EP0042902A1 - Machine à piston à gaz chaud et son utilisation dans des installations calorifiques, frigorifiques et de production d'énergie - Google Patents

Machine à piston à gaz chaud et son utilisation dans des installations calorifiques, frigorifiques et de production d'énergie Download PDF

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Publication number
EP0042902A1
EP0042902A1 EP80810217A EP80810217A EP0042902A1 EP 0042902 A1 EP0042902 A1 EP 0042902A1 EP 80810217 A EP80810217 A EP 80810217A EP 80810217 A EP80810217 A EP 80810217A EP 0042902 A1 EP0042902 A1 EP 0042902A1
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EP
European Patent Office
Prior art keywords
heat exchanger
heat
machine according
burner
tubes
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Withdrawn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
EP80810217A
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German (de)
English (en)
Inventor
Treuhand Gmbh Fides
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to EP80810217A priority Critical patent/EP0042902A1/fr
Priority to US06/275,787 priority patent/US4435959A/en
Priority to JP56102211A priority patent/JPS5779233A/ja
Publication of EP0042902A1 publication Critical patent/EP0042902A1/fr
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/02—Hot gas positive-displacement engine plants of open-cycle type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular

Definitions

  • the present invention relates to a hot gas piston machine with a heat exchanger and to the use of the same in various systems such as heating and cooling systems and gas turbine systems.
  • the hot-air motor 4 is in this example a two-cycle hot-air motor, for example having a power of 10 kW and 4 cylinders with a total of 6000 cm 3 Content.
  • the heat exchanger 6 consists of a number Tubes 7. In the present example there are 150 tubes per cylinder with a diameter of 2.5 mm and a length of 500 mm. The tubes are arranged with respect to the flame 8 in such a way that the tubes of a cylinder are heated as evenly as possible.
  • the method of operation is as follows: In the bottom dead center area of the piston 9 of a cylinder, the purging takes place, that is to say the heated air exits the cylinder and is fed to the burner as warm combustion air at a temperature of, for example, 300 ° C., while the cold fresh air flows into the Cylinder enters (crankcase flushing). During the subsequent compression, the air enters the tubes of the heat exchanger, which are heated by the hot gases of the burner flame and transfer the heat to the enclosed air. This causes an increase in pressure and the piston does the work when moving downwards. The purging then takes place again in the bottom dead center area, etc.
  • tubes or the like which form the upper end of the compression space and the air contained therein is heated very quickly, eliminates the need for the use of otherwise customary heat exchangers with valves.
  • the number and size of the tubes must be matched to the strength and size of the flame and the period of the bulb.
  • the effective surfaces of the tubes are determined in such a way that the heat is transferred to the working gas quickly enough.
  • An increase in the overall efficiency is also achieved by supplying preheated combustion air to the burner via the feed line 10. Because the tubes protrude into the hot water area of the boiler, a certain temperature regulation is achieved and thus overheating of the tube ends is avoided.
  • the mechanical energy obtained on the output shaft 11 can for example be used to generate electrical energy, which enables autonomous operation of this system and possibly of the building in which the system is located.
  • the electrical energy can be used to operate a heat pump.
  • the exhaust gases from the burner reach the exhaust gas line 12.
  • the hot water supply 13 and the return 14 can also be seen.
  • FIG. 2 shows a thermal power plant with a gas turbine.
  • a gas turbine 15 with the compressor group 16 and the intercoolers 17 can be seen at the output of the incineration plant.
  • the output shaft of the gas turbine is designated by 18.
  • the fresh air passes from the inlet 19 through the compressor groups 16 and the intercoolers 17 into the cylinder inlet 20, is driven into the tubes of the heat exchanger in the compression phase of the piston, is heated and reaches the feed line 10 of the burner 1 via the cylinder outlet 21.
  • FIG. 1 The working diagram of this air circuit is shown in FIG.
  • the air passes through inlet 17 point A and is compressed in the compressor group and intercooler, points B, 'C, D, and reaches the cylinder at E.
  • the compression phase from E to F takes place in the heat exchanger, and the expansion and working phase at the cylinder outlet and in the feed line to the burner, points G and H.
  • the heat supply in the burner increases the volume of the gas, I, and cools down at a constant pressure the heat exchangers, J, and expansion in the gas turbine, K to get into the exhaust pipe.
  • the hatched area means the additional work gained on the output shaft 11 of the hot-air engine, while the remaining area corresponds to the work on the gas turbine shaft 18.
  • FIG. 3 shows a further, improved embodiment variant of the motor from FIG. 1. It is possible to increase the efficiency of the heat exchanger and to prevent the tubes from overheating by bending the tubes or fins in such a way that the end of the air duct comes close to the beginning, so that the hot ends of the tubes of the compression space heat less warm inlets. This can be carried out, for example, as shown in FIG. 3, the tubes 22 of the heat exchanger being bent and the ends having the beginnings being connected to one another in a heat-conducting manner. In this embodiment variant, a blower 23 is used instead of the usual pumping action of the two-stroke piston in the crankcase housing. A variant of the tubes or fins of the heat exchanger is shown in FIG. 4.
  • alloyed cast iron or another, highly conductive metal is suitable.
  • the section V - V is shown in FIG. 5, the slot width b being 0.5-5 mm in the present example.
  • the air is preheated when it flows into the fins.
  • FIGS. 6-10 A number of further exemplary embodiments are shown schematically in FIGS. 6-10.
  • FIG. 6 and its section 7 show an embodiment variant in which the heat exchanger 50 consists of round hollow bodies provided with ribs on the inside and outside.
  • the outer hollow body 51 with outer fins 52 is heated on the outside by the flame and gives off its heat through the wall and the inner fins 53 to the air flowing in at 54.
  • the particularly strongly heated amount of air reaches the top at 55 in the inner hollow body 56, which is closed at 57 and gives off the heat partially via fins 58 to the air flowing in at 54, so that the ge entire amount of air in the compression space is brought to about the same temperature.
  • the slot width b is again in the millimeter range.
  • FIG. 8 and its section 9 show a further embodiment variant, in which the exchangers 59 with the outer, 60, and inner, 61, hollow bodies are not cylindrical, but rectangular, and have ribs 62.
  • FIG 10 shows a further embodiment in which the exchanger 63 g prepared by ekantete and welded panels are constituting an outer, 64, and an inner, 65, hollow bodies, which are provided with ribs 66th
  • the mode of action is similar to the previous examples.
  • the large-area, lamellar-shaped heat exchangers can be produced by pulling, turning, broaching, milling, pressing, edging, welding or casting, ie practically by all manufacturing processes. It needs to be always ensured that the air ducts so stay small that a large heat exchange area is created and thus also the g rosse flow rate of the compressed air in this little Ziwschensch sufficiently high, so that a good heat transfer to the compressed air is possible. In some embodiments, this heat transfer must occur within 40 ms. However, in order to avoid larger throttling losses in the heat exchanger, it is advisable to keep the flow velocity in the tubes or fins approximately constant.
  • these air channels are designed such that they are from the input 27 or 54, and slightly tapered, that is, the cross section of the air channels should be when entering horses g his than the deflection point 25, or 55, or at the end points 26 and 57 .
  • a further increase in efficiency and in particular combustion can be achieved by the flame front pulsing.
  • the number of piston cylinders and the length and configuration of the air supply line 10 are coordinated such that the flame oscillates between the two points S1 and S2. With appropriate coordination of this vibration it can be achieved that the flame front is always at a time that is favorable for heat transfer, i.e. when the piston is at top dead center, near the heat exchanger, i.e. located at S2. This pulsation also promotes heat transfer.
  • FIG. 7 shows an application example of hot gas piston machines in which a total of three machines are used which allow the autonomous operation of a heat pump and a cooling unit.
  • the boiler 28 with the heating water supply 29 and the return 30 and the burner 31 can be seen.
  • the first hot air motor 32 is designed as in the previous example according to FIG. 3, the tubes or fins 22 also being designed differently, for example as shown in FIGS. 4 to 10 could be.
  • the first hot air motor 32 drives a second hot air piston machine 33, which is designed as a heat pump.
  • the pistons 34 and 35 of the two machines sit on the same shaft 36 and are radially offset.
  • the heat exchanger 37 of the heat pump projects into a boiler room 38 of the boiler, into which room the cool return water flows.
  • the heat exchanger works at much lower temperatures and in water, other materials can be used than for the heat exchanger tubes, which come into contact with the hot and corrosive gases of the burner flame. However, it is also important in this case that the tubes or fins of the heat exchanger 37 rapidly transfer those generated in them by the compression of the air Ensure warmth to the surrounding water.
  • the two machines are supplied with the necessary fresh air by a common blower 39 with a control flap 40.
  • this hot air motor-heat pump combination is as follows:
  • the shaft 36 driven by the hot air motor 32 drives the pistons 35 of the heat pump, which compresses the fresh air coming from the fan 39 into the tubes of the heat exchanger serving as the upper compression space and to approximately 100 to 300 ° C. heated.
  • the heat reaches the boiler space 38 via the heat exchanger 37, as a result of which the water contained therein is heated to approximately 50 to 90 ° C. This is an advantage over the usual heat pumps, which only allow heating water heating up to approx. 50 ° C.
  • the expanded air which has been cooled to, for example, 0 ° C.-30 ° C., comes out via an outlet 41, although it may also be required for cooling purposes, for example for operating a cooling or fresh-keeping system.
  • the cylinder groups on the one hand and the fresh air supply on the other must be coordinated and controlled.
  • a further hot gas piston machine can be used as the cooling unit, which in principle works like a heat pump running in reverse.
  • the air piston machine 42 is driven by an electric motor 43, and a combination similar to that described above is also possible for driving this machine.
  • the air coming from the fan 44 is compressed and heated in the tubes of the heat exchanger 45.
  • the heat exchanger 45 protrudes into a cooling chamber 46, through which air is driven by a fan 47. This air causes a cooling of the compressed and heated air via the heat exchanger 45, which when expanding to for example, -20 ° C is cooled.
  • This cooled air passes through the outlet 48 and the open flap 49 (shown in FIG.
  • the water supply temperature is approximately 5 ° C. can lower.
  • the air heated by the compressed air, via the heat exchanger 45 to about 80-120 ° C. can be used to heat the domestic water. Since it is an air-air heat exchanger in the present case, the material and the dimensions of the tubes or fins of the heat exchanger 45 must be adapted to this. But you can also indirectly heat the process water by means of the heat exchanger 45 if no warm air is required. In a machine designed as a heat pump and driven by a motor, the heat exchanger can give off its heat to the heating medium, which can be water, oil or air. It is advantageous if the heating medium is additionally circulated by means of a pump or blower.
  • the diameter of the tubes or lamellae can vary within a wide range, expediently covering a range of 1-5 mm 0 and a length of 100-1000 mm, preferably a diameter or slot width b of 1.5 - 3 mm and a length of 400 - 600 mm is used.
  • the wall thickness and in particular also the surface design and the material are adapted to the circumstances, i.e. in the case of a heat exchanger in the area of the burner flame or in a liquid medium such as water or in air.
  • a number other than two cylinders can also be selected.
  • the firebox can be lined fireproof. However, care must be taken to ensure that the tube ends are not heated excessively and that they are cooled.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP80810217A 1980-07-01 1980-07-01 Machine à piston à gaz chaud et son utilisation dans des installations calorifiques, frigorifiques et de production d'énergie Withdrawn EP0042902A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP80810217A EP0042902A1 (fr) 1980-07-01 1980-07-01 Machine à piston à gaz chaud et son utilisation dans des installations calorifiques, frigorifiques et de production d'énergie
US06/275,787 US4435959A (en) 1980-07-01 1981-06-22 Hot-gas piston-type engine and use thereof in heating, cooling and power plants
JP56102211A JPS5779233A (en) 1980-07-01 1981-06-30 Thermal gas piston type engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP80810217A EP0042902A1 (fr) 1980-07-01 1980-07-01 Machine à piston à gaz chaud et son utilisation dans des installations calorifiques, frigorifiques et de production d'énergie

Publications (1)

Publication Number Publication Date
EP0042902A1 true EP0042902A1 (fr) 1982-01-06

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EP80810217A Withdrawn EP0042902A1 (fr) 1980-07-01 1980-07-01 Machine à piston à gaz chaud et son utilisation dans des installations calorifiques, frigorifiques et de production d'énergie

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US (1) US4435959A (fr)
EP (1) EP0042902A1 (fr)
JP (1) JPS5779233A (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101509437B (zh) * 2009-03-24 2011-10-05 哈尔滨翔凯科技发展有限公司 高效高温型外燃机

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR0143212B1 (ko) * 1993-04-30 1998-08-17 김광호 벌마이어 히트펌프의 냉,난방수 순환장치
US5664421A (en) * 1995-04-12 1997-09-09 Sanyo Electric Co., Ltd. Heat pump type air conditioner using circulating fluid branching passage
US20070101717A1 (en) * 2005-11-04 2007-05-10 Gerald Beaulieu Energy recuperation machine system for power plant and the like

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE868806C (de) * 1947-11-03 1953-02-26 Georges Bolsezian Teilweise im Kreislauf arbeitende Gasturbinenanlage
GB689484A (en) * 1949-08-17 1953-03-25 Philips Nv Improvements in or relating to heat exchangers
DE1173608B (de) * 1959-02-04 1964-07-09 Steinmueller Gmbh L & C Taschenluftvorwaermer
DE2154714A1 (de) * 1971-11-04 1973-05-10 Motoren Werke Mannheim Ag Erhitzer fuer einen heissgasmotor
DE2420405A1 (de) * 1973-04-30 1974-11-14 Nrg Inc Turbotriebwerk
CH560318A5 (fr) * 1972-03-22 1975-03-27 Hubers Cornelius
DE2433947A1 (de) * 1974-07-15 1976-02-05 Jun Karl Thurn Waermeaustauschmotor
DE2826603A1 (de) * 1977-07-18 1979-02-01 Ford Werke Ag Roehrenwaermetauscher fuer zwei gase von stark unterschiedlichen druecken und verfahren zu seiner herstellung

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US966032A (en) 1910-01-17 1910-08-02 Guillaume Mann Hot-air motor.
GB1412935A (en) 1971-10-05 1975-11-05 Stobart A F Fluid heating systems
GB1508996A (en) 1974-05-20 1978-04-26 Automotive Prod Co Ltd Power plants which include at least one hot gas engine
JPS5215947A (en) 1975-07-25 1977-02-05 Nissan Motor Co Ltd External heat thermal engine
GB1563699A (en) 1975-08-27 1980-03-26 Atomic Energy Authority Uk Stirling cycle thermal devices
US4008574A (en) 1975-10-20 1977-02-22 Rein Charles R Power plant with air working fluid

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE868806C (de) * 1947-11-03 1953-02-26 Georges Bolsezian Teilweise im Kreislauf arbeitende Gasturbinenanlage
GB689484A (en) * 1949-08-17 1953-03-25 Philips Nv Improvements in or relating to heat exchangers
DE1173608B (de) * 1959-02-04 1964-07-09 Steinmueller Gmbh L & C Taschenluftvorwaermer
DE2154714A1 (de) * 1971-11-04 1973-05-10 Motoren Werke Mannheim Ag Erhitzer fuer einen heissgasmotor
CH560318A5 (fr) * 1972-03-22 1975-03-27 Hubers Cornelius
DE2420405A1 (de) * 1973-04-30 1974-11-14 Nrg Inc Turbotriebwerk
FR2227430A1 (fr) * 1973-04-30 1974-11-22 Nrg Inc
DE2433947A1 (de) * 1974-07-15 1976-02-05 Jun Karl Thurn Waermeaustauschmotor
DE2826603A1 (de) * 1977-07-18 1979-02-01 Ford Werke Ag Roehrenwaermetauscher fuer zwei gase von stark unterschiedlichen druecken und verfahren zu seiner herstellung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101509437B (zh) * 2009-03-24 2011-10-05 哈尔滨翔凯科技发展有限公司 高效高温型外燃机

Also Published As

Publication number Publication date
JPS5779233A (en) 1982-05-18
US4435959A (en) 1984-03-13

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