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US3200582A - Hot-gas reciprocating machine - Google Patents

Hot-gas reciprocating machine Download PDF

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US3200582A
US3200582A US320982A US32098263A US3200582A US 3200582 A US3200582 A US 3200582A US 320982 A US320982 A US 320982A US 32098263 A US32098263 A US 32098263A US 3200582 A US3200582 A US 3200582A
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piston
spaces
space
units
fluid
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US320982A
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English (en)
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Dros Albert August
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US Philips Corp
North American Philips Co Inc
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US Philips Corp
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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
    • 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
    • F02G2244/00—Machines having two pistons
    • 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
    • F02G2244/00—Machines having two pistons
    • F02G2244/50—Double acting piston machines
    • 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
    • F02G2270/00—Constructional features
    • F02G2270/85—Crankshafts

Definitions

  • the invention relates to a hot-gas reciprocating machine, particularly a cold-gas refrigerator, comprising one or more compression spaces of variable volume, cornmunicating with one or more expansion spaces also of variable volume, said spaces having, in operation of the machine, different mean temperatures, whilst the connection between the spaces includes regenerators, through which a medium can flow to and fro between the sai spaces, whilst the machine comprises piston-like bodies adapted to move with a phase difference for varying the volumes of the expansion space and of the compression space, said piston-like bodies being coupled with a driving gear.
  • hot-gas reciprocating machine is to denote not only a hot-gas engine but also a cold-gas refrigerator and a heat pump operating on the reverse hot-gas engine principle.
  • the unit in which the thermodynamic cycle is performed is termed hereinafter the cooling unit.
  • coupling is to be understood in this connection to mean not only a fixed connection between the pistons and the driving gear but also a member which controls the movement of the pistons in accordance with the movement of the driving gear or conversely. In this way a simple coupling between the driving gear and the relevant pistons is obtained.
  • the invention has for its object to provide a further improvement of a hot-gas reciprocating machine with the coupling described above between the pistons and the driving gear and is characterized in that the machine comprises at least two pump units, each of which comprises a pair of double-acting pistons adapted to reciprocate in closed, fluid-filled cylinders and in that the machine comprises furthermore at least two pairs of cooling units, each comprising a compression piston, adapted to reciprocate in a cylinder, a cooler,;a regenerator, a freezer or heater and an expansion piston adapted to reciprocate in a cylinder, whilst each of the spaces of one pair of cooling units positioned, on the side remote from the Working space of the expansion pistons associated with said space, communicates with one of the spaces on either side of one of the pistons of the first pump unit and each of the spaces positioned, on the side remote from the working space of the compression piston associated with said space, communicates with one of the spaces on either side of one of the pistons of the second pump unit, whilst each of the spaces of the other
  • An advantage of said machine consists in that with each pump unit the spaces on either side of one of the doubleacting pistons communicate with the spaces on the side of the compression pistons of a pair of cooling units remote from the working space, whereas the spaces on either side of the other double-acting piston of said pump unit communicate with the spaces on the side remote from the working space, of the expansion pistons of the other pair of cooling units. It is thus ensured that the variation of forces on the pump rod, during the movement of the rod in one direction, is substantially identical to the variation of forces on the pump rod during the movement of said rod in the other direction. As a result the load on the driving gear is as uniform as possible.
  • a further advantage of said arrangement is that the energy released during the expansion of the working medium in one pair of cooling units via the fluid columns and one double-acting piston of a pump unit, is directly transferred to the other double-acting piston of said pump unit, said energy being again transferred via the fluid columns to the compression pistons. The eiliciency of the machine is thus extremely furthered.
  • the pump units and the pairs of cooling units may be arranged relatively to each other in an arbitrary manner, an advantageous and compact construction of a hot-gas reciprocating machine is obtained by an arrangement of the units in accordance with the invention, which is characterized in that the pump units are pairwise arranged in a V and are connected with a common crank shaft, whereas each of the cooling units is arranged substantially between planes intersecting in the centre line of the crank shaft and determined by the centre lines of the pump units, and in that in a projection to a plane at right angles to the centre line of the crank shaft the centre lines of the two pump units and the centre line of each cooling unit form a triangle.
  • An advantageous embodiment of the hot-gas reciprocating machine described above is characterized in accordance with the invention, in that one pair of cooling units is arranged between the two pump units so that the spaces on the side remote from the working space of the compression pistons associated with said cooling units are orientated towards the first pump unit communicating with said space, whilst the spaces, on the side of the expansion pistons of said cooling units remote from the working space, are orientated towards the second pump unit associated with said space, whereas the other pair of cooling units is arranged between the two pump units so that the spaces on the side of the compression pistons associated with said cooling units remote from the working space are orientated towards the second pump unit communicating with said space and the spaces on the side of the expansion pistons associated with said cooling units remote from the working space are orientated towards the first pump unit communicating with said space.
  • a further advantageous hot-gas reciprocating machine embodying the invention has the feature that in each cooling unit each piston is connected with a control-slide, which is displaced'during the movement of the piston associated with it along a wall portion of the fluid-filled spaces on the side remote from the working space in said space, whilst in the wall portion controlled by said slide at least one fluid inlet and one fluid outlet are provided, said openings being arranged so that the fluid inlet duct is released, when the piston moves beyond its extreme, prescribed position, whereas the fluid outlet duct is released, when the piston occupies its deepest position in the cooling unit.
  • An advantageous hot-gas reciprocating machine embodying the invention is characterized in that the cylinder of each cooling unit, in which a piston is adapted to move, terminates in a further cylindrical part, in which the piston-like control-slide is adapted to move, whilst the machine comprises one or more ducts establishing a communication between the spaces on either side of the control-slide, whilst the fluid inlet duct and the fluidoutlet duct join the wall of the further cylindrical part.
  • the hot-gas reciprocating machine In order to start the hot-gas reciprocating machine according to the invention the pistons must occupy given positions in the cooling units, which positions correspend with the pistons of the pistons of the pump units at the instant concerned.
  • the hot-gas reciprocating machine according to the invention has the feature that each of the fluid-filled spaces in each cooling unit communicates with a further fluid-supply duct, the passage of which is blocked during the operation of the machine, whereas at the position of the control-slide the opens out a further fluid-outlet duct, the passage of which can be released when the machine is prepared for a start, whilst the openings of the fluid-outlet ducts are disposed so that they are free when the relevant piston occupies its starting position.
  • the hot-gas reciprocating machine is characterized in that the interconnected pistons of each of the pump units are furthermore connected with a further piston-like body located in line with their centre line, said body being adapted to reciprocate in a closed cylinder, whilst in the space above said piston-like body there opens a fluid-inlet duct, by which compressed fluid can be inserted into said space,
  • a further advantageous hot-gas reciprocating machine embodying the invention is characterized in that the machine comprises a pump device,.the pump duct of which can be caused to communicate by way of a controlmember with the various fluid-supply ducts of the machine, whilst there is furthermore provided a fluid con tainer, with which can communicate fluid-outlet ducts of the machine via a control-member. r n
  • FIGS. 1, 2 and 3 show partly in a sectional view and in three orthognal elevations a hot-gas reciprocating machine formed by a cold gas refrigerator.
  • FIG. 4 shows diagrammatically a gold-gas refrigerator with the associated control-device, whilst for clarity only one pair of cooling units is shown.
  • FIGS. 5 and 6 show diagrammatically two different views of agold-gas refrigerator, in which the pump units are arranged parallel to each other.
  • reference numeral 1 designates a crank casing, on which the pump units I and II are arranged in a V.
  • the machine comprises furthermore two pairs of cooling units A A and B B which communicate by ducts with the pump units.
  • the pump units I and II comprise each a housing constructed from two portions 2 and 3.
  • the partitions 4 and 5 form a closed space, which is subdivided by the partition 6, the cylinder 7 and the movable piston 8 into two spaces 9 and 10.
  • a closed space .is' formed, which is subdivided by the partition 11, the cylinder 12 and the piston 13, movable in the former, into the. separated spaces 14 and 15.
  • With the portion 3 communicates a further cylindrical portion 16, in which the end 77 of the pump rod 17 with the pistons 8 and 13 is adapted to reciprocate;
  • In the cylindrical portion 16 opens out a supply .duct 1%.
  • The. pump rod 17 is connected via a crank driving mechanism housed in the crank casing 1 with the crank shaft 19, which is coupled in turn with an engine 19'.
  • the cooling units A A and B B comprise each a cylinder 29, in which the expansion piston 21 is adapted to reciprocate.
  • Each cooling unit comprises furthermore a freezer 22, a regcnerator 23, a cooler 24 and a cylinder 25, in which the compression piston 26 is adapted to re-' ciprocate; End plates 27, 28 are interconnected by rods 2?. These rods 29 are so constructed as to absorb the forces on the cooling units.
  • the space 30, on the side of the expansion piston 21 remote from the working space, is filled with fluid and the space 31 on the side of the compression piston 25 remote from the working space is also filled with fluid.
  • the space 31 of each of the cooling units A and A communicates via duct 32 with the space 14- of the pump unit I, whereas the space 31 of .the cooling unit A communicates via a duct 33 with the space 15 of the pump unit I.
  • the space 30 of the cooling unit A communicates by way of a duct 34 with the space 10 of the pump unit II, whereas the space 30 of the cooling'unit Ag communicates via a duct 35 with the space 9 of the pump unit II. It will appear thcrefromthat, whereasthe ducts 32 and 33 are parallel to each other, the ducts 34 and 35.
  • V r V r
  • the relevant, fluid-filled spaces of the pair of cooling units B communicate in a similar manner with the spaces of the pump units, the arrangement of said cooling units. being, however, such that the fluid-filled spaces 31 are: orientated towards the. pumpunit II, whereas the fluidfilled spaces 30 are orientated towards the pump unit I.
  • the space 31 of the cooling unit B communicates via a duct 36 with the space 14 of the pump unit IIandthe,
  • space 31 of the cooling unit B communicates via a duct 37 with the space of the pump unit II.
  • the ducts 36 and 37 are again parallel to each other.
  • the space 34) of the cooling unit B communicates via a duct 3% with the space 9 of the pump unit I and the space 30 of the cooling unit B communicates via a duct 39 with the space 10 of the pump unit I. From the drawing it will be seen that the ducts 38 and 39 are also parallel to each other.
  • the cooling units A A B B are furthermore provided with a supply duct 40 and an outlet duct 41 for cooling water. It will be apparent that, if desired, two or more coolers may be interconnected, so that they are traversed in series by the coolant.
  • each cooling unit is all provided with an inlet 43 and an outlet 44 for the medium to be cooled. Also the freezers may, if desired, be interconnected so that they are traversed in series by the medium to be cooled.
  • the regenerator 23, the freezer 22 and adjacent parts of each cooling unit are surrounded by insulating material 46.
  • the cooling units are furthermore provided, for reinforcing the structure, with plates 47, accommodating the cooling units pairwise and being secured to supports 48, which are connected with the crank casing l.
  • the compression pistons 26 and the expansion pistons 21 of all cooling units are provided with a piston rod 49.
  • Each of these piston rods 49 supports a plunger-shaped control-slide 50, which is movable in a cylindrical portion 51, which is in open communication at one end with the connecting duct concerned between the fluid spaces in the cooling units and the fluid spaces in the pump units.
  • the other side of the cylindrical portion 51 communicates through a duct 52 also freely with the said connecting duct.
  • With the cylindrical portion 51 communicates a fluidoutlet duct 53.
  • the opening of the fluid-outlet duct 53 in the portion 51 is disposed so that it can be released by thecontrol-slide 59, when the relevant piston connected with said slide occupies its deepest position in the cooling unit.
  • cylindrical portion 51 communicates furthermore a fluid-inlet duct 54, the opening of which in the cylindrical portion 51 is disposed so that it is released when the piston concerned passes beyond its outermost, prescribed position.
  • cylindrical portion 51 communicates a further fluid-supply duct 55 and a further fluid-outlet duct 56, the passages of which are blocked in the operational condition of the machine.
  • FIG. 4 in which the hot-gas reciprocating machine of FIGS. 1, 2 and 3 is shown diagrammatically. Corresponding structural parts are designated in FIG. 4 by the same references as in FIGS. 1, 2 and 3. It should furthermore be noted that for the sake of clarity only one pair of cooling units i.e. A and A is shown in FIG. 4, the various pistons being shown in their positions occupied when the machine is started.
  • the control-member not shown in FIGS. 1, 2 and 3 comprises, as is shown in FIG. 4, a control-slide S7, by means of which a number of ports can be closed or released.
  • the control-slide 57 is connected by a rod 58 with a ring 59, in which an eccentric disc 60, seated on a shaft 61, is adapted to turn.
  • the shaft 61 is provided with a hand wheel 62.
  • the machine comprises furthermore an oil pump 63, the pump duct of which opens out in a buffer space 64.
  • the oil suction duct 65 opens out in the reservoir 66.
  • an automatic control-valve 67 the pressure in the buffer space is kept constant.
  • the machine operates as follows:
  • the hand wheel 62 moves via the eccentric disc 60 the control-slide 57 into a position in which the port 68 is open.
  • the control-slide 57 is arranged so that, when the port 68 is open, also the ports 69 and 70 are free. In this position of the slide 57 also the ports 71 and 72 are free.
  • oil can flow out of the buffer space 64 via the duct 73 through the port 71 towards the ports 69 and trate into the cooling units.
  • the duct 76 opens out in the reservoir 66.
  • the pistons 21 and 26 are prevented from penetrating further into the cooling units. They then occupy their starting positions.
  • oil can flow out of the bulfer space 64 through the duct 73 and the ports 72 and 68 into the duct 18. Consequently, compressed oil is introduced into the space 16 of the pump units.
  • the portion 77 of the pump rod 17 is subjected to pressure in the direction of the crank shaft, so that the pistons of the pump units are compelled to occupy the positions shown in FIG. 4.
  • valve 7 8 is opened during the pressure increase of the oil, so that oil flows out of the space 16 via the duct 79 towards the reservoir 66. The machine is then ready for starting.
  • the hand wheel 62 is actuated so that the control-slide 57 closes the ports 68, 69, 76, 71, 72 and 75. Then the motor driving the crank shaft 19 is caused to rotate.
  • the pump pistons 8 and 13 are also set moving so that the fluid columns cause the pistons 21 and 26 of the cooling units to move.
  • the working spaces of the two cooling units of each pair communicate via a connecting duct 89, including a variable valve 81, freely with each other, so that the machine starts without load.
  • the control-valve 81 in the connecting duct is closed, so that the machine starts producing cold according to the Sterling cycle.
  • the fluid leaking out of the system results in that the pistons 21 and 26 are urged excessively outwardly by the gas pressure in the working space. This is avoided by providing in the portion 51 accommodating the control-slide 5% a port 83, which is released, when the relevant piston passes beyond its extreme, prescribed posi tion.
  • the port 83 communicates with the fluid supply duct 54, so that fluid can flow'from the fluid pump into the, space 31 or 36), when the control-slide 5i) releases the port 83.
  • the stroke of the piston concerned is limited on the outer side and the fluid leaking away during the stroke is recovered.
  • control members 85 Each of these control-memhers comprises a cylinder 86, in which a plunger 87 is adapted to reciprocate.
  • the space 88 on one side of the plunger 87 communicates via a duct 89 with the space 90 beneath the rolling diaphragm 84-.
  • the fluidfilled space 31, on the side of the piston 26, remote from the working space, communicates via a duct l with cylinder 86.
  • the ducts 89 and 91 include helices 92, which ensure that rapid pressure variations in the spaces 96 and 31 are damped, so that they do not occur in the cylinder 86.
  • the piston 26 travels with a fair amount of clearance V in its cylinder so that, since the pressure in the space 31 exceeds the pressure in the space 90, fluid flows towards the space 90. If no further steps were taken, the pressures in the spaces 31 and 90 would soon become equal to each other.
  • the fluid fed to the space 99 now flows via the duct 89 to the space 88 in the cylinder 86.
  • the helix 94 is chosen sothat with the correct pressure difference the plunger '87 partly releases the opening of the duct 93.
  • the fluid fed to the space 88 can flow via the duct 93 out of said space.
  • plunger 87 re-occupies its initial position and the fluid is again permitted to flow.
  • FIG. 4 shows for the sake of clarity only one controlmechanism 85; however, in practice, all rolling diaphragms are provided with such a control-mechanism.
  • FIGS. 5 and 6 show diagrammatically a hot-gas reciprocating machine, formed by a cold-gas refrigerator, in two elevations; the pump units I and II are arranged parallel to each other on a crank casing 101.
  • the pistons of each of these pump units are connected by means of piston rods 117, universal joints 118, connecting rods 119 with cranks 121 and 120 respectively of the crank shaft 122 accommodated in the crank casing 101.
  • The. cranks 120 and 121 are turned through 90 relatively to each other in order to obtain the desired phase difference between the pistons moving in the cooling units.
  • the machine comprises again two pairs of cooling units A A and B B Said cooling units and the pump units I and II maybe constructed in the same manner as the corresponding units described with reference to FIGS. 1, 2 and 3.
  • cooling units A and A are located in. a plane located in front of the plane of the pump units I and II and parallel thereto, whereas the cooling units B and B are disposed in a plane located behind the plane of the pump units.
  • the centre lines of the cooling units A and A cross the centre lines of the cooling units B and B
  • the cooling units A and A communicate on one side and on the other side via ducts 134 and 135 respectively 8 with the pump unit II.
  • the ducts 132,”133'and 134, 135 extend pairwise parallel to each other.
  • the cooling units B and B communicate on one side via ducts 136 and 137 respectively with the pump unit II and on the other side via ducts 138 and 139 respectively with the pump unit I, whereas the ducts 136 and 137 are substantially parallel to each other and the ducts' 138 and 139 are arranged crosswise. Thus the correct phase difference between the pistons moving in the various'cooling units is obtained. i
  • the advantage of the machine illustrated in FIGS. 5 and 6 is that the length thereof, i.e. the distance between the centre lines of the pump units'is small as compared with other arrangements of pump units and cooling units. This may be usefulin places where space is a problemi Although the drawing shows only two pump units parallel to. each other, it will be obvious that the machine may be extended with further pump units without any difliculty.
  • a hot-gas reciprocating apparatus comprising at least two pairs of units in each of which a working medium performs a thermodynamic cycle, each unit having a compression space of variable volume and an expansion space of variable volume, means connecting'said compression space with said expansion space, said connect- 1ng means including a cooler, regenerator and a heat exchanger, said spaces having relatively differe'nt mean temperatures, said Working medium adapted to flow alternately in said spaces and through said cooler, regenerator and heat exchanger, a cylinder housing piston-like elements, said piston-like elements being adapted to move with a relative phase difference in order to vary the volumes of said compression and expansionspaces, a driving gear, said piston-like elements being coupled to said driving gear, at least two pump units, each of said pump units comprising two closed, fluid-filled cylinders, a pair of double-acting pistons being a compression piston and an expansion piston adapted to move in said fluid-filled cylinders whereas in the first pair of unitseach of the spaces positioned on the side of the associated expansion piston remote from said
  • thermodynamic cycle is performed in one pair of units in which the thermodynamic cycle is performed so that the spaces, on the side of compression pistons remote from said compression space, are orientated towards the first pump unit communicating with said spaces, while the spaces, on the side of the expansion pistons remote from said expansion space, are orientated towards the second pump unit communicating with said spaces and in that the other pair of units in which the thermo-dynamic cycle is performed is arranged between the two pump units so that the spaces, on the side of the compression pistons remote from said compression space, are orientated towards the second pump unit communicating with said spaces, whereas the spaces, on the side of the expansion pistons remote from said expansion space, are orientated towards the first pump unit communicating with said spaces.
  • a hot-gas reciprocating apparatus comprising at least two pairs of units in which a working medium performs a thermo-dynamic cycle, each unit having a compression space of variable v'olume and an expansion space of variable volume, means connecting said compression space with said expansion space, said connecting means including a cooler, regenerator and a heat exchanger, said spaces having relatively different mean temperatures, said working medium adapted to flow alternately in said spaces and through said cooler, regenerator and heat exchanger, a cylinder housing piston-like elements, said piston-like elements being adapted to move with a relative phase difference in order to vary the volumes of said compression and expansion spaces, a driving gear, said piston-like elements being coupled to said driving gear, at least two pump units arranged parallel to each other, each of said pump units comprising two closed, fluidfilled cylinders, a pair of double-acting pistons being a compression piston and an expansion piston adapted to move in said fluid-filled cylinders whereas in the first pair of units each of the spaces positioned on the side of the associated expansion piston remote from said expansion space
  • a hot-gas reciprocating apparatus comprising at least two pairs of units in which a working medium performs a thermodynamic cycle, each uni-t having a compression space of variable volume and an expansion space of variable volume, means connecting said compression space with said expansion space, said connecting means including a cooler, regenerator and a heat exchanger, said spaces having relatively different mean temperatures, said working medium adapted to flow alternately in said spaces and through said cooler, regenerator and heat exchanger, a cylinder housing piston-like elements, said piston-like elements being adapted to move with a relative phase difference in order to vary the volumes of said compression and expansion spaces, a driving gear, said pistonlike elements being coupled to said driving gear, at least two pump units arranged parallel to each other, each of said pump units comprising two closed, fluid-filled cylinders, a pair of double-acting pistons being a compression piston and an expansion piston adapted to move in said fluid-filled cylinders whereas in the first pair of units each of the spaces positioned on the side of the associated expansion piston remote from said expansion space communicates with
  • each of the pistons adapted to reciprocate in the cylinder of each unit in which the thermodynamic cycle is performed further comprises another cylindrical part constituting said control-slide which is adapted to move in a further cylindrical part of each of the cylinders is in which said piston-like elements are moveable and in that the apparatus comprises at least one duct interconnecting the two spaces on either side of the control-slide and in that the inlet duct and the outlet duct are in contact with the wall of said other cylindrical part.
  • a hot-gas reciprocating apparatus as claimed in claim 5 further comprising a fluid supply duct and wherein each of the fluid-filled spaces in each unit in which the thermo-dynamic cycle is performed communicates with said fluid supply duct, the passage of which is blocked in operation of the apparatus, whereas at the location of the control-slide a further fluid outlet duct opens out, the passage of which is also blocked in the operation of the apparatus and in that the passages of said ducts can be released when the apparatus is prepared for starting and in that the openings of the outlet ducts are arranged so that they are uncovered when the relevant piston occupies its starting position.
  • a hot-gas reciprocating apparatus as claimed in claim 7 further comprising a closed cylinder, a further piston-like body adapted to move therein, and wherein 1 1 the interconnected pistons of each of the pump units are furthermore connected With said piston-like body located substantially in their center lines, and in that the space above said piston-like body communicates With said fluid supply duct through which compressed fluid can be introduced into said space whereby the pistons of the pump units are driven in their starting positions.
  • a hot-gas reciprocating apparatus as claimed in claim l-fu-rther comprising a control member, a plurality of fluid supply ducts and outlet ducts, a pump device having a pump ductpwhich can be caused to communicate through said control memlver with said fluid supply ducts of the apparatus, and in that there is furthermore pr0- vided a fluid reservoir, with which the fluid outlet ducts of said apparatus can be caused to communicate through said control member.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
US320982A 1962-11-26 1963-11-04 Hot-gas reciprocating machine Expired - Lifetime US3200582A (en)

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NL285957 1962-11-26

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US (1) US3200582A (de)
AT (1) AT241912B (de)
BE (1) BE640436A (de)
CH (1) CH424828A (de)
DE (1) DE1260494B (de)
DK (1) DK122474C (de)
ES (1) ES293813A1 (de)
FR (1) FR1383207A (de)
GB (1) GB1064733A (de)
NL (1) NL285957A (de)
OA (1) OA00905A (de)
SE (1) SE305222B (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0119846A2 (de) * 1983-03-21 1984-09-26 Texas Instruments Incorporated Kühler mit pneumatisch gesteuertem getrenntem Zyklus
US4712378A (en) * 1985-03-29 1987-12-15 Aisin Seiki Kabushiki Kaisha Driving apparatus for stirling cycle engine
US9234480B2 (en) 2012-07-04 2016-01-12 Kairama Inc. Isothermal machines, systems and methods

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FR2450342A1 (fr) * 1979-02-28 1980-09-26 Girodin Marius Moteur a dilatation

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US2484392A (en) * 1945-08-30 1949-10-11 Hartford Nat Bank & Trust Co Hot-air engine actuated refrigerating apparatus
US2567637A (en) * 1947-01-31 1951-09-11 Hartford Nat Bank & Trust Co Hot gas piston apparatus with flexible crank coupling
US2590519A (en) * 1948-01-21 1952-03-25 Hartford Nat Bank & Trust Co Hot-gas engine or refrigerator
US2616248A (en) * 1949-01-27 1952-11-04 Hartford Nat Bank & Trust Co Hot-gas reciprocating engine
US2616245A (en) * 1948-10-12 1952-11-04 Hartford Nat Bank & Trust Co Double-acting hot gas engine having at least three closed thermodynamic cycles
US2657552A (en) * 1950-06-10 1953-11-03 Hartford Nat Bank & Trust Co Hot gas engine refrigerator
US2657528A (en) * 1948-12-24 1953-11-03 Hartford Nat Bank & Trust Co Hot gas engine enclosing two thermodynamic cycles
US2664699A (en) * 1950-11-24 1954-01-05 Hartford Nat Bank & Trust Co Multicylinder double-acting hotgas reciprocating engine
US2771751A (en) * 1953-07-24 1956-11-27 Hartford Nat Bank & Trust Co Gas-fractionating installation
US3117414A (en) * 1961-07-14 1964-01-14 Wisconsin Alumni Res Found Thermodynamic reciprocating apparatus

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FR1128275A (fr) * 1955-07-28 1957-01-03 Compresseur hermétique oléo-pneumatique

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US2484392A (en) * 1945-08-30 1949-10-11 Hartford Nat Bank & Trust Co Hot-air engine actuated refrigerating apparatus
US2567637A (en) * 1947-01-31 1951-09-11 Hartford Nat Bank & Trust Co Hot gas piston apparatus with flexible crank coupling
US2590519A (en) * 1948-01-21 1952-03-25 Hartford Nat Bank & Trust Co Hot-gas engine or refrigerator
US2616245A (en) * 1948-10-12 1952-11-04 Hartford Nat Bank & Trust Co Double-acting hot gas engine having at least three closed thermodynamic cycles
US2657528A (en) * 1948-12-24 1953-11-03 Hartford Nat Bank & Trust Co Hot gas engine enclosing two thermodynamic cycles
US2616248A (en) * 1949-01-27 1952-11-04 Hartford Nat Bank & Trust Co Hot-gas reciprocating engine
US2657552A (en) * 1950-06-10 1953-11-03 Hartford Nat Bank & Trust Co Hot gas engine refrigerator
US2664699A (en) * 1950-11-24 1954-01-05 Hartford Nat Bank & Trust Co Multicylinder double-acting hotgas reciprocating engine
US2771751A (en) * 1953-07-24 1956-11-27 Hartford Nat Bank & Trust Co Gas-fractionating installation
US3117414A (en) * 1961-07-14 1964-01-14 Wisconsin Alumni Res Found Thermodynamic reciprocating apparatus

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0119846A2 (de) * 1983-03-21 1984-09-26 Texas Instruments Incorporated Kühler mit pneumatisch gesteuertem getrenntem Zyklus
EP0119846A3 (en) * 1983-03-21 1985-11-06 Texas Instruments Incorporated Pneumatically controlled split cycle cooler
US4712378A (en) * 1985-03-29 1987-12-15 Aisin Seiki Kabushiki Kaisha Driving apparatus for stirling cycle engine
US9234480B2 (en) 2012-07-04 2016-01-12 Kairama Inc. Isothermal machines, systems and methods

Also Published As

Publication number Publication date
DK122474B (de) 1972-03-06
DE1260494B (de) 1968-02-08
ES293813A1 (es) 1964-01-16
AT241912B (de) 1965-08-25
CH424828A (de) 1966-11-30
SE305222B (de) 1968-10-21
GB1064733A (en) 1967-04-05
NL285957A (de)
FR1383207A (fr) 1964-12-24
OA00905A (fr) 1968-03-22
DK122474C (da) 1972-07-31
BE640436A (de) 1964-05-26

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