EP1247050A1 - Periodic refrigerating machine - Google Patents
Periodic refrigerating machineInfo
- Publication number
- EP1247050A1 EP1247050A1 EP01915128A EP01915128A EP1247050A1 EP 1247050 A1 EP1247050 A1 EP 1247050A1 EP 01915128 A EP01915128 A EP 01915128A EP 01915128 A EP01915128 A EP 01915128A EP 1247050 A1 EP1247050 A1 EP 1247050A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat exchanger
- pulse tube
- heat
- expander
- compressor
- 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.)
- Granted
Links
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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
- F25B9/145—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle pulse-tube cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G2243/00—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes
- F02G2243/30—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders
- F02G2243/50—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders having resonance tubes
- F02G2243/54—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders having resonance tubes thermo-acoustic
-
- 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
- F25B2309/14—Compression machines, plants or systems characterised by the cycle used
- F25B2309/1403—Pulse-tube cycles with heat input into acoustic driver
-
- 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
- F25B2309/14—Compression machines, plants or systems characterised by the cycle used
- F25B2309/1407—Pulse-tube cycles with pulse tube having in-line geometrical arrangements
-
- 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
- F25B2309/14—Compression machines, plants or systems characterised by the cycle used
- F25B2309/1408—Pulse-tube cycles with pulse tube having U-turn or L-turn type geometrical arrangements
-
- 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
- F25B2309/14—Compression machines, plants or systems characterised by the cycle used
- F25B2309/1418—Pulse-tube cycles with valves in gas supply and return lines
-
- 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
- F25B2309/14—Compression machines, plants or systems characterised by the cycle used
- F25B2309/1419—Pulse-tube cycles with pulse tube having a basic pulse tube refrigerator [PTR], i.e. comprising a tube with basic schematic
-
- 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
- F25B2309/14—Compression machines, plants or systems characterised by the cycle used
- F25B2309/1424—Pulse tubes with basic schematic including an orifice and a reservoir
- F25B2309/14241—Pulse tubes with basic schematic including an orifice reservoir multiple inlet pulse tube
-
- 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
- F25B2309/14—Compression machines, plants or systems characterised by the cycle used
- F25B2309/1426—Pulse tubes with basic schematic including at the pulse tube warm end a so called warm end expander
Definitions
- the invention relates to a thermal power amplifier for periodically operating chillers and a method to operate such a thermal cycle.
- a refrigeration process which works on the principle of a Stirling engine, can be constructed so that there are no mechanical components to be moved in the cold part of such an engine.
- the cooler of this type consists of a compressor piston which is moved periodically at ambient temperature, a thermally insulated regenerator, a likewise thermally insulated pulse tube, which is provided at both ends with heat exchangers, and an expansion piston which is also operated at ambient temperature. Both pistons are moved so that the following cycle is carried out in the pulse tube: compression of the gas;
- the temperature can typically be reduced from room temperature to about 25 K [I, II], with two-stage devices even below 4 K [III].
- the work thus obtained can be used to drive a pulse tube cooler.
- the thermal power amplifier from a compressor device to which a first heat exchanger is attached which emits heat to the surroundings.
- a regenerator is attached to this.
- This heat exchanger is therefore called a heater.
- the pulse tube of the power transmitter is then attached to the heater and is completed with a heat exchanger that emits heat.
- the pulse tube cooler is attached to this last heat exchanger, and the last heat exchanger of the power amplifier is the first of the pulse tube cooler, if you will.
- the heat exchanger which forms the useful cold zone, lies between the regenerator and the pulse tube of the pulse tube cooler.
- Claim 2 the Stirling process with piston expander
- Claim 3 the Stirling process with passive expander
- Claim 4 the Gifford-McMahon mode of operation with a high and low pressure reservoir, both with Connect one valve each to the regenerator, and with a passive expander as in claim 3 and finally
- Claim 5 the Gifford-McMahon mode of operation with a compression device, as described in claim 4, and one each with a controllable valve vers en Zule * do * ⁇ r v * "* m high and low pressure reservoir, the valve-controlled expander, to the pulse tube.
- the pulse tube amplifier can be electrically heated on the one hand (claim 6), and on the other hand, similar to a Stirling engine, other heat sources such as solar heating or combustion [5] can also be used (claim 7). In this case, the radiator can be operated with an even lower requirement for primary energy.
- the pulse tube amplifier i.a. achieved the following advantages: better efficiency, i.e. less primary energy with the same cooling capacity; Cost-effective production of the cooler - compared to a mechanical compressor, the pulse tube amplifier is a very easy to manufacture assembly, the additional effort outweighs the cost savings due to a smaller compressor; lower operating costs; Low maintenance costs - the pulse tube amplifier itself is maintenance-free, the additional components required for the pulse tube cooler, such as compressors and valves, which require regular maintenance or replacement, are sufficient in a smaller design and are therefore cheaper.
- FIG. 1 shows the schematic structure of the refrigerator as a series Circuit from a thermal amplifier with a pulse tube cooler and the representation of the temperature curve along the same
- FIG. 2a shows the realization as a Stirling type with a double piston
- FIG. 2b shows the realization as a Stirling type with a single piston and double-outlet phase shifter
- FIG. 2c Gifford-McMahon type with double inlet phase shifter
- FIG. 2d Gifford-McMahon type with active phase shifter
- FIG. 3a the phase diagram of the oscillations of pressure and volume flow on the optimized pulse tube cooler
- FIG. 3b shows the phase diagram of the oscillations of pressure and volume flow on the cold machine, the series connection of pulse tube amplifier and pulse tube cooler,
- FIG. 4 shows the construction of the refrigeration machine with a valve-operated thermal amplifier
- the compressor and expander are operated in such a way that the following cycle is run through in the pulse tube:
- the entire gas column cools down, at the left end below the temperature of the heat exchanger located there.
- the temperature that occurs in the stationary case along the pulse tube cooler is shown below.
- the pulse tube cooler can be operated in different ways. Ent ⁇ speaking operating schemes are shown in Figures 2a to 2d, m combination with the thermal amplifier. The respective
- thermal power booster also known as a compressor or pulse tube compressor
- the thermal power booster functions like a pulse tube cooler
- both systems, the power booster and the pulse tube cooler can be treated using the same methods.
- a known calculation method [IV] provides good in tune with experiments.
- a typical case here is a
- the calculation assumes harmonic, ie sinusoidal pulsations of pressure and volume flow.
- the relationships between the pressure p and the volume flow U shown in the diagram / phase diagram according to FIG. 3a result at different positions, such as the regenerator inlet, RE, pulse tube inlet, PTE, and pulse tube outlet, PTA.
- the volume flow U PT E in the pulse tube on the side facing the compressor leads the pressure p PT present in the pulse tube by approximately 30 °, whereas the gas flow U PT A lags the pressure by approximately 45 ° on the opposite side. Similar operating conditions should occur on a pulse tube amplifier if it is designed for optimal energy conversion.
- U R , E thus identifies the volume flow fed into the regenerator of the amplifier at room temperature.
- the volume flow U R , A present at the heated end of this regenerator is distinguished by a longer length due to the thermal expansion of the gas and by a small rotation due to the empty volume in the regenerator.
- the difference between U RA and U PT ⁇ , E the gas flow present at the hot end of the pulse tube comes about when the heater unit flows through.
- the pointers p R / E , P PT ⁇ and p PT2 mark the prints at the room temperature f- 1 1 v (__ r *. R-1 __> r-. __. C_ * ⁇ -.
- a cooling power of 110 W at 50 K can be achieved.
- the compressor output is reduced by 50%, but in addition a heating output of 1700 W at 1000 K must be fed in. This reduces the total electrical drive power from 6000 W to 4700 W, 3000 W at the compressor and 1700 W at the heating.
- the pipe connection between the outlet of the regenerator and the entrance to the pulse tube is heated by the gas flame.
- the pulse tube cooler is coupled to the output of the jerk cooler.
- the practical implementation of a cooler with the aforementioned performance data is shown by way of example in FIG. 4.
- the left assembly in the figure represents the compressor with high and low pressure buffer tanks, HD and ND, and the alternately operated valves, solenoid or rotary valves.
- the middle group represents the single-stage pulse tube cooler to be operated, and the right assembly shows to scale the power or pulse tube amplifier adapted to it.
- Its regenerator has a similar structure to that of the cooler, with only the pore size being adapted to the higher temperature range.
- a ceramic body wrapped with heating wire can be used as a largely conventional design as direct heating.
- the pulse tube is optimized in terms of length and diameter so that a temperature a little above ambient temperature (approx. 300 K + ⁇ T) arises at the lower end, and that the phase relationship between pressure and gas flow is adapted to the requirements of the series connection.
- the heat previously supplied at high temperature is recooled to ambient temperature.
- a similar recooling takes place in the compressor. Therefore, the heat exchanger installed between the pulse tube amplifier and the pulse tube cooler can be constructed in a similar way to the plate exchanger which is integrated in the compressor.
- the linear alignment of the pulse tube power amplifier in Figure 4 is based on practical considerations. Pulse tube amplifiers and coolers are shown on the same scale. The main dimensions and operating parameters are summarized in Table 1.
- the regenerator consists of stacked 100 mesh SS, 62 mm diameter, 2 mm thick. This is followed by the heat exchanger in the form of the heater, which uses 1700 W and generates 1000 K. It has an inner diameter of 55.2 mm and is 140 mm long. The empty space is 50%.
- the pulse tube with the above dimensions follows. It has a wall thickness of 2 mm and consists of high temp. Steel 1.4961. At the pulse tube exit there is a flow smoother made of a 200 mesh SS, about 15 mm thick.
- the heater is covered with a first radiation shield. Another encases this, about a third of the regenerator and about one
- the heat must be transferred to the working gas from a burner chamber located outside the gas space or from a collector space for solar heating.
- the pulse tube amplifier can be operated with a gas or oil burner according to the schematic illustration in FIG.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Amplifiers (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10001460A DE10001460A1 (en) | 2000-01-15 | 2000-01-15 | Pulse tube power amplifier and method for operating the same |
DE10001460 | 2000-01-15 | ||
PCT/EP2001/000124 WO2001051862A1 (en) | 2000-01-15 | 2001-01-08 | Periodic refrigerating machine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1247050A1 true EP1247050A1 (en) | 2002-10-09 |
EP1247050B1 EP1247050B1 (en) | 2004-10-20 |
Family
ID=7627597
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01915128A Expired - Lifetime EP1247050B1 (en) | 2000-01-15 | 2001-01-08 | Periodic refrigerating machine |
Country Status (6)
Country | Link |
---|---|
US (1) | US6622491B2 (en) |
EP (1) | EP1247050B1 (en) |
JP (1) | JP3857587B2 (en) |
AT (1) | ATE280369T1 (en) |
DE (3) | DE10001460A1 (en) |
WO (1) | WO2001051862A1 (en) |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100454271B1 (en) * | 2002-08-16 | 2004-10-26 | 엘지전선 주식회사 | Heat-Driving Acoustic Orifice Pulse Tube Cryocooling Device |
JP4035069B2 (en) * | 2003-02-27 | 2008-01-16 | 財団法人名古屋産業科学研究所 | Piping equipment equipped with a sound amplifying / attenuator using thermoacoustic effect |
US20050103615A1 (en) * | 2003-10-14 | 2005-05-19 | Ritchey Jonathan G. | Atmospheric water collection device |
WO2005106352A2 (en) * | 2004-03-10 | 2005-11-10 | Praxair Technology, Inc. | Low frequency pulse tube with oil-free drive |
JP2008286507A (en) * | 2007-05-21 | 2008-11-27 | Sumitomo Heavy Ind Ltd | Pulse tube refrigerator |
DE102008050653B4 (en) * | 2008-09-30 | 2013-09-12 | Institut für Luft- und Kältetechnik gGmbH | Heat engine according to the pulse tube principle |
DE102008050655B4 (en) * | 2008-09-30 | 2011-02-10 | Fox-Service Gmbh | Exhaust system for motor vehicles with integrated heat engine |
US8950193B2 (en) | 2011-01-24 | 2015-02-10 | The United States of America, as represented by the Secretary of Commerce, The National Institute of Standards and Technology | Secondary pulse tubes and regenerators for coupling to room temperature phase shifters in multistage pulse tube cryocoolers |
CN103017401B (en) * | 2012-12-12 | 2015-06-03 | 浙江大学 | Acoustic power amplifying device capable of adopting cold energy |
JP6286837B2 (en) * | 2013-03-05 | 2018-03-07 | いすゞ自動車株式会社 | Thermoacoustic refrigeration equipment |
DE102013005304A1 (en) | 2013-03-22 | 2014-09-25 | Technische Universität Ilmenau | Device and method for generating a cooling capacity |
US11041458B2 (en) * | 2017-06-15 | 2021-06-22 | Etalim Inc. | Thermoacoustic transducer apparatus including a working volume and reservoir volume in fluid communication through a conduit |
US11193191B2 (en) * | 2017-11-28 | 2021-12-07 | University Of Maryland, College Park | Thermal shock synthesis of multielement nanoparticles |
CN109990496B (en) * | 2017-12-29 | 2021-10-08 | 同济大学 | Tandem pulse tube refrigerator |
JP6913039B2 (en) * | 2018-01-25 | 2021-08-04 | 住友重機械工業株式会社 | Pulse tube refrigerator |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4858441A (en) * | 1987-03-02 | 1989-08-22 | The United States Of America As Represented By The United States Department Of Energy | Heat-driven acoustic cooling engine having no moving parts |
JP2706828B2 (en) * | 1989-11-01 | 1998-01-28 | 株式会社日立製作所 | refrigerator |
JPH03194364A (en) * | 1989-12-25 | 1991-08-26 | Sanyo Electric Co Ltd | Cryostatic freezer |
JP2902159B2 (en) * | 1991-06-26 | 1999-06-07 | アイシン精機株式会社 | Pulse tube refrigerator |
CN1098192A (en) * | 1993-05-16 | 1995-02-01 | 朱绍伟 | Rotary vascular refrigerator |
JPH0719635A (en) * | 1993-06-29 | 1995-01-20 | Naoji Isshiki | Pulse tube refrigerator |
JP3624542B2 (en) * | 1996-04-30 | 2005-03-02 | アイシン精機株式会社 | Pulse tube refrigerator |
US5791149A (en) * | 1996-08-15 | 1998-08-11 | Dean; William G. | Orifice pulse tube refrigerator with pulse tube flow separator |
JPH10132404A (en) * | 1996-10-24 | 1998-05-22 | Suzuki Shiyoukan:Kk | Pulse pipe freezer |
US5722243A (en) * | 1996-11-13 | 1998-03-03 | Reeves; James H. | Pulsed heat engine for cooling devices |
JP2880142B2 (en) * | 1997-02-18 | 1999-04-05 | 住友重機械工業株式会社 | Pulse tube refrigerator and method of operating the same |
JP4147697B2 (en) * | 1999-09-20 | 2008-09-10 | アイシン精機株式会社 | Pulse tube refrigerator |
US6374617B1 (en) * | 2001-01-19 | 2002-04-23 | Praxair Technology, Inc. | Cryogenic pulse tube system |
-
2000
- 2000-01-15 DE DE10001460A patent/DE10001460A1/en not_active Withdrawn
- 2000-12-12 DE DE10061922A patent/DE10061922C2/en not_active Expired - Fee Related
-
2001
- 2001-01-08 AT AT01915128T patent/ATE280369T1/en not_active IP Right Cessation
- 2001-01-08 DE DE50104203T patent/DE50104203D1/en not_active Expired - Lifetime
- 2001-01-08 JP JP2001552033A patent/JP3857587B2/en not_active Expired - Fee Related
- 2001-01-08 EP EP01915128A patent/EP1247050B1/en not_active Expired - Lifetime
- 2001-01-08 WO PCT/EP2001/000124 patent/WO2001051862A1/en active IP Right Grant
-
2002
- 2002-07-15 US US10/194,262 patent/US6622491B2/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO0151862A1 * |
Also Published As
Publication number | Publication date |
---|---|
US20030019218A1 (en) | 2003-01-30 |
ATE280369T1 (en) | 2004-11-15 |
JP2003523495A (en) | 2003-08-05 |
DE10061922A1 (en) | 2001-08-02 |
DE10001460A1 (en) | 2001-08-02 |
EP1247050B1 (en) | 2004-10-20 |
DE10061922C2 (en) | 2003-10-30 |
JP3857587B2 (en) | 2006-12-13 |
US6622491B2 (en) | 2003-09-23 |
DE50104203D1 (en) | 2004-11-25 |
WO2001051862A1 (en) | 2001-07-19 |
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