EP0246227B1 - Rotationsgeschwindigkeitskontrolleinrichtung für maschinen mit veränderlichem hub - Google Patents

Rotationsgeschwindigkeitskontrolleinrichtung für maschinen mit veränderlichem hub Download PDF

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Publication number
EP0246227B1
EP0246227B1 EP85905954A EP85905954A EP0246227B1 EP 0246227 B1 EP0246227 B1 EP 0246227B1 EP 85905954 A EP85905954 A EP 85905954A EP 85905954 A EP85905954 A EP 85905954A EP 0246227 B1 EP0246227 B1 EP 0246227B1
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Prior art keywords
bounce
piston
chamber
engine
pair
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French (fr)
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EP0246227A1 (de
EP0246227A4 (de
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Anton Braun
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/20—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the driving speed
    • 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
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads

Definitions

  • the invention relates to a free piston engine according to US-A-3501088, in particular as depicted in fig. 3
  • a free piston engine compressor In devices running with their natural frequency, such as free piston machines, their frequency or cyclic speed is a function of the energy input portion and energy output portion of the device, such as the power piston energy input portion and compressor piston energy output portion of a free piston engine compressor.
  • the speed of such an engine compressor will vary in a given fixed natural relationship with variations of compressor volumetric flow and compressor intake pressures and/or discharge pressures.
  • a greater volumetric flow rate is typically required at the lower intake and discharge pressures involved in operating at low ambient temperatures.
  • even at maximum piston stroke not only is the volumetric output per stroke reduced by the lower intake pressure, but the rate of volumetric flow is further substantially reduced by the lower natural frequency which the engine compressor will assume under the influence of both the lower intake and discharge pressures.
  • This invention involves the recognition of a need for a free piston engine which could vary engine speed over a very wide range and for selective use with any one of a number of different types of energy absorbing devices and with rather simple control elements.
  • the desired wide control range for such an engine can be achieved by use of specially located and constructed bounce chambers, and moreover by means of lower pressures in such specially located bounce chambers capable of operating without a pressurized reservoir of high pressure bounce control fluid.
  • the energy absorbing device involves a compressor or heat pump
  • such a combination is capable of operating the control section with a separate fluid from that of the working compressor or heat pump section, and with less complex control elements than would otherwise be needed.
  • a vibration-free compressor with an engine speed controller and a contamination-free compressor for compressing freon or the like.
  • the present invention accordingly includes a speed control device that allows changing the speed of a free piston engine compressor or similar energy absorbing device (EAD) within wide margins, or maintaining the speed of a free piston engine-driven electric generator or alternator within very narrow margins, independent from conditions of the energy input section or the energy absorbing section which may, in the case of the generator require a very wide range of control to maintain a substantially constant speed, and in the case of compressor or heat pump EAD's, require substantial speed changes needed, for example, as compressor demand changes from low volume-high pressure to high volume-low pressure operation, and which in both instances is the very opposite of what the engine would do or the manner in which it would respond, if it did not include the control means and the structural arrangement and relative location of bounce chambers of this invention.
  • EAD energy absorbing device
  • the present invention thus provides a variable stroke free piston engine which can be selectively connected to any one of several different energy absorbing devices, and in which the engine speed (frequency of reciprocation) can be controlled and adjusted in response to an extremely broad range of changes in the demands on a specific energy absorbing device (EAD) connected to and driven by the piston engine.
  • EAD specific energy absorbing device
  • the desired range of control forces can be effectively provided by adjustment of the working pressures in two bounce chambers specifically located at an intermediate position along the axis of a reciprocating piston rod assembly in a free piston engine which has a power piston at one end and a connecting means at the other end for driving connection with a movable member of the selected energy absorbing device.
  • a bounce piston unit having oppositely directed and oppositely acting bounce piston faces compresses the air or gas in one bounce chamber during a power piston expansion stroke of the piston rod assembly from the power piston end toward the EAD connection end and then compresses the air or gas in the other bounce chamber during the return (i,e. compression) stroke of the power piston.
  • the invention provides a negative first bounce chamber at a relative location between one bounce piston working face and the power piston end of the piston rod assembly, and a positive second bounce chamber at a relative location between the other bounce piston working face and the EAD end of the piston rod assembly.
  • the first and second bounce chambers are most efficiently and effectively provided by a single bounce cylinder in which opposite faces of only one double-acting bounce piston are used to separate the two bounce chambers, thus eliminating half of the frictional losses that would be developed between the usual piston rings and the inner bounce cylinder wall surfaces, if the bounce piston unit had two piston members, and also minimizing the net pressure differentials between the two chambers separated by such a single bounce piston.
  • the invention further provides control means for such machines which includes at least one pair of bounce chamber pressure control openings (one opening in each bounce chamber), and at least one pair of variably (e.g., incrementally or intermittently) adjustable bounce pressure control valves (one for each of the bounce chamber control openings of said pair).
  • Each control valve of said one pair when opened partially, fully, incrementally or intermittently, provides for direct connection of the bounce chamber, through its bounce chamber pressure control opening, to the ambient atmospheric air outside the bounce cylinder.
  • Each of said controls valves is further connected to its respective bounce chamber control opening for variably and substantially simultaneously adjusting each of the variable pressure control valves of said pair and thereby similarly changing (i.e. in the same direction, both upwardly or both downwardly) the respective bounce chamber working pressures in response to changes in the demands on the particular EAD involved.
  • control valves of said one pair are located and arranged to adjust the maximum outlet pressures for each bounce chamber. It is also possible to arrange such valves to adjust the minimum inlet pressures for each bounce chamber, or even to provide two such control valve pairs, one pair for inlet pressures and one pair for outlet pressures.
  • the invention also provides for the further combination of means for relatively adjusting at least one pair of the respective variable pressure control valves in opposite senses, thereby making it possible to shift the successive top dead center positions of the power piston in its power cylinder in response to a signal from an engine efficiency sensing means which indicates relative efficiency or inefficiency of combustion and operation of the engine.
  • a signal can be made available, for example, from a knock sensor of the type responsive to and indicative of incipient knocking in the power cylinder, i.e. at a top dead center position of the power piston just short of that at which actual knocking might occur.
  • a knock-sensing means is shown, for exapmle, in my prior United States patent no. 3,853,100.
  • the cyclic speed of the reciprocating assembly varies closely with the square root of the total mean or average force driving the reciprocating assembly.
  • the cyclic speed can be substantially altered by raising or lowering the pressures in each of the bounce chambers, since the component forces driving the bounce piston are a product of their respective piston areas and the corresponding pressures acting on them.
  • mean effective pressures of the engine or power cylinder it can be shown that to double the cyclic engine speed the bounce pressures PB will have to be increased by approximately three times the product of the mean effective engine pressure MEP times the ratio of the power piston area AE over the bounce piston area AB, i.e. PB is nearly equal to 3 MEP (AE/AB).
  • a further advantage in having the bounce chamber of the speed control section independent of the selected energy absorbing device, such as the compressor piston of a compressor or heat pump, is that the maximum pressures in the bounce chambers of the speed control section of the present invention can be kept to a minimum.
  • the energy absorbing device to be removably attached to the outer end of the engine power assembly includes a compressor piston in a compressor cylinder
  • this compressor cylinder can also be constructed to provide a further (third) bounce chamber between the outer end of the engine and the compressor piston.
  • Such a third bounce chamber can be used at the back side of the compressor piston in such a way as to help keep the bounce pressures in the two speed control bounce chambers of the engine substantially equal and thus to their lowest possible maximum cylinder pressure.
  • one or both chambers of the speed control bouncer can be made to temporarily act as compressors until the refrigerant compressor is able to assume the power input from the driver or power section. Similar situations exist, for example, in free piston engine electric generators which could be similarly controlled by the speed control bouncer.
  • the invention is thus not merely in the use or control of bounce piston control pressures alone or the use of two bounce chambers as a control. It also involves the specific relative location of bounce piston faces and bounce chambers to provide adequate control piston areas without blocking or limiting the area for the EAD connection end of the engine. This further makes possible the provision and use of an optimum number of piston faces and an optimum assignment of power and control functions to such piston faces, including the allocation of speed control functions to the specifically located oppositely-acting bounce chambers and bounce piston faces and the possibility of using ambient atmospheric air as a control fluid to provide a wide range of control in a manner compatible with the selective attachment of different energy absorbing devices.
  • the reference numeral 10 designates a free-piston engine power cylinder which has a fuel inlet 11, an air inlet 12, an exhaust outlet 13 in a power section 10p of the cylinder, and conventional air inlet and outlet check valves in a scavenging air section 10s thereof.
  • a power piston 15 is connected to a bounce bounce piston 16 by a piston rod 17 extending through a bearing 14 in a wall between said pistons. Scavenging air may be suitably delivered from 10s to 10p through a conduit 12a by using the inner face (i.e. the right hand face, as viewed in Fig. 1) of the power piston 15 as a scavenging piston during the expansion stroke of piston 15 toward the right.
  • a double-acting bounce piston 16 is located in a common bounce cylinder 18 having piston rod bearings 19 and 20 and air flow inlet openings 21 and 22, one on each side of piston 16. Piston 16 divides cylinder 18 into a negative first bounce chamber 18n and a positive second bounce chamber 18p, respectively.
  • the respective bounce chambers are provided with pressure control means which include a pair of pressure control inlet openings 21 and 22, one in each bounce chamber, and a pair of pressure control outlet openings 25 and 26, one in each bounce chamber.
  • An adjustable pressure-actuated inlet control or check valve 23 is located in opening 21, and a similar or identical adjustable check valve 24 is located in opening 22.
  • Outlets 25 and 26 are provided with variably adjustable pressure-actuated high pressure outlet control valves 27 and 28 to control air flow out of the cylinder and thereby the maximum working pressures and the bounce energy in the bounce chambers.
  • An energy absorbing device illustrated as a compressor cylinder 29 at the outer end of the engine,has an outlet opening 30 with a check valve 31 therein, an inlet opening 32 with a check valve 33 therein and a compressor piston 34 therein.
  • Piston 34 is connected to bounce piston 16 by a piston rod 35, preferably through a bellows seal 36 at the other end of cylinder 29.
  • Inlet valves 23 and 24 have tension springs for normally closing the valve elements therein, each being manually adjustable to change the pressure drop across each valve. In the simplest case, where the clearance volume in each of the two bounce chambers is equal, the pressure drop across the valves would be simultaneously lowered or raised to control the cyclic speed of the machine.
  • the boxes 23a and 24a have conventional manually adjustable means therein for adjustably changing the spring tension. To change the spring tension automatically, the adjustable means may be actuated by a sensor responsive to changes in demands on the selected energy absorbing device, such as the temperature of a space to be heated or the engine speed required for a specific application. For the compressor of Fig.
  • a conventional speed responsive or temperature responsive sensor 37 may be connected to controls 23a and 24a through a suitable mechanism 38.
  • the sensor may be responsive to compressor flow, changes in temperature needs and/or cyclic speed requirements of the engine, or to combinations thereof, or to other suitable control signals.
  • the sensing means itself may be of a known type but is connected through a mechanism 38 which variably and substantially simultaneously and similarly (i.e. in the same direction) adjusts each of the variable pressure control valves 23 and 24 and thereby similarly changes the respective working pressures in bounce chambers 18n and 18p. Suitable mechanisms are further described herein in connection with Figs. 10 and 11.
  • the present control means includes bleed means providing a substantially continuously open limited leakage path of small effective cross section primarily out of each bounce chamber. Such leakage paths are provided, for example, by the small bleed openings 18a and 18b in Fig. 1.
  • valves 23,24,27 and 28 are located and constructed for direct connection between the corresponding bounce chambers and ambient atmospheric air outside the bounce cylinder.
  • Non-pressure-actuated valves may also be provided in series with or in lieu of the valves 23 and 24.
  • the outlet valves 27 and 28 have compression springs therein for normally holding the valves closed. They likewise have conventional means 25a and 25b for adjusting their compression. Automatic means can be provided as shown in Fig. 11 to adjust these valves in a manner similar to that for valves 23 and 24. Such adjustment may be in addition to or in place of the means for valves 23 and 24. In many machines it is most effective to provide such automatic variable adjustment and control for the outlet valves 27 and 28 only, and insure proper functioning by providing any required flow into the bounce chambers through preset inlet check valves 23 and 24, in which case the small bleed openings 18a and 18b can be eliminated.
  • combustion of fuel in the chmaber to the left of piston 15 causes the power assembly (power piston 15, bounce piston 16 and piston rod 17,35) and attached compressor piston 34 to move to the right.
  • This causes a build-up of pressures in the scavenge air chamber 10s to the right of piston 15, in the positive bounce chamber 18p at the right face of piston 16 and in the compression chamber 29c to the right of piston 34.
  • a reduced pressure occurs in the negative bounce chamber 18n at the left face of the bounce piston 16.
  • the chamber 29a to the left of compressor piston 34 may be exposed to ambient atmosphere, but should preferably be constructed to provide a third bounce chamber between the compressor chamber and bounce chamber 18p for establishing the basic work balance between the work in the power section and the work in the compressor section. The energy stored in the bounce chambers is regained by their use to return the power assembly and compressor piston to their left hand positions for the next power stroke.
  • the work diagrams have the power stroke lines shown as solid lines while the return lines are shown as broken lines. It can thus be seen that the net work per cycles of each unit of the machine is the difference in the areas under each of the lines.
  • the valves in the bouncer unit may be adjusted temporarily to cause the bouncer to act as a compressor and, thereby, temporarily increase the load to absorb the energy of the engine.
  • the piston rod and power assembly in the engine of Fig. 1 thus provides two pistons with a total of four working faces, one for the power section, one for the scavenging section, and two for the bounce chambers of the control section.
  • this assembly is connected to the working piston of a compressor type of energy absorbing device, the two additional piston faces provided by such working piston can also be fully utilized, i.e. one face as a compressor working face, and the other face as a bounce control piston face for a further (i.e. third) bounce chamber control section.
  • a maximum range of speed control is obtainable within the general constraints imposed by the maximum allowable cylinder pressures and space limitations.
  • the modification of the invention illustrated in Fig. 8 is basically the same in relative location and control of bounce chambers as that of Fig. 1 in that it has a power cylinder 110 at one end, a connection to a compressor 129 at the other end, and a bouncer assembly 118 with separate negative and positive bounce cylinders 118a and 118b providing negative and positive bounce chambers 118n and 118p, respectively, between the power piston end of the power assembly and the opposite end of the piston rod, which is attached to drive the compressor piston.
  • a Braun counterbalancing mechanism 139 such as disclosed in U.S.A. Patent 3,501,088 and a small compressor 140 have been added to provide a vibration free compressor and a higher pressure air source for varying the air pressure in the bounce chambers.
  • a sensor and control means 137 controls the air pressures in the bounce chambers in response to engine speed. Air flows from auxiliary compressor 140, through conduit 140a to sensor controlled means 137 and through conduits 138 to valve adjusters 123a and 124a.
  • the negative bounce chamber is designated by numeral 118n and the positive by 118p.
  • Other elements similar to those of Fig. 1, have numbers differing by 100.
  • fuel inlet 111, air inlet 112 receiving scavenging air through conduit 112a from chamber 110s, exhaust opening 113, openings 121, 125, 122, 126, 130 and 132 correspond to openings 11, 12, 13, 21, 25, 22, 26, 30 and 32 in Fig. 1.
  • Fig. 8 and 9 modification is the same as that of Fig. 1 except that the smaller diameter bouncer pistons require higher air pressures to properly adjust the bounce pressures.
  • the smaller bounce pistons are necessary to enable the counterbalancing outer racks to straddle the bouncer cylinders as they move in the opposite direction to the movement of the pistons.
  • Fig. 10 is a schematic diagram similar to Fig. 1, showing another preferred emboidment of the present invention, in which the variable stroke free piston machine includes a power assembly with a piston 215 at one end of the axially movable piston rod 217, 235 and with a connection means 235a at the second or outer end of the piston rod for selective and removable driving connection to an appropriate energy absorbing device 229 which could be the piston of a compressor, as in Fig. 1, or an axially reciprocable electric generator member, or the piston of a heat pump assembly.
  • an appropriate energy absorbing device 229 which could be the piston of a compressor, as in Fig. 1, or an axially reciprocable electric generator member, or the piston of a heat pump assembly.
  • the power assembly includes a double-acting bounce piston 216, which moves back and forth axially within a bounce cylinder 218, so that the respective faces 216n and 216p of piston 216 divide the bounce cylinder 218 into an inner or negative first bounce chamber 218n between the power piston and the bouncer piston, and an outer or positive second bounce chamber 218p on the opposite side of the bouncer piston 216, i.e. between the bouncer piston and the outer piston rod end carrying the load connection 235a for the working member of the energy absorbing device or load.
  • the effective cross sectional area of the double-acting bouncer piston 216 is substantially greater than that of the power piston, as already described, by a factor in the range from at least 1.5 to at least 4 times the area of the power piston 215.
  • Fig. 10 which correspond to similar elements in Fig. 1 are given numbers in the 200 series, with the last two numbers corresponding generally to the similarly numbered parts in Fig. 1.
  • the controls for the bounce chambers 218n and 218p include respective inlet openings 221 and 222 controlled by spring loaded inlet valves 223 and 224. These valves are biased downwardly in Fig. 10 by adjustable springs 223a and 224a, which are connected respectively to the outer ends 241 and 242 of a generally horizontal control lever 243 pivoted on a horizontal (as shown) axis or shaft 244 carried by a vertically movable support slider 246. This slider is supported in turn for limited vertical movement within a tubular vertical housing 247 having its upper end secured to the bottom of the bounce cylinder 218 or a corresponding frame portion.
  • the vertical position of the movable support slider 246 may be adjusted by a vertically movable link 248 having its lower end pivoted on shaft 244 and its upper end 249 pivoted at 251 to one end of a two-armed lever 252 pivoted at an intermediate point 253 to another supporting bracket or frame member 254.
  • the outer end 256 of lever arm 252 can be positioned along a scale 257 to establish a relatively lower or higher pressure range simultaneously within each of the bounce chambers 218n and 218p, by pushing the pivot point 244 of the control lever 243 downwardly to a greater or lesser degree and thus increasing or reducing to a corresponding extent the tension of springs 223a and 224a which control the entrance of atmospheric air to both bounce chambers at the low end of the pressure range which is achieved in such chambers as the volume of each bounce chamber approaches its maximum.
  • lever arm 252 may be controlled manually or automatically.
  • an automatic control is shown, in which the outer end 256 of lever arm 252 is connected as shown schematically at 258 to a speed responsive or temperature responsive controller shown schematically at 259.
  • the respective bounce chambers 218 n and 218p are provided with constantly-open bleed openings or orifices 218a and 218b, respectively. These orifices provide limited but desirable and substantially continuous leakage of air from the bounce chambers to help reach the desired bounce pressures for which the inlet valves 223 and 224 are being controlled.
  • the bounce chambers are provided with pressure relief openings 225 and 226, which are capable of substantial relief of pressure from stroke to stroke, at whatever maximum pressure range has been established by the variable pressure relief valves 227 and 228.
  • the relief pressure for these valves can again be set by manual adjustment of the spring tension therein or, as further described in Fig. 11, they may be controlled substantially simultaneously (due to the rapid back and forth strokes of the bouncer piston 216 with the piston rod assembly 217, 235) to control the apparatus by correspondingly limiting the maximum pressures within the two bounce chambers.
  • the lever arm 243 includes an integral downwardly projecting adjusting arm 261 perpendicular to arm 243 which can be controlled at its lower end 262 to rock the complete lever member 243, 261 in a clockwise or counterclockwise direction around its supporting pivot 244, in response to control signals from another sensor, such as the well-known knock sensors for signaling incipient knocking of an engine within its power cylinder.
  • the lower end 262 of lever arm 261 may be normally urged to the right by a connecting link 263 pivotally connected at 263a to a horizontally movable piston 264, urged to the right in Fig. 10 by spring 266 within cylinder 267.
  • the rocking of the lever arm 261 to the right in Fig. 10 will reduce the tension of spring 224a and correspondingly increase the tension of spring 223a, so that air can enter bounce chamber 218p at a slightly higher pressure in chamber 218p and could enter bounce chamber 218n at a slightly lower pressure in chamber 218n than existed just before such movement of lever end 262 to the right.
  • lever arm 261 can be pushed to the left in Fig. 10 by admission of air under appropriate pressure to the control chamber 268 at the right of piston 264.
  • Such pressure can be applied under the control of a normally closed solenoid valve 269 which can be opened to admit compressed air or gas, either from the scavenge pump of such an engine or from any other source of pressure indicated generally at 271, which supplies the necessary pressurized control air or gas through check valve 272.
  • the chamber 268 in which piston 264 can be moved against the urging of spring 266 by an increase of pressure within the chamber is also provided with a bleed opening 273, in order to permit reduction of pressure in chamber 268 and corresponding movement of piston 264 back to the right under the influence Of spring 266, to the extent that the normally closed solenoid valve 269 is not being actuated in response to a signal indicating incipient knock at the power cylinder.
  • a knock sensing device is indicated schematically at 274 in Fig. 10.
  • the signal from a well-known type of knock sensor will open the normally closed solenoid valve to increase the pressure in chamber 268, move piston 264 and lever arm 262 gradually to the left, and thus rock the lever arm 243 so as to increase the tension of spring 224a, decrease the tension of spring 223a, and thus substantially simultaneously (because of the frequency of the engine strokes) make it more difficult for air to enter the bounce chamber 218p, less difficult for air to enter, 218n, and thus rapidly establish a lower range of pressure in the positive bounce chamber, with a corresponding reduction in the force exerted against face 216p of the double-acting bounce piston during the return or compression stroke of the piston assembly, and a corresponding and substantially simultanious increase in the pressure range within chamber 218n, which, in turn, will reduce the work available in chamber
  • valve 269 When the knock sensor signal is thus eliminated, valve 269 will resume its normally closed position, and the escape of pressure from chamber 268 through bleed opening 273 will reverse the control process, all of which happens within short time intervals, in view of the relatively high frequency of reciprocation of the piston rod in this type of free piston engine.
  • the "top-dead center" position of the power piston will intermittently (within these short time intervals) oscillate between the incipient knock position and a small distance short of this point of maximum engine efficiency, irrespective of where the position of incipient knocking may occur under the influence of operating conditions such as engine intake air temperature, air-to-fuel ratio, throttle position, octane number of fuel, altitude and others.
  • operating conditions such as engine intake air temperature, air-to-fuel ratio, throttle position, octane number of fuel, altitude and others.
  • the device of Fig. 10 further emphasizes the advantages of providing a single bounce cylinder with closed ends through which a piston rod assembly, with a power piston at one end and an energy absorbing load device connection at the other end can reciprocate axially, and in which the rod is provided with a double-acting bounce piston inside the bounce cylinder, which defines two bounce chambers of substantially equal circular cross section.
  • a double-acting bounce piston inside the bounce cylinder which defines two bounce chambers of substantially equal circular cross section.
  • bounce piston faces cross-sectional areas which are not only substantially equal to each other in the respective bounce chambers, but are also substantially larger, as shown in Figs. 1 and 10, than the area of the power piston, makes it possible to provide total bounce chamber forces (i.e. piston area times instantaneous pressure) great enough to establish and/or maintain the desired high degree of control over the operation of the piston rod and power assembly under the varying load and frequency conditions required by whatever specific energy absorbing device (e.g., compressor piston, heat pump assembly piston, or axially movable electric generator member) is selected for connection to the outer end of the piston rod.
  • a specific energy absorbing device e.g., compressor piston, heat pump assembly piston, or axially movable electric generator member
  • the small constantly-open bleed openings such as 218a and 218b, further provide limited inlet and outlet functions in each bounce chamber, and their function should be included in certain cases. Such function can also be achieved as part of the construction or operation of the variable pressure bounce chamber valves, or by limited leakage along the shaft seals at the respective end walls of the bounce chambers, or even by limited leakage around the periphery of the bounce piston from one bounce chamber to the other. In all cases, however, the desired functions of such bleed openings should be supplemented (or provided) by at least one pair (one in each bounce chamber) of variable bounce chamber pressure inlet control valves, or one pair (one in each bounce chamber) of variable bounce chamber pressure relief valves, or preferably by both such pairs.
  • Fig. 11 shows an embodiment of the invention in which the desired control of the free piston machine is specifically achieved by a pair of pressure relief outlets 325 and 326 (one in each of the bounce chambers 318n and 318p). These pressure relief outlet means are controlled by variable pressure outlet valves 327 and 328 as shown schematically in Fig. 11.
  • a pair of small constantly-open bleed openings 318a and 318b (one in each of the bounce chambers 318n and 318p), is also provided. Both the bleed openings and the variable pressure relief valves are shown, for example, as located in the axial end walls of bounce chamber 318, which are also provided with central bearing portions and seals at 319 and 320 to receive the axially movable piston rod assembly 317, 335.
  • This rod has a power piston 315 at its inner end and a connection 335a at its outer end for readily removable connection to a moving member 334 of a selected energy absorbing device 329 which is also removably secured to the outer end of the machine at 341.
  • Fig. 11 Elements in Fig. 11 which correspond to similar elements in other figures are given numbers in the 300 series, with the last two numbers corresponding generally to the similarly-numbered parts in Fig. 1.
  • the power piston 315 moves axially within a power cylinder 310 and compresses the appropriate fuel mixture in combustion chamber 310p during a compression stroke of the power assembly 317, 335 and its associated parts from right to left in Fig. 11. Combustion of the fuel mixture in chamber 310p then drives the power piston315 and associated piston rod to the right in Fig. 11 in the appropriate power stroke needed for operation of the energy absorbing device member 334.
  • the double-acting bounce piston 316 carried by the piston rod divides the cylindrical bounce chamber 318 into a first bounce chamber 318n toward the power piston end of the machine and a second bounce chamber 318p toward the load connection means at the other end of the machine.
  • These bounce chambers are used for control of the machine, and the controls include the constantly open restricted openings 318a and 318b, respectively (one in each chamber) in combination with the pair of pressure relief openings 325 and 326 controlled by variable pressure valve members 327 and 328, respectively described above.
  • the closing forces of the valves are adjustably set by spring members 343 and 344 which are compressed between the valves and two respective control abutments 345 and 346.
  • Abutment 345 projects upwardly from a slider member 347 which is supported for relative sliding within the hollow receiving chamber 348 of a telescoping outer slider member 349.
  • Slider 349 is relatively slidable along the same axis as member 347 within the channel 351 of a slide support 352 secured to the bottom of bounce cylinder 318 or to an appropriate frame member of the engine.
  • the inner slider member 347 is provided with an extension shaft 354 extending axially through the outer slider 349 to a piston 356 within a control cylinder 357 at the outer end of slider member 349 which carries abutment 346.
  • pressure may be increased within the cylinder chamber 358 at the left side (as viewed in Fig. 11) of piston 356.
  • variable pressure regulator valve 359 connected to a source 360 of pressurized air or gas can feed such pressurized fluid through inlet 362 into chamber 358 in response to signals from a suitable sensor shown schematically at 361, such as a signal from a speed responsive sensor indicating an undesired decrease in speed or frequency of the free piston machine.
  • a vent 355 keeps the outer end of cylinder 357 at ambient pressure, so piston 356 is free to move out in response to pressure increases in chamber 358.
  • the increased valve closing pressures of springs 343 and 344 can thus provide increased maximum pressure levels within the respective bounce chambers 318n and 318p to increase the speed of engine operation until the signal from the speed regulator permits regulator valve 359 to close. At that point, pressure will be relieved within chamber 358 of the slider cylinder 357 by means of the small bleed orifice 363. If the pressure drops to a point where the sliders move apart far enough to cause another undesired drop in engine speed, the control process just described will be repeated, so that the engine speed may vary slightly in a cyclical manner close to the desired engine speed. This control arrangement responds to undesired decreases in speed, but it should be understood that such a control system could also be made responsive to undesired increases in engine speed.
  • the slider members 347 and 349 and their spring-controlling abutments 345 and 346 can be moved axially as a unit to increase the relief pressure imposed by spring 343 and simultaneously decrease the spring pressure imposed by spring 344, or vice versa.
  • a piston 364, rigidly connected to the outer end of slider 349 is received in a control cylinder 367 fixed to a stationary engine part or frame at 366.
  • a spring 365 between the outer end of slider 349 and the inner end (left end, as viewed in Fig. 11) of fixed cylinder 367 normally urges the total assembly of sliders 347 and 349 in a direction (left in Fig. 11) to apply maximum spring pressure at 343 on relief valve 327 and to apply minimum spring pressure at 344 on relief valve 328.
  • the pressure in cylinder chamber 368 may be controlled, for example, in response to signals from a known knock sensor 374 of the type described in connection with Fig. 10.
  • a signal from such an incipient knock snnsor can open a solenoid-controlled valve 369 to feed compressed air or gas from an appropriate source 371 (such as the scavenge pump chamber 310s or any other suitable source of pressure) through a check valve 372 into the inlet of chamber 368.
  • Valve 369 will then close, and bleed orifice 373 will provide for slow release of pressure from chamber 368 to let the sliders move back and increase the bounce relief pressure at valve 326, so that the engine operation can again approach the incipient knocking point, where operation is generally believed to be most efficient.
  • the upper dead center position of power piston 315 can cycle within a narrow range close to the incipient knock point to maintain the desired efficiency of engine operation.
  • control systems shown in Fig. 11 operate to provide the desired bounce chamber pressure ranges by variably controlling the maximum pressures within such chambers, without relying on the controls at the low pressure ends of such ranges as more fully described in connection with Fig. 10.
  • Fig. 11A shows a preferred modification of the device of Fig. 11, in which the pair of small constantly open bleed openings 318a and 318b are replaced by inlet openings 321 and 322 controlled by one-way inlet valves 323 and 324 for the respective bounce chambers 318n and 318p.
  • the inlet pressure at which the inlet valve will open may be preset, or variably adjusted as shown schematically at 323a and 324a, and the inlet valves are provided with restricted orifices 323b and 324b which are "upstream" from the bounce chamber inlet openings and one-way valve portions.
  • Such restricted orifices are open directly to the ambient air at atmospheric pressure and are restricted primarily to limit the rate at which air can be sucked into the respective bounce chambers during the intervals in which the one-way check valves are open.
  • Such restricted orifices may be as small as .02 inches in effective diameter, to limit the inward flow of ambient air when the inlet valves are opened.
  • the inlet valves are thus useful in providing for limited replacement of control air within the respective bounce chambers, while the major control of bounce chamber working pressures is achieved as described in connection with Fig. 11 by the indicated variable adjustments of the maximum pressures at which the respective bounce chamber exhaust valves 327 and 328 will be opened.
  • the inlet check valves can be set, however, to let the control means work with higher bounce pressures.
  • Figs. 11 and 11A have both safety and operating advantages in providing a particularly wide range of bounce chamber control pressures primarily by controlling the maximum pressures in such chambers.
  • the present invention provides a wide range of control possibilities by providing at least one "negative” or inner bounce chamber positioned toward the power piston end of such an engine, i.e. between a bounce piston face on the piston rod of the engine and the power piston itself, in combination with a so-called “positive” or outer bounce chamber positioned toward the outer end of the engine, i.e. between the inner bounce chamber and the load connection means at the other end of the piston rod of the free piston engine assembly.
  • the available flexibility of control provided by such relative locations and by the indicated relative cross sectional areas of the bounce chambers helps to make possible the use of different energy absorbing devices with the same basic power unit, by selectively and removably connecting such different devices, as shown schematically at 335a and 341 in Fig. 11, to the closed outer end of the outer bounce chamber or to some other appropriate frame part, and by using the same power assembly and piston rod 317, 335 to drive the desired movable member 334 of the particular energy absorbing device chosen for a specific application.
  • the energy absorbing device is a working compressor (or pump), as specifically shown in Fig.1
  • the invention provides a relative location of engine parts which permits the compressor or pump chamber to be separated from, and thereby effectively sealed off from the engine speed controlling bounce cylinders.
  • This permits use of a working fluid in the compressor or pump chamber which is different from e.g. incompatible with the controlling fluid, such as air, which is used in the engine bounce cylinder.
  • While the invention is specifically illustrated in a free piston engine for driving compressor, it may also be used in such an engine for driving an electric alternator or some other energy absorbing device (EAD) that is subject to varying loads as described herein, or which requires an engine responsive to a wide range of changes demanded by a particular load device.
  • EAD energy absorbing device

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Control Of Velocity Or Acceleration (AREA)
  • Control Of Electric Motors In General (AREA)
  • Actuator (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Supercharger (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Sealing Devices (AREA)

Claims (19)

1. Freikolbenmaschine mit veränderlichem Hub, umfassend eine Antriebseinrichtung mit einer axial hin und her bewegbaren Kolbenstange (17, 117, 217, 317) mit entgegengesetzten ersten und zweiten Enden, einem am ersten Ende befestigten Antriebskolben (15, 115, 215, 315), einer am zweiten Ende vorhandenen Verbindungseinrichtung zum Antrieb eines bewegbaren Teils eines gewünschten Energieverbrauchers (EAD) (29, 129, 229, 329), und einer zwischen dem ersten und dem zweiten Ende an der Kolbenstange befestigten, doppelt wirkenden Rückwurfkolbeneinheit (16, 116, 216, 316) mit einer ersten und einer zweiten Rückwurfkolben-Arbeitsfläche, die dem ersten bzw. dem zweiten Kolbenende zugewandt ist, so daß sich die Kolbenstange, der Antriebskolben, die Rückwurfkolbeneinheit und die EAD-Verbindungseinrichtung als Einheit während aufeinanderfolgender abwechselnder Kompressionshübe des Antriebskolbens in Richtung des ersten Endes und während Expansionshüben des Antriebskolbens in Richtung des zweiten Endes der Kolbenstange hin und her bewegen, und eine in Axialrichtung feste Rückwurfzylindereinrichtung (18, 118, 218, 318), die mit der Rückwurfkolbeneinheit zusammenarbeitet und die am einer relativen axialen Stelle zwischen der ersten Arbeitsfläche des Rückwurfkolbens und dem Antriebskolbenende der Kolbenstange eine negative erste Rückwurfkammer (18n) sowie an einer relativen axialen Stelle zwischen der zweiten Arbeitsfläche des Rückwurfkolbens und dem EAD-Verbindungsende der Kolbenstange eine positive zweite Rückwurfkammer (18p) bildet,
   gekennzeichnet durch eine Steuereinrichtung für die Maschine mit mindestens einem Paar von Rückwurfkammer-Drucksteueröffnungen (21, 22) (eine in jeder Rückwurfkammer), mindestens einem Paar von veränderlich verstellbaren Rückwurf-Drucksteuerventilen (23, 24) (eines für jede der Rückwurfkammer-Steueröffnungen des besagten Paares) zur Steuerung des, einer Einrichtung zur Verbindung jedes Steuerventils des besagten einem Paares mit seiner jeweiligen Rückwurfkammer-Steueröffnung zur veränderlichen Verstellung der Arbeitsdrücke in den jeweiligen Rückwurfkammern, und einer auf Änderungen in den Anforderungen des gewünschten Energieverbrauchers ansprechende Einrichtung (37), die mit dem besagten einen Paar von Steuerventilen wirkungsmäßig verbunden ist, um jedes der veränderlichen Drucksteuerventile des besagten einen Paares während des Betriebs der Maschine veränderlich und im wesentlichen gleichzeitig sowie ähnlich (d.h. in gleicher Druckänderungsrichtung) zu verstellen und dadurch den jeweiligen Rückwurfkammer-Arbeitsdruck in jeder Rückwurfkammer ähnlich zu verändern, nämlich beide aufwärts oder beide abwärts, um die Maschinenfrequenz in Übereinstimmung mit den geänderten Anforderungen effektiv zu steuern.
2. Freikolbenmaschine nach Anspruch 1, wobei die Fläche der ersten und der zweiten Arbeitsfläche des Rückwurfkolbens um einen Faktor im Bereich von mindestens 1,5 bis mindestens 4 größer ist als die Arbeitsfläche des Antriebskolbens.
3. Freikolbenmaschine nach Anspruch 2, wobei die Flächen der ersten und der zweiten Arbeitsfläche des Rückwurfkolbens im wesentlichen gleich sind.
4. Freikolbenmaschine nach Anspruch 1, wobei die Rückwurfkammer-Drucksteueröffnungen des besagten mindestens einen Paares von Öffnungen und die entsprechenden veränderlich verstellbaren Rückwurfdruck-Steuerventile dieses Paares so angeordnet und gestaltet sind, daß zwischen den entsprechenden Rückwurfkammern und der umgebenden Atmosphärenluft außerhalb der Rückwurfzylindereinrichtung eine direkte Verbindung besteht, wenn die Steuerventile offen sind, wobei die Rückwurfkammern die Maschine effektiv steuern, ohne einen Druckbehälter mit einem Hockdruck-Rückwurfsteuerfluid zu erfordern.
5. Freikolbenmaschine nach Anspruch 4, wobei die Rückwurfzylindereinrichtung einen einzelnen gemeinsamen Rückwurfzylinder (18) aufweist, der die erste und die zweite Rückwurfkammer (18n, 18p) bildet, und wobei die erste und die zweite RückwurfkolbenArbeitsfläche die entgegengesetzten Flächen eines einzelnen Rückwurfkolbens sind, der sich innerhalb des gemeinsamen Rückwurfzylinders hin und her bewegt und in diesem die erste und die zweite Rückwurfkammer voneinander trennt.
6. Freikolbenmaschine nach Anspruch 5, wobei der gewünschte Energieverbraucher eine Kolbenmaschine mit einem zu der Kolbenstange (35) der Maschine koaxialen Kompressorzylinder ist und wobei sein bewegliches Element zur Verbindung mit dem zweiten Ende der Antriebsstange ein Kompressorkolben ist, der in dem Kompressorzylinder axial bewegbar gelagert ist.
7. Freikolbenmaschine nach Anspruch 6, wobei der Kompressorzylinder und der Kompressorkolben eine von dem Rückwurfzylinder der Maschine getrennte und dadurch effektiv abgedichtete Kompressorkammer zum Betrieb mit einem Antriebsfluid bilden, das von dem in dem Rückwurfzylinder der Maschine verwendeten Steuerfluid, beispielsweise Luft, verschieden, z.B. inkompatibel mit diesem, ist.
8. Freikolbenmaschine nach Anspruch 6, wobei in der Maschine zwischen der hinteren (inneren) Fläche des Antriebskolbens und der negativen ersten Rückwurfkammer ein Spülabschnitt (105) vorgesehen ist, und wobei der Kompressorkolben des gewünschten Energieverbrauchers eine Fläche, die als Arbeitskompressorfläche dient, und eine entgegengesetzte Fläche aufweist, die als Rückwurfkolbenfläche einer zwischen der Arbeitskompressorkammer und der positiven ersten Rückwurfkammer der Maschine angeordneten weiteren Rückwurfkammer (29a) dient.
9. Freikolbenmaschine nach Anspruch 1, wobei die Steuereinrichtung eine weitere Maschinensteuereinrichtung mit einer auf einen Betriebszustand der Maschine ansprechenden Einrichtung zur Messung des Maschinenwirkungsgrades aufweist, die mit den veränderlich verstellbaren Rückwurfkammer-Drucksteuerventilen mindestens des besagten einen Paares wirkungsmäßig verbunden ist, um jedes dieser veränderlichen Drucksteuerventile des besagten Paares veränderlich und im wesentlichen gleichzeitig sowie entgegengesetzt (d.h. in entgegengesetzten Richtungen) zu verstellen, dadurch die jeweiligen Rückwurfkammer-Arbeitsdrücke in zueinander entgegengesetzten Richtungen zu verschieben und somit aufeinanderfolgende obere Totpunktlagen des Antriebskolbens und der Kolbenstange in relativer axialer Richtung mit der Tendenz zu verschieben, den gewünschten Maschinenwirkungsgrad aufrecht zu erhalten.
10. Freikolbenmaschine nach Anspruch 9, wobei die Einrichtung zur Messung des Maschinenwirkungsgrades ein Klopffestigkeits-Meßgerät (274, 374) aufweist, das auf einsetzendes Klopfen der Maschine an oberen Totpunktlagen des Antriebskolbens kurz vor denjenigen Punkten anspricht, bei denen ein tatsächliches Klopfen auftreten könnte.
11. Freikolbenmaschine nach Anspruch 1, wobei die Steuereinrichtung ferner ein zweites Paar von Rückwurfkammer-Drucksteueröffnungen (321, 322) (eine für jede Rückwurfkammer) und ein entsprechendes zweites Paar von Rückwurfkammer-Steuerventilen (323, 324) (eines für jede Rückwurfkammer) aufweist, und wobei die jeweiligen Steuerventile des zweiten Paares zur weiteren Steuerung der Rückwurfkammerdrücke verstellbar sind.
12. Freikolbenmaschine nach Anspruch 1, wobei die Steuereinrichtung ferner eine Entlüftungseinrichtung mit einer kleinen Entlüftungsöffnung (18a, 18b) aufweist, die einen im wesentlichen kontinuierlich offenem begrenzten Leckpfad zwischen jeder Rückwurfkammer und der umgebenden Atmosphäre außerhalb der Rückwurfkammer bildet, und wobei die veränderlichen Rückwurfdruck-Steuerventile weiterhin die relative Luftströmung zwischen den jeweiligen Rückwurfkammern und der umgebenden Atmosphäre außerhalb diese Rückwurfkammern steuern.
14. Freikolbenmaschine nach Anspruch 1, wobei der gewünschte Energieverbrauchr ein Kompressor ist, die doppelt wirkende Rückwurfkolbeneinheit und die Rückwurfzylindereinrichtung eine diese mindestens teilweise umgebende Ausgleichseinheit (139) aufweisen, und die Machine ferner einen die Ausgleichseinheit mit der Kolbenstange verbindenden Umkehrmechanismus aufweist.
15. Freikolbenmaschine mit kombinierten Kompressor nach Anspruch 14, wobei der Umkehrmechanismus Zahnstangen und Ritzel umfaßt.
16. Freikolbenmaschine nach Anspruch 1, wobei die Rückwurf-Drucksteuerventile des besagten einen Paares Rückwurf-Einlaßdrucksteuerventile (27, 28) zum selektiven Verstellen der minimalen Einlaßdrücke jeder Rückwurfkammer sind.
17. Freikolbenmaschine nach Anspruch 1, wobei die Rückwurf-Drucksteuerventile des besagten einen Paares DruckentlastungsAuslaßventile zur selektiven Verstellung der maximalen inneren Drücke jeder Rückwurfkammer sind.
18. Freikolbenmaschine nach Anspruch 17, wobei die Steuereinrichtung ein zweites Paar von Rückwurfkanmer-Drucksteueröffnungen (321, 322) (eine in jeder Rückwurfkammer) und ein Paar von Rückwurf-Einlaßdrucksteuerventilen (323, 324) (eines für jede Steueröffnung des zweiten Paares) umfaßt, um die minimalen Einlaßdrücke jeder Rückwurfkammer vorzugehen.
19. Freikolbenmaschine nach Anspruch 18, wobei die Rückwurf-Einlaßdrucksteuerventile eine verengte Öffnung (323b, 324b) enthalten, die zur umgebenden Atmosphärenluft offen ist und dadurch das Einströmen von Luft in die Rückwurfkammern begrenzt, wenn die Einlaßdrucksteuerventile bei Auftreten von relativ niedrigen Drücken innerhalb der Rückwurfkammern geöffnet werden.
EP85905954A 1985-10-10 1985-10-10 Rotationsgeschwindigkeitskontrolleinrichtung für maschinen mit veränderlichem hub Expired - Lifetime EP0246227B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85905954T ATE68037T1 (de) 1985-10-10 1985-10-10 Rotationsgeschwindigkeitskontrolleinrichtung fuer maschinen mit veraenderlichem hub.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US1985/001997 WO1987002423A1 (en) 1985-10-10 1985-10-10 Cyclic speed control apparatus in variable stroke machines

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EP0246227A1 EP0246227A1 (de) 1987-11-25
EP0246227A4 EP0246227A4 (de) 1990-02-05
EP0246227B1 true EP0246227B1 (de) 1991-10-02

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JP (1) JPS63502523A (de)
AT (1) ATE68037T1 (de)
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BR (1) BR8507298A (de)
DE (1) DE3584293D1 (de)
DK (1) DK294187A (de)
HU (1) HUT48949A (de)
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GB2214569B (en) * 1988-01-21 1992-06-24 Barry John Rymer Internal combustion piston engine
WO1993001393A1 (en) * 1991-07-10 1993-01-21 Wbm Pty. Ltd. Piston motion control in free piston driver
AUPM597094A0 (en) * 1994-05-31 1994-06-23 Hansen, A.M. Dynamic linear mass accelerator
AU705580B2 (en) * 1994-05-31 1999-05-27 Thermo-Dynamic Systems Limited A gas driven mechanical oscillator and method
AU664531B3 (en) * 1994-05-31 1995-11-16 Anthony Maurice Hansen A gas driven mechanical oscillator and method
JP2008223628A (ja) * 2007-03-13 2008-09-25 Mazda Motor Corp フリーピストンエンジンの制御装置
EP2405138B1 (de) * 2009-01-28 2015-03-11 J.C.R. Van Der Hart Holding B.v. Pumpvorrichtung

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Publication number Priority date Publication date Assignee Title
US481527A (en) * 1892-08-23 Ernest c
US2355924A (en) * 1941-09-03 1944-08-15 Soc Es Energie Sa Free piston machine
US3020706A (en) * 1957-12-03 1962-02-13 Participations Eau Soc Et Control means for free-piston or semi-free piston engines
US2959159A (en) * 1958-05-16 1960-11-08 Battelle Development Corp Free-piston internal combustion apparatus
US3159331A (en) * 1962-07-20 1964-12-01 Borsig Ag Multi-stage free piston type compressor
FR1371354A (fr) * 1963-07-25 1964-09-04 Soc Es Energie Sa Perfectionnements apportés aux autogénérateurs à piston libre
US3501088A (en) * 1968-07-22 1970-03-17 Anton Braun Balanced free piston engine
US3853100A (en) * 1973-02-16 1974-12-10 A Braun Free piston engine with antiknock means
FR2441073A1 (fr) * 1978-11-13 1980-06-06 Moiroux Auguste Compresseur a action directe equipe d'un piston monobloc
US4568251A (en) * 1982-05-11 1986-02-04 Anton Braun Cyclic speed control apparatus in variable stroke machines

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AU581044B2 (en) 1989-02-09
NO872410L (no) 1987-07-09
WO1987002423A1 (en) 1987-04-23
ATE68037T1 (de) 1991-10-15
HUT48949A (en) 1989-07-28
DK294187A (da) 1987-07-15
EP0246227A1 (de) 1987-11-25
DE3584293D1 (de) 1991-11-07
NO872410D0 (no) 1987-06-09
BR8507298A (pt) 1987-11-03
AU5094285A (en) 1987-05-05
DK294187D0 (da) 1987-06-09
JPS63502523A (ja) 1988-09-22
EP0246227A4 (de) 1990-02-05

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