GB2188374A - Forced convector heater including a hot gas reciprocating engine - Google Patents
Forced convector heater including a hot gas reciprocating engine Download PDFInfo
- Publication number
- GB2188374A GB2188374A GB08709635A GB8709635A GB2188374A GB 2188374 A GB2188374 A GB 2188374A GB 08709635 A GB08709635 A GB 08709635A GB 8709635 A GB8709635 A GB 8709635A GB 2188374 A GB2188374 A GB 2188374A
- Authority
- GB
- United Kingdom
- Prior art keywords
- hot gas
- heater
- heat
- gas reciprocating
- cooler
- 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
- 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
- F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
- F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
- F02G1/053—Component parts or details
- F02G1/055—Heaters or coolers
-
- 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
- F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
-
- 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
- F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
- F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
- F02G1/044—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines having at least two working members, e.g. pistons, delivering power output
-
- 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
- F02G2243/02—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having pistons and displacers in the same cylinder
-
- 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
- F02G2243/02—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having pistons and displacers in the same cylinder
- F02G2243/04—Crank-connecting-rod drives
-
- 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
- F02G2255/00—Heater tubes
-
- 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
- F02G2256/00—Coolers
-
- 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
- F02G2257/00—Regenerators
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
SPECIFICATION
A hot gas reciprocating apparatus
This invention generally reiates to hot gas reciprocating apparatus, and more particularly, to a simplified stirling cycle type engine in which heat from an external source is converted to useful mechanical energy.
Astirling cycletype engines arewell know bathe prior art. Stirling cycle machine is a device which operates on a regenerative thermodynamic cycle, with cyclic compression and expansion ofthe working fluid at different temperature levels, and where the flow is controlled by volume changes so thatthere is a net conversion of heat to work or vice versa. In a typical stirling cycle engine, operating as a prime mover, heat is suppliedtotheworking fluid at some high temperature Th, when the fluid is in a hot chamber. Part ofthe heat is converted to workwhen working fluid, due to the absorbed heat, expands and thereby pushes on a piston, which is coupled to a crank shaft and inparts rotary motion thereto.The working fluid is then displaced by a displacer through a regeneratorandforced intoacold chamber, which is at some lower temperature Ti.
Thereafter, the working fluid is forced out of the cold chamber by the displacer through the regenerator into the hot chamber and as it passes the regenerator it reabsorbs some of the heat previously deposited thereat. Inthehotchamberitagain absorbsheatand the cycle of operation repeats itself.
In the stirling cycle engine operating as the prime mover, the working fluid expansion takes place in the hot chamber, while most ofthe compression takes place in the cold chamber. As is appreciated by those familiarwiththe art when stirling cycle is used in a hot-gas enginetheworking fluid expansion occurs in the hot chamberwhile the compression ofthe working fluid, during which heat is rejected, takes place in the cold chamber. In either type machine the working fluid is shifted between the two chambers through a regenerator by means of the displacer. The motion ofthe latter is generally synchronized with the piston motion by means of mechanical linkages which adds to the complexity of the machine.
The theroreticaS maximum afficiency of a hot-gas engine is determined bythefollowing formula: (Th - T1)/Th whereinTh devotestheabsolutetemperature prevailing on the hot side of the engine and T1 the absolute temperature prevailing on the cold side of the engine. Therefore, it is important in the first place in connection with a satisfactory efficiency to maintain the temperature on the hot side of the engine as high as possible and on the cold side ofthe engine as low as possible.
It is a primary object of this invention to provide an improvement heat gas reciprocating apparatus which are achieved high efficiency.
It is another object ofthis invention to provide a heat-gas reciprocating apparatus which is simple in construction and easy to manufacturing.
It is another object ofthis invention to provide a
new heating device which utilize the compact heat
gas reciprocating apparatus.
A hot gas reciprocating apparatus according to this invention includes a power piston and a displacer both of which are slidably fitted within a cylinder. An internal space of the cylinder is devided
by the movable displacer into two chambers. These two chambers are connected to one anotherthrough a cooler, a regenerator and a heater. Each cooler and heatercomprisesa plurality of pole shaped members which consist of an outertube element and innertube element to define a double passage way.
The cooler and heater are parallel extended from an outer peripheral surface of the cylinderto place the opposing each other and axially offset.
The invention will now be described, byway of example, with reference to the accompanying drawings, in which Figure lisa vertical sectional view of a hot gas reciprocating apparatus according to one embodiment ofthis invention.
Figure2is a plan view of a hot gas reciprocating apparatus in Figure 1.
Figure 3is a side view of a hot gas reciprocating apparatus in Figure 1.
Figure 4 is a partially cross-sectional view of a hot gas reciprocating apparatus illustrating the flow of working fluid.
Figure 5is a schematic cross sectional view of a hot gas reciprocating apparatus to illustrate the another embodiment of this invention.
Figure6is a cross sectional view taken a lineA-Ain
Figure 5.
Figure 7is a diagrammatic view qf a heating device which utilize the hot gas reciprocating apparatus.
Figure 8 is a vertical sectional view of a convective type heater utilizing a hot gas reciprocating apparatus according to one embodiment of this invention.
Figure 9is a plan viewofthe heater in Figure8.
Referring to Figure 1, a hot gas reciprocating apparatus according to embodiment of this invention is shown. The apparatus 1 comprises an annular housing 10 having a cylinder 11, a cylinder cap 12 disposed on the one end portion of cylinder 11 to close the one end opening of cylinder 11 and a crank case 13.
Displacer piston 14 is slidably fitted within cylinder 11 to divided the cylinder into two chambers. A power piston 15 is also slidably fitted witin cylinder 11 to place in lower position of cylinder 11; atop surface of power piston 15 is faced to the bottom surface of displacer piston 14. Therefore, upper chamber of cylinder 11 is fanction as heat chamber 11 a and a space defined between displacer piston 14 and power piston 15 is function as cold chamber 11 b.
Both pistons 14,15 are linked to a crankshaft 16 which is rotatably supported in crank case 13 through bearings 17. Crank shaft 16 hasthree cranks 16a, 16b, 16e therein, and the two autside ones 16a, 16c,which lieatthesameangle, are linked to power piston 15 bytwo parallel connecting rods 18a, 18b.
Displacer piston 14 is actuated from middle crank 16b,which is offset bya certain anglefrom the other two 16a, l6cthrough rod 19which is linked to connecting rod 20 fastened on crank 1 6b through linkage means 21.
An annular cylindrical member 21 is disposed on an outer peripheral surface of cylinder 11 with a gap to define a regenerating space R, i.e.. regenerator30 is defined by outer peripheral surface of cylinder 11 and cylindrical member21. Cylindrical member21 placed on the upper portion of cylinder and fixed on cylinder 11 through connecting member 22 buy a plurality of bolts 23. That is connecting member 22 is disposed on a radial flange portion 111 radially projecting from outer peripheral surface of cylinder 11, and lower end portion of cylindrical member 21 is fitted on the upper end surface of connecting member 22 to fastened thereon. The upperend surface of cylindrical member 21 is fitted on the end surface ofcylindercap 12.As shown in Figures 2 and 3, cylinder cap 12 and cylindrical member 21 are fastened to one another by a plurality of bolts 24.
Referring to Figures 1 and 2, a plurality of heaters 25 are disposed on cylinder cap 12 to radially extend.
Each heaters 25 comprises an outer tube element 251 ofwhich outer end opening is closed and an inner tube element 252. One end portion of outer tube element 251 is fixed on cylinder cap 12to communicate with a inner space of outertube element 251 and a hollow space 121 formed in cylinder cap 12. Hollow space 121 is connected to the regenerating space Rthrough opening 121a of space 121. Therefore, the inner space ofoutertube element 251 is communicated with the space R of regenerator 30 through hollow space 121 and opening 121a.
Also, one end portion ofinnertube element 252 is fixed on cylinder 12 to open on the inner surface of cylinder 12. Innertube element 252 extends into follow space 121 and innerspaceofoutertube element 251 with a small gap 31 to define passage way ofthe medium gas.
A plurality of coolers 26 are disposed on connecting member 22 to radially extend. These coolers 26 are projected from the opposite side ofthe apparatus from which heaters 25 extend and axially offset. Each coolers 26 comprises an outertube element25l withpluralfins26laandaninnertube element 262. Outertube element 261 is closed the one end opening and fixed on connecting member 22 to communicate between the inner space of outer tube element 251 and a hollow space 221 formed in connecting member 22. Hollow space 221 is connected to the space R of regenerator 30 through opening 221 a, therefore the inner space ofoutertube element 261 is communicated with the space R of regenerator 30 through hollow space 221 and opening 221 a.Innertube element 262 is fixed on cyclinder 11 and extends into the inner space of outer tube element 261 and hollow space 221 with a gap 32 to define a passage way ofthe medium gas. Inner tube element is open on the innersurface of cylinder 11 to face the cold chamber 11 b. Thus, heat chamber 11 a and cold chamber 11 b are connected with one anotherthrough heater 25, hollow space 121, regenerator space R, hollow space 221 and cooler 26.
Regenerator 30 comprises plural wire cloth 33 disposed in the space of regenerator 30 as wind up the outer peripheral surface of cylinder 12, and is placed between heater 25 and cooler 26 to prevent unnecessary wastage of the heat. During the passed medium gas which is heated by heater 25, the hot gas yields heat before entering the cooler, and when the gas streams back, it takes up the stored heat again prior to its entry into the heater 25.
When this apparatus supplies mechanical energy the heat of heat source 33 is transmitted to the gas which is enclosed in the apparatus as the working medium through heater 25. The heat left in the gas after expansion and after passing through regenerator 30 is absorbed by the cooling airvia cooler 26. The outer peripheral surface of outertube element 261 of cooler 26 is thus provided with plural this 261 a to promote the heat exchange of cooler 26.
In this case the thermal cyclic process in the apparatus and due to the difference in phase between the movement of the power piston 15 and displacer piston 14 is as follows; compression of the gas in heat chamber 1 la, heating in the heater 25 by externally positioned heat source 33, followed by the expansion stroke of power piston 15; the expanding gas flows through regenerator 30 wherein it gives off a great part of the heat avairable in the gas. The expanded gas is deprived in cooler 26 of the remaining heat and flows into cold chamber 11 b. The compression stroke then takes place, the gas in cold chamber 11 b back to heat chamber 11 a and absorbs again the heat accumulated in regenerator 30.This is followed by heating again and the cycle is repeated with each cycle of movement of power piston 1 Sand displacer piston 14.
Referring to Figure 7 and 8, a force convection type heater 100 which is utilized hot gas reciprocating apparatus, one of embodiments is explained referred with Figures 1-4, is shown. In the hot gas reciprocating apparatus contained in their heater 100, similar parts are represented by the same reference numerals as in the embodiment shown in
Figures 1-3, and any description ofthe similar parts are ommitted to simplity the description. Heater 100 includes a blow duct 110 provided with a cold air intake opening 111 and warming airsupplyopening 112, and combusion pipe 120to supplythe heatas the heat source.
Blow duct 1 lOcomprises a outerductelement 11 Oa which is formed integral with an outer casing of heater 100 and an inner duct element 11 0b which is divided the blow duct space C from heating space H in which combustion pipe 120 is placed. An opening 113 is formed on the midway portion of inner duct element 11 0b to intakethewarming airfrom heating space H disposed on combusion pipe 120. The hot gas reciprocating apparatusl one of which embodiments is described in Figures 1-3 is disposed within blow duct 110. A blast fan 34 which is fixed on the outer terminal end of drive shaft 16 ofthe apparatus is placed on air intake opening 111 to intake the cold air from outside of heater 100 into blowductli0, and also main portion of the apparatus including cooler 26 is disposed in the blow duct which is expose to the intaked cold air. The cold air is thus flowed into blow duct 110 due to operation of blastfan 34, and during the passed in duct 110, cold air is cooled the outer surface of apparatus 1 and effected the heat exchange with the gas contained in the apparatus through cooler 26. During flow toward warming airsupply opening 112, the cold air mix with the hot air supply from heating space H through opening 113.The upperend portion of apparatus 1 extends into the heating space; heater 25 extends as placed on the upper portion ofcombusion pipe 120 with a gap, and also placed on the heat air passage way which comprises the opening 113. Therefore, heater 25 of apparatus 1 is heated by combusion pipe 120.
In this construction of the heater 100, when the gas enclosed in the hot gas reciprocating apparatus 1 is heated by combusion pipe 120through heater 25 which extends to the upper portion of combusion pipe 120 of heater 100, the heat left in the gas after expansion and after passing through regenerator 30 isabsorbed bythecooling airviacooler26which is supplied the operation of fan 46.The thermal cyclic process in the hot gas reciprocating apparatus and due to the difference in phase between the movement of power piston 15 and displacer piston 14 is as follows; compression ofthe gas in heat chamber 11 a, heating in heater 25 by combusion pipe 120, followed by the expansion stroke of power piston 15; the expanding gas flowsthrough regenerator 30, wherein it gives off a great part of the heat avairable in the gas. The expanded gas is deprived in cooler 26 ofthe remaining heat and flows into cold chamber 11 b. The compression stroke then takes place, the gas in cold chamber 11 b back to heat chamber 11 a and absorbs again the heat accumulated in regenerator 30. This is followed by heating again and the cycle is repeated with each cycle of movement of power piston 15 and displacer piston 14.Thefan 34fixed on the outerterminal end of drive shaft 16 is thus rotated due to reciprocation of power piston 15 and displacer piston 14through crank shaft 16.
As a result of rotation of fan 34, cool air is taken into blow duct 110through air intake opening 111 and flows toward warming airsupplyopening 112 during cooled the cooler 26. During passed the duct 110, warming airflow into duct 1 10from heating space H through opening 113 is mixed with the cool air. So thaw coo air is warmc' b' he wa;-ming air and supplied to the room through opening 112.
As mention above, in the forced convectortype heater, the fan which is included in the heater for cause the airflow within the heater is driven bythe hot gas reciprocating apparatus, and mostly part of the hot gas reciprocating apparatus is disposed in the blow duct. The heater ofthe reciprocating apparatus only extends on the upper portion of combustion pipe of heater which is separated from the blow duct. Therefore, thetemperature difference between the heaterand the cooler is securely established, to thereby accomplished the high efficiance of the reciprocating apparatus.
This invention has been described in detail in connection with the preferred embodiments, but these are examples only and this invention is not restricted thereto. It will be easily understood by those skilled in the art that other variations and modifications can be easily made within the scope of this invention.
Claims (2)
1. Aforced convectortype heater including a blow duct having a cold air intake opening and a warming air supplying opening and divided into a passage of cold air and a heating space, a combustion pipe disposed on the heating space and a blastfan disposed in said cold air intake opening, wherein a hot gas reciprocating apparatus is disposed in said blow duct and said fan is fixed on an outer terminal end of a crank shaft of said apparatus, said hot gas reciprocating apparatus having a heater means and a cooler means, and said heater means projecting radially from said apparatus to extend on the upper portion of said combustion pipe.
2. A forced convector type heater as claimed in claim 1, wherein said cooler of said hot gas reciprocating apparatus is exposed in said duct.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24997083A JPS60142152A (en) | 1983-12-28 | 1983-12-28 | Hot air room heating machine utilizing hot gas engine |
| JP24996983A JPS60142042A (en) | 1983-12-28 | 1983-12-28 | Hot gas engine |
| JP24997183A JPS60142039A (en) | 1983-12-28 | 1983-12-28 | Structure of thermal gas engine |
| GB08432734A GB2154285B (en) | 1983-12-28 | 1984-12-28 | A hot gas reciprocating apparatus |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| GB8709635D0 GB8709635D0 (en) | 1987-05-28 |
| GB2188374A true GB2188374A (en) | 1987-09-30 |
| GB2188374B GB2188374B (en) | 1988-09-28 |
Family
ID=27449617
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB08709635A Expired GB2188374B (en) | 1983-12-28 | 1987-04-23 | A hot gas reciprocating apparatus |
Country Status (1)
| Country | Link |
|---|---|
| GB (1) | GB2188374B (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB899351A (en) * | 1960-04-08 | 1962-06-20 | Webasto Werk Baier Kg W | Improvements in and relating to heating devices for fluids |
-
1987
- 1987-04-23 GB GB08709635A patent/GB2188374B/en not_active Expired
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB899351A (en) * | 1960-04-08 | 1962-06-20 | Webasto Werk Baier Kg W | Improvements in and relating to heating devices for fluids |
Also Published As
| Publication number | Publication date |
|---|---|
| GB8709635D0 (en) | 1987-05-28 |
| GB2188374B (en) | 1988-09-28 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PCNP | Patent ceased through non-payment of renewal fee |
Effective date: 19961228 |