US3839858A - Reciprocating machine - Google Patents

Reciprocating machine Download PDF

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Publication number
US3839858A
US3839858A US00319846A US31984672A US3839858A US 3839858 A US3839858 A US 3839858A US 00319846 A US00319846 A US 00319846A US 31984672 A US31984672 A US 31984672A US 3839858 A US3839858 A US 3839858A
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Prior art keywords
fluid
chamber
compressor
pipe connection
valve
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Expired - Lifetime
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US00319846A
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English (en)
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Avermaete G Van
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AVERMAETE G VAN
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AVERMAETE G VAN
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Priority claimed from BE777548A external-priority patent/BE777548A/xx
Priority claimed from BE785549A external-priority patent/BE785549R/xx
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    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • 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
    • F02G2275/00—Controls
    • F02G2275/40—Controls for starting
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2102—Adjustable

Definitions

  • ABSTRACT This invention relates to a combustion reciprocating machine of the kind in which combustion takes place outside of the chamber in which the pressurized fluid ,is expanded, on the one hand, to provide an efficient and fast operating starting device, which cannot be implemented in a satisfactory manner, particularly as regards the starting time, in this type of reciprocating machine by a battery and an electric starter such as tion takes place an adequate flow of pressurised fluid at a satisfactory pressure, whatever may be the working conditions of the reciprocating machine and this in such a manner that the latter shall have a satisfactory operating flexibility and be able to provide immediately a reasonable output, no matter what the working condition may be.
  • the present invention has for its object a reciprocating machine comprising at least one chamber wherein is fitted a piston to compress a fluid, at least one chamber wherein is provided a piston driven by the expansion of the said fluid, these two pistons being mounted on one and the same shaft fitted in order to provide an alternating motion to each of the pistons in their respective chamber, an enclosure, provided inbetween the two chambers and connected to the latter by connection pipes, in which the compressed fluid is'delivered and from whichis withdrawn the fluid to be ex panded, means for raising the temperature of the fluid in the enclosure and means for authorizing the admission and the exhaust of the fluid in each one of the chambers.
  • the invention aims essentially in a combustion motor of the kind in which combustion takes place outside of the chamber in which the pressurized fluid is expanded, on the one hand, to provide an efficient and fast.
  • operating starting device which cannot be implemented in a satisfactory manner, particularly as regards the starting time, in this type of reciprocating machine by a battery and an electric starter such as those used for running in conventional internal combustion engines and, on the other hand, to provide a device to pressurise the fluid and a regulator permitting to ensure in the said enclosure wherein combustion takes place an adequate flow of pressurised fluid at a satisfactory pressure, whatever may be the working conditions of the reciprocating machine and this in such a manner that the latter shall have a satisfactory operating flexibility and be able to provide immediately a reasonable output, no matter what the working condition may be.
  • valve coupled with the electric starter of the reciprocating machine, so that the valve shall be open for a set time during the running in of the motor and shall allow fluid to flow from the reserve to the connection pipe.
  • the means assuring the communication of the reserve of compressed fluid with the pipe connection connecting the first stage of the compressor to the second stage of the latter comprise a distributor wherein are mounted differential pistons subject to the pressure ruling in the pipe connection connecting the first stage of the compressor to the second stage thereof and to the pressure ruling in the pipe connection connecting the second compressor stage to the said enclosure, this distributor being fitted to admit or cut off the flow of the fluid originating from the said fluid reserve 7 to the pipe connection connecting the first to the secfirst and second compressor stages, the latter means tion, the means connecting the reserve of pressurised fluid tothe pipe connection connecting the second 3 stage of the compressor'to the said enclosure comprise a normally closed, electromagnetically controlled, uniond compressor stage when the pressures ruling in the said two pipe connections vary one with reference to the other.
  • the distributor is connected to an adjustable sequential operation valve mounted downstream of the distributor, with reference to the pipe connection connecting the second compressor stage to the said enclosure in order to prevent the differential pistons from moving continuously inside the distributor in order to admit and stop the flow of fluid from the reserve into the pipe connection connecting the twocompressor stages when the pressures ruling inside the said two pipe connections are close to their state of equilibrium determined by the characteristics of the compressor, such sequential operation valve being inserted between the distributor chamber connected to the pipe connection which connects the second compressor stage to the said enclosure and to such pipe connection.
  • FIG. 1 is a diagrammatic sectional view of a combustion reciprocating machine of the said kind provided with the starting, compression and regulating devices according to the invention.
  • FIG. 2 is a diagrammatic partial view illustrating a modified form of the regulating device shown in FIG. 1.
  • FIG. 3 is an elevational sectional view of the said distributor drawn to a larger scale than the FIG. 1.
  • FIG. 4 is a diagrammatic view similar to that of FIG. 1 partially broken away, showing a regulating device to be associated with the starting, compression and regulating devices illustrated in FIG. 1 when it is foreseen to heat the fluid in the pipe connection connecting the second compressor stage to the said enclosure, by the expanded fluid escaping from the chamber in which expansion of the fluid takes place.
  • FIG. 5 is a partly broken elevational view of a device allowing to simultaneously vary the admission time and the exhaust time in the motor chamber where the fluid is expanded.
  • FIG.,6 is a detailed viewalong line VI-VI of FIG. 5,
  • FIGS. 7 and 8 are cross-sectional views along lines VIIVII and VIIIVIII of FIG. 5.
  • the reciprocating machine comprises two chambers l and 2 in each of which is fltted a piston provided with an alternating motion.
  • Thetwo pistons 3 and 4 are mounted on one and the same shaft 5, the piston 3 being used to compress a fluid, while the piston 4 is driven by the expansion of such fluid, an enclosure or combustion chamber 6 being provided between the two chambers 1 and 2 to which it is connected by pipe connections 7 and 8 so that the pressurized fluid shall. flow into the chamber 6 and that the fluid to be expanded shall be withdrawn from the latter, means 9 being provided to raise the temperature of the fluid in the chamber 6 as well as means 10 and 11 to authorise the ad mission and the escape respectively of the fluid for each of the chambers.
  • the piston 3 being double acting in order to provide, with the chamber 1, a two stage compressor, a pipe connection 12 being provided to interconnect, through a cooler 13, the two compressor stages, while the second compressor stage is connected to the combustion chamber 6 by the pipe connection 7, the reciprocating machine comprising a reserve 14 of fluid compressed to a higher pressure than that which may be reached during the running of the reciprocating machine by the fluid inside the pipe 7, means 15 to connect such reserve 14 and the pipe 7 connecting the second compressor stage to the chamber 6, means 16 to connect the fluid reserve l4 and the pipe 12 connecting the first to the second compressor stage as well as means 17 communicating simultaneously with the pipe connections 7 and 12 connecting the second compressor stage to the chamber 6 and the first to thesecond compressor stage respectively, such means 17 being controlled by the pressurised fluid inside such pipe connections 7 and 12in order to
  • the means 15 which are fitted to connect the fluid reserve 14 and the pipe 7 connecting the second compressor stage to the combustion chamber 6 have for their object to permit, on starting the reciprocating matime on running in the reciprocating machine and allow the flow of pressurised fluid from the reserve 14 to the combustion chamber 6 via the pipe connection 7.
  • a controlled unidirectional valve 18, coupled toanpelectric device, notshown, for starting up the reciprocating machine so that the valve 18 shall remain open for a preset means 15 also comprise a pressure reducer 19 which reduces the pressure of the fluid to a pressure practically equal to that which it is possible to attain during the running of the reciprocating machine by the fluid contained in the pipe connection 7 connecting the second compressor stage to the combustion chamber 6, a gauge 20 being advantageously provided to permit checking the pressure of the fluid in the reserve 14 as well as a stop valve 21 allowing to cut off the said reserve 14 from the reciprocating machine, particularly in the case of an extended stoppage of the latter, in order to prevent any leakage of pressurised fluid contained in the reserve 14 through the pipe connections and the reciprocating machine.
  • the means 16 which, on account of the action of a distributor l7 byvirtue of the pressurised fluid inside the pipe connections 7 and 12, connect the reserve l4 and the pipe connection 12 connecting the two compressor stages and are also used to assure a supply of pressurised fluid originating from the reserve 14 in the circuit between the first and second compressor stage in order to achieve a practically constant equilibrium between the pressure of the fluid inside the pipe connection 12 and the pressure of the fluid inside the pipe 7 so that the same flow of fluid shall be available in the chamber 6 at an adequate pressure on changes of the running speed of the reciprocating machine when variations of its working conditions occur, as such equilibrium is only achieved by the two stage compressor on its own after a certain lapse of time, which would of course impair the flexibility of the said reciprocating machine.
  • These means 16 connecting the reserve 14 with the pipe connection 12 comprise a unidirectional valve 22 controlled through a microvalve 23 by the distributor 17, the differential pistons 24 and 24' of which are subjected to the pressure ruling in the pipe 12 and the pipe 7 through the ducts 17' and 25.
  • the unidirectional valve 22 is connected to the reserve 14, downstream of the closing valve 21 at a location between the valve 21 and the valve 18. This valve 22 is fitted to permit the flow of the fluid originating from the reserve to the pipe connection 12 when the pressure of the fluid rises in the pipe connections 7 and 17 and when the equilibrium between'the pressures ruling in the pipe connections 7 and 12, determined by the compressor characteristics, is broken.
  • microvalve 23 The purpose of the microvalve 23 is to reduce the force needed at the distributor 17 to control valve 22 as it is, on the one hand, connected to the pipe connection 26 connecting such valve 22 to the reserve 14, a pressure reducing valve 27 being provided on this branch and, on the other hand, connected to the valve 22, the pistons of which are fitted in such a manner that the low pressure fluid, acting on the opening of the microvalve 23, as controlled by the distributor 17, may overcome the pressure of the reserve fluid and ensure the opening of the valve 22 and thus permit the fluid to pass from the reserve 14 to the pipe connection 12.
  • the distributor 17 is associated with an adjustable sequential valve 28 mounted inbetween the pipe connection 7 and the chamber of the distributor 17, described below. communicating with such pipe connection 7.
  • a safety valve 29 is advantageously provided between the pipe connection 12 and the distributor l7 and the valve 22, the said valve 29 being fitted to close when a pressure higher than a preset pressure practically equal to the a ized fluid originating from thejreserve 14 to enter the pipe connection Hand to raise the pressure in the latter to a value which might prove dangerous for the compressor.
  • the distributor 17 comprises a cylinder 30 wherein are assembled the said differential pistons 24 and 24 able to move one with reference to the other, the piston 24 being subjected, through the pipe connection 25 to the action of the fluid within the pipe connection 12, while the piston 24 is subjected to the action of the fluid within the pipe connection 7 through the pipe connection 17'.
  • the piston 24 is provided, on he one hand, with a peripherical recess providing a leak-proof chamber in communication, through an opening 31 wit the pipe connections 17 and 7 and, on the other hand, with an axial recess 32 communicating with the chamber 30 and wherein is housed an element 33 of the piston 24 having a cross-section corresponding to that of the recess 32 and provided with tightness members 34, the piston 24' being provided opposite to the element 33 with acentral stem 35 providing the control stem of the distributor for operating the microvalve 23.
  • the two pistons 24 and 24' are further fitted in order to determine in the cylinder 30 four chambers isolated in a leak-proof manner from one another and laid out in the following manner: a first chamber 36 into which opens the pipe connection 25 communicating with the pipe connection 12, a second chamber 37 determined by the pistons 24 and 24 and vented to atmosphere through an opening 38 of the cylinder, a third chamber 30 being provided by the said peripherical recess and lastly a fourth chamber 39 vented to atmosphere through an opening 40 provided in the cylinder 30.
  • a spring 41 is provided in the chamber 39 in order to cooperate with the piston 24 while studs 42 are provided in the portion 43 of the piston 24. These studs 42 are of decreasing lengths and their axes are parallel to those of the pistons 24 and 24-.
  • Each of these studs 42 comprises a peripherical stop 45 positioned inside the chamber 30 and limiting their movement in the direction of the arrow 46 and extend across the chamber 37 so as to be able to rest on piston 24'.
  • Spring 41 is selected in such a manner that it forces piston 24 against its stop 47 for the minimum set pressure allowed in the chamber36 and that its maximum compression shall correspond to the maximum determined pressure allowed in such chamber 36, the stroke of the spring 41 being substantially equal to the differenc'e in length be-' stop 48 being also provided to limit the stroke of the piston 24.
  • the strain of the spring 41 is adjustable by means of a control screw 50 cooperating with the cylinder 30.
  • a spring 51 is also provided to cooperate with the piston 24', the strain of this spring being likewise adjustable by means of a control screw 52.
  • Valve 22 might also be controlled-as shown in FIG. 2 immediately from the distributor 17 by means of an electromagnet 53.
  • a pushrod 54 might also be provided supported on component 55 of the piston 24 and controlled by an aneroid case 56, such push rod being pivotaly mounted in 57 so as to raise its pressure, because of the action of the aneroid case on component 55 of the piston 24' when the atmospheric pressure drops.
  • the reserve 14 may be recharged with pressurised fluid
  • pipe connection 7 connecting the second compressor stage with the chamber 6 is connected by a duct 58 to the duct 59 connecting the reserve 14 to the valve 18, upstream of the latter with reference to the said reserve so as to refurnish the latter.
  • a valve 60 is provided in the duct 58 and is normally closed so as to prevent, on starting the reciprocating machine, and with a low pressure of the fluid in the reserve, that part of the fluid compressed by the compressor shall be used to charge up the reserve 14 and thus endanger the starting of the reciprocating machine, the same applying during changes inthe speed of the latter when, in order to retain all the, output of the reciprocating machine, the
  • a nonreturn check valve 61 is advantageously provided between the valve 60 and the reserve l4 and is fitted so that, even when such valve 60 is in the open position, the pressurised fluid may not enter such reserve l4 unless the pressure ruling inside the latter is less than that inside the pipe connection 7, and this always in order that a maximum pressure shall be available in the pipe connection 7 so that the reciprocating machine shall retain its full power during changes in speed or working conditions.
  • a throttle 62 may also be provided in the pipe connection 58 in order to throttle the flow of the pressurised fluid to the reserve 14 when the valve 60 and the non-return check valve 61 permit such flow.
  • a heat exchanger 63 may be mounted in the pipe connection 7 connecting the second compressor stage to the chamber 6 in order to preheat the fluid flowing from the said compressor to the chamber 6, such heat exchanger 63 being connected to the exhaust of the chamber 2 wherein the expansion of the fluid takes place.
  • a device to balance the pressure ruling in .the pipe connection 7 and that ruling in the chamber 6 is particularly interesting, because in the course of accelerations of the reciprocating machine,
  • the pressure rises in the chamber 6 and the compressor is obliged to raise sharply the pressure in such pipe 7 in order to keep the reciprocating machine running, which is difficult because of the heatexchanger 63 and ing the second compressor stage to the chamber 6, upstream of the latter, and having for its object to direct the pressurised fluid originating from the compressor to the means 10 allowing the admission of the fluid to the chamber 2 in order to cool such means 10 swept by the fluid at high temperature originating from the chamber 6.
  • a non-return valve 80 and a throttle 81 are provided in this by-pass 79 in order to restrict the flow of fluid in this by-pass to the means 10 so that in the pipe connection 7, a maximum quantity of fluid will be available to supply the chamber 6 on variations of the speed of the reciprocating machine.
  • the pipe connection 7 also comprises a non-return valve 82 mounted in the pipe connection 12 in order to prevent any back-flow of of the important volume of fluid contained in the pipe run of the latter.
  • this balancing device comprises a non-return valve 64 in order to prevent a back flow of the fluid contained in the chamber 6 towards the pipe connection 7, a cylinder 65 in which is fitted a piston 66, a valve 67, a duct 68 connecting the chamber 6 with the chambers 69 and 70 determined within the cylinder 65 and the valve 67 by the piston 66 and the plunger 71 of the valve and ducts 72, 72 and 72 connecting the pipe connection 7, be-
  • the pressurised fluid closes the non-return valve 64 and influences the plunger 71 of the valve 67'and the piston 66 compressing the fluid located in the chamber 73 of cylinder 65, in the duct 72 and the chamber 74 of the valve 67.
  • the latter which is normally closed, opens and allows the fluid compressed by the piston 66 to flow from the chamber 74 of the valve 67 to the pipe connection 7 through the duct 72", this assisting the compressor to raise the pressure in the pipe connection 7 on a sharp increase of pressure in the enclosure 6, a non-return valve 76 and a throttle 77 being advantageously provided in the duct 72' in order to allow pressurised fluid to enter chamber 73 of the cylinder 65 only when the pressure inside the latter is below the pressure ruling in the chamber 78 of valve 67.
  • the reciprocating machine according to the invention comprises advantageously, asshown in FIG. 1, a by-pass 79, provided in the pipe connection -7 connectfluid between the second and the first compressor stages.
  • the admission time of said fluid in motor chamber 2 can advantageously be varied by acting on admission valve 10.
  • the pressure in combustion chamber 6 and upstream said chamber is increased in order to reach a higher combustion pressure at idling and at partial working conditions, which results, on the one hand, in increasing the motor efflciency and, on the other hand, in limiting the intervention of the motor regulat ing device hereinbefore described.
  • said pressure increase in chamber 6 results in an efficiency lowering of the compressor, this lowering must not particularly be taken into account because said efficiency lowering will not substantially affect the above-mentioned pressure.
  • Said means 90 are formed (see portion of FIG. 5 on the right of broken line 91) by two earns 92 and 93 mounted on a shaft 94 rotated by the motor and controlling the admission valve through a moving equipment 95 of Caprotti type (FIG.
  • Said moving equipment 95 comprises a rocking lever 96 pivoting around a fixed shaft 97 and the ends of which each support a follower 98 or 99 cooperating with one of the earns 92 or 93, cam 92 being locked on shaft 94 while cam 93 is free rotating on the latter, a sliding means 100 being provided on shaft 94 to control the angular movement of cam 93 with respect to the cam 92.
  • Shaft 94 has a threaded portion 101 forming an endless screw with very elongated pitch, which cooperates with the sliding means 100 and, when the latter longitudinally moves in parallel to the axis of shaft 94, causes the rotation of cam 93 around the latter, by means of two rods 102 which are parallel to the axis of shaft 94 and are diametrically opposed, said rods being J fixed to cam 93 by means of their threaded end 103 and According to this invention, the exhaust time of the fluid of motor chamber 2 can also be varied by acting on exhaust valve 11.
  • either the control device of the exhaust valve is alleviated when the back-pressure in chamber 2 is lower than the pressure in combustion chamber 6, or the pinging is prevented which can exist in said device, particularly at the level of the rocker-arm when the back-pressure in chamber 2 is higher than the pressure in chamber 6.
  • means 107 are provided on the motor, which are intended to vary for a given speed of the motor the exhaust time in chamber 2 in terms of the resisting torque. Said means 107 are formed (see portion of FIG.
  • the admission time and the exhaust time in chamber 2 can be caused to si ⁇ multaneously vary for a given rotation speed of the motor, in terms of the resisting torque, in order to combine previously mentioned advantages resulting on the one hand, from the variation of the admission time and on the other hand from the variation of the exhaust time.
  • cams 92 and 93 and earns 108 and 109, as well as all the elements cooperating therewith are mounted on a common shaft 94 having a threaded portion 101 with which the sliding means 100 and 111 cooperate, said means being simultaneously activated by rod systerns 105 and 112, from the motor accelerator, through control rod 106.
  • the rod systems 105 and 112 are arranged so that the said variations are such that when the admission time is increased, the exhaust time is reduced and vice versa. It results from a consideration of rod systems 105 and 112 (FIGS. 5 and 6) that the varia tion of exhaust time is lower than the variation of admission time. However, according to the motor characteristics, it can be quite well conceived to have either substantially equal viarations of admission and. exhaust times, or a variation of exhaust time which'is higher than that of admission'time.
  • the chamber 6 wherein the temperature increase of compressed fluid is obtained advantageously comprises a safety valve 113 which is regulated so as to open at a determined pressure, the latter being higher than the normal working pressure ofthe motor and lower than the breaking pressure of the combustion chamber 6.
  • Said valve 113 is either open to atmosphere or connected to the motor exhaust pipe.
  • the reciprocating machine may operate in a closed circuit and provide a so-called hot air.reciprocating machine.
  • the exhaust of the chamber 2 is connected to the entry of the first compressor stage','a cooler beingthen mounted between the said exhaustand the compressor.
  • Reciprocating machine comprising at least one chamber wherein is fitted a piston to compress a fluid, at least one chamber wherein is provided a piston driven by the expansion of the said fluid, these two pistons being mounted on one and the same shaft fitted in order to provide an alternating motion to each of the pistons in their respective chamber, an enclosure, provided in between the two chambers and connected to the latter by connection pipes, in which the compressed fluid is delivered and from which is withdrawn the fluid to be expanded, means for raising the temperature of the fluid in the enclosure and means for authorizing the admission andthe exhaust of the fluid in each one of the chambers, the reciprocating machine being characterised in that the piston used for pressurising the fluid in the said chamber is double acting in order to provide a two stage compressor, connection pipes being provided to interconnect the two comipressor stages as well as the second stage thereof to the said enclosure, the said reciprocating machine comprising a reserve of fluid compressed to a pressure exceeding that which may be reached during the running of the reciprocating machine by the fluid comprised in the pipe connection of the reciprocating machine
  • a reciprocating machine as claimed in claim 2 characterised in that a gauge and a stop valve are provided between the said reserve of pressurised fluid and the said unidirectional valve.
  • characterised-in thatjthe means assuring thecomrnunication of thereserve of compressed fluid with the pipe connection connecting the first stage of the compressor to the second stage of the latter comprise a distributor wherein are mounted differential pistons subject to the pressure ruling in the pipe connection connecting the first stage of the compressor to the second stage thereof and to the pressure ruling in the pipe connection connecting the second compressor stage to the said enclosure, this distributor being fitted to admit or cut off the flow of the fluid originating from the said fluid reserve to the pipe connection connecting the first to the second compressor stage when the pressures ruling in the said two pipe connections vary one with reference to the other.
  • the push rod being fitted to increase its pressure, because of the action of the aneroid case on the said piston by means of the said element when the atmospheric pressure drops.
  • the means connecting the reserve of pressurised fluid to the pipe connection connecting the first and second compressor stages comprise a unidirectional valve, controlled by the said distributor and connected to the reserve of pressurised fluid, downstream of the closing valve and upstream of the unidirectional valve and of the pipe connection connecting the first to the second stage of the compressor, such valve being fitted to permit the flow of the fluid originating from the reserve to the latter pipe connection when the equilibrium between the
  • a reciprocating machine as claimed in claim 1 characterised in that the pipe connection connecting the second compressor stage and the said enclosure communicates with a duct connecting the reserve of pressurised fluid to a electromagnetically controlled unidirectional valve, upstream of the latter with reference to the fluid reserve in order to refill the latter with pressurised fluid.
  • a reciprocating machine as claimed in claim 16 characterised in that a throttle is provided in the said duct in order to throttle the flow of the fluid to the reserve when the valve and the nonreturn check valve permit such flow.
  • a reciprocating machine as claimed in claim 1 characterised in that a heat exchanger is provided in the pipe connection connecting the compressor to the said enclosure, this heat exchanger, used for preheating 21.
  • the means permitting to balance the said pressures comprise a cylinder in which is fitted a double acting piston detemining two chambers in the said cylinder, a valve provided with a double acting plunger determining four chambers inside the valve along th axis of the plunger, a duct assuring the com munication of the said enclosure with a first chamber of the cylinder and a first terminal chamber of the valve, ducts being provided to assure the communication of the second end chamber of the valve with the duct connecting the second compressor stage to the enclosure upstream of the heat exchanger, the second cylinder chamber with the internal chamber of the valve nearest the second end chamber of the valve and the second chamber of cylinder with the internal chamber of the valve nearest the first end chamber of the said valve, such normally closed valve being fitted so as to open when the pressure rises sharply in the enclosure in order to connect the two internal chambers of the valve.
  • a reciprocating machine as claimed in claim 1 characterised in that it is mounted in a closed circuit so as to provide a so-called hot-air" reciprocating machine, the exhaust of the chamber wherein the fluid expands being connected to the entry of the first compressor stage, a cooler being mounted in the duct connecting the said exhaust to the compressor.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US00319846A 1971-12-30 1972-12-29 Reciprocating machine Expired - Lifetime US3839858A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
BE777548A BE777548A (fr) 1971-12-30 1971-12-30 Moteur,
BE785549A BE785549R (enrdf_load_stackoverflow) 1972-06-28 1972-06-28

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US (1) US3839858A (enrdf_load_stackoverflow)
DE (1) DE2264237A1 (enrdf_load_stackoverflow)
FR (1) FR2167154A5 (enrdf_load_stackoverflow)
IT (1) IT974757B (enrdf_load_stackoverflow)

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US4149370A (en) * 1977-02-28 1979-04-17 Eduardo Ayala Vargas Self starting internal combustion engine with means for changing the expansion ratio
US4730588A (en) * 1986-04-25 1988-03-15 Fuji Jukogyo Kabushiki Kaisha Valve operating system for an automotive engine
US5682738A (en) * 1995-03-02 1997-11-04 Barber; John S. Heat engines and waste destruction mechanism
US5964087A (en) * 1994-08-08 1999-10-12 Tort-Oropeza; Alejandro External combustion engine
US6092365A (en) * 1998-02-23 2000-07-25 Leidel; James A. Heat engine
US6094915A (en) * 1995-03-06 2000-08-01 Negre; Guy Method and devices for eliminating the pollution of cyclic internal combustion engines with an independent combustion chamber
FR2831598A1 (fr) * 2001-10-25 2003-05-02 Mdi Motor Dev Internat Groupe motocompresseur-motoalternateur a injection d'air comprime additionnel fonctionnant en mono et pluri energies
US20110011053A1 (en) * 2009-07-14 2011-01-20 Benham Roger A Adiabatic external combustion with low pressure positive displacement motor
WO2013066186A1 (en) * 2011-11-01 2013-05-10 Heggen Lars Harald A method for quick startup of hot gas engines/stirling engines
CN104564416A (zh) * 2014-11-18 2015-04-29 西安交通大学 一种星型连杆传动的斯特林发动机
US9157322B2 (en) 2012-06-08 2015-10-13 Roger A. Benham Journal-less crankshaft and non-friction variable speed transmission with inherent clutch and free spin
WO2018206412A1 (de) * 2017-05-09 2018-11-15 Frauscher Holding Gmbh Heissgasmaschine mit stufenkolben

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Publication number Priority date Publication date Assignee Title
DE3233391A1 (de) * 1982-09-09 1984-03-22 Breinlich, Richard, Dr., 7120 Bietigheim-Bissingen Motor und zubehoer, insbesondere kohlebrennstoffmotor
DE3330983A1 (de) * 1983-08-27 1985-03-21 Breinlich, Richard, Dr., 7120 Bietigheim-Bissingen Motor mit zubehoer, insbesondere kohlebrennstoffmotor und motor mit massnahmen zur steigerung der leistung bei geringem gewicht

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US1847260A (en) * 1927-08-06 1932-03-01 Delos G Haynes Power apparatus
US1995320A (en) * 1931-05-29 1935-03-26 Frederick F Murray Means for starting a diesel driven locomotive
US2688230A (en) * 1950-08-30 1954-09-07 Milliken Humphreys Continuous combustion engine
US3577729A (en) * 1969-03-11 1971-05-04 Glenn B Warren Reciprocating internal combustion engine with constant pressure combustion
US3520132A (en) * 1969-06-18 1970-07-14 Glenn B Warren Stored air supercharger for reciprocating internal combustion engine with constant pressure combustion

Cited By (16)

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US4149370A (en) * 1977-02-28 1979-04-17 Eduardo Ayala Vargas Self starting internal combustion engine with means for changing the expansion ratio
US4730588A (en) * 1986-04-25 1988-03-15 Fuji Jukogyo Kabushiki Kaisha Valve operating system for an automotive engine
US5964087A (en) * 1994-08-08 1999-10-12 Tort-Oropeza; Alejandro External combustion engine
US5682738A (en) * 1995-03-02 1997-11-04 Barber; John S. Heat engines and waste destruction mechanism
US6094915A (en) * 1995-03-06 2000-08-01 Negre; Guy Method and devices for eliminating the pollution of cyclic internal combustion engines with an independent combustion chamber
US6092365A (en) * 1998-02-23 2000-07-25 Leidel; James A. Heat engine
FR2831598A1 (fr) * 2001-10-25 2003-05-02 Mdi Motor Dev Internat Groupe motocompresseur-motoalternateur a injection d'air comprime additionnel fonctionnant en mono et pluri energies
US20110011053A1 (en) * 2009-07-14 2011-01-20 Benham Roger A Adiabatic external combustion with low pressure positive displacement motor
WO2013066186A1 (en) * 2011-11-01 2013-05-10 Heggen Lars Harald A method for quick startup of hot gas engines/stirling engines
US9157322B2 (en) 2012-06-08 2015-10-13 Roger A. Benham Journal-less crankshaft and non-friction variable speed transmission with inherent clutch and free spin
CN104564416A (zh) * 2014-11-18 2015-04-29 西安交通大学 一种星型连杆传动的斯特林发动机
CN104564416B (zh) * 2014-11-18 2016-01-20 西安交通大学 一种星型连杆传动的斯特林发动机
WO2018206412A1 (de) * 2017-05-09 2018-11-15 Frauscher Holding Gmbh Heissgasmaschine mit stufenkolben
US11215139B2 (en) 2017-05-09 2022-01-04 Frauscher Holding Gmbh Hot gas engine having a step piston
JP7202365B2 (ja) 2017-05-09 2023-01-11 フラッシャー ホールディング ゲーエムベーハー 段付ピストンを有する高温ガスエンジン
US11725607B2 (en) 2017-05-09 2023-08-15 Frauscher Holding Gmbh Hot air engine having a step piston

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IT974757B (it) 1974-07-10
FR2167154A5 (enrdf_load_stackoverflow) 1973-08-17
DE2264237A1 (de) 1973-07-05

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