US20130118175A1 - Piston engine drivable using a steam power process - Google Patents

Piston engine drivable using a steam power process Download PDF

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Publication number
US20130118175A1
US20130118175A1 US13/812,804 US201113812804A US2013118175A1 US 20130118175 A1 US20130118175 A1 US 20130118175A1 US 201113812804 A US201113812804 A US 201113812804A US 2013118175 A1 US2013118175 A1 US 2013118175A1
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United States
Prior art keywords
piston
cylinder
engine
internal
piston engine
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.)
Abandoned
Application number
US13/812,804
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English (en)
Inventor
Nadja Eisenmenger
Hans-Christoph Magel
Andreas Wengert
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MAGEL, HANS-CHRISTOPH, WENGERT, ANDREAS, EISENMENGER, NADJA
Publication of US20130118175A1 publication Critical patent/US20130118175A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B29/00—Machines or engines with pertinent characteristics other than those provided for in preceding main groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F01B9/023—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft of Bourke-type or Scotch yoke
    • 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
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to a piston engine which can be driven via a steam power process.
  • the invention relates to a piston engine which can be driven via a steam power process and which serves to use the waste heat of an internal-combustion engine.
  • Internal-combustion engines convert the energy of the fuel into mechanical energy in order to drive vehicles and the like. However, a substantial portion of the energy is thereby released as waste heat which is directed away by the cooling system or in the exhaust gas of the internal-combustion engine. In order to use this thermal energy, it is conceivable for a steam power process to be coupled to the internal-combustion engine. The thermal energy from the internal-combustion engine can thereby be used to produce steam which is expanded in an expansion engine and which consequently provides additional energy which can be used to drive the vehicle or to produce auxiliary energy. In this instance, however, there is produced the problem that a large expansion volume of the expansion engine is necessary for a high degree of efficiency of the steam power process whereas the structural space situation in an internal-combustion engine is, however, generally very constrained.
  • the piston engine according to the invention has the advantage that a good degree of efficiency can be obtained with a compact construction type.
  • the piston engine can also be accommodated in a confined structural space situation in an internal-combustion engine, or the like, and have sufficient working volume at the same time.
  • the piston engine may be combined with an internal-combustion engine in order to convert the waste heat of the internal-combustion engine into additional driving energy.
  • Such a combination is particularly efficient in order to use waste heat in a commercial vehicle because, in this instance, the internal-combustion engine discharges great power and consequently a large quantity of heat is also available in order to produce steam. The fuel consumption of the internal-combustion engine can thereby be reduced.
  • a piston engine which is constructed as a reciprocating piston steam engine and which has a Scotch yoke crank mechanism is particularly advantageous. Substantially the same speed range can thereby be obtained for the piston engine as for the internal-combustion engine and consequently the mechanical energy discharged by the piston engine can be discharged directly to the crankshaft of the diesel engine or the gas engine. On the one hand, a small structural size of the piston engine is particularly important in this instance.
  • crankshaft of the piston engine may be located precisely on the crank axis of the internal-combustion engine so that no additional structural space for power transmission via one or more toothed wheels, a chain or a belt is necessary. Therefore, it is particularly advantageous for a crank axis of a crankshaft of the piston engine to be located on a crank axis of the internal-combustion engine.
  • the cylinder is further advantageous for the cylinder to be directed horizontally or downwards from the crank axis of the crankshaft in relation to an installation position of the internal-combustion engine.
  • a piston engine which is constructed as a two-piston reciprocating piston engine and which has opposing cylinders with a Scotch yoke drive
  • a relatively compact structural form can be achieved. Owing to the cylinders located at both sides of the crankshaft, however, this structural form does not have a flexible orientation of the cylinders because the possible fitting positions are limited. Particularly in this case, only horizontal installation may be advantageous here, the remaining auxiliary units having to be adapted.
  • a piston engine which is constructed as a one-cylinder steam engine and which operates with the single-cycle method is fitted to the internal-combustion engine.
  • This structural form allows a small structural size and flexible positioning.
  • the single cylinder of the piston engine can be fitted to the internal-combustion engine in a flexible manner in terms of the angular position.
  • a cylinder diameter of the cylinder piston may nevertheless be determined so as to be relatively small.
  • crankshaft or another shaft of the piston engine may be located directly on the crank axis or shaft axis of the internal-combustion engine and the cylinder of the piston engine can be positioned in an available gap in the internal-combustion engine owing to the one-sided structural space.
  • a compact piston engine may also be positioned at other locations, for example, in the region of the transmission bell housing between the internal-combustion engine and the transmission.
  • fitting laterally to the internal-combustion engine is advantageous, the crankshaft of the piston engine (steam engine) being orientated parallel with the crankshaft of the internal-combustion engine. It is thereby possible to bring about a simple operative connection of the two crankshafts via toothed wheels or chains or belts.
  • a very compact structural size of the steam engine is also necessary therefor.
  • a one-cylinder structural form is advantageous, the cylinder being orientated approximately parallel with the travel direction of the cylinder of the internal-combustion engine. In this instance, these combinations also afford the necessary freedom for positioning the cylinder structural space for the drive connection.
  • an additional cylinder bore an additional cylinder piston which is arranged in the additional cylinder bore and an additional rod which is connected at least indirectly to the additional cylinder piston to be provided, for the additional rod to be directed out of the additional cylinder bore, for the additional cylinder piston to delimit in the additional cylinder bore, at one side, a third working space and, at the other side, a fourth operating space, and for the rod and the additional rod to be connected to each other at least indirectly.
  • a piston engine having precisely two cylinders may be constructed.
  • a dual-action cylinder piston can be constructed with relatively little complexity in a piston engine in which a Scotch yoke drive and a bearing arrangement of a slider crank on the rods which act as transmission rods are provided. It is thereby possible to obtain practically double the stroke space with the same structural space being required, whereby the degree of efficiency of the piston engine is increased.
  • the return space constructed in the cylinder pistons can be used directly as additional operating space.
  • the sealing of the additional working spaces is then brought about at the transmission rod, respectively. Consequently, additional sealing locations are not required.
  • additional sealing elements in particular piston rings.
  • the piston engine being constructed as a reciprocating piston steam engine using the single-cycle principle and with Scotch yoke crank operation in conjunction with an internal-combustion engine, consequently, there can be produced a particularly low-consumption and cost-effective combination engine which comprises the internal-combustion engine and the piston engine and which complies with the requirements in terms of service-life of a commercial vehicle.
  • the cylinder piston it is advantageous for the cylinder piston to have, at one side, a first lateral face and, at the other side, a second lateral face, for the first lateral face and the second lateral face to be directed away from each other, for the first lateral face of the cylinder piston in the cylinder bore to delimit the first operating space and for the second lateral face of the cylinder piston in the cylinder bore to delimit the second operating space. It is thereby possible to achieve alternating actuation of the cylinder piston owing to alternating filling of the operating spaces with vapor-like operating fluid.
  • the rod at the second lateral face of the cylinder piston may be connected to the cylinder piston and for the rod to extend at least approximately perpendicularly relative to the second lateral face through the second operating space.
  • the rod may be rigidly connected to the cylinder piston.
  • the force acting on the cylinder piston may advantageously be transmitted via the rod to a crankshaft or the like.
  • an inlet for the first operating space and an inlet for the second operating space may be provided and for vapor-like operating fluid to be alternately directed into the first operating space and the second operating space via the inlet for the first operating space and via the inlet for the second operating space.
  • the inlets may be advantageously constructed as valve-controlled inlets.
  • an outlet for the first operating space and an outlet for the second operating space to be provided and for at least partially depressurized vapor-like operating fluid to be able to be alternately discharged from the first operating space and the second operating space via the outlet for the first operating space and via the outlet for the second operating space.
  • the outlets may advantageously be constructed as valve-controlled outlets.
  • Gaseous operating fluid which is under relatively high pressure can be directed via the inlets into the operating spaces.
  • the depressurized gaseous operating fluid can then be directed, for example, to a condenser via the outlets.
  • crankshaft which is arranged in a crankshaft space to be provided, for the crankshaft to have a crankshaft journal on which a sliding block is arranged, for the rod to be connected to a slider crank arranged in the crankshaft space and for the crank slider to have a slot-like recess, in which the sliding block is introduced.
  • a slider crank mechanism can thereby be constructed.
  • a piston engine in the form of a reciprocating piston steam engine can be constructed with a Scotch yoke crank mechanism.
  • the cylinder bore is also advantageous for the cylinder bore to be directed horizontally or downwards from the crank axis of the crankshaft in relation to an installation position of the internal-combustion engine. In this region, no auxiliary units are generally arranged in the internal-combustion engine so that the structural space available can be used.
  • the steam power process may be constructed as an ORC process (Organic Rankine Cycle process).
  • ORC process Organic Rankine Cycle process
  • the thermal energy of the waste heat is converted into mechanical energy via the ORC process.
  • the waste heat can advantageously be transmitted to the operating fluid of the ORC process from an exhaust gas of the internal-combustion engine or an exhaust gas return line via a heat exchanger.
  • the operating fluid may be based at least substantially on water.
  • the operating fluid can be vaporized at the heat exchanger. That vapor can subsequently be depressurized in the piston engine which acts as an expansion engine, the mechanical energy being acquired.
  • the operating fluid is subsequently cooled in a condenser and supplied to a pump.
  • the operating fluid can thereby be compressed in the fluid phase by the pump to the pressure level for the repeated vaporization at the heat exchanger.
  • the circuit is thereby closed.
  • the rod is connected, on the one hand, rigidly to the cylinder piston and, on the other hand, rigidly to the slider crank. It is further advantageous for there to be provided a bearing on which the rod directed out of the cylinder bore is supported.
  • the bearing may advantageously be constructed by a bearing face.
  • the bearing can further be lubricated by a lubricant from the crankshaft space. Consequently, the rod is supported displaceably on the bearing, a compact construction being made possible.
  • the piston engine forming a combination engine with the internal-combustion engine.
  • a steam engine is combined with an internal-combustion engine.
  • the piston engine can be operatively connected in mechanical terms to a drive train of a vehicle.
  • the piston engine is fitted to an internal-combustion engine, it is advantageous for the piston engine to be fitted to the internal-combustion engine at the front, or for the piston engine to be fitted to the internal-combustion engine at the side.
  • a gear casing or the like which is also required for other units may be used in order to produce the mechanical operative connection.
  • the cylinder bore is also advantageous for the cylinder bore to be orientated at least approximately parallel with a cylinder of the internal-combustion engine. Particularly in the case of a single-cylinder construction of the piston engine, the cylinder is preferably directed upwards.
  • FIG. 1 is a schematic cross section of a piston engine in accordance with a first embodiment of the invention
  • FIG. 2 shows an arrangement of the piston engine of the first embodiment of the invention illustrated in FIG. 1 in an internal-combustion engine and
  • FIG. 3 is a schematic cross section of the piston engine illustrated in FIG. 1 in accordance with a second embodiment of the invention.
  • FIG. 1 is a schematic illustration of a piston engine 1 in accordance with a first embodiment of the invention.
  • the piston engine 1 is driven via a steam power process.
  • the piston engine 1 can be used particularly in an internal-combustion engine of a motor vehicle in order to use the waste heat of the internal-combustion engine.
  • the piston engine 1 then converts the waste heat into mechanical energy which can be used, for example, as additional drive energy or to drive an auxiliary unit, in particular an electrical generator.
  • the piston engine 1 according to the invention is also suitable for other applications.
  • the piston engine 1 has a housing portion 2 and a cylinder 3 which is connected to the housing portion 2 .
  • the piston engine 1 has precisely one cylinder 3 .
  • the cylinder 3 of the piston engine 1 has a cylinder bore 4 , in which a cylinder piston 5 is arranged.
  • the cylinder piston 5 is arranged in this instance in the cylinder bore 4 in a manner displaceable along an axis 6 of the cylinder bore 4 .
  • the cylinder piston 5 has, at one side, a first lateral face 7 and, at the other side, a second lateral face 8 .
  • the cylinder piston 5 delimits in the cylinder bore 4 a first operating space 9 with the first lateral face 7 .
  • the cylinder piston 5 delimits a second operating space 10 in the cylinder bore 4 with the second lateral face 8 .
  • Valve-controlled inlets 12 , 13 are provided in the cylinder 3 .
  • Valve-controlled outlets 14 , 15 are further provided in the cylinder 3 .
  • the inlet 12 and the outlet 14 are associated with the first operating space 9 .
  • the inlet 13 and the outlet 15 are associated with the second operating space 10 .
  • highly pressurized, vapor-like operating fluid can be introduced into the first operating space 9 via the inlet 12 .
  • An actuating force is applied to the cylinder piston 5 in the direction 11 via the pressure of the gaseous operating fluid.
  • the gaseous operating fluid in the first operating space 9 thereby becomes depressurized.
  • the outlet 15 can be opened in order to discharge the already depressurized, remaining operating fluid from the second operating space 10 .
  • an inverse actuation of the cylinder piston 5 may be carried out counter to the direction 11 .
  • the valve-controlled inlet 13 is opened in order to introduce highly pressurized, gaseous operating fluid into the second operating space 10 .
  • the inlet 11 for the first operating space 9 is closed in this instance.
  • the outlet 14 for the first operating space 11 can now be opened in order to discharge the depressurized, gaseous operating fluid from the first operating space 9 when the cylinder piston 5 is actuated counter to the direction 11 . Consequently, an alternating actuation of the cylinder piston 5 is possible.
  • the piston engine 1 has a rod 20 which acts as the transmission rod 20 .
  • the rod 20 is connected at one side to the cylinder piston 5 at the second lateral face 8 .
  • the rod 20 is rigidly connected to the cylinder piston 5 .
  • the rod 20 is orientated with respect to the axis 6 in this instance so that the rod 20 is orientated perpendicularly to the second lateral face 8 .
  • the rod 20 is connected at the other side to a slider crank 23 which is arranged in the crankshaft space 21 .
  • the connection of the rod 20 to the slider crank 23 is also constructed in a rigid manner in this instance. Consequently, the rod 20 extends through the second operating space 10 and into the crankshaft space 21 .
  • the cylinder bore 4 is separated from the crankshaft space 21 by a housing portion 24 .
  • a bearing face 25 which adjoins the crankshaft space 21 is constructed on the housing portion 24 .
  • the bearing face 25 forms a bearing 25 ′, on which the rod 20 which is directed out of the cylinder bore 4 is supported.
  • Lubricating oil is preferably located in the crankshaft space 21 . This lubricating oil can also be used to lubricate the bearing face 25 . Consequently, advantageous supporting of the rod 20 on the bearing face 25 is possible.
  • annular sealing elements 26 , 27 which are arranged behind the bearing face 25 can be provided. Introduction of lubricating oil into the second operating space 10 , and consequently mixing of the gaseous operating fluid, on the one hand, and the lubricating oil, on the other hand, is thereby prevented.
  • the crank mechanism of the piston engine 1 has a sliding block 28 which is arranged on a crankshaft journal 29 of the crankshaft 22 .
  • the sliding block 28 is in this instance introduced into a slot-like recess 30 of the slider crank 23 . It is thereby possible to convert the reciprocating movement of the rod 20 into a rotational movement of the crankshaft 22 .
  • the lubrication of the crank mechanism is brought about in this instance by means of the lubricating oil provided in the crankshaft space 21 .
  • piston rings 31 , 32 which improve sealing between the operating spaces 9 , 10 and, at the same time, prevent friction between the cylinder piston 5 and the cylinder bore 4 . Frictional wear can thereby be reduced and a reliable sealing action ensured at the same time.
  • a piston engine 1 which is in the form of a reciprocating piston steam engine and which operates with the single-cycle principle can advantageously be constructed so as to have precisely one cylinder 3 .
  • the cylinder piston 5 introduces its force via the rod 20 to the slider crank mechanism and consequently the crankshaft 22 . All the inlets 12 , 13 and outlets 14 , 15 are controlled.
  • the reciprocating piston movement of the cylinder piston 5 is transmitted to the crankshaft 22 by the slider crank drive with the slider crank 23 and the sliding block 28 which is arranged on the crankshaft journal 29 .
  • the slider crank 23 is supported on the bearing location formed by the bearing face 25 via the rod 20 . That bearing is located in the oil region because it adjoins the crankshaft space 21 .
  • the operating fluid is alternately depressurized in the operating spaces 9 , 10 . Consequently, both the upward and the downward movements of the cylinder piston 5 contribute to the power production.
  • a great expansion volume is thereby achieved in a small structural space of the piston engine 1 .
  • a small structural length is further achieved from one crank axis 33 of the crankshaft 22 as far as one end 34 of the cylinder 3 .
  • the piston engine 1 can thereby be flexibly arranged in an internal-combustion engine or the like.
  • FIG. 2 shows an arrangement of the piston engine 1 illustrated in FIG. 1 in an internal-combustion engine 35 .
  • the internal-combustion engine 35 has, for example, a cylinder 36 which is orientated perpendicularly or vertically relative to an installation position. This is possible, for example, in a configuration as a series cylinder.
  • a plurality of auxiliary units 37 , 38 , 39 are arranged at the front side of the internal-combustion engine 35 .
  • a crank axis 33 of the internal-combustion engine 35 is orientated perpendicularly relative to the plane of the drawing in this embodiment.
  • the piston engine 1 can now advantageously be arranged at the front side of the internal-combustion engine 35 , the structural space left unoccupied by the auxiliary units 37 to 39 being able to be used.
  • the piston engine 1 is arranged at the front side of the internal-combustion engine 35 in such a manner that the crank axis 33 of the piston engine 1 corresponds to the crank axis 33 of the internal-combustion engine 35 .
  • That fitting arrangement is particularly advantageous because the power transmission from the piston engine 1 to the internal-combustion engine 35 can be carried out without additional toothed wheels, chains and belts.
  • FIG. 3 is a schematic cross section of the piston engine 1 illustrated in FIG. 1 in accordance with a second embodiment.
  • the piston engine 1 has an additional cylinder 3 ′.
  • An additional cylinder bore 4 ′, in which an additional cylinder piston 5 ′ is arranged, is constructed in the additional cylinder 3 ′.
  • the additional cylinder piston 5 ′ can also be actuated along the axis 6 in this instance.
  • the cylinder piston 5 ′ has a first lateral face 7 ′ and a second lateral face 8 ′. At the first lateral face 7 ′, the cylinder piston 5 ′ delimits a third operating space 40 . At the second lateral face 8 ′, the cylinder piston 5 ′ delimits a fourth operating space 41 .
  • the cylinder piston 5 ′ can be actuated together with the cylinder piston 5 so that both cylinder pistons 5 are displaced either in the direction 11 or counter to the direction 11 .
  • Inlets 12 ′, 13 ′ are provided in the additional cylinder 3 ′. Furthermore, outlets 14 ′, 15 ′ are provided in the additional cylinder 3 ′. The inlet 12 ′ and the outlet 14 ′ are associated with the third operating space 40 in this instance. The inlet 13 ′ and the outlet 15 ′ are associated with the fourth operating space 41 .
  • a rod 20 ′, via which the cylinder piston 5 ′ is connected to the slider crank 23 , is further provided. In this instance, the rod 20 ′ is rigidly connected to the cylinder piston 5 ′ at the second lateral face 8 ′. Consequently, the displacement force acting on the cylinder piston 5 can be transmitted to the slider crank 23 via the rod 20 ′.
  • the rod 20 ′ is supported on a bearing 25 ′ in this instance.
  • pressurized, gaseous operating fluid is alternately introduced into the third operating space 40 and the fourth operating space 41 .
  • the inlets 12 ′, 13 ′ are alternately opened.
  • the actuation of the inlets 12 , 13 and the inlets 12 ′, 13 ′ for the two cylinders 3 , 3 ′ may occur in a synchronized manner.
  • the actuation of the outlets 14 , 15 for the cylinder 3 and the outlets 14 ′, 15 ′ for the cylinder 3 ′ can also occur in a synchronized manner.
  • a piston engine 1 having mutually opposing cylinders 3 , 3 ′ and consequently mutually opposing cylinder pistons 5 , 5 ′ can be constructed, the cylinder pistons 5 , 5 ′ introducing their forces to the crankshaft 22 via the slider crank mechanism.
  • the reciprocating piston movement of the two cylinder pistons 5 , 5 ′ is transmitted to the crankshaft 22 .
  • the slider crank 23 is advantageously supported on the two bearing locations 25 , 25 ′ which are arranged at the two sides of the crank axis 33 .
  • the sealing of the crankshaft space 21 which is filled with lubricating oil with respect to the cylinder bores 4 , 4 ′ is brought about in this embodiment via the bearings 25 , 25 ′.
  • An additional sealing may also optionally be provided by means of sealing elements.
  • the first operating space 9 and the fourth operating space 41 can simultaneously be filled with gaseous operating fluid so that, during the expansion of the operating fluid, an actuation of the slider crank 23 in the direction 11 is brought about. Subsequently, an opposed actuation can be brought about by introducing the gaseous operating fluid, on the one hand, into the second operating space 10 and, on the other hand, into the third operating space 40 .
  • Each of the cylinder pistons 5 , 5 ′ is thereby acted upon at both sides. It is thereby possible to have a compact construction of the piston engine 1 with a large expansion volume being constructed at the same time.
  • the piston engine 1 of the second embodiment illustrated in FIG. 3 can be fitted to an internal-combustion engine 35 .
  • the piston engine 1 of the second embodiment can be arranged in the internal-combustion engine 35 illustrated in FIG. 2 in that there is brought about a horizontal installation position in relation to the axis 6 of the piston engine 1 and a displacement, on the one hand, of the auxiliary unit 37 upwards and, on the other hand, optionally of the auxiliary unit 39 upwards.
  • the crank axis 33 of the crankshaft 22 of the piston engine 1 then corresponds to the crank axis 33 of the internal-combustion engine 35 .
  • the piston engine 1 then forms with the internal-combustion engine 35 a combination engine 1 , 35 .
  • the piston engine 1 is operatively connected in mechanical terms to a drive train 33 of a vehicle. If the piston engine 1 is fitted to the internal-combustion engine 35 , the piston engine 1 can be fitted to the internal-combustion engine 35 at the front or the piston engine 1 can be fitted to the internal-combustion engine 35 at the side.
  • the cylinder bore 4 is preferably orientated at least approximately parallel with the cylinder 36 of the internal-combustion engine 35 .
  • the fitting is particularly advantageous if precisely one cylinder bore 4 is provided. Owing to the compact construction, favorable fitting positions in the internal-combustion engine 35 are thereby produced.
  • the cylinder piston 5 it is advantageous for the cylinder piston 5 to have, at one side, a first lateral face 7 and, at the other side, a second lateral face 8 , for the first lateral face 7 and the second lateral face 8 to be directed away from each other, for the first lateral face 7 of the cylinder piston 5 to delimit the first operating space 9 in the cylinder bore 4 and for the second lateral face 8 of the cylinder piston 5 to delimit the second operating space 10 in the cylinder bore 4 . Consequently, it is also advantageous in this instance for the rod 20 to be connected to the cylinder piston 5 at the second lateral face 8 of the cylinder piston 5 and for the rod 20 to extend through the second operating space 10 at least approximately perpendicularly relative to the second lateral face 8 .
  • an inlet 12 for the first operating space 9 and an inlet 13 for the second operating space 10 to be provided and for vapor-like operating fluid to be able to be directed alternately into the first operating space 9 and the second operating space 10 via the inlet 12 for the first operating space 9 and via the inlet 13 for the second operating space 10 ,
  • an outlet 14 for the first operating space 9 and an outlet 15 for the second operating space 10 to be provided and for at least partially depressurized vapor-like operating fluid to be able to be discharged alternately from the first operating space 9 and the second operating space 10 via the outlet 14 for the first operating space 9 and via the outlet 15 for the second operating space 10 .
  • crankshaft 22 which is arranged in a crankshaft space 21 to be provided, for the crankshaft 22 to have a crankshaft journal 29 on which a sliding block 28 is arranged, for the rod 20 to be connected to a slider crank 23 which is arranged in the crankshaft space 21 and for the slider crank 23 to have a slot-like recess 30 in which the sliding block 28 is introduced.
  • crank axis 33 of the crankshaft 22 it is also advantageous for a crank axis 33 of the crankshaft 22 to be arranged on a crank axis 33 of the internal-combustion engine 35 . Consequently, it is also advantageous for the cylinder bore 4 to be orientated horizontally or downwards from the crank axis 33 in relation to an installation position of the internal-combustion engine 35 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
US13/812,804 2010-07-28 2011-07-07 Piston engine drivable using a steam power process Abandoned US20130118175A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010038538.7 2010-07-28
DE102010038538A DE102010038538A1 (de) 2010-07-28 2010-07-28 Über einen Dampfkraftprozess antreibbare Kolbenmaschine
PCT/EP2011/061465 WO2012013470A1 (fr) 2010-07-28 2011-07-07 Moteur à piston pouvant être entraîné par le biais d'un processus de force motrice à vapeur

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US20130118175A1 true US20130118175A1 (en) 2013-05-16

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US13/812,804 Abandoned US20130118175A1 (en) 2010-07-28 2011-07-07 Piston engine drivable using a steam power process

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US (1) US20130118175A1 (fr)
CN (1) CN103026001A (fr)
DE (1) DE102010038538A1 (fr)
WO (1) WO2012013470A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10436345B1 (en) 2018-05-22 2019-10-08 Woodward, Inc. Simplified mechanism for a scotch yoke actuator

Families Citing this family (4)

* Cited by examiner, † Cited by third party
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FR3002286B1 (fr) 2013-02-21 2016-09-02 Exoes Systeme de conversion d'energie thermique des gaz d'echappement d'un moteur a combustion.
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