ersten Betriebskreislaufes bzw. des Wär mepumpenbetriebs auch in Aufwärmphasen der Verbrennungskraft maschine, wenn diese stark abgekühlt ist und z. B. ein Tem peraturniveau von nur -20°C (-4°F) hat, empfiehlt sich die Verwendung von CO2 als Wärmeträger bzw. eines Wärmeträ gers oder Wärmeträgergemischs mit vergleichbaren physikali schen Eigenschaften, so daß durch Kompression und Expansion hierfür ausreichend große Temperaturdifferenzen erzielbar sind.For the use of the first operating circuit or the heat pump operation even in warm-up phases of the internal combustion engine when it has cooled down significantly and z. B. has a tem perature level of only -20 ° C (-4 ° F), the use of CO 2 as a heat transfer medium or a heat transfer medium or heat transfer medium mixture with comparable physical properties is recommended, so that it is sufficiently large for this by compression and expansion Temperature differences can be achieved.
Ein Beispiel für Verfahrensbedingungen im ersten Betriebs kreislauf 7 beim Aufheizen bei kalter Verbrennungskraftma schine von -20°C (-4°F) ist in dem Druck-Enthalpie-Dia gramm der Fig. 3 durch das Diagramm I dargestellt. Dabei sind die verschiedenen Positionen im Kanalnetz 3 und die zugehö rigen Verfahrenzustände im Druck-Enthalpie-Diagramm auf glei che Weise durch A bis D bezeichnet. Entsprechend ist bei spielsweise der Druck- und Temperaturzustand an der Position A in Strömungsrichtung vor dem Kompressor 8 im Druck-Enthal pie-Diagramm ebenfalls mit A bezeichnet. A' bezeichnet in Fig. 3 die Schnittstelle der Linie von D nach A mit der Kurve der Zustandsänderung von flüssig zu dampfförmig und ist somit charakteristisch für die Verdampfungstemperatur bei dem die sem Beispiel entsprechenden Druck des Kühlmediums CO2.An example of process conditions in the first operating circuit 7 when heating in a cold internal combustion engine of -20 ° C (-4 ° F) is shown in the pressure enthalpy diagram of FIG. 3 by the diagram I. The various positions in the sewer network 3 and the associated procedural states in the pressure-enthalpy diagram are denoted in the same manner by A to D. Correspondingly, the pressure and temperature state at position A in the flow direction upstream of the compressor 8 in the pressure enthalpy diagram is also denoted by A in example. A 'indicated in FIG. 3, the interface of the line from D to A with the curve of the change of state from liquid to vapor, and is thus characteristic of the evaporation temperature at which the sem example corresponding pressure of the coolant CO 2.
Beispiel beim Heizen bei kalter Verbrennungskraftmaschine
nach Diagramm I der Fig. 3:
Example of heating in a cold internal combustion engine according to diagram I in FIG. 3:
Umgebungstemperatur: -20°C (253°K, -4°F),
A: 14 bar, -25°C (248°K, -13°F),
B: 110 bar, +150°C (423°K, +302°F),
C: 110 bar, +30°C (303°K, +86°F),
D: 14 bar, -30°C (243°K, -4°F).Ambient temperature: -20 ° C (253 ° K, -4 ° F),
A: 14 bar, -25 ° C (248 ° K, -13 ° F),
B: 110 bar, + 150 ° C (423 ° K, + 302 ° F),
C: 110 bar, + 30 ° C (303 ° K, + 86 ° F),
D: 14 bar, -30 ° C (243 ° K, -4 ° F).
Da somit der CO2-Wärmeträger nach Verlassen des Wärmetau schers, d. h. bei A, eine Temperatur von -25°C hat, kann er bereits bei einer Temperatur des Kühlmediums der Verbren nungskraftmaschine von -20°C aus diesem Wärme aufnehmen. Diese steht nach Kompression des CO2-Wärmeträgers im Kompres sor 8 im Klimatisierungswärmetauscher 12 bei einer Temperatur von 150°C sofort bzw. wenige Sekunden nach Start der kalten Verbrennungskraftmaschine 2 zur Verfügung. Da die Verbren nungskraftmaschine 2 den Kompressors 8 antreibt, nimmt diese aufgrund ihrer elektronischen Regelung auch im Leerlauf ent sprechend mehr Energie auf, so daß in ihrem Kühlmedium mehr Wärme zur Verfügung gestellt wird, um im Wärmetauscher 24 an den CO2-Wärmeträger übertragen zu werden. So ergibt sich bei spielsweise beim Antrieb des Kompressors mit 3 kW eine Wär meabgabe von der Verbrennungskraftmaschine 2 an ihr Kühlme dium von ca. 4 kW und am Klimatisierungswärmetauscher 12 eine Heizleistung von 7 kW.Since the CO 2 heat transfer medium after leaving the heat exchanger, ie at A, has a temperature of -25 ° C, it can already absorb heat at a temperature of the cooling medium of the internal combustion engine from -20 ° C. After compression of the CO 2 heat transfer medium in the compressor 8 in the air conditioning heat exchanger 12 at a temperature of 150 ° C., this is available immediately or a few seconds after the cold internal combustion engine 2 starts. Since the combustion engine 2 drives the compressor 8 , this takes up more energy accordingly due to its electronic control even when idle, so that more heat is made available in its cooling medium to be transferred in the heat exchanger 24 to the CO 2 heat transfer medium . For example, when driving the compressor with 3 kW, there is a heat emission from the internal combustion engine 2 to its cooling medium of approx. 4 kW and at the air conditioning heat exchanger 12 a heating power of 7 kW.
Bei zunehmender Erwärmung des Kühlmediums der Verbrennungs
kraftmaschine und nachlassendem Wärmebedarf zur Beheizung des
Fahrgastraumes kann die Leistung des Kompressors 8 zunehmend
bis nahezu auf Null zurückgeregelt werden, so daß er nur
noch die Aufgabe hat, den Druckverlust zu kompensieren, der
beim Zirkulieren des Wärmeträgers im Betriebskreislauf 7 ent
steht. Durch dieses Zirkulieren, ohne Kompression und Expan
sion, wird die vom Kühlmedium der Verbrennungskraftmaschine 2
im Wärmetauscher 24 an den CO2-Wärmeträger übertragene Wärme
zum Klimatisierungswärmetauscher 12 gefördert. Der Druckver
lust für dieses kompressionslose Zirkulieren beträgt z. B. 6
bar, und es ergibt sich ein Zustandsverlauf von A bis c ent
sprechen dem Diagramm 11 der Fig. 3. Der Zustand nach Position
C ist aufgrund fehlender Expansion an den Ventilen 10, 11
identisch mit demjenigen an der Position D des Kanalnetzes 3.
Bei solcher Zirkulation ergeben sich entsprechend Diagramm II
folgende Zustandswerte:
With increasing heating of the cooling medium of the internal combustion engine and decreasing heat requirements for heating the passenger compartment, the output of the compressor 8 can be regulated back to almost zero, so that it only has the task of compensating for the pressure loss that occurs when the heat carrier circulates in the operating circuit 7 arises. Through this circulation, without compression and expansion, the heat transferred from the cooling medium of the internal combustion engine 2 in the heat exchanger 24 to the CO 2 heat transfer medium is conveyed to the air conditioning heat exchanger 12 . The Druckver loss for this compression-free circulation is z. B. 6 bar, and there is a state curve from A to c correspond to the diagram 11 of FIG. 3. The state after position C is identical to that at position D of the duct network 3 due to the lack of expansion at the valves 10 , 11th . With such circulation, the following state values result according to diagram II:
A: 62 bar, +80°C (353°K, 176°F),
B: 68 bar, +89°C (362°K, 192°F),
C/D: 65 bar, +30°C (303°K, 86°F).A: 62 bar, + 80 ° C (353 ° K, 176 ° F),
B: 68 bar, + 89 ° C (362 ° K, 192 ° F),
C / D: 65 bar, + 30 ° C (303 ° K, 86 ° F).
Falls die Klimaanlage auch eine Regelung der Luftfeuchtigkeit im Fahrgastraum ermöglichen soll, so kann dies auf an sich bekannte Weise durch Kühlen und Auskondensieren von Wasser aus dem Belüftungsstrom 17 erfolgen, jedoch ist in diesem Fall zur anschließenden Erwärmung auf die gewünschte Tempe ratur ein zusätzlicher Heizwärmetauscher 31 erforderlich, der die Wärme vom Wärmeträger des Kühlsystems der Verbrennungs kraftmaschine 2, d. h. vom ersten Kanalnetz 1 erhält. Dieser läßt sich durch einen geregelten Strömungsverteiler 32 zu schalten.If the air conditioning system should also allow regulation of the air humidity in the passenger compartment, this can be done in a manner known per se by cooling and condensing water from the ventilation stream 17 , but in this case an additional heating heat exchanger 31 is required for subsequent heating to the desired temperature required that receives the heat from the heat transfer medium of the cooling system of the internal combustion engine 2 , ie from the first duct network 1 . This can be switched by a regulated flow distributor 32 .
Claims (6)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19806654A DE19806654A1 (en) | 1998-02-18 | 1998-02-18 | Air conditioning system for a motor vehicle powered by an internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19806654A DE19806654A1 (en) | 1998-02-18 | 1998-02-18 | Air conditioning system for a motor vehicle powered by an internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| DE19806654A1 true DE19806654A1 (en) | 1999-08-19 |
Family
ID=7858090
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| DE19806654A Withdrawn DE19806654A1 (en) | 1998-02-18 | 1998-02-18 | Air conditioning system for a motor vehicle powered by an internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| DE (1) | DE19806654A1 (en) |
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| DE102004040989B4 (en) * | 2003-08-19 | 2006-11-23 | Visteon Global Technologies, Inc., Dearborn | Heat pump and air conditioning for one vehicle |
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