US3501088A - Balanced free piston engine - Google Patents

Balanced free piston engine Download PDF

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Publication number
US3501088A
US3501088A US746541A US3501088DA US3501088A US 3501088 A US3501088 A US 3501088A US 746541 A US746541 A US 746541A US 3501088D A US3501088D A US 3501088DA US 3501088 A US3501088 A US 3501088A
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piston
engine
balancing
power
compressor
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Anton Braun
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Tectonics Companies Inc
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Assigned to TECTONICS COMPANIES, INC., A CORP. OF MN reassignment TECTONICS COMPANIES, INC., A CORP. OF MN ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: COMPRESSOR PARTNERS LTD., HILLIARD-LYONS PATENT MANAGEMENT, INC., A CORP. OF KY, HLPM NETHERLANDS BV, A DUTCH CORP.
Assigned to TECTONICS COMPANIES reassignment TECTONICS COMPANIES ASSIGNMENT OF ASSIGNORS INTEREST. SEE DOCUMENT FOR DETAILS Assignors: BRAUN, ANTON T.
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    • 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
    • F02B71/00—Free-piston engines; Engines without rotary main shaft
    • 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
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/047—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft with rack and pinion

Definitions

  • ABSTRACT F THE DISCLOSURE A balanced, free piston engine in which the power piston is connected to a reciprocally movable member of a driven energy absorbing device, such as the compressor piston in a gas compressor, so that all main pistons in the engine, including the power piston and the movable member move together as a unit during the operation of the engine.
  • a separate control piston is also connected with the power piston and is reciprocally movable therewith in a control cylinder so as to provide and/ or regulate the energy necessary for satisfactory operation of the engine through a range of different 'operating conditions.
  • Dynamic balance of the engine is achieved by utilizing a balancing and synchronizing assembly having a counterbalancing movable weight which is arranged for translational movement with respect to the engine housing in an opposite direction to the power piston during the operation of the engine and which is constructed so that the absolute product of the weight of the counter-balancing movable weight of the lbalancing and synchronizing assembly times the length of its stroke is equal to the absolute product of the sum of the weights of the power assembly, i.e., the power piston and all other elements which are connected to and move with the power piston, times the corresponding length of the stroke of the power piston.
  • the balancing and synchronizing assembly is connected with the power assembly by a rack and pinion arrangement, and is positioned and supported within the engine housing so that the losses, due to friction, resulting from the interconnection of the power assembly and the balancing and synchronizing assembly and from the movement of balancing and synchronizing assembly in the engine housing are minimized.
  • This invention relates to an improved, balanced free piston engine, and more particularly to an improved dynamically balanced, free piston engine which may be used as a compact, relatively small and lightweight power unit for operating various types of energy absorbing devices,
  • Prior free piston engines have been designed to operate energy absorbing devices; however, these prior free piston engines were generally designed for use with only one energy absorbing device and usually were unadaptable for use with another.
  • balanced free piston engines have usually included at least a pair of piston assemblies which were mounted for reciprocal movement within axially aligned cylinders and which were caused to move in opposite directions within their respective cylinders.
  • Each of the piston assemblies usually comprised a power piston and at least one compressor and/or bouncer piston, with the pistons of each piston assembly being connected together so that the piston assembly moved together as a unit.
  • Dynamic balance was achieved in these engines by constructing the assemblies so that their weights were equal and so that the length of their strokes were equal. Also, as described in the Anton Braun United States patent application, Ser. No. 805,063, namelyd Dec. 17, 1968, dynamic bal- 3,501,088 Patented Mar.
  • a balanced free piston engine which may use only a single power piston and which has no counter-moving main pistons.
  • all main pistons i.e., power pistons, bouncer compressor pistons, or scavenge compressor pistons
  • a counter-balancing movable weight translationally moves in the opposite direction with respect to the housing to balance the engines.
  • the improved, balanced, free piston engine of the present invention includes a power piston which is connected with a reciprocally movable member in the energy absorbing device, for example, the compressor piston in a reciprocal compressor, that is being driven by the irnproved free piston engine.
  • the improved free piston engine includes a separate control piston which reciprocates within a control cylinder, and which moves with the power piston so as to perform as a return means, ie., to supply suicient return energy for satisfactory operation of the engine through a range of different operating conditions or, in other words, to always supply the proper energy to return the power piston to the desired top-deadcenter position.
  • the energy absorbing device is a compressor
  • the return energy may be supplied from the compressor itself rather than from a separate piston.
  • the improved engine of the present invention includes a novel balancing and synchronizing assembly.
  • the counter-balancing movable weight of the balancing and synchronizing assembly is mounted adjacent a power assembly, i.e., the power piston and all other elements carried by and moving with the power piston, which moves parallel to, but in an opposite direction to the movement of the counter-balancing movable weight of the balancing and synchronizing assembly.
  • the weight of the counter-balancing movable weight of the balancing and synchronizing assembly is selected so as to be substantially equal to the weight of the power assembly, and the distance through which the counter-balancing movable weight of the balancing and synchronizing assembly and the power assembly move during the operation are equal so that dynamic balance is achieved in the engine.
  • One of the advantages of the novel balancing and synchronizing assembly is that its weight may be relatively easily changed so that dynamic balance may always be achieved, although the weights of the reciprocating portions of the energy absorbing devices connected with the engine may vary considerably.
  • the balancing and synchronizing assembly is connected with the power assembly by means of a plurality of racks, carried by the power assembly and by the balancing and synchronizing assembly, and at least one pair of pinions mounted for rotation, ⁇ about fixed axes, between the racks of the power assembly and the racks of the balancing and synchronizing assembly.
  • the improved balanced free piston engine of the present invention may be utilized, as a power package, to drive a variety of energy absorbing devices of the type using a reciprocatory power input for operation, since the engine may be constructed so that one end of a reciprocating shaft projects from the engine housing and may be attached to the movable member of an energy absorbing device to drive the same.
  • the energy absorbing device a compressor
  • the energy absorbing device is attached directly to the engine housing with one end of the shaft being directly attached to a compressor piston, although, of course, the engine and the energy absorbing device could be spaced apart, if desired.
  • an object of the present invention to provide an improved, balanced, free piston engine wherein the power piston and a reciprocal movable member of an energy absorbing device, driven by the free piston engine, are connected and move together as a unit.
  • a further related object of the present invention is to provide an improved, balanced, free piston engine wherein any and all main pistons (power pistons, scavenge compressor pistons, or bounce compressor pistons) in the engine translationally move together with respect to the engine housing and are balanced by the oppositely directed translational movement of a counterbalancing movable weight of a novel balancing and synchronizing assembly.
  • a still further related object of the present invention is to provide an improved, balanced free piston engine including a control piston which is a part of and moves with the power assembly and which is arranged so as to supply substantially all, or a part of, the return energy necessary for the proper thermodynamic balance of the engine.
  • a still further related object of the present invention is to provide an improved, balanced free piston engine having a separate control piston.
  • Another object of the present invention is to provide an improved, balanced, free piston engine which is relatively light weight and compact.
  • a related object of the present invention is to provide an improved, balanced, free piston engine wherein the required overall length of the engine need not be substantially greater than four times the length of the swept stroke of the power piston utilized in the engine plus the length required for the energy absorbing device.
  • Another object of the present invention is to provide an improved, balanced free piston engine of the type described wherein the energy absorbing device is a compressor powered by the engine and wherein the compressor piston is connected with the power piston so that the compressor piston and the power piston move together as a unit.
  • Still another object of the present invention is to provide an improved, balanced, free piston engine wherein the power piston and the reciprocally movable member in the energy absorbing device driven by the engine are structurally interconnected and wherein dynamic balance of the engine is achieved by the utilization of a novel balancing and synchronizing assembly having a counterbalancing movable weight, the weight of which being easily changeable so that the engine may be used to power various different energy absorbing devices.
  • the counterbalancing movable weight of the novel balancing and synchronizing assembly is arranged so as to be always translationally moved in the opposite direction to the power assembly with respect to the engine housing so that the product of the weight of the counter-balancing movable weight of the balancing and synchronizing assembly times its stroke plus the product of the weight of the power assembly times the corresponding stroke of the power assembly is equal to zero.
  • a further object of the present invention is to provide a rack and pinion arrangement for connecting the power assembly, with the novel balancing and synchronizing assembly, which arrangement includes double racks connected with and carried by the power assembly and racks mounted on the balancing and synchronizing assembly so that each rack of the balancing and synchronizing assembly faces one of the racks connected with the power assembly.
  • a pair of pinions, mounted for rotation about xed axes, are positioned between the facing racks so that the teeth of the pinions engage the teeth of the facing racks whereby the balancing and synchronizing assembly is caused to move in the opposite direction to the direction of movement of the power assembly with minimal losses, due to friction.
  • a still further object of the present invention is to provide an improved, balanced, free piston engine of the type described wherein the balancing and synchronizing assembly includes means for balancing the normal components of the forces created by the transmission of forces between the teeth of the pinions and the teeth of the racks so as to minimize the losses, due to friction, resulting from the utilization of the balancing and synchronizing assembly.
  • FIGURE 1 is a vertical cross-sectional view of an embodiment of the improved, balanced free piston engine of the present invention shown connected with an energy absorbing device.
  • FIGURE 2 is a vertical cross-sectional view taken along the section line 2--2 in FIGURE l.
  • FIGURE 3 is a schematic, vertical cross-sectional view of another embodiment of the improved, balanced free piston engine of the present invention shown connected with an energy absorbing device.
  • FIGURE 4 is a schematic, vertical cross-sectional view of another embodiment of the improved, balanced free piston engine of the present invention shown connected with a double-acting compressor.
  • FIGURE 5 is a schematic, vertical cross-sectional view of another embodiment of the improved, balanced free piston engine of the present invention shown connected with an outwardly compressing compressor.
  • FIGURE 6 is a schematic, vertical cross-sectional view of another embodiment of the improved, balanced free piston engine of the present invention shown connected with an outwardly compressing compressor.
  • FIGURE 7 is a schematic, vertical cross-sectional view of another embodiment of the improved, balanced free piston engine of the present invention shown connected with an inwardly compressing compressor.
  • FIGURE 8 is a schematic, vertical cross-sectional view of another embodiment of the improved, balanced free piston engine of the present invention shown connected with an outwardly compressing compressor.
  • FIGURE 1 embodiment An improved, balanced free plston engine 11 of the present invention is shown in FIGURES l and 2, and includes a power section 12 and a balancer-synchronizer section 13.
  • An energy absorbing device shown diagrammatically at 14, is spaced from the right end of the balancer-synchronizer section 13.
  • the energy absorbing device 14 may be a compressor, such as shown in FIGURES 4-8, a pump, a generator, a power saw or any other device which utilizes or absorbs reciprocatory power.
  • the power section 12 includes a cylinder housing 15 which has a power cylinder 16 formed therein.
  • a power piston 17 is positioned within the cylinder 16 for reciprocal movement therein.
  • the piston includes an outer face 18, a recessed inner face 19 and a skirted side wall 21.
  • Piston rings 22 are carried in grooves formed in the piston 17 for minimizing the leakage of gases between the cylinder 16 and the piston 17.
  • the left end 23 of the housing 15 is closed by cylinder head 24 which is bolted to the end 23 of the housing by a plurality of bolts 25.
  • a conventional fuel injector unit 27 is positioned in a central aperture 28 formed in the head 24 so that its inner end communicates with the chamber 216.
  • return energy By proper selection of the return energy, as explained below, air is compressed in combustion chamber 26 by the leftward movement of piston 17 until the air pressure and temperature in chamber 26 have been raised beyond the auto-ignition point, at which time the fuel introduced into chamber 26 through fuel injector unit 27 will effectively burn in accordance with the principles of operation of conventional diesel engines.
  • combustion may also operate in accordance with the principles of conventional spark ignition or stratied charge engine.
  • the housing 15 also includes an integral, radially outwardly extending-portion 29, which has a generally annular chamber 31 formed about the right end 32 of the cylinder 16.
  • the chamber 31 communicates with the end portion 33 of the cylinder 16 to the right of the inner face 19 of the piston 17.
  • the right end of the housing portion 29, and thus the housing 15, are fastened to a wall 34 by a plurality of bolts, two of which being shown at 35, so that the wall closes both the right end of the chamber 31 and the left end of the synchronizer section 13.
  • the wall 34 has a central aperture 36 formed therein so that the central longitudinal axes of the aperture and the cylinder 16 are coaxial. Conventional shaft seals 37 are positioned in the aperture 36, for reasons hereinafter explained.
  • the wall 34 also has a conventional one-way valve 38 positioned therein which permits air or gas in the interior of the synchronizer section 13 to pass or be drawn into chamber 31.
  • Conventional one-way valves are positioned in the housing 15 and control the ingress of air or fuel-air mixture into the chamber 31.
  • a plurality of inlet ports are formed in the housing 15 and permit the air or mixture in chamber 31 to flow into the chamber 26 of cylinder 16.
  • a plurality of exhaust ports or openings are also formed in the housing 15 and permit the combustion gases in the combustion chamber 26 to be exhausted from the cylinder 16. To insure proper blow-down, the ports 42 are positioned closer to the left end 23 of the housing 15 than the ports 41.
  • the ports 41 and 42 are arranged, relative to the combustion chamber 26, so that the chamber 26 will be properly scavenged during normal operation of the engine.
  • the piston 17 controls the iiow of air or gas through the ports 41 and 42.
  • the communication between the end portion 33 of the cylinder 16 and the chamber 31 permits the piston 17 to provide a scavenging pump action for the engine section 12.
  • air or mixture is drawn through the valve 39 into the chamber 31 and into the end portion 33 of the cylinder 16.
  • chamber 31 After combustion in chamber 26 drives or forces the piston 17 to move to the right, as shown in FIGURE 1, the piston compresses the air or mixture in the end portion 33 of the cylinder 16 and thus in the chamber 31 so that when the ports 41 and 42 are uncovered by the piston, the chamber 31 is a source of pressurized air or mixture to scavenge the chamber 26.
  • piston 17 is a part of a power assembly 43 that includes, in addition, all other main pistons (power pistons, scavenge compressor pistons, or bouncer compressor pistons) and all the other parts of the engine and the energy absorbing device which move with and are connected with the power piston 17.
  • piston 17 is fastened to the left end of a shaft 44 by means of a bolt 45.
  • the right end of the shaft 44 is connected with the left end of a double rack member 46.
  • a control piston 47 is connected to the right end of the double rack member 46.
  • a second shaft 48 is connected to the right face of the piston 47 and interconnects the piston 47 with the reciprocally movable portion of the energy absorbing device 14.
  • the power assembly 43 includes the power piston 17, the shaft 44, the double rack member 46, the control piston 47, the shaft 48, and the reciprocal movable portion of the energy absorbing device 14, together with the bolt 45, and any other fastening means utilized to interconnect the aforementioned parts, and the piston rings carried by the pistons.
  • the component parts of the power assembly 43 are described more fully hereinafter.
  • the shaft 44 interconnecting the power piston 17 and the double rack member 46, extends into the synchronizer section 13 of the engine through the aperture 36 formed in the wall 34 and is sealed by the conventional shaft seals 37 positioned in the aperture 36 so as to minimize leakage of gas or lubricant between the shaft and aperture.
  • the synchronizer section 13 includes a housing 49 which, as noted above, has its left end closed by the wall 34.
  • the same bolts 35 used to fasten the housing 15 ⁇ to the wall 34 are also used to secure the housing 49 to the wall 34.
  • An end wall 51 closes the right end of the housing 49 and is formed integrally with the side wall 52 of the housing, as shown in FIGURE 1.
  • the wall 51 could also be a separate member attached to the housing 49 ⁇ by a plurality of bolts.
  • the end wall 51 has a central, stepped aperture S3 formed therein designed to receive the flanged right end 54 of a control cylinder 55.
  • the flanged end 54 of the control cylinder 55 is arranged in the stepped aperture 53 so that the control cylinder 55 cannot be moved axially to the left, relative to the end wall 51, and so that the central longitudinal axes of the cylinders 16 and 55 are coaxial.
  • a closure wall 56 is attached to the right side of the end wall 51 by a plurality of bolts, two of which being shown at 57, so that the wall 56 covers the right end of control cylinder 55.
  • the wall 56 includes an opening 58 positioned so that its central axis is coaxial to the central axis of the aperture 53.
  • the second shaft 48 extends through the opening 58 formed in the wall 516, and a conventional shaft seal 59 is mounted in the opening 58 so as to minimize leakage of gas or lubricant between the shaft l48 and the opening 58.
  • the shaft ⁇ 48 is arranged in axial alignment with the shaft 44.
  • the control piston 47 is mounted within the control cylinder 55.
  • the length of the control cylinder 55 is slightly greater than the maximum possible length of the stroke of the piston 17, and thus the stroke of the control piston 47, so that the piston 47 will, at all times, remain in control cylinder 55.
  • Conventional piston seals 61 are positioned about the periphery of the piston 47 so as to minimize leakage between the piston 47 and control cylinder 55.
  • the right end 54 of the cylinder 55 is closed by the Wall 56 so that the control piston 47 functions as a positive bouncer piston within the cylinder 55.
  • the left end of the cylinder 55 is open to the interior of the housing 49.
  • the control piston 47 works in the cylinder 55 with a preselected compression ratio so; that sufficient return energy is obtained by supplying the bouncer chamber, i.e., the space in cylinder 55 between control piston 47 and wall 56, with gas or air of appropriate pressure, and thus to return the piston 17 to its ring position in cylinder 16 whereby combustion in chamber 26 can effectively initiate another cycle of operation of the engine.
  • control piston 47 and control cylinder 55 are designed to provide the requisite return energy required for the piston 17 so that the engine 11 does not have to depend on obtaining return energy from the energy absorbing device 14.
  • the diameter of the control piston 47 and control cylinder S may be relatively small, as compared to the diameter of the piston 17, although the actual diameters will be a function of the actual operating conditions of the engine, the compression ratio of the bouncer chamber, its charging pressure and other design parameters.
  • the engine 11 since all the parts of the power assembly 43 move in the same direction, the engine 11, would be dynamically unbalanced and thus would be subject to serious vibrational problems.
  • the engine 11 includes a balancing and synchronizing assembly 62 mounted within the housing 49.
  • the balancing and synchronizing assembly 62 is connected with the power assembly 43 through the double rack member 46.
  • the balancing and synchronizing assembly 62 also includes a pair of pinions 63 and 64 which are mounted for rotation about fixed axes on a pair of shafts 65 and 66, respectively.
  • the ends of the shafts 65 and 66 are supported by a pair of fixed side plates 67 and 68, which are positioned on opposite sides of the double rack member 46.
  • One end of each of the plates 67 and 68 is secured to the right face of the wall member 34 and the other ends 69 thereof project to the right from the wall 34 towards the end wall 51 of the housing 49.
  • the plates 67 and 68 are spaced an equidistance from the double rack member 46 so that the member 46 can slide freely between the plates 67 and 68, and are positioned so that the plates are substantially parallel to each other and to the central axis of the power assembly 43.
  • the shafts -65 and 66 are supported by the plates 67 and 68 approximately midway between the wall 34 and the ends 69 of the plates and are positioned vertically on opposite sides of the longitudinal central axis of the double rack member 46 and equidistant from the member 46, with the longitudinal central axes of the shafts ⁇ 65 and 66 being arranged at 90 to the longitudinal central axes of the power assembly 43.
  • the distance between the plates 67 and 68 is sufficient so that the pinions 63 and 64 can rotate freely between the plates.
  • the double rack member 46 includes upper and lower racks 71 and 72 which are formed in back-to-back fashion so that the teeth thereof project substantially radially outwardly from the member 46.
  • the teeth of the racks 71 and 72 are arranged so that there is always engagement -between the teeth of the racks 71 and 72 and the teeth of the pinions 63 and 64, respectively, whereby reciprocatory movement of the power assembly, and thus the racks 71 and 72, causes corresponding rotary movement of the pinions 63 and 64.
  • the balancing and synchronizing assembly 62 includes a pair of movable wall members 73 and 74 which are pO- sitioned adjacent to and parallel with the lxed side plates 67 and 68, respectively, with the movable members 73 and 74 being positioned a greater distance from the double rack member 46 than the plates 67 and 68 so that the movable members 73 and 74 can slide freely with respect to the fixed plates 67 and 68.
  • a pair of racks 75 Iand 76 are carried by and positioned between the upper and lower ends of the movable wall members 73 and 74, as shown in FIGURE 2.
  • a plurality of pins or rivets extend through the racks 75 and 76 and the ends of the movable members 73 and 74 and are used to secure the racks 75 and 76 to the movable members 73 and 74.
  • the racks 75 and 76 are positioned so that the teeth thereof project toward the teeth of the racks 71 and 72, respectively, i.e., project substantially radially inwardly relative to the double rack member 46, and engage the pinions 63 and 64, respectively, diametrically opposite the points of engagement between the teeth of the pinions 63 and 64 and the racks 71 and 72, respectively.
  • the balancing and synchronizing assembly 62 can reciprocate freely with respect to the housing 49 and to any relatively xed member therein and with respect to any parts of the power assembly 43.
  • the racks 75 and 76 are secured together by the movable members 73 and 74 so as to prevent relative movement therebetween and because the racks 71 and 72 are integrally formed, in a back-to-back relationship, on the double rack member 46, the normal components of the forces created by the transmission of forces between the teeth of the racks and pinions are balanced.
  • This arrangement of the racks and pinions eliminates a major cause of frictional losses and minimizes the energy losses, due to friction, resulting from the transfer of forces between the balancing and synchronizing assembly 62 and the power assembly 43. Furthermore, frictional losses and dynamic loading of the gear teeth, due to manufacturing errors, are further reduced by the fact that the racks 71 and 72 tend to float between, and the racks 75 and 76 tend to oat on the pinions 63 and 64 and are selfaligning in that they inherently seek a position, relative to the pinions 63 and 64, in which the dynamic forces created by the engagement between the teeth of the racks 71, 72, 75 and 76 and the pinions 63 and 64 are minimized.
  • the product of the sum of the weight associated to move with the counter-balancing movable weight of the balancing and synchronizing assembly 62 i.e., the weight of the movable members 73 and 74 and the pins 77, plus the weight of the racks 75 and 76 times the distance the counter-balancing weight of assembly 62 moves during a stroke of the engine must be equal to the product of the sum of the weights associated to move with the power assembly 43 times the length of the corresponding stroke of the assembly 43 in the opposite direction to the motion of the counterbalancing weight of the assembly 62.
  • the engine 11 is suitable for use with various diiferent energy absorbing devices, which, of course, means that the weight of the element of the energy absorbing device 14 which is attached to and carried by the end of the shaft 48 may vary depending on what type of energy absorbing device is being driven by the engine.
  • the movable members 73 and 74 have been designed so that they can be readily removed and replaced by movable wall members of different weights so that the counter-balancing weight of the balancing and synchronizing assembly 62 may be easily varied without affecting the structure or operation of the engine.
  • the unique structure and structural arrangement of the engine permits the total length of the engine to be substantially equal to four times the swept stroke of the piston 17, plus the length required for the energy absorbing device 14.
  • combustion occurs in chamber 26 near the top-dead-center position 17, i.e., when the piston 17 has moved to its leftmost operating position, and such combustion, together with any other energy in the engine 11 and/or the device 14 available to support the rightward movement of the power assembly 43, causes the piston 17, and thus the rest of the power assembly 43 including the connecting part of the balancing and synchronizing assembly 62, rack member 46, to be moved translationally to the right with respect to the housing.
  • the counter-balancing weight of the balancing and synchronizing assembly 62 are translationally moved to the left in housing 49.
  • the counter-balancing weight of the balancing and synchronizing assembly 62 including the racks 75 and 76, translationally moves to the right.
  • Theengine 78 shown schematically in FIGURE 3, has a power section 79 and synchronizer section 81 which are substantially identical, in structure and mode of operation, to sections 12 and 13, respectively, of engine 11, except that the synchronizer section 81 does not include a control piston and cylinder, such as the piston 47 and cylinder 5,5 utilized in section 13 of engine 11.
  • the second shaft 48 directly interconnects the right end of double rack member 46 with the reciprocally movable portion of the energy absorbing device 14.
  • a control cylinder 82 is positioned between the right end wall 83 of the power section 79 and the left end wall 84 of the synchronized section 81.
  • control cylinder 82 may be an integral part of the housing 49.
  • a control piston 85 is positioned for reciprocal movement in the control cylinder 82.
  • the left face 86 of the control piston 85 is connected with the face 19 of the piston 17 by a shaft 87 which extends through a sealed aperture in the wall 83.
  • the right face 88 of the control piston 85 is connected with the left end of the double rack member 46 by a shaft 89 which extends through a sealed aperture in the wall 84.
  • a first chamber 91 is defined in the cylinder 82 between the wall 83 and the face 86 of the piston 85, and a second chamber 92 is defined in cylinder 82 between wall 84 and face 88 of the piston 85.
  • the chambers 91 and 92 may function as bouncer chambers or one of the chambers may be utilized as a scavenge pump which may be used to supplement or instead of the scavenge pump action provided by piston 17.
  • engine 78 permits a larger diameter control piston to be utilized which, in turn, ermits lower pressure levels to be used in the chambers 91 and 92.
  • the provision of two bounced chambers permits relative exibility in controlling the operation of the engine whereby thermodynamic balance of the engine can be achieved through a wide range of design and operating parameters.
  • the arrangement of engine 78 minimizes the chances that the lubricant used in the power section 79 will contaminate or be mixed with the lubricant in the synchronizer section 81, and vice versa, since the pressure in the chambers 91 and/or 92 can be kept higher than the pressures in the power and synchronizer sections 79 and 81.
  • FIGURE 4 embodiment-The engine 93 shown schematically in FIGURE 4, includes power section 94 and a synchronized section 95 substantially identical in structure tothe power section and synchronizer sections 12 and 13, respectively, of the engine 11.
  • the engine 93 differs from engine 11 in that in engine 93, the energy absorbing device driven by the engine is a double acting compressor 96 positioned adjacent to the right end wall 51 of the synchronizer section 95.
  • the compressor 96 includes a compressor piston 97 which is attached to the end of the shaft 48 for reciprocal movement therewith within a compressor cylinder 98, which, in FIGURE 3, is formed as an integral part of the housing 49.
  • Conventional compressor inlet and outlet valves permit the ingress and egress of air or gas into and out of the compressor chamber 102 formed between the left end wall 51 of the section 96 and the inner face 103 of the piston 97.
  • conventional compressor inlet and outlet valves two of which being shown schematically at 104 and 105, permit the ingress and egress of air or gas into and ⁇ out of the compressor chamber 106 formed between the outer face 107 of the piston 97 and the right end wall 108 of the compressor housing 98.
  • a passage 109 is formed in the end wall S1 and permits communication between the closed end of the control cylinder 55 and the atmosphere.
  • One-way valve 111 is positioned within the passage 109 so as to permit air or gas to flow only into the closed end of the cylinder 5S.
  • the passage 109 is utilized in engine 93 to insure that there is always sufficient air or gas within the closed end of cylinder 55 so that the control piston 47 can peiform its intended function.
  • the passage 109 could :be connected with a source of air or gas under pressure, rather than the atmosphere, if desired.
  • the clearance volume of the chamber 106 assists in providing return energy for the continuous operation of the engine, and the clearance volume in the chamber 102 assists the rightward movement of the power assembly 43, including the compressor piston 97. Otherwise the operation of the engine 93 is identical to that of engine 11.
  • FIGURE 5 embodiment- Engine 112 is substantially identical, in structure, to engine 93 in that the power and synchronizer sections 113 and 114 are identical in structure to sections 94 and 95 and the energy absorbing device is a compressor 115.
  • compressor 115 differs from compressor 96 in that compressor 115 is a single acting, outwardly compressing compressor.
  • a chamber 116 formed between the end wall 51 of the section 114 and the inner face 103 of the piston 97 functions as a negative bouncer chamber.
  • One-way valves 117 and 118 are positioned in passages in the end wall 51 and permit the pressurized air or gas in chamber 116 to flow into the interior of the synchronizer section 114 and into the closed end of cylinder 55, respectively, when the pressure of the air or gas in chamber 116 exceeds a preselected value as a result of the movement of the piston 97 to the left, within compressor cylinder 98.
  • a passage and valve arrangement such as passage 109 and valve 111 used in engine 93, could be used in engine 112 in place of valves 117 and/or 118. Otherwise, the operation of engine 112 is substantially identical to that of engine 93.
  • FIGURE 6 embodiment.-Engine 119 is substantially identical, ⁇ in structure and mode of operation, to engine 112 with the only significant structural difference being that the control piston 121 and control cylinder 122 of engine 119 are not positioned within the synchronizel section 123 of engine 119, as are piston 47 and cylinder 55 in engine 112, but rather are positioned to the right of the end wall 108 of the outwardly compressing compressor 124.
  • control cylinder 122 consisting of an annular side wall 125 and a closed end wall 126, is secured to the end wall 108 of the compressor 124.
  • a shaft 127 extends through a sealed aperture 128 in the wall 108 and connects the control piston 121 to the compressor piston 97 so that the piston 121 moves with piston 97, and thus with the power assembly 43 in the engine 119.
  • the control piston 121 and the control cylinder 122 are arranged so that the longitudinal central axes of the piston 121, cylinder 122, and the power assembly 43 of the engine 119 are coaxial.
  • a positive bouncer chamber 129 is defined in cylinder 122 between the outer face 131 of the piston 121 and the end wall 126.
  • a negative bouncer chamber 132 is defined in the cylinder 122 between the inner face 133 of the piston 121 and the wall 108.
  • One-way valve 134 is positioned in the side wall 125 of the cylinder 122 to permit the air or gas in chamber 132 to escape to the atmosphere upon the air or gas reaching a predetermined pressure.
  • One-way valve 135 is positioned in the end wall 126 of the cylinder 122 to permit air or gas to be drawn into the chamber 129, either from the atmosphere or from a source of pressurized air or gas, not shown.
  • a groove in the side wall 125 of cylinder 122 could be utilized instead of the valves 134 and/or 135. The groove would permit communication, around the periphery of the piston 121, between the chambers 129 and 132 during a portion of the stroke of the piston.
  • One of the advantages of positioning the control piston and the cylinder, as described in engine 119, is that it facilitates the maintenance and repair thereof.
  • -Engine 136 is generally similar, in structure and mode of operation, to engines 93, 112 and 119 except that the engine 136 does not utilize a separate control piston and control cylinder and that the energy absorbing device is an inwardly compressing compressor 137. More specifically, power section 138 and synchronizer section 139 of engine 136 are identical, in structure and mode of operation, to sections 94 and 95, respectively, of engine 93 with, of course, the exception that section 139 does not include a separate control piston and cylinder, such as piston 47 and cylinder 55 in engine 93.
  • the compressor 137 includes a positive bouncer chamber 141 formed between the outer face 142 of piston 143 and the end wall 108.
  • the piston 143 performs both as the compressor piston and the separate control piston, such as pistons 47 and 121, were utilized in the engines 93, 112 and 119, i.e., to provide necessary return energy for the power assembly and to provide a means for controlling the operation of the engine.
  • engine 136 One of the advantages of engine 136 is the great simplicity of its structure. Engines of this type are particularly suitable for constant load applications.
  • FIGURE 8 embodiment.--Engine 144 is generally similar, in structure, to engine 136 in that it does not utilize a separate control piston and control cylinder arrangement. However, engine 144 is connected with the drives and outwardly compressing compressor 145, as ⁇ contrasted with the inwardly compressing compressor 137 of engine 136.
  • the power section 146 and synchronizer section 147 of engine 144 are identical, in structure and mode of operation, to the sections 138 and 139, respectively, of engine 136.
  • the compressor includes a negative bouncer chamber 148 formed between the end wall 51 of the synchronizer section 147 and the inner face 149 of the piston 151.
  • the piston 151 like piston 143, the piston 151, alone, performs the functions of compressor piston and the separate control piston utilized in engines 93, 112 and 119.
  • a one-way valve 152 is positioned in the cylinder 98 to permit air or gas to be drawn into the chamber 148.
  • valve 152 may be reversed so as to discharge air or gas from chamber 148 if that is the desired control effect.
  • main piston as used herein is meant to include only those pistons (power pistons, scavenge compressor pistons, 0r bouncer compressor pistons) which perform the main or principal operating functions of the free piston engines of the present invention.
  • the main pistons are pistons 17 and 47 in engines 11, 93 and 112; the main pistons are pistons 17 and 85 in engine 78; the main pistons are pistons 17 and 121 in engine 19; and the main piston is piston 117 in engines 136 and 144.
  • main pistons should be distinguished from so-called auxiliary pistons, such as oil pump pistons, water pump pistons, fuel pump pistons and the like, which may also be used in or on engines of the present invention and which may move either with or in the opposite direction to the main pistons during operation of the engines of the present invention.
  • auxiliary pistons such as oil pump pistons, water pump pistons, fuel pump pistons and the like
  • an auxiliary oil pump piston could be attached to and moved with the walls 73, 74 of the synchronizing and balancing assembly 62, in the opposite direction to the main pistons
  • an auxiliary oil pump piston could be attached to and moved with power assembly 43, in the same direction as the main pistons.
  • the weight of any auxiliary piston could be considered as being a part of the movable weight of the balancing and synchronizing assembly or the power assembly, as the case may be, for the purpose of balancing the engine.
  • main pistons as used herein should be distinguished from the term 13 power assembly.
  • power assembly includes the main pistons, the movable member of the energy absorbing device, and the means for connecting the main pistons together and for interconnecting the mainpistons with the movable member of the energy absorbing device.
  • theengines specifically described herein could be modified without affecting the principles of the present invention'.
  • more than one power piston 17 or power section 12 could be utilized with one engine.
  • other types of gears and/or linkages could be utilized to interconnect the power assembly 43 and the balancing and synchronizing assembly 62.
  • the length of the stroke of assembly 62 couldbe different than the length of the stroke of the assembly 43.
  • the engine shown in FIGURE 3 could be'modied by positioning the control cylinder 82 and the control piston 85 between the synchronizer section 81 and the energy absorbing device 14.
  • An improved, balanced free piston engine adapted to drive a variety of energy absorbing devices that include reciprocally movable input means
  • the improved engine comprising: housing means including a power cylinder; a power piston mounted in said power cylinder for reciprocal movement therein a direction substantially parallel to the longitudinal central axis of said power cylinder and defining an internal combustion chamber with said power cylinder; power assembly means including the power piston and means connected with the power piston and adapted to be connected with the movable means of an energy absorbing device to be driven by the engine, the components of the power assembly means, and the movable means of an energy absorbing device, being reciprocally movable together as a unit; means, associated with the power assembly means, for returning the power piston to its top-dead-center position in the power cylinder; and balancing and synchronizing means including a counter-balancing means mounted for translational movement with respect to the housing adjacent the power assembly means and between the power cylinder and the movable means of an energy absorbing device, the counter-balancing means having a pre
  • the connecting means of the power assembly means includes means having first and second racks formed thereon, in back-to-back relationship, intermediate its ends; wherein said counter-balancing means of the balancing andsynchronizing means includes third and fourth racks mounted thereon with the first and third racks being positioned so that the teeth of the third rack are facing the teeth of the rst rack and the second and fourth racks being positioned so that the teeth of the fourth rack are facing the teeth of the second rack; wherein said interconnecting means includes rst and second gears mounted for rotation on the housing between the rst and third racks and the second and fourth racks, respectively, so that the teeth of the gears engage the teeth of the adjacent racks; wherein said balancing and synchronizing means is mounted so that there is no substantial sliding contact between the housing means and said balancing and synchronizing means; and wherein frame means interconnects the third and fourth racks so that there is no relative movement therebetween and so that the normal components of the forces created
  • the return means includes a housing having a control cylinder formed therein with the central longitudinal axis of said control cylinder being coaxial with the central longitudinal axis of the connecting means, and a control piston connected with the connecting means for reciprocation with the connecting means within said control cylinder.
  • the connecting means of the power assembly means includes a shaft means; wherein the control piston is connected with and carried by the shaft means, intermediate the ends of the shaft means, and is separate from the movable means of an energy absorbing device; and wherein a wall closes the end of said control cylinder remote from the power piston, with the other end of said control cylinder being open.
  • the connecting means of the power assembly means includes a shaft means; wherein one end of the shaft means is connected ⁇ with the power piston; wherein the energy absorbing device includes a compressor which comprises: a compressor housing including a compressor cylinder; a compressor piston connected with the other end of the shaft means and mounted for reciprocal movement in said compressor cylinder, the cornpressor piston and compressor cylinder defining at least one compressor chamber in said compressor cylinder; and compressor inlet and outlet valve means mounted in the compressor housing for permitting the ingress and egress of gas into and from said compressor chamber.
  • said shaft means has first and second racks mounted thereon, in back-to-back relationship, intermediate its ends; and wherein said counter-balancing means of the balancing and synchronizing means includes third and fourth rack means mounted thereon with the first and third racks being positioned so that the teeth of the third rack are facing the teeth of the first rack with the second and fourth racks being positioned so that the teeth of the fourth rack are facing the teeth of the second rack; wherein said interconnecting means includes first and second gears mounted for rotation on the housing between the first and third racks and the second and fourth racks, respectively, so that the teeth of the gears engage the teeth of the adjacent racks; wherein said balancing and synchronizing means is mounted so that there is no substantial sliding contact between the housing means and said balancing and sychronizing means; and wherein frame means interconnects the third and fourth racks so that there is no relative movement therebetween and so that the normal components of the forces created by the transmission of forces between the teeth of the rack
  • the return means includes a control cylinder arranged so that the central longitudinal axis of said control cylinder is coaxial with the central longitudinal axis of the shaft means and a control piston connected with the shaft means for reciprocation with the shaft means within said control cylinder.
  • control piston is connected with and carried by the shaft means, intermediate the ends of the shaft means, and is separate from the movable means of an energy absorbing device; and wherein a wall closes the end of said control cylinder remote from the power piston, with the other end of said control cylinder being open.
  • control means is positioned between the balancing and synchronizing means and the compressor and is arranged whereby the pressure therein prevents oil from the balancing and synchronizing means from leaking into the compressor.
US746541A 1968-07-22 1968-07-22 Balanced free piston engine Expired - Lifetime US3501088A (en)

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US (1) US3501088A (fr)
JP (1) JPS4935643B1 (fr)
CH (1) CH549153A (fr)
DD (1) DD98727A6 (fr)
DE (1) DE1937053A1 (fr)
FR (1) FR2013491A6 (fr)
GB (1) GB1285952A (fr)
IE (1) IE33649B1 (fr)
IL (1) IL32670A0 (fr)
NL (1) NL6911203A (fr)
SE (1) SE351264B (fr)
SU (1) SU550128A3 (fr)
ZA (1) ZA695189B (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2407028A1 (de) * 1973-02-16 1974-08-22 Anton Braun Freikolbenmaschine
DE2419581A1 (de) * 1973-04-30 1974-11-21 Anton Braun Kolbenmaschine
US4568251A (en) * 1982-05-11 1986-02-04 Anton Braun Cyclic speed control apparatus in variable stroke machines
WO1987002423A1 (fr) * 1985-10-10 1987-04-23 Anton Braun Appareil de reglage de la vitesse cyclique des machines a course variable
US4782796A (en) * 1986-07-17 1988-11-08 Anton Braun Unsymmetrical free piston engine
WO1989000245A1 (fr) * 1985-02-26 1989-01-12 Anton Braun Chambres de rebond pour compresseurs de moteurs lineaires multi-cylindres
DE2953905C2 (fr) * 1979-11-28 1992-05-14 Anton Minneapolis Minn. Us Braun
US6749408B1 (en) * 1999-10-18 2004-06-15 Engineering & Drilling Machinery As Piston pump
US20170016387A1 (en) * 2015-07-17 2017-01-19 Tonand Inc. Internal Combustion Engine with Integrated Air Compressor
US20230055142A1 (en) * 2021-08-18 2023-02-23 DRiV Automotive Inc. Damper assembly and syringe pump

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2660970A1 (fr) * 1990-04-12 1991-10-18 Minoru Rech Avancee I Systeme de moteur a piston libre.
WO1993001393A1 (fr) * 1991-07-10 1993-01-21 Wbm Pty. Ltd. Commande du mouvement d'un piston dans un entrainement a piston libre
CN100419213C (zh) * 2005-01-21 2008-09-17 刘战国 齿条齿轮机构传动式发动机
AT508410B1 (de) * 2009-07-13 2013-08-15 Ve Vienna Engineering Forschungs Und Entwicklungs Gmbh Schwingungskompensierter freikolbenmotor
FR2963805A1 (fr) * 2010-08-12 2012-02-17 Const Metalliques Et Mecaniques E C M M Et Dispositif de transmission d'effort pour un moteur a piston et moteur a piston comprenant un tel dispositif
CZ2012891A3 (cs) * 2012-12-11 2014-03-05 Jan Novotný Pohonná jednotka zahrnující spalovací motor, pístové hydraulické čerpadlo a hydrogenerátor

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2027877A (en) * 1932-02-23 1936-01-14 Pescara Raul Pateras Motor compressor
US2925072A (en) * 1953-04-15 1960-02-16 Schmidt Paul Power plant with one cylinder and airborne piston

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2027877A (en) * 1932-02-23 1936-01-14 Pescara Raul Pateras Motor compressor
US2925072A (en) * 1953-04-15 1960-02-16 Schmidt Paul Power plant with one cylinder and airborne piston

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2407028A1 (de) * 1973-02-16 1974-08-22 Anton Braun Freikolbenmaschine
DE2419581A1 (de) * 1973-04-30 1974-11-21 Anton Braun Kolbenmaschine
DE2953905C2 (fr) * 1979-11-28 1992-05-14 Anton Minneapolis Minn. Us Braun
US4568251A (en) * 1982-05-11 1986-02-04 Anton Braun Cyclic speed control apparatus in variable stroke machines
WO1989000245A1 (fr) * 1985-02-26 1989-01-12 Anton Braun Chambres de rebond pour compresseurs de moteurs lineaires multi-cylindres
WO1987002423A1 (fr) * 1985-10-10 1987-04-23 Anton Braun Appareil de reglage de la vitesse cyclique des machines a course variable
US4782796A (en) * 1986-07-17 1988-11-08 Anton Braun Unsymmetrical free piston engine
WO1989012735A1 (fr) * 1986-07-17 1989-12-28 Anton Braun Moteur a piston libre asymetrique
US6749408B1 (en) * 1999-10-18 2004-06-15 Engineering & Drilling Machinery As Piston pump
US20170016387A1 (en) * 2015-07-17 2017-01-19 Tonand Inc. Internal Combustion Engine with Integrated Air Compressor
US20230055142A1 (en) * 2021-08-18 2023-02-23 DRiV Automotive Inc. Damper assembly and syringe pump

Also Published As

Publication number Publication date
ZA695189B (en) 1971-04-28
DD98727A6 (fr) 1973-07-12
NL6911203A (fr) 1970-01-26
GB1285952A (en) 1972-08-16
FR2013491A6 (fr) 1970-04-03
SE351264B (fr) 1972-11-20
CH549153A (de) 1974-05-15
SU550128A3 (ru) 1977-03-05
IL32670A0 (en) 1969-09-25
DE1937053A1 (de) 1970-11-19
IE33649L (en) 1970-01-22
JPS4935643B1 (fr) 1974-09-25
IE33649B1 (en) 1974-09-18

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