EP2336680A2 - Dispositif de climatisation doté d'un dispositif de transmission de pression et procédé de fonctionnement d'un dispositif de climatisation - Google Patents

Dispositif de climatisation doté d'un dispositif de transmission de pression et procédé de fonctionnement d'un dispositif de climatisation Download PDF

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Publication number
EP2336680A2
EP2336680A2 EP10193863A EP10193863A EP2336680A2 EP 2336680 A2 EP2336680 A2 EP 2336680A2 EP 10193863 A EP10193863 A EP 10193863A EP 10193863 A EP10193863 A EP 10193863A EP 2336680 A2 EP2336680 A2 EP 2336680A2
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EP
European Patent Office
Prior art keywords
refrigerant
working
cylinder
pressure
conditioning device
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Withdrawn
Application number
EP10193863A
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German (de)
English (en)
Other versions
EP2336680A3 (fr
Inventor
Gerald Holtz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2336680A2 publication Critical patent/EP2336680A2/fr
Publication of EP2336680A3 publication Critical patent/EP2336680A3/fr
Withdrawn legal-status Critical Current

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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
    • F25B27/00—Machines, plants or systems, using particular sources of energy

Definitions

  • the invention relates to a device for a pressure transmission between two working groups, in particular between two refrigerant circuits of an air conditioning device according to the preamble of claim 1.
  • the invention relates to an air-conditioning device with two working circuits, in particular an air-conditioning device for cooling and / or heating with two refrigerant circuits, according to the preamble of patent claim 5.
  • the invention relates to a method for operating an air conditioning device with two working circuits according to the preamble of patent claim 8.
  • thermally driven heat pumps which operate by means of an ad- and Absorbtions revitalizes known.
  • methods are known which use thermal energy to generate a cooling capacity. This is done via a coupling of a so-called Organic Rankine Cycle (ORC) process with a refrigerant process.
  • ORC Organic Rankine Cycle
  • the liquid refrigerant is brought to a high pressure by means of a liquid pump and evaporated while supplying heat in a generator.
  • the vaporized, high pressure refrigerant is expanded in a turbine.
  • the energy gained in this process is transmitted to the coupled circuit via a wave.
  • the compressor in the coupled circuit compresses the refrigerant, the compressor being driven by the energy recovered in the other circuit.
  • the temperature and pressure increase due to the action of the compressor. Heat is then dissipated in a condenser. After a subsequent expansion of the refrigerant, the temperature drops accordingly, so that, for example, a building can be cooled.
  • the coupling of the two working groups is carried out in the prior art thus via a common shaft of the turbine and compressor, wherein the turbine is driven in a circuit and takes place via the shaft, a drive of the compressor of the other circuit.
  • a disadvantage of such methods and devices is that they require a complex technique and a lot of space.
  • the invention has for its object to provide a method, an apparatus and an air conditioning device, which provide a simple and space-saving coupling of two working groups.
  • it is an object to provide a method, a device and an air-conditioning device which are easy to retrofit into existing solutions.
  • a more effective solution should be created.
  • the inventive device for a pressure transmission between two working groups is characterized in that this with a first double-acting cylinder with piston, which is arranged in a first working group, and a second double-acting cylinder with piston, which in a is arranged second working group, is formed, wherein the first piston is connected to the second piston via a linkage.
  • the first cylinder acts as a pressure transmitter and the second cylinder as a pressure booster.
  • an inlet to the cylinders is each optionally fluidically connectable to a first or a second cylinder side separated by the respective piston, wherein a drain from the respective cylinder corresponding to the second and the first cylinder side connected is.
  • a control device is provided, by means of which a switchover of flow paths of the inlet to and / or from the first cylinder takes place in parallel to a switching over of the flow paths of the inlet to and / or from the second cylinder ,
  • the air-conditioning device according to the invention with two working circuits in particular an air-conditioning device for cooling and / or heating with two refrigerant circuits, is characterized in that the working cycles are coupled via a device according to the invention.
  • An embodiment of the present invention provides that the working groups are designed as integrated working groups, in particular a heat pump or cooling device.
  • working groups are designed as separate working groups, in particular a heat pump or cooling device.
  • the method according to the invention for operating an air-conditioning device with two working circuits is characterized in that a pressure of a first working cycle is transferred to a pressure of a second working cycle, the transmission taking place in particular by means of a (pressure) device according to the invention.
  • An embodiment of the present invention provides that flow paths are switched to and / or from the cylinders so that pressure is transmitted continuously.
  • Yet another embodiment of the present invention contemplates that flow paths to and / or from the cylinders are switched upon reaching maximum travel distances of the pistons.
  • the device according to the invention and the method according to the invention can be used in various work processes.
  • the invention can be used in building air conditioning or vehicle air conditioning.
  • the invention can also be used, for example, as a retrofit module for existing heating systems or as an additional module for new heating appliances.
  • the invention can also be integrated in a boiler.
  • a refrigerant process heat is supplied by the boiler, so that the existing refrigerant in a refrigerant circuit evaporates.
  • the required heat is not taken from a combustion chamber of the boiler, but from a boiler flow.
  • the refrigerant vapor flows into the device designed as a pressure converter according to the invention, and the pressure converter, driven by the upper refrigerant process, drives the lower refrigerant process directly. This means that the refrigerant is compressed in the lower process.
  • the evaporator absorbs heat from the outside air. In the condenser, the heat introduced from the boiler and from the outside air into the refrigerant process is transferred to the heating return. In the return of the heating circuit, the energy content of the water is about 0 kW.
  • the energy content of the water for example, 12 kW, which are composed of 2 kW of ambient heat and 10 kW boiler heat. After firing through the boiler, the energy content is about 22 kW, because here the boiler has fired about 10 kW. Behind the generator 10 kW are taken to drive the refrigerant process. This means that the 12 kW that goes into the heating circuit consists of 10 kW of boiler heat and 2 kW of regenerative environmental heat, which corresponds to an efficiency of around 120%.
  • the procedure is as follows.
  • heat for example, solar heat, engine heat and the like
  • a refrigerant evaporates.
  • This refrigerant vapor flows into the device designed as a pressure converter, and the pressure converter drives the lower refrigerant process directly, driven by the upper refrigerant process.
  • the refrigerant is compressed in the lower process.
  • no turbines or the like are used to gain work and this work by means of z.
  • the invention allows the use of waste heat for cooling. Furthermore, no expensive turbine for work transmission or the like is needed. As a result, significantly smaller dimensions can be realized in an adsorption process without it to performance losses comes. Due to the direct energy transfer, higher efficiencies can be achieved.
  • Fig. 1 schematically shows in a block diagram an embodiment of the invention as an air conditioning device 100 with partially integrated working circuits 10, 20, schematically represented by the semicircular arrows.
  • the device 100 comprises an evaporator 22, with which, for example, heat from, for example, a building, a vehicle interior or the like is taken, as shown by the arrow pointing to the evaporator 22.
  • the device 100 comprises a generator 12, with which, for example, heat from, for example, a solar system or a car engine is fed in, as represented by the arrow pointing to the generator 12.
  • the device 100 per working cycle 10, 20 comprises a capacitor 14, 22, wherein the two capacitors 14 and 22 in the embodiment according to Fig. 1 integrated as a common capacitor 13/23 are formed.
  • the device 100 comprises a liquid pump 11, with which a liquid refrigerant is brought to a higher pressure.
  • an expansion valve 21 is further provided, is reduced with the pressure.
  • a device 30 designed as a pressure converter which is also included in the device 100, work is transferred from the upper working cycle 10 to the lower working cycle 20.
  • a collection and / or expansion tank 14 located between the condenser 13/23 and the device 30, a collection and / or expansion tank 14. The individual components are connected to each other via corresponding lines, in particular fluidly connected.
  • the same refrigerant such as the refrigerant R410a, R152a, R134 or the like.
  • the liquid pump 11 increases the pressure of the liquid refrigerant flowing through the device 100 from the operating point 3 to the operating point 6.
  • the liquid refrigerant supplied via the liquid pump 11 is evaporated from the operating point 6 to the operating point 7 while supplying heat (represented by the arrow pointing towards the generator 12).
  • the vapor at the operating point 7 refrigerant flows into the pressure converter.
  • the print converter includes such as in Fig.
  • the pistons 61, 66 which are interconnected by means of a linkage 69.
  • the pistons 61, 66 are each in a cylinder 60, 65 in which they can move freely from left to right and from right to left.
  • the vapor refrigerant flows with, for example, a pressure of 17.6 bar in the right part of the cylinder 60.
  • a part of the cylinder 60 is under pressure, which presses against a surface of the first piston 61.
  • This pressure is transmitted to the other piston 66 due to the fact that the two pistons 61, 66 are interconnected by the linkage 69.
  • the pistons 61, 66 move from left to right according to the pressure gradient.
  • That in the Fig. 1 schematically illustrated method is, for example, a refrigerant method by heat from a boiler fed (from operating point 6 via the generator 12 to operating point 7), so that the refrigerant evaporates.
  • the heat is not taken from the combustion chamber of the boiler, but from the boiler supply.
  • the refrigerant vapor (operating point 7) flows into the pressure converter and the The pressure converter, powered by the upper refrigerant process or process, directly drives the lower refrigerant process.
  • This means that the refrigerant is compressed in the lower process (from operating point 1 through the pressure converter to operating point 2).
  • the evaporator 22 heat is absorbed from the outside air (from operating point 4 via the evaporator 22 to operating point 1).
  • the condenser 13/23 the heat introduced from the boiler and from the outside air into the refrigerant process is delivered to a heating return (from operating point 5/2 via the condenser 13/23 to operating point 3).
  • the air-conditioning device 100 thus has two working circuits 10, 20 and is formed in the illustrated embodiment as air conditioning for cooling and / or heating with two refrigerant circuits.
  • the two working circuits 10, 20 are coupled to one another via a device 30 designed as a pressure converter.
  • a device 30 designed as a pressure converter.
  • the working cycles 10, 20 formed at least partially integrated.
  • Fig. 2 schematically shows in a block diagram an embodiment of the invention as an air conditioning device with two separate working circuits 10, 20. Accordingly, no common capacitor 13/23 is provided. Otherwise, the air-conditioning devices 100 correspond to Fig. 1 and Fig. 2 so that a detailed description of already described components and functional processes or operating points can be dispensed with.
  • the air-conditioning device 100 As well as the air conditioning device 100 after Fig. 1 indicates the air-conditioning device 100 Fig. 2 two working circuits 10, 20 on.
  • the air-conditioning device 100 according to Fig. 2 is formed in the illustrated embodiment as air conditioning for cooling and / or heating with two refrigerant circuits.
  • the two formed as a refrigerant circuit working circuits 10, 20 are coupled to each other via the designed as a pressure converter device 30.
  • the working cycles 10, 20 are formed separately.
  • the device 30 for pressure transmission between the two working circuits 10, 20, more precisely between the two refrigerant circuits of the air-conditioning device 100 comprises a first double-acting cylinder 60 with a piston 61, which is arranged in a first working circuit 10, and a second double-acting cylinder 65 with Piston 66, which is arranged in the second working circle 20.
  • the first piston 61 is connected to the second piston 66 via a linkage 69, as more closely associated with FIG Fig. 4 is connected.
  • Characterized in that the refrigerant circuits are formed separately, and different refrigerants can flow in the refrigerant circuits. Accordingly, for example, in the left refrigerant circuit 10, which is also called a drive circuit, the refrigerant R134a flows.
  • the refrigerant circuit 20 which is also referred to as a cooling circuit flows, for example, the refrigerant R410A. Due to the separate design of the working circuits 10, 20, the refrigerant does not mix. Otherwise, the operation is the same as in the embodiment according to FIG Fig. 1 , Since the circuits 10, 20 are formed separately, instead of having a common capacitor 13/23, as in Fig. 1 , two capacitors 13, 23 are provided. In the first working circuit 10, the capacitor 13 is provided. The second working circuit 20 has the capacitor 23.
  • Fig. 3 schematically shows a diagram in which the pressure over the enthalpy during the operation of the invention is shown.
  • the operating points are shown in the diagram.
  • isotherms are also drawn schematically, the states of the working fluid, more precisely of the refrigerant, are shown.
  • the first working cycle 10 runs in accordance with the operating points 3 - 6 - 7 - 5.
  • the second working cycle runs according to the operating points 1 - 2 - 3 - 4.
  • Schematically, the various markings of the components of the air conditioning 100 are drawn on the diagram to the process to clarify.
  • the refrigerant In the first refrigeration cycle 10, heat from, for example, a boiler is fed from operating point 6 via the generator 12 to operating point 7, so that the refrigerant evaporates.
  • the pressure remains essentially the same, as indicated by the isobars.
  • the enthalpy of the refrigerant increases accordingly due to the heat energy supply.
  • the refrigerant vapor flows from the operating point 7 into the pressure converter, and the pressure converter, driven by the upper refrigerant process 10, directly drives the lower refrigerant process 20.
  • the refrigerant From the operating point 5, the refrigerant flows via the condenser 13/23 or 13 to the operating point 3.
  • the refrigerant via the generator heat energy to the outside, wherein the pressure remains substantially constant.
  • the fluid pump 11 the refrigerant is brought to a higher pressure level at substantially constant enthalpy and reaches from operating point 3 via the fluid or liquid pump 11 to the operating point 6, whereby the first working circuit 10 closes.
  • the refrigerant is compressed in the lower cooling process from operating point 1 via the pressure converter to operating point 2.
  • the evaporator 22 Heat is absorbed from the outside air, so that the refrigerant is brought at a substantially constant pressure from the operating point 4 via the evaporator 22 to the operating point 1 to a higher enthalpy level.
  • the condenser 13/23, 23 the heat introduced from the boiler and from the outside air into the refrigerant process is released to the heating return, whereby the enthalpy decreases again at substantially constant pressure.
  • Fig. 4 shows schematically in four subfigures 4a to 4d, the operation of the inventive device 30 according to Fig. 1 and 2 in four different states.
  • the device 30 for pressure transmission between the two working circuits 10, 20, more precisely between the two refrigerant circuits of the air-conditioning device 100 comprises a first double-acting cylinder 60 with a piston 61, which is arranged in a first working circuit 10, and a second double-acting cylinder 65 with Piston 66, which is arranged in the second working circle 20.
  • the first piston 61 is connected to the second piston 66 via a linkage 69.
  • the pistons move in operation simultaneously due to the connection via the linkage 69 from left to right and back.
  • an adjusting means 41 (which leads from the operating point 7 to the left part of the cylinder 60) and an adjusting means 44 (which leads from the right part of the cylinder 60 to the operating point 5) are opened.
  • the two other actuating means 42 (leading from the right part of the cylinder 60 to the first actuating means 41 or operating point 7) and 43 (leading from the left part of the cylinder 60 to the operating point 5 and the actuating means 44) are closed.
  • the circuit of the adjusting means 51-54 looks accordingly.
  • the adjusting means 51 (from operating point 1 to the left part of the cylinder 65) and 54 (from the right part of the cylinder 65 to the operating point 2) are opened.
  • the adjusting means 52 (from the right part of the cylinder 65 to the operating point 1) and 53 (from the left part of the cylinder 65 to the operating point 2) are closed.
  • the two pistons 61, 66 rightmost to the cylinders 60, 65 by opening and closing the flow paths of the refrigerant by means of driving the adjusting means 41-44 and 51-54 at the cylinder 60 in the pressure transfer, the process is reversed.
  • the flow path for under pressure P2 (17.6 bar) refrigerant in the left part of the cylinder 1 is closed.
  • the flow path for the refrigerant under pressure P2 (17.6 bar) is now open in the right-hand part of the cylinder 60.
  • the adjusting means 42, 43 and 52, 53 are open.
  • the right part of the cylinder 1 is under the pressure P2 of 17.6 bar and the left part under the pressure P1 of 10.4 bar.
  • the flow paths of the refrigerant to the condenser 13/23, 23 (operating point 5) are simultaneously changed by the respective, designed as a valve actuating means 43rd , 53 to the condenser 13/23, 23 is closed and the lower right valve 44, 54 to the condenser 13/23, 23 is opened.
  • the two pistons 61, 66 now reverse their direction and move from right to left, that is in the direction of the first cylinder 60. There is again a pressure transfer from the upper (first, 10) working cycle to the lower (second, 20) working cycle , The process is as described above. However, the pistons 61, 66 now move from right to left, that is from the second cylinder 60 to the first cylinder 65, as indicated by Fig. 4c can be seen. When the pistons 61, 66 have moved all the way to the left, the process is reversed again by switching the flow paths by means of the valves.
  • both refrigerant streams are collected and, from then on, passed into the condenser 13/23, 23 in which the refrigerant condenses.
  • a portion of the refrigerant flows in the lower working circuit 20 to the evaporator and another part is brought by means of the liquid pump 11 to pressure and fed to the generator 12.
  • Fig. 5 shows schematically in two subfigures two embodiments of the invention, once without (5a) and once with (5b) heat storage.
  • the climate device 100 has solar collectors 200. This heat is recovered from solar radiation and fed to the generator 12.
  • the generator 12 heats the refrigerant and the heated refrigerant enters the pressure converter.
  • the refrigerant flows to the capacitor 13/23 arranged in an outer area 300.
  • temperatures of 35 ° C for example, the refrigerant, which has a temperature of 40 ° C, cooled.
  • the cooled to about 35 ° C refrigerant then flows on to a node where the until then integrated working groups 10, 20 separate.
  • the refrigerant branches to the generator 12.
  • the generator 12 the refrigerant is reheated as described above.
  • the refrigerant flows to the evaporator 22.
  • the refrigerant evaporates at a prevailing ambient temperature of 24 ° C - for example, a room temperature - and takes in the evaporation, for example, heat at a temperature of 15 ° C.
  • the environment is cooled accordingly.
  • the heated refrigerant passes to the pressure converter by the refrigerant is driven by the first working circuit 10, compressed and passes together with the refrigerant from the first working circuit into the collecting container 14.
  • the refrigerant in the outdoor area in Fig.
  • a heat accumulator 28 is provided.
  • the heat of the refrigerant is thus temporarily stored in the heat storage designed as a hot water tank.
  • Both embodiments according to Fig. 5a and 5b have at least partially integrated working circuits 10, 20, so that the same refrigerant is used for both circuits.
  • Fig. 6 schematically shows in a block diagram a further embodiment of the invention in a heating circuit with boiler.
  • the energy content of the refrigerant formed as water is about 0 kW.
  • the energy content of the water is 12 kW. These are composed of 2 kW of ambient heat and 10 kW of boiler heat.
  • the energy content is about 22 kW, because here the boiler has fired about 10 kW of heat energy.
  • 10 kW are taken to drive the refrigerant process.
  • the air-conditioning device 100 is according to Fig. 6 as air conditioning with partially integrated working circuits 10, 20 is formed. The basic structure has been described above accordingly, so that here a detailed description can be omitted.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP10193863.7A 2009-12-09 2010-12-06 Dispositif de climatisation doté d'un dispositif de transmission de pression et procédé de fonctionnement d'un dispositif de climatisation Withdrawn EP2336680A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200910057630 DE102009057630A1 (de) 2009-12-09 2009-12-09 Klimatisierungsvorrichtung und thermisch betriebenes Wärmepumpenmodul mit Druckübertrager sowie Verfahren zum Betreiben

Publications (2)

Publication Number Publication Date
EP2336680A2 true EP2336680A2 (fr) 2011-06-22
EP2336680A3 EP2336680A3 (fr) 2014-03-19

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP10193863.7A Withdrawn EP2336680A3 (fr) 2009-12-09 2010-12-06 Dispositif de climatisation doté d'un dispositif de transmission de pression et procédé de fonctionnement d'un dispositif de climatisation

Country Status (2)

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EP (1) EP2336680A3 (fr)
DE (2) DE202009018245U1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105910386A (zh) * 2016-06-06 2016-08-31 洛阳普瑞曼自动控制技术有限公司 一种智能化的轻质汽油转换装置
CN112534135A (zh) * 2018-07-22 2021-03-19 奥弗技术Stp有限责任公司 机械制冷系统

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2918946A4 (fr) * 2012-09-13 2016-10-05 Bingxin Gong Appareil de réfrigération

Family Cites Families (6)

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Publication number Priority date Publication date Assignee Title
US3988901A (en) * 1975-02-18 1976-11-02 Scientific-Atlanta, Inc. Dual loop heat pump system
US4779427A (en) * 1988-01-22 1988-10-25 E. Squared Incorporated Heat actuated heat pump
SE9603170D0 (sv) * 1996-08-30 1996-08-30 Bengt Adolfsson Förfarande och anordning vid en läskedrycksautomat
US6138457A (en) * 1998-02-27 2000-10-31 Applied Power Technology Incorporated Combustion powered cooling system
DE19813220C2 (de) * 1998-03-26 2002-12-12 Univ Dresden Tech Kolbenexpansionsmaschine und Verfahren zur Einbindung dieser Maschine in einen transkritischen Kompressionskälteprozeß
DE102005053589A1 (de) * 2005-11-10 2007-05-16 Richard Engelmann Solar betriebene Kältemaschine

Non-Patent Citations (1)

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Title
None

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105910386A (zh) * 2016-06-06 2016-08-31 洛阳普瑞曼自动控制技术有限公司 一种智能化的轻质汽油转换装置
CN112534135A (zh) * 2018-07-22 2021-03-19 奥弗技术Stp有限责任公司 机械制冷系统

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Publication number Publication date
DE102009057630A1 (de) 2011-06-16
EP2336680A3 (fr) 2014-03-19
DE202009018245U1 (de) 2011-05-12

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