EP0851183A2 - Kälteanlage - Google Patents
Kälteanlage Download PDFInfo
- Publication number
- EP0851183A2 EP0851183A2 EP97122135A EP97122135A EP0851183A2 EP 0851183 A2 EP0851183 A2 EP 0851183A2 EP 97122135 A EP97122135 A EP 97122135A EP 97122135 A EP97122135 A EP 97122135A EP 0851183 A2 EP0851183 A2 EP 0851183A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- refrigerant
- line
- refrigeration system
- iii
- refrigerant circuit
- 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- Withdrawn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
Images
Classifications
-
- 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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
-
- 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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
Definitions
- the invention relates to a refrigeration system for generating low temperatures, including several thermally coupled Refrigerant circuits, with each circuit having at least one Compressor, a condenser, an expansion valve and has an evaporator and via a pressure line, a Liquid line, an injection line and a Suction line is closed.
- the invention is therefore based on the object To provide refrigeration system of the type mentioned above, in which Temperatures of around -125 ° C and lower at comparative low pressures can be achieved.
- This task is characterized by the characteristics of the Main claim solved.
- the thermal coupling via heat exchanger takes place and the refrigerant of each downstream Refrigerant circuit in the heat exchanger via the refrigerant of the upstream refrigerant circuit is pre-cooled.
- a temperature of up to about -125 ° C and lower be achieved.
- the heat exchanger as Plate heat exchangers are designed and that the Plate heat exchangers work in counterflow. This is one low-loss heat transfer possible in the heat exchangers, what the achievement of a low temperature in the third Refrigerant cycle favors. Furthermore, the Evaporator side of the for thermal coupling of the Refrigerant circuits serving heat exchangers in each Evaporator outlet area with the hot inlet side of the condenser, so that on the on one side a residual evaporation of the refrigerant and on the on the other hand, cooling the refrigerant as far as possible is favored.
- first refrigerant circuit as Refrigerant a pentafluoroethane / trifluoroethane mixture
- second refrigerant circuit as refrigerant trifluoromethane
- third refrigerant circuit as a refrigerant Tetrafluoromethane
- These refrigerants exhibit the properties necessary for the operation of the system h, p-diagram and are CFC-free. It continues to act are approved safety refrigerants that are not flammable.
- the refrigerant in the first Refrigerant circuit evaporates at around -40 ° C and around -45 ° C is liquefied that the refrigerant in the second Refrigerant circuit evaporates at around -75 ° C and at around -30 ° C is liquefied and that the refrigerant in the third Refrigerant circuit evaporates at around -130 ° C and at around -65 ° C is liquefied. So there are three different ones Temperatures for different purposes, process engineering and production processes, tapped.
- the third refrigerant circuit is advantageous the pressure line with the suction line via a bypass line connectable, so that in this refrigerant circuit particularly high pressure start of the refrigeration system in the Bypass is possible.
- the bypass line can expediently be via a Solenoid valve can be opened or closed, which is a enables convenient control.
- Another useful embodiment of the invention provides that in at least one refrigerant circuit Liquid line is connected to a container.
- the container can easily be used as a buffer for the refrigerant flow to serve.
- At least one Refrigerant circuit is a partial flow of the refrigerant from the Pressure line via a branch line into a Heat exchanger directed there gives heat to that in the The refrigerant located in the suction line is removed via a Return line fed back to the pressure line. This leads to to overheat the one in the suction line Refrigerant and for further cooling of the Pressure line supplied refrigerant and contributes to Performance increase in the refrigeration system and to protect the Compressor at.
- the partial flow is advantageously via a valve adjustable and can therefore be used on different Working conditions are adjusted.
- Refrigerant circuits in your liquid line Solenoid valve, a sight glass and a filter dryer have, is a shift of the refrigerant in The refrigeration system cannot come to a standstill the condition of the refrigerant improves as well as the Performance of the filter dryer can be checked.
- Another preferred embodiment of the invention provides that the compressor of each refrigerant circuit via vibration compensators with the pipe system is connected and that in the pressure line of each Refrigerant circuit a silencer is provided, so that mechanical vibrations of the compressor on the one hand and Pulsation vibrations of the refrigerant on the other hand Line system can be decoupled as far as possible.
- low and low are in the refrigerant circuits High pressure side of the compressor with one each Pressure meter and a pressure switch.
- the refrigerant circuits may become inadmissible if they occur Pressure peaks can be switched off.
- Refrigeration system three cooling levels I, II, III, with the Cold level I almost the input level with the highest Temperature level and cold level III the output level with represents the lowest temperature level.
- the cold levels I, II, III are thermal via heat exchangers 6, 20 coupled so that a cascade refrigeration system is created.
- cold level I is now closer described.
- the refrigeration cycle of cold level I points as Basic building blocks a condenser 11, an expansion valve 2, an evaporator 201 and a compressor 15.
- Compressor 15 is connected to the condenser 11 via a Pressure line D
- the Evaporator 201 in turn with the compressor 15 via a Suction line S connected to the cooling circuit of cooling level I.
- the refrigerant is at about -40 ° C in Evaporator 201 evaporates.
- a mixture is used as the refrigerant from 50% pentafluoroethane and 50% trifluoroethane.
- the compressor 15 is over Vibration compensators 14 with the pipe system of Refrigeration circuit I connected.
- the vibration compensators 14 keep mechanical vibrations of the compressor from Remote pipe system, causing damage or cracks be avoided.
- the Vibration compensator 14 in the pressure line D is a Muffler 16 downstream to keep away from Pulsation vibrations of the refrigerant from the pipe system.
- the refrigerant then passes into an oil separator 17, which is used to separate compressor oil from the refrigerant serves and via a ball shut-off valve 92 Return line feeds the oil to the compressor again.
- a heat exchanger 12 is provided in the pressure line D.
- the vaporous refrigerant is then air-cooled Condenser 11 liquefied with a further decrease in temperature and gets into the liquid line F.
- a liquid collector 10 In the Liquid line F is still a liquid collector 10 provided, which is quasi as a buffer for the volume flow of the refrigerant acts.
- a blow-off valve ensures 8 for the reduction of inadmissible peak pressures, if this not previously by the pressure switches 23 or 24 took place.
- the liquid collector 10 is a service valve 9 downstream.
- a Filter dryer 5 To freeze the expansion valve 2 and to avoid contamination of the refrigerant is a Filter dryer 5 provided. About a sight glass 4 can Level of the refrigerant and its moisture content in the liquid line F and thus also the Performance of the filter dryer 5 can be checked.
- a solenoid valve 3 provided that when the refrigerant circuit is at a standstill shuts off so that there is no relocation of the Refrigerant is coming.
- the refrigerant then continues through a heat exchanger 13 headed.
- the heat exchanger also has the function of Liquid separator, which will be explained later.
- the Heat exchanger 13 is the heat of the in Liquid line F refrigerant to the in the Suction line S, coming from the evaporator 201 vaporous refrigerant transferred.
- the heat exchanger 13 is used in this regard to supercool the liquid Refrigerant and therefore leads to an increase in Cooling capacity. This flows from the heat exchanger 13 liquid refrigerant then into the expansion valve 2. That Expansion valve 2 leads via the injection line E. Evaporator 201 the expanded refrigerant.
- the cold level is I with the cold level II coupled together via the heat exchanger 20
- the Heat exchanger 20 is a counter-current plate heat exchanger is the evaporator 201 with a through the Heat exchanger 20 formed condenser 202 of the cold stage II connects.
- Through the plate heat exchanger is one low-loss heat transfer from cold level II to Cold level I possible. So the working temperature in Evaporator 201 in about -40 ° C and in the condenser 202 in about -30 ° C.
- the expansion valve 2 via suitable measuring devices 21 with the output of the Evaporator 201 connected to the suction line S, which the Measure the pressure and temperature of the refrigerant vapor.
- This is the one flowing into the evaporator Refrigerant flow or the overheating of the refrigerant vapor regulated.
- the refrigerant vapor then passes through the Suction line S to the heat exchanger 13 and takes there how already explained, heat from in the liquid line F refrigerant present, causing additional overheating of the refrigerant in the suction line S.
- the Heat exchanger 13 also serves as Liquid separator, which is used in the refrigerant vapor to remove any residual liquid that may still be present.
- Liquid separation and overheating are said to be one Avoid damaging the compressor 15.
- the cold stages II and III constructed similarly to cold stage I and only have minor changes. Because the cold level I in detail has been described, should be used for cold levels II and III only the differences are explained.
- cold level II is one in the refrigeration cycle Connection line V 'with an overflow valve 7' intended.
- This connecting line V ' connects the Pressure line D 'with the suction line S'. Because at a standstill the refrigeration system gradually starts to cool down again Ambient temperature can heat up in the piping system enormous pressures occur. To damage the Preventing the pipe system therefore opens it Overflow valve 7 'when a certain one is reached Peak pressure and releases the connecting line V 'that in turn in connection with a surge tank 18 'stands. Pressure peaks in the surge tank 18 ' A blow-off line A is supplied via the blow-off valve 8 '.
- the thermal coupling takes place Cold level II with cold level III via the heat exchanger 6, which on the cold stage II an evaporator 601 and in cold stage III forms a condenser 602.
- the Heat exchanger 6 is a counter-current plate heat exchanger, which transmit the thermal energy with little loss can.
- a bypass line B is also provided, which the Connects pressure line D '' with suction line S ''.
- the Bypass line B has a solenoid valve 31. Because at the start the cold level III from the ambient temperature due to the Refrigerant properties are particularly high pressures, the solenoid valve 31 is first opened during startup and so that the bypass line B is released. Only when that Refrigerant of cold level III through the condenser 602 has given off sufficient heat and the pressure in the Line system has dropped, the solenoid valve 31 is again closed. This is a gentle start of cold stage III possible in bypass operation. In cold stage III is behind the expansion valve 2 ′′ provided an evaporator 1, which removes the necessary heat of vaporization from the ambient air.
- the evaporator 1 can have appropriate thermal Insulations 100 are placed in rooms where extreme low temperatures are necessary or desirable.
- the Compressor 15 of the cold stage I started, which the Working temperature of the first cold stage I in the evaporator 201 is brought to about -40 ° C. Due to the heat transfer in the Heat exchanger 20 is already the refrigerant in the Cold stage II pre-cooled and the working pressure reduced to here too the pressure level has dropped so much that the Compressor 15 'which can additionally compress refrigerant, without unwanted pressure peaks.
- the Operating temperature of the evaporator 601 is then approximately - 75 ° C.
- This temperature level is correspondingly above the Transfer heat exchanger 6 to cold stage III, whereby again a pre-cooling of the refrigerant used there takes place and in a corresponding manner when a certain reduced pressure levels also the compressor 15 '' cold stage III starts to work.
- the achievable Temperature level in evaporator 1 during continuous operation is in around -125 ° C.
- the temperature level of the condenser 202 or the condenser 602 is about -30 ° C or -65 ° C.
- temperatures are also lower than -125 ° C achievable. According to the invention there is also Possibility of using other refrigerants with only two Cold levels similarly low temperatures at similar to achieve low pressures.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
Description
Claims (14)
- Kälteanlage zur Erzeugung von tiefen Temperaturen, umfassend mehrere thermisch gekoppelte Kältemittelkreisläufe, wobei jeder Kreislauf mindestens einen Verdichter, einen Verflüssiger, ein Expansionsventil und einen Verdampfer aufweist und über eine Druckleitung, eine Flüssigkeitsleitung, eine Einspritzleitung und eine Saugleitung geschlossen wird, dadurch gekennzeichnet, daß mindestens zwei, vorzugsweise drei Kältemittelkreisläufe (I, II, III) mit unterschiedlichen geeigneten Kältemitteln vorgesehen sind, wobei die thermische Kopplung über Wärmetauscher (6 bzw. 20) erfolgt und das Kältemittel eines jeden nachgeschalteten Kältemittelkreislaufs (III bzw. II) im Wärmetauscher (6 bzw. 20) über das Kältemittel des jeweils vorgeschalteten Kältemittelkreislaufs (II bzw. I) vorgekühlt wird.
- Kälteanlage nach Anspruch 1, dadurch gekennzeichnet, daß die Wärmetauscher (6 bzw. 20) als Plattenwärmetauscher ausgeführt sind, die vorzugsweise im Gegenstrom arbeiten.
- Kälteanlage nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, daß im ersten Kältemittelkreislauf (I) als Kältemittel eine Pentafluorethan/Trifluorethan-Mischung, im zweiten Kältemittelkreislauf (II) als Kältemittel Trifluormethan und im dritten Kältemittelkreislauf (III)als Kältemittel Tetrafluormethan eingesetzt wird.
- Kälteanlage nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß das Kältemittel im ersten Kältemittelkreislauf (I) bei etwa -40°C verdampft und bei etwa -45°C verflüssigt wird, daß das Kältemittel im zweiten Kältemittelkreislauf (II) bei etwa -75°C verdampft und bei etwa -30°C verflüssigt wird und daß das Kältemittel im dritten Kältemittelkreislauf (III) bei etwa -130°C verdampft und bei etwa -65°C verflüssigt wird.
- Kälteanlage nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß bei mindestens einem Kältemittelkreislauf (II, III) die Druckleitung (D', D'') über eine Verbindungsleitung (V',V'') mit der Saugleitung (S', S'') verbindbar ist und die Saugleitung (S', S''), mit einem Druckbehälter (18', 18'') verbunden ist.
- Kälteanlage nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß bei dem dritten Kältemittelkreislauf (III) die Druckleitung (D'') mit der Saugleitung (S'') über eine Bypassleitung (B) verbindbar ist, die vorzugsweise über ein Magnetventil (31) geöffnet bzw. geschlossen werden kann.
- Kälteanlage nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß bei mindestens einem Kältemittelkreislauf (I) die Flüssigkeitsleitung (F) in Verbindung mit einem Behälter (10) steht.
- Kälteanlage nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß bei mindestens einem Kältemittelkreislauf (II, III) ein vorzugsweise über ein Ventil (91', 91'') einstellbarer Teilstrom des Kältemittels von der Druckleitung (D', D'') über eine Abzweigungsleitung (T', T'') in einen Wärmetauscher (13', 13'') geleitet wird, dort Wärme an das in der Saugleitung (S', S'') befindliche Kältemittel abgibt und über eine Rückführleitung (R', R'') wieder der Druckleitung (D', D'') zugeführt wird.
- Kälteanlage nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, daß in mindestens einem Kältemittelkreislauf (I) das in der Flüssigkeitsleitung (F) befindliche Kältemittel durch einen Wärmetauscher (13) geleitet wird und dort Wärme an das in der Saugleitung (S) befindliche Kältemittel abgibt.
- Kälteanlage nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß die Kältemittelkreisläufe (I, II, III) in ihrer Flüssigkeitsleitung (F, F', F'') ein Magnetventil (3, 3', 3''), ein Schauglas (4, 4', 4'') und einen Filtertrockner (5, 5', 5'') aufweisen.
- Kälteanlage nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß der Verdichter (15, 15', 15'') eines jeden Kältemittelkreislaufs (I, II, III) über Schwingungskompensatoren (14, 14', 14'') mit dem Leitungssystem verbunden ist.
- Kälteanlage nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, daß in der Druckleitung (D, D', D'') eines jeden Kältemittelkreislaufs (I, II, III) ein Geräuschdämpfer (16, 16', 16'') und/oder ein Ölabscheider (17, 17', 17'') vorgesehen ist.
- Kälteanlage nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, daß der in den Kältemittelkreisläufen (I, II, III) in der Saugleitung (S, S', S'') vorgesehene Wärmetauscher (13, 13', 13'') gleichzeitig die Funktion eines Flüssigkeitsabscheiders aufweist.
- Kälteanlage nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, daß in den Kältemittelkreisläufen (I, II, III) Nieder- und Hochdruckseite des Verdichters jeweils mit einem Druckmesser (22, 22', 22'') bzw. (25, 25', 25'') und einem Druckschalter (23, 23', 23'') bzw. (24, 24', 24'') versehen sind.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19653244 | 1996-12-20 | ||
DE1996153244 DE19653244A1 (de) | 1996-12-20 | 1996-12-20 | Kälteanlage |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0851183A2 true EP0851183A2 (de) | 1998-07-01 |
EP0851183A3 EP0851183A3 (de) | 2000-04-05 |
Family
ID=7815494
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97122135A Withdrawn EP0851183A3 (de) | 1996-12-20 | 1997-12-16 | Kälteanlage |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0851183A3 (de) |
DE (1) | DE19653244A1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010031335A1 (de) * | 2010-07-14 | 2012-01-19 | Werner & Pfleiderer Lebensmitteltechnik Gmbh | Kälteanlage zum Kühlen von Teigprodukten |
DE102005049950B4 (de) * | 2005-10-19 | 2014-04-03 | Kälteconcept GmbH | Verfahren zur Erzeugung tiefer Temperaturen und eine danach arbeitende Kaskadenkälteanlage |
WO2021121546A1 (de) | 2019-12-16 | 2021-06-24 | Mainklima Gmbh | Kompressionskälteanlage für elektrische kältekammer |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE20003397U1 (de) * | 2000-02-24 | 2000-09-21 | Pucel Markus | Schaltschrankkühlgerät in Kaskadenschaltung mit Kältemittel R 600a |
DE10011538B4 (de) * | 2000-03-01 | 2011-07-07 | Institut für Luft- und Kältetechnik gemeinnützige Gesellschaft mbH, 01309 | Einrichtung zur Kühlung von Nutz- und Brauchwasser |
CN101865589B (zh) * | 2010-07-14 | 2012-03-28 | 天津商业大学 | 环保、无氟超低温库 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4028079A (en) * | 1976-02-23 | 1977-06-07 | Suntech, Inc. | Cascade refrigeration system |
FR2474151A1 (fr) * | 1980-01-21 | 1981-07-24 | Inst Francais Du Petrole | Procede de production de chaleur au moyen d'une pompe a chaleur utilisant un melange specifique de fluides comme agent de travail |
US4550574A (en) * | 1983-06-02 | 1985-11-05 | Sexton-Espec, Inc. | Refrigeration system with liquid bypass line |
US4727727A (en) * | 1987-02-20 | 1988-03-01 | Electric Power Research Institute, Inc. | Integrated heat pump system |
JP3208151B2 (ja) * | 1991-05-28 | 2001-09-10 | 三洋電機株式会社 | 冷凍装置 |
DE4228415C1 (en) * | 1992-08-31 | 1993-09-16 | Stal-Astra Gmbh Kaelteanlagen, 21509 Glinde, De | Refrigeration system for food display cabinet - has high and low pressure circuits for refrigeration medium allowing different food compartments to be held at different temp. levels |
WO1994021919A1 (en) * | 1993-03-25 | 1994-09-29 | Robert Arden Higginbottom | Equalization of load across a compressor upon shutdown |
US5447038A (en) * | 1993-11-16 | 1995-09-05 | Reefco Manufacturing Corporation | Apparatus for simultaneously providing multiple temperatures using an automatically configurable cooling system having both cascade and single compressor modes |
-
1996
- 1996-12-20 DE DE1996153244 patent/DE19653244A1/de not_active Ceased
-
1997
- 1997-12-16 EP EP97122135A patent/EP0851183A3/de not_active Withdrawn
Non-Patent Citations (1)
Title |
---|
None |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005049950B4 (de) * | 2005-10-19 | 2014-04-03 | Kälteconcept GmbH | Verfahren zur Erzeugung tiefer Temperaturen und eine danach arbeitende Kaskadenkälteanlage |
DE102010031335A1 (de) * | 2010-07-14 | 2012-01-19 | Werner & Pfleiderer Lebensmitteltechnik Gmbh | Kälteanlage zum Kühlen von Teigprodukten |
WO2021121546A1 (de) | 2019-12-16 | 2021-06-24 | Mainklima Gmbh | Kompressionskälteanlage für elektrische kältekammer |
Also Published As
Publication number | Publication date |
---|---|
EP0851183A3 (de) | 2000-04-05 |
DE19653244A1 (de) | 1998-06-25 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE69003067T2 (de) | Kälteanlage. | |
DE102006035784B4 (de) | Kälteanlage für transkritischen Betrieb mit Economiser und Niederdruck-Sammler | |
DE3637071C2 (de) | Verfahren und Vorrichtung zum Verdichten von Gasen | |
DE10307039A1 (de) | Klimaanlage | |
DE102013210177A1 (de) | Kühlsystem und Kühlprozess für den Einsatz in Hochtemperatur-Umgebungen | |
DE102005049950B4 (de) | Verfahren zur Erzeugung tiefer Temperaturen und eine danach arbeitende Kaskadenkälteanlage | |
EP0851183A2 (de) | Kälteanlage | |
DE102005029275A1 (de) | Verfahren zum Verflüssigen eines Kohlenwasserstoff-reichen Stromes | |
EP1892457B1 (de) | Verfahren und Vorrichtung zur Speicherung von Brenngas, insbesondere von Erdgas | |
EP0783658B1 (de) | Verfahren und vorrichtung zum kühlen von gasen | |
DE102005021154B4 (de) | Abtausystem für Verdampfer von Kälteanlagen und Wärmepumpen sowie ein Verfahren zum Betrieb hierzu | |
DE102008043823B4 (de) | Wärmepumpenanlage | |
DE19840409C1 (de) | Verfahren und Vorrichtung zur Gasreinigung | |
DE202007017723U1 (de) | Anlage für die Kälte-, Heiz- oder Klimatechnik, insbesondere Kälteanlage | |
EP0539816A1 (de) | Vorrichtung zum Abtauen von Kälte-Trocknern unter 0 Grad Celcius | |
DE102019121925B4 (de) | Gasentspannungsanlage mit LNG-Erzeugungsanlage | |
DE3916025C2 (de) | ||
DE102007063619A1 (de) | Kälteanlage mit als Gaskühler betreibbarem Wärmeübertrager | |
EP2686622A2 (de) | Kältegerät | |
DE202018001404U1 (de) | Einrichtung zum Temperieren von durch Filter gereinigten flüssigen Mediums | |
DE202022106923U1 (de) | Kältekreislauf | |
EP4317841A1 (de) | Prüfkammer und verfahren zur steuerung | |
EP1808655A2 (de) | Kälteanlage | |
CH665708A5 (de) | Verfahren zum betreiben eines kaeltemittelkreislaufs und kaeltemittelkreislauf zur durchfuehrung des verfahrens. | |
DE4404787B4 (de) | Kälteanlage mit ölüberfluteten Schraubenverdichtern |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AT BE CH DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE |
|
AX | Request for extension of the european patent |
Free format text: AL;LT;LV;MK;RO;SI |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AT BE CH DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE |
|
AX | Request for extension of the european patent |
Free format text: AL;LT;LV;MK;RO;SI |
|
AKX | Designation fees paid | ||
REG | Reference to a national code |
Ref country code: DE Ref legal event code: 8566 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN |
|
18D | Application deemed to be withdrawn |
Effective date: 20001006 |