US3598094A - Crankless reciprocating machine - Google Patents

Crankless reciprocating machine Download PDF

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US3598094A
US3598094A US18794A US3598094DA US3598094A US 3598094 A US3598094 A US 3598094A US 18794 A US18794 A US 18794A US 3598094D A US3598094D A US 3598094DA US 3598094 A US3598094 A US 3598094A
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piston
pin
cam
reciprocating machine
cylinder
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US18794A
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Daisaku Odawara
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    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/04—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces
    • F01B3/045—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces by two or more curved surfaces, e.g. for two or more pistons in one cylinder
    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F01B3/0005—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having two or more sets of cylinders or pistons
    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0082—Details
    • F01B3/0085—Pistons
    • F01B3/0088—Piston shoe retaining means
    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0082—Details
    • F01B3/0094—Driving or driven means
    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/04—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces
    • F01B3/06—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces by multi-turn helical surfaces and automatic reversal
    • 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
    • F01B7/00—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • 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
    • F01B7/00—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F01B7/02—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with oppositely reciprocating pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/08—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion
    • F16H25/12—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion with reciprocation along the axis of rotation, e.g. gearings with helical grooves and automatic reversal
    • 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
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • 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
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18296—Cam and slide
    • Y10T74/18336—Wabbler type

Definitions

  • the mechanism comprises at least one pin finnly connected to a piston or pistons so as to be immovable relative thereto and extending radially outwardly therefrom, and an endless cam mounted in a fixed part or a rotating part, said pin and said cam operatively connecting the reciprocating motion of said piston or pistons with the rotary motion of said rotating part.
  • the present invention relates to reciprocating machines, and in particular to a crankless reciprocating machine which is provided with a novel mechanism for converting a rotary motion into a reciprocating motion or vice versa.
  • crank mechanism for converting a reciprocating motion into a rotary motion.
  • the crank mechanism has disadvantages in that it entails a serious loss of energy by friction or otherwise, in addition to causing noises and vibrations in operation. Accordingly, there is much to be desired in the operational efficiency of conventional reciprocating machines. Further, the crank mechanism tends to cause the cylinder to be deformed into an egg shape because of wear, resulting in a shorter effective life of the machines themselves.
  • vibrations may increase as the number of revolution increases. This is due primarily to an imbalance of the structure involving connecting rods and crank arms. A further increase in the number of revolutions may cause the breakage of bolts securing connecting rods and the scattering of balance weights, resulting in a serious damage to the side cover or the frame.
  • the present invention obviates all the disadvantages of conventional reciprocating piston machines referred to above.
  • the principal object of the invention is to provide a crankless reciprocating machine provided with a novel mechanism which ensures that a reciprocating motion is converted into a rotary motion and a rotary motion into a reciprocating motion in balanced operation.
  • Another object is to provide a motion conversion mechanism which comprises at least one pin firmly connected to a piston or pistons so as to be immovable relative thereto and extending radially outwardly therefrom, and an endless cam mounted in a fixed part or a rotating part, said pin and said cam operatively connecting the reciprocating motion of said piston or pistons with the rotary motion of said rotating part.
  • the rotating part comprises a cam means formed with a cam groove on its inner side surface, and a rotary shaft, said rotary shaft being supported by a fixed cylinder in which a piston is rcciprocably mounted.
  • the rotating part includes a cylinder means having a piston mounted therein and a rotary shaft or shafts firmly fixed to said cylinder means, said rotary shaft or shafts being supported by a fixed casing which is formed with an endless cam groove on its inner surface.
  • FIG. I is a longitudinal sectional view of one embodiment of the crankless reciprocating machine according to this invention.
  • FIG. 2 is a side view of a hollow cylindrical member forming a cam groove
  • FIG. 3 is a longitudinal sectional view of a second embodiment of this invention.
  • FIG. 4 is-a transverse sectional view along'the line IV-IV of FIG. 6 showing a third embodiment of this invention
  • FIG. 5 is a developmental sectional view along thecircle a of FIG. 4;
  • FIG. 6 is a longitudinal sectional view along the line VI-VI of FIG. 4; 7
  • FIG. 7 is a sectional view of a fourth embodiment of this invention, and which is a modification of the" third embodiment
  • FIG. 8 is a longitudinal sectional view of a fifth embodiment of this invention which includes two machines of the third embodiments arranged in back to back relation;
  • FIG. 9 is a longitudinal sectional view of a sixth embodiment of this invention having a pin extending both inwardly and outwardly in the radial direction;
  • FIG. 10 is a longitudinal sectional view of a seventh embodiment of the invention constructed as an internal combustion engine
  • FIG. I I is a longitudinal sectional view of an eighth embodiment of this invention in which the cam means and the rotary shaft are connected to each other through a gearing;
  • FIG. 12 is a perspective view of a cam means fonned with a cam for controlling suction and discharge valves on one end surface, and with a gear on the outer circumferential surface;
  • FIG. 1-3 is a longitudinal sectional view of aninth embodiment of this invention in which the rotary shaft extends through a fixed cylinder block;
  • FIG. 14 is a longitudinal sectional view of a tenth embodiment of this invention in which two pistons are arranged in face to face relation; Y
  • FIG. 15 is a longitudinal sectional view of an eleventh em? bodiment of this invention. i
  • FIG. I6 is a sectional view showing a bufferd'evice disposed between the pinand antifriction means
  • FIG. 17 a to f are developmental views in explanation of various forms of cam grooves
  • FIG. I8 is a longitudinal sectional view of a twelfth embodiment of this invention.
  • FIG. 19 is a longitudinal sectional view of a thirteenth embodiment of this invention.
  • FIG. 20 is a longitudinal sectional view of a fourteenth embodiment of this invention constructed as a rotary pump
  • FIG. 21 is a. sectional view along the line XXI-XXI of FIG. 20;
  • FIG. 23 is a longitudinal sectional view of a sixteenth embodiment of this invention.
  • FIGS. I to l7 each of which has a rotating part comprising a cammeans and a rotary shaft, said rotary shaft being supported by a fixed cylinder.
  • a piston 3 secured to oneend-of a pistorr rod 4 is mountedin a cylinder 2. of a fixed cylinder block 2.1 3 iiieuch a manner that said piston is slidable' fin said cyliiider but restrained against rotation relative to the cylinder.
  • a pin mounting portion 7 Secured to the other end. of the piston rod 'd'for slidablemovement in the cylinder 2 like the piston 3 is a pin mounting portion 7 to which is secured a pin 8 extending; radially outwa'r'dlye and adapted for converting a reciprocating inotion intoi'a. rotary motion or vice versa.
  • a cam means2 0fmounted concentrically with the cylinder 2 is secured to a rotary shaft I and immova- FIG. 22 is. a longitudinal sectional view of a fifteenth emble relative to said rotary shaft.
  • the cam means encloses that portion of the cylinder 2 in which said pin 8 operates.
  • the rotaryshaft l is rotatably mounted on the cylinder block 21 through bearing 17.
  • the cam means comprises two hollow cam members 6 and 6 which form a cam groove 18 on the inner surface of the cam means.
  • the pin 8 extends through a slot formed in the cylinder block 21, and its outer end is loosely fitted in said cam groove 18.
  • the cam groove 18 forms a closed or endless curve on the innersurface of the cam means 20.
  • the cam means 20 is constructed such that the piston 3 makes at least one reciprocating motion for each complete revolution of the cam means.
  • the cam members 6 and 6' are hollow cylindrical members each having a curved end, and the curved ends of the two hollow cylindrical cam members 6 and 6' are complementary to each other as shown in FIG. 2.
  • the two cam members 6 and 6' disposed as shown in FIG. 2 are fitted in the cam means 20 in such a manner that the two members are spaced apart a predetermined distance from each other so as to provide the cam groove 18 of desired width.
  • FIG. I can be constructed such that aplurality of cylinders are disposed in the machine.
  • FIG. 3 One example of such construction is shown in FIG. 3 as a second embodiment of the invention.
  • two piston rods 4 each having a piston 3 connected to one end are connected at the other end to a common pin mounting portion 7, with the pistons 3 facing opposite directions.
  • Two units of this piston pin mounting portion combination are mounted coaxially in a fixed cylinder block 2].
  • the cylinder 2 is in the form of an elongated cylinder in the cylinder block, with the two piston-pin mounting portion combinations forming a common operating chamber therebetween.
  • Cam means 20 corresponding in number to the piston-pin mounting portion combination units are mounted concentrically in the cylinder 2 for rotation.
  • Each cam means 20 is formed with a gear 22 on its outer circumferential surface, said gear 22 being in meshing engagement with a gear 23 secured to the rotary shaft 1. Accordingly, the reciprocating motion of the pistons 3 causes the cam means 20 to move in rotary motion through the pin 8 received in the cam groove, and the rotary motion of the cam means causes in turn the rotary shaft 1 to rotate through the gears 22 and 23in meshing engagement with each other. It will be evident from the figure that the two units of piston-pin mounting portion combination form a mirror image with respect to the central transverse scction of the cylinder block 2]. It is to be understood that the number of thdaforpmentionedirnits arranged coaxially in the cylinder is not iitcd to two shown, and that the number of units tharcan bemountcd is indefinite theoretically.
  • FIG. I A plurality of theimachines sho-wnin FIG. I can be arranged circumaxially about the axisof the rotaryshaft land parallel thereto. This arrangement istshown in FIGS. 4 to 6.
  • the machine shown in these figures comprises six cylinders 2 mounted circumaxially about the rotary shaft 1 and parallel thereto.
  • the cam means 20 is formedI'with"a'cam groove 18 which receives therein all the pins 8 each of which is mounted on the pin mounting portion 7 of each unit of piston-pin mounting portion combination and extends radially outwardly.
  • the cylinders 2 need not be disposed circumaxially about the rotary shaft on one circle; they may be arranged such that they are disposed on a plurality of concentric circles as shown in FIG. 7.
  • units of piston-pin mounting portion combination disposed on different circles may conveniently be combined with each other and the pin mounting portions of these units may be fixedly connected together, so that the pin of the unit disposed on the circle of the largest diameter can extend radially to be received in the cam groove. It will be evident that the units of piston-pin mounting portion combination having their pin mounting portions fixedly connected together'can move as a unit in reciprocating motion.
  • FIG. 8 shows a machine which comprises two sets of the machine of FIG. 6 arranged in end to end relation with respect to the end plate of the cam means 20 which is formed integrally.
  • the pistons are arranged symmetrically with respect to the cam means 20. If two cam grooves 18 are formed symmetrically with respect to the center face of the cam means 20, the pistons 3 will move symmetrically with respect to the center face of the cam mearis. A fully balanced construction can thus be obtained in a reciprocating machine.
  • the machine shown in FIG. 9 has a boss 24 enclosing the re tary shaft 1.
  • the boss 24 is formed with a cam groove l5 in the form of a closed or endless curve on its outer circumferential surface.
  • the pin 8 extends not only radially outwardly to be loosely fitted in the cam groove 18, but also through the pin mounting portion 7 and radially inwardly to be loosely fitted in the cam groove 15.
  • the cam groove I5 is formed by arranging the curved ends of two hollow cylindrical members 5 and 5' in spaced relation from each other.
  • the cam grooves 15 and 18 are constructed in such a manner that each pin 8 is maintained normal to the axis of the piston at all times when the pistons move in reciprocating motion.
  • the machine illustrated in FIG. 9 has antifriction means, such as roller bearings, for example, attached to the portion of the pin 8 which extends through the slot 16, so that the. thrust created when the pin 8 moves along the curved surfaces of the cam grooves I5 and 18 can be borne by said antifriction means.
  • Each of the pins 8 of the machine shown in FIG. 9 has two ends received in the cam grooves 15 and 18 respectively and supported therein.
  • This arrangement permits no couple of forces or bending force to be applied to the pistons 3, so that the pistons can be restrained against scratching the inner surface of the cylinder. Since the force applied by the piston 3 is divided and directed to the opposite ends of the pin 8, each end of the pin 8 carries substantially half the force applied to one end of the pin when only one end of the pin is received in the cam groove. This is one advantageoffered by the invention in designing machines of this type.
  • a device in which a piston has a pin projecting therefrom and received in a groove formed in a cylinder whereby the piston can move in rotary motion in the cylinder as the former moves in reciprocating motion in the latter.
  • the piston and the cylinder move in rotary motion besides moving in reciprocating sliding motion relative to each other. This makes it impossible to provide an effective seal to the machine even if a piston ring is used.
  • the piston and the cylinder do not move in'rotary motion relative to each other in the machine constructed according to this invention, the machine can be sealed as effectively as if the piston ring were used in the crank mechanism.
  • an added advantage of the machine provided by this invention lies in the fact that it is free from an imbalance in operation occurring in motion conversion which .has plagued the machine relying on the conventional crank mechanism.
  • FIG. I0 shows a seventh embodiment of this invention in which the crankless reciprocating machine is constructed as an internal combustionengine. This machine has a fixed In FIG. 10, each of the pistons 3 is mounted in one of the,
  • Each piston 3 has a pin 8 secured thereto and extending radially therefrom, the end of each pin 8 being received, through a double antifriction means 9, the cam groove 18 formed on the inner surface of the cam means 20.
  • the cam means is secured to the rotary shaft I through a flange 12, the cam means 20 and the rotary shaft 1 rotating as a unit.
  • the rotary shaft I is not journaled directly by the cylinder block 21; the rotary shaft I is supported by a shaft I4 secured to the cylinder block 21 through a bearing 28 mounted in the flange l2f'lhe cam means 20 is rotatably supported by the outer casing 13 through roller bearings 17.
  • Each pin 8 is receivedin the cam groove 18 through an antifriction means or roller bearing 9 mounted on its outer end far from the piston 3.
  • the antifriction means may have a largest possible diameter. It will be evident that the larger the diameter of the antifriction means, the lower is the number of revolutions of the antifriction means about the pin 8.
  • cam means 10 and II which are formed with cam faces 29 and respectively (FIG. 12).
  • the fixed cylinder block 21 is formed with tappets 34 and which are disposed such that they are positioned on the paths of cam faces 10 and II respectively.
  • the tappets actuate oscillating arms 62 and 53 through push rods 37 and 38 respectively, thereby opening and closingsuction and discharge valves 26.
  • 36 designates ig-' nition plugs and 25 is a cylinder head in which a suction and discharge duct is formed.
  • FIG. I0 is a view in section showing the machine in two planes normal to each other and taken through the center axis ofthe machine.
  • the eighth embodiment shown in FIG. 11 represents a development of the second embodiment shown in FIG. 3.
  • the cylinder block 21 is formed with a plurality of cylinders 2 extending therethrough in each of which are mounted two pistons 3 secured to opposite ends of a piston rod 4.
  • Formed in the center portion of each piston rod 4 is a pin mounting portion 7 from which a pin 8 extends radially outwardly.
  • the end of each pin 8 is received, through a double antifriction means 9, in the cam groove 18 formed in the cam means 20 as is the case with the embodiment shown in FIG. 10.
  • each cylinder 2 is provided with a suction and discharge valve 26 and an ignition plug 36, the valves and plugs being disposed on opposite end surfaces of the cylinder block 21.
  • the cam means 20 is provided with a gear 22 on its outer circumferential surface which is in meshing engagement with a gear 23 keyed to the rotary shaft I rotatably journaled by the fixed cylinder block 21.
  • a gear 22 on its outer circumferential surface which is in meshing engagement with a gear 23 keyed to the rotary shaft I rotatably journaled by the fixed cylinder block 21.
  • FIG. II is a view in section showing the machine in two planes normal to each other and taken through the center axis of the machine.
  • FIG. 12 shows the cam portions I0 and II and their respective cam faces 29 and 30. These cam portions I0 and II are disposed on the opposite end surfaces of the cam means 20 of FIG. II.
  • the gear 22 is mounted on the outer circumferential surface of the cam means 20.
  • the ninth embodiment shown in FIG. I3 is a modification of the embodiment shown in FIG. 10, in which the rotary shaft I extends through the fixed cylinder block 2
  • the mechanism for operating the valves, pistons, cam means and cam groove of this embodiment are identical with those of the embodiment shown in FIG. l0, except for the fact that the cam means 20 is not journaled by an outer casing but is connected to the rotary shaft 1 and immovable relative thereto, said rotary shaft I being rotatably supported by the cylinder block 2] through bearings 17.
  • This arrangement is advantageous when the machine is rotated at a high speed, for the peripheral speed of the cam means will be greatly increased as the rate of revolution of the machine is increased, making it difficult to support the cam means on its outer surface.
  • the bearings I7 are preferably provided with thrust bearing surfaces 3].
  • the tenth embodiment shown in FIG. I4 has two pistons 3 disposed inface to face relation in a single cylinder 2.
  • the two pistons in one cylinder have a stroke which is twice as great as the stroke of a single piston, and the space between the two pistons changes its volume at a rate twice as high as the rate at which the space would change its volume if only one piston were used. This permits to achieve a high resistance to heat in operation.
  • Cam means 20 are rotatably mounted within the cylinder block 21 in its opposite end portions. Each cam means 20 is formed with a cam groove I8 on its inner surface.
  • Said sliding block 40 is slidably mounted within a bush 39 connected to the cylinder block 2l and immovable'relative thereto.
  • the bush 39 is formed with a slot I6 through which the opposite ends of the pin 8 extend.
  • each pin is received and supported in a cam groove I8 at its opposite ends.
  • the cam grooves 18 of the machine shown in FIG. I4 are in the fomi of a curve shown in FIG. [7b.
  • the machine is thus provided with a cam groove for a 4-cycle operation, the machine is so constructed that two explosions occur during one rotation of the rotary shaft I, and suction and discharge valves are also constructed for a Z-cycle operation. Accordingly, the
  • the bush 39 and the sliding block 40 do not move in rotary motion relative to each other but move-in sliding motion relative to each other.
  • the pin 8 has mounted on its ends roller bearings 9 as are the case with the embodiments shown in FIGS. I0, II and 13.
  • a bearing 41 for supporting the piston rod 4 is mounted on the inner end of the bush 39.
  • Each bush 39 and said sliding block 40 serve as a cylinder and a piston in a way and constitute a means for supplying an air-fuel mixture to the cylinder 2.
  • the bearing 41 is formed with a duct 44 therethrough, in which is mounted a valve 43 under the influence of a spring 48. Said spring normally urges the valve 43 to close the duct 44.
  • the valve 43 is opened so as to deliver an air-fuel mixture from chamber III to chamber II.
  • the sliding block 40 is provided with a valve 42 and a spring 49 which act as-a check means.
  • Said check means operates in such a manner that an air-fuel mixture is supplied into the operation chamber III from outside when the pressure in said chamber is negative, and when the pressure in said chamber is increased as a result of the sliding movement of the sliding block 40, the valve is closed so as to prevent the airfueI-in the operation chamber III from flowing backwardly.
  • the sliding block 40 is formed with a main duct 51 for air-fuel mixture supply and a branch duct 50 branching off from said main duct to open in the operation chamber III and having said valve 42 mounted therein.
  • the air-fuel mixture in the operation chamber III begins to be compressed when the slotl6 is completely closed and the sliding block 40.
  • the volume in the operation the cylinder so that a sufficiently large quantity of air-fuel mixture can be supplied to the chamber III.
  • FIG. 15 showsan embodiment which combines the fifth embodiment shown in F 8'with the sixth embodiment shown in FIG. 9 and functions as an internal combustion engine.
  • the dam means 20 having the shape shown inrFlG. 5 is provided with a boss 24, through which the rotary shaft Iv extends and is immovable relative thereto.
  • the rotary shaft is rotatably mounted on-thc cylinder block 21 through the bearings I7.
  • the cam grooves I8 formed by the hollovi lcylindricalincmbers 6 and G are-disposed on the inner surface ollthebo's 'sl f of the cam means 20, while the cam grooves formed by the hollow cylindrical members 5 and 5 are disposed-on 6 outer surface'of the boss 24.
  • the cam grooves 18 and 15 are disposed relative to each other ihsuch a manner'that the pin 8 having its oppositezends received in said cam grooves is correctly disposed radially.
  • pin 8 is provided with antifrietion means 25 at the portioniwhere the pin- 8 extends through the slot 16, in order to *cai'ry the thrust applied to the ,pin when the reciprocating motion of the piston is converted into the rotary motion of the cam means 20.,The forces required for the conversion or motion are distributed to the opposite ends of the pin, thereby reducing the forces-applied to each end of the pin and the side surfaces of the cam grooves. This arrangement is very advantageous in designing the machine. 7
  • cam portions I0 and II for controlling the suction and discharge valves 26 are disposed on the end surfaces of the hollow cylindricalj'memb ers 5 which is disposed over the boss 4 in enclosing relation.
  • a buffer means for" absorbing .shock may be mounted betweenthe pin and the antifriction means, in order to reduce the shock to which-the pin 8 is subjected.
  • This buffer means may be one which relies on'oil or is formed of rubber.
  • the em bodimentshown in FIG. l6 relies on oil.
  • the pin'8 has at its end a grooved disc 54 in which is fittedan outeridisc 55.split into two portions and having projections positioned" against the grooves of the disc 54.
  • a space 56 Positioned between the grooves of the disc 54 and the projections of the outer disc 55 is a space 56 in which oil is sealed. In this case; the shock applied by the antifriction means is not transmitted directly to the pin but attenuated by the oil in the space 56, thereby preventing damage to the pin 8.
  • 57 designates 0 rings for preventing the leak of oil.
  • the cam groove 18 of the crankless reciprocating machine may vary its shape and configuration depending on whether the machine is used for a Z-cycle operation or a 4-cycle operation. Since the surface of the cam means which is large in area can be used to accommodate the cam groove, it is possible to provide for not only a 2-cycle or 4-cycle operation as aforementioned but also a 6-cycle operation when required. In machines of this type, it has hitherto been customary that the piston can make only one reciprocating motion during one rotational motion. The present invention permits the piston to make one to three reciprocating motions or more during one rotational motion. thereby increasing the output accordingly. FIG.
  • FIG. 170 shows the cam groove for a 2-cycle operation used with a compressible fluid.
  • FIGS. 17b and 17c are the cam grooves for 4-cycle operation and a 6-cycle operation respectively.
  • the cam groove for the cycle provided with a cooling stroke is shown in FIG. I7d.
  • the cooling cycle is provided in order to directly remove heat from the surfaces of piston and cylinder by drawing air by suction and discharging same as wcll as to completely scavenge the cylinder.
  • the piston need not cover the whole stroke distance in the cooling stroke; the usual practice is for the piston to move in reciprocating motion only a part of the stroke distance as shown in FIG. "(1. It is thus one of the advantages of the present invention that the piston can be arranged to 7 move in reciprocating motion through a part of the stroke distance when required. 7
  • crankless reciprocating machine useful as an expansion machine.
  • an expansible material is caused to operate in the operation chamber to provide a .tuming force
  • the cam groove suitable for use with this application is shown in FIG. 1 172.
  • the cam groove for a two cycle operation using a noncompressible fluid is shown in FIG. 17].
  • crankless reciprocating machine can be adapted for all types of operation in which the length of effective stroke of the piston and the time interval required for the piston to cover the stroke distance can he varied as desired.
  • the machine can be constructed in such a manner that the piston moves in quick feed and slow return or stops for a predetermined time interval.
  • the rotating part includes a cylinder means having a piston mounted therein and a rotary shaft or shafts firmly fixed to said cylinder means, and
  • an endless cam groove is formed on the inner side surface of a fixed casing.
  • concentric with each other are connected to opposite ends of a cylinder means and immovable relative to each other. These parts which constitute the rotating part are rotatably mounted in a fixed casing 81 by bearings 77 which support said rotary shafts 61.
  • a cylinder 62 is formed in the cylinder means 80. Slidably mounted in said cylinder 62 is a piston 63 to which a piston rod 64 is secured at one end.
  • the piston rod 64 is firmly connected at the other end to a pin mounting portion 67 slidable in the cylinder 62 together with the piston 63 as a unit and mounting a motion conversion pin 68 projecting radially outwardly of the cylinder.
  • the pin 68 extends through a slot 76 formed in the cylinder means 80, and the outer end of the pin 68 is received and moveable in a cam groove 78 formed by two cam mem bers 66 and 66 disposed on the inner surface of the fixed cas ing.
  • Said cam groove is in the form of a closed curve on the inner surface of the fixed casing, and the piston 63 makes at least one reciprocating motion while the cylinder means 80 makes one complete revolution.
  • the cam members 66 and 66 are hollow cylindrical members each having a curved end as is the case with the cam members 6 and 6' of FIG. 2. At least one of the rotary shafts 61 aligned axially and immovable relative to each other extends through one of the end walls of the fixed casing 81 and functions as an output shaft when the machine is used as an internal combustion engine or an expansion engine. It functions as an input shaft when the machine is used as a pump or a compressor.
  • FIG. 18 can be arranged such that multiple cylinders may be mounted.
  • FIG. 19 One example of this adaptation is shown in FIG. 19 as a thirteenth embodiment of the invention.
  • two pistons 63, and 63 each connected to one end of each of the piston rods 64 and 64 which are connected at the other end to opposite sides of a common pin mounting portion 67, are disposed in back to back relation and form a unit.
  • Two units are illustrated as being mounted coaxially in the cylinder means 80.
  • the cylinders 62 are in the form of an elongated cylinder in the cylinder means, two pistons in the center and the cylinder wall defining a common operation chamber.
  • Two cam grooves 78 and 78 are formed on the inner surface of the fixed casing 81.
  • the two units form a mirror image with respect to the center transverse section of the cylinder means 80. It is to be understood that the invention is not limited to the number and the arrangement of units described and illustrated herein, and that the number of units that can be arranged in the cylinder is infinite theoretically as is the case with the second embodiment illustrated in FIG. 3.
  • the multiple units of cylinders can be arranged not only coaxially as shown in FIG. 19 but parallel to and circumaxially about the axis of the rotary shaft like the third embodiment shown in FIGS. 4, and 6 and on a plurality of concentric circles as shown in FIG. 7.
  • the fourteenth embodiment shown in FIG. 20 is constructed as a rotary pump.
  • the cylinder means 80 including cylinders 62 arranged parallel to and circumaxially about the axis of the rotary shaft 61, spacer collar 82, piston rod rest 74, spacer ring 83 and bearing disc 72 are all keyed to the rotary shaft 61 for rotation therewith as a unit.
  • the bearing disc 72 is rotatably supported by the fixed casing 81 through a thrust bearing 84, and formed with bearing openings 73 each for supporting a piston rod at one end.
  • Each piston rod 64 is sup- .9 ported at the otherv end by one of the bearing members 65 each constituting the bottom of a cylinder 62.
  • the bearing members 65 also serve to center the pistons 63 with respect to the cylinders 62. Formed substantially in the center portion of verted into forces acting on the pin to urge the same to rotate aiong the cam groove.
  • the piston rest 74 is formed with a slot 76 disposed axially ofthe piston rod 64 for receiving therein the inner end portion of the pin 68 extending radially inwardly.
  • the slot 76 serves to guide said inner end portion of the pin 68 which moves in reciprocating motion with the piston 63 as a unit.
  • the outer surface of the piston rest 74 in the vicinity of the slot 76 serves to support the smooth surface of the pin mounting portion 67 and prevent the axial deflection of the piston rod 64.
  • the inner surface of the piston rest 74 in the vicinity of the slot 76 serves to support a slider means 75 mounted on the inner end of the pin 68.
  • the slider means 75 is supported by an antifriction means consisting of four rollers 70, for example, on four points on said inner end of the pin (See FIG. 21).
  • This arrangement ensures that the pin 68 is supported in such amanner that it is positively and precisely aligned axially at all times. It will readily be apparent that it is significant to maintain the pin in a position in which it is positively aligned axially at all times, because the antifriction means 69 will tend to slip out of the cam groove 78 unless the pin 68 is positively aligned axially.
  • the cam groove 78 is generally inclined relative to the direction of reciprocating motion of the piston rod 64.
  • the provision of said slider means 75 is conducive to preventing the deflection of the piston rod 64 caused by the arrangement set forth hereinabove and the deflection of the piston rod 64 caused by centrifugal forces applied thereto as the number of revolution of the machine increases.
  • the cam groove 78 will tend to apply to the pin a force directed axially of the piston rod 64. This force acts at the same time to cause the pin 68 to rotate parallel to the plane of the figure about the pin mounting portion 67.
  • the provision of the slider means 75 is also conducive to preventing this action.
  • the frictional dragging of the piston rod 64 on the piston rod rest 74 can be reduced by the rollers 70 of the slider means 75.
  • the fixed casing 81 is provided with a front cover 93 which is fixed thereto, said cover 93 being formed with a suction port 91 and a discharge port 93.
  • the cam groove is in the form of a curve of FIG. 17f for a two cycle operation.
  • the distance between the suction port 91 and the discharge port 92 should be selected such that the spacing is larger than the diameter of the cylinder 62 in order to prevent said two ports from being short-circuited through one of the cylinders 62 when said particular cylinder is released from indexing with the suction port and moved to be indexed with the discharge port.

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Cited By (32)

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US3745887A (en) * 1971-03-31 1973-07-17 Temco Contact Ltd Engine power unit
US3893433A (en) * 1973-07-02 1975-07-08 Resonance Motors Inc Rotary engine with rotating cylinders
US4157079A (en) * 1974-01-14 1979-06-05 Kristiansen Haakon H Internal combustion engine and operating cycle
US4180028A (en) * 1975-07-11 1979-12-25 Richter Paul A Fluid operated device
US4213427A (en) * 1978-06-16 1980-07-22 Alfonso Di Stefano Rotary engine
WO1982003889A1 (en) * 1981-04-27 1982-11-11 Stinebaugh Donald E Internal combustion engine
US4365940A (en) * 1978-06-14 1982-12-28 Toshio Hosokawa Rotary piston pump of axial type
WO1983001088A1 (en) * 1981-09-23 1983-03-31 Prodromos Bekiaroglou Engine with rotating cylinder wall
US4553508A (en) * 1981-04-27 1985-11-19 Stinebaugh Donald E Internal combustion engine
US4565165A (en) * 1984-02-17 1986-01-21 Papanicolaou John P S Internal combustion engine
US4658768A (en) * 1981-12-28 1987-04-21 Carson Douglas T Engine
WO1988005495A1 (en) * 1987-01-16 1988-07-28 Geelong Engine Co., Pty. Ltd. Axial engine
US4834033A (en) * 1986-10-31 1989-05-30 Larsen Melvin J Apparatus and method for a balanced internal combustion engine coupled to a drive shaft
AU610126B2 (en) * 1987-01-16 1991-05-16 Geelong Engine Co. Pty. Ltd. Axial engine
WO1995020722A1 (fr) * 1994-01-28 1995-08-03 Shouren Wu Moteur a explosion a piston
US5799629A (en) * 1993-08-27 1998-09-01 Lowi, Jr.; Alvin Adiabatic, two-stroke cycle engine having external piston rod alignment
FR2818314A1 (fr) 2000-12-19 2002-06-21 Robert Giacomin Machine alternative a pistons opposes
US6435145B1 (en) 2000-11-13 2002-08-20 Moises Antonio Said Internal combustion engine with drive shaft propelled by sliding motion
US6662775B2 (en) 1999-03-23 2003-12-16 Thomas Engine Company, Llc Integral air compressor for boost air in barrel engine
US6698394B2 (en) 1999-03-23 2004-03-02 Thomas Engine Company Homogenous charge compression ignition and barrel engines
US20040206316A1 (en) * 2003-04-16 2004-10-21 Terry Buelna Rotary piston motor
WO2004104376A1 (en) * 2003-05-23 2004-12-02 Attegro Inc. An engine with drive ring
US20070079791A1 (en) * 2005-10-07 2007-04-12 Bradley Raether WaveTech engine
US20080141801A1 (en) * 2005-10-07 2008-06-19 Wavetech Engines, Inc. Systems and methods for facilitating conversion between reciprocating linear motion and rotational motion
US7469662B2 (en) 1999-03-23 2008-12-30 Thomas Engine Company, Llc Homogeneous charge compression ignition engine with combustion phasing
WO2009056295A1 (de) * 2007-10-31 2009-05-07 Herbert Huettlin Kolbenmaschine
US8046299B2 (en) 2003-10-15 2011-10-25 American Express Travel Related Services Company, Inc. Systems, methods, and devices for selling transaction accounts
RU2450138C2 (ru) * 2010-03-15 2012-05-10 Игорь Антонович Холмянский Двигатель внутреннего сгорания
US20120192829A1 (en) * 2009-09-24 2012-08-02 Jin Hee Choi Crankless engine
NL2007988C2 (en) * 2011-12-16 2013-06-18 Griend Holding B V Cam follower with an angled axis of rotation.
US9032917B1 (en) * 2011-04-21 2015-05-19 Mark McNitt Barrel cam rotating cylinder engine
RU2833366C1 (ru) * 2023-11-10 2025-01-20 Владимир Сергеевич Остапенко Бесшатунный двигатель внутреннего сгорания

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DE3313611A1 (de) * 1983-04-14 1984-10-18 Siegfried 8598 Waldershof Imelauer Motor-/pumpen-aggregat
DE3326294A1 (de) * 1983-07-21 1985-01-31 Heinz 7303 Neuhausen Adomeit Ein oder mehrstufige kolbenkraftmaschine mit kurvengesteuerter kolbenbewegung
FR2574474A1 (fr) * 1984-12-07 1986-06-13 Snyders Rene Moteur deux temps
GB2205361A (en) * 1986-10-09 1988-12-07 Ah Soon Lee Compact air compressor
DE3731786A1 (de) * 1987-07-02 1989-01-12 Ernst Reimers Antriebsanordnung
DE4018354A1 (de) * 1990-06-08 1991-12-12 Ernst Reimers Antriebsanordnung
HRP970053B1 (en) * 1997-01-07 2009-10-31 Čular Želimir Two-stroke engine with spirally operating piston
JP2004263686A (ja) * 2003-01-06 2004-09-24 Toyota Industries Corp 往復動型ポンプ及び真空ポンプ

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US1572068A (en) * 1921-08-31 1926-02-09 Advanced Engine Co Inc Engine
US1569525A (en) * 1922-04-26 1926-01-12 Ivan L Owens Rotary engine
US1802902A (en) * 1928-05-12 1931-04-28 Brau Marcel Internal-combustion engine
US1876506A (en) * 1929-11-25 1932-09-06 Lee Engineering Res Corp Engine
US2269106A (en) * 1938-03-23 1942-01-06 Anton R Hoffmann Internal combustion motor
US2274097A (en) * 1938-10-27 1942-02-24 John B Sheerer Crankless engine
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Cited By (44)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3745887A (en) * 1971-03-31 1973-07-17 Temco Contact Ltd Engine power unit
US3893433A (en) * 1973-07-02 1975-07-08 Resonance Motors Inc Rotary engine with rotating cylinders
US4157079A (en) * 1974-01-14 1979-06-05 Kristiansen Haakon H Internal combustion engine and operating cycle
US4180028A (en) * 1975-07-11 1979-12-25 Richter Paul A Fluid operated device
US4365940A (en) * 1978-06-14 1982-12-28 Toshio Hosokawa Rotary piston pump of axial type
US4213427A (en) * 1978-06-16 1980-07-22 Alfonso Di Stefano Rotary engine
WO1982003889A1 (en) * 1981-04-27 1982-11-11 Stinebaugh Donald E Internal combustion engine
US4553508A (en) * 1981-04-27 1985-11-19 Stinebaugh Donald E Internal combustion engine
WO1983001088A1 (en) * 1981-09-23 1983-03-31 Prodromos Bekiaroglou Engine with rotating cylinder wall
US4658768A (en) * 1981-12-28 1987-04-21 Carson Douglas T Engine
US4565165A (en) * 1984-02-17 1986-01-21 Papanicolaou John P S Internal combustion engine
US4834033A (en) * 1986-10-31 1989-05-30 Larsen Melvin J Apparatus and method for a balanced internal combustion engine coupled to a drive shaft
WO1988005495A1 (en) * 1987-01-16 1988-07-28 Geelong Engine Co., Pty. Ltd. Axial engine
AU610126B2 (en) * 1987-01-16 1991-05-16 Geelong Engine Co. Pty. Ltd. Axial engine
US5799629A (en) * 1993-08-27 1998-09-01 Lowi, Jr.; Alvin Adiabatic, two-stroke cycle engine having external piston rod alignment
WO1995020722A1 (fr) * 1994-01-28 1995-08-03 Shouren Wu Moteur a explosion a piston
US6662775B2 (en) 1999-03-23 2003-12-16 Thomas Engine Company, Llc Integral air compressor for boost air in barrel engine
US6698394B2 (en) 1999-03-23 2004-03-02 Thomas Engine Company Homogenous charge compression ignition and barrel engines
US7469662B2 (en) 1999-03-23 2008-12-30 Thomas Engine Company, Llc Homogeneous charge compression ignition engine with combustion phasing
US6986342B2 (en) 1999-03-23 2006-01-17 Thomas Engine Copany Homogenous charge compression ignition and barrel engines
US6435145B1 (en) 2000-11-13 2002-08-20 Moises Antonio Said Internal combustion engine with drive shaft propelled by sliding motion
FR2818314A1 (fr) 2000-12-19 2002-06-21 Robert Giacomin Machine alternative a pistons opposes
US6938590B2 (en) * 2003-04-16 2005-09-06 Terry Buelna Rotary piston motor
US20040206316A1 (en) * 2003-04-16 2004-10-21 Terry Buelna Rotary piston motor
WO2004104376A1 (en) * 2003-05-23 2004-12-02 Attegro Inc. An engine with drive ring
US8046299B2 (en) 2003-10-15 2011-10-25 American Express Travel Related Services Company, Inc. Systems, methods, and devices for selling transaction accounts
US20070079791A1 (en) * 2005-10-07 2007-04-12 Bradley Raether WaveTech engine
US7360521B2 (en) 2005-10-07 2008-04-22 Wavetech Engines, Inc. Reciprocating engines
US20080141801A1 (en) * 2005-10-07 2008-06-19 Wavetech Engines, Inc. Systems and methods for facilitating conversion between reciprocating linear motion and rotational motion
US8171812B2 (en) 2005-10-07 2012-05-08 Wavetech Engines, Inc. Systems and methods for facilitating conversion between reciprocating linear motion and rotational motion
US8141475B2 (en) * 2007-10-31 2012-03-27 Herbert Huettlin Piston machine
CN101842554B (zh) * 2007-10-31 2013-01-30 赫伯特·许特林 活塞压缩机
US20100269688A1 (en) * 2007-10-31 2010-10-28 Herbert Huettlin Piston Machine
CN101842554A (zh) * 2007-10-31 2010-09-22 赫伯特·许特林 活塞压缩机
WO2009056295A1 (de) * 2007-10-31 2009-05-07 Herbert Huettlin Kolbenmaschine
JP2011501032A (ja) * 2007-10-31 2011-01-06 ヒュットリン，ヘルベルト ピストン機械
US20120192829A1 (en) * 2009-09-24 2012-08-02 Jin Hee Choi Crankless engine
RU2450138C2 (ru) * 2010-03-15 2012-05-10 Игорь Антонович Холмянский Двигатель внутреннего сгорания
US9032917B1 (en) * 2011-04-21 2015-05-19 Mark McNitt Barrel cam rotating cylinder engine
NL2007988C2 (en) * 2011-12-16 2013-06-18 Griend Holding B V Cam follower with an angled axis of rotation.
WO2013095112A1 (en) * 2011-12-16 2013-06-27 Griend Holding B.V. Cam follower with an angled axis of rotation
CN104066930A (zh) * 2011-12-16 2014-09-24 格瑞恩控股公司 具有成角度的旋转轴线的凸轮从动件
CN104066930B (zh) * 2011-12-16 2017-04-26 格瑞恩控股公司 具有成角度的旋转轴线的凸轮从动件
RU2833366C1 (ru) * 2023-11-10 2025-01-20 Владимир Сергеевич Остапенко Бесшатунный двигатель внутреннего сгорания

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GB1228181A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1971-04-15
FR1562381A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1969-04-04
DE1751073A1 (de) 1970-08-13

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