US3901093A - Axial piston machine - Google Patents

Axial piston machine Download PDF

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Publication number
US3901093A
US3901093A US382221A US38222173A US3901093A US 3901093 A US3901093 A US 3901093A US 382221 A US382221 A US 382221A US 38222173 A US38222173 A US 38222173A US 3901093 A US3901093 A US 3901093A
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Prior art keywords
piston
cone
swash
machine according
plate
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Expired - Lifetime
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US382221A
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English (en)
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Maurice G Brille
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Individual
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Priority claimed from FR7227465A external-priority patent/FR2194226A5/fr
Priority claimed from FR7321387A external-priority patent/FR2232951A6/fr
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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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/28—Control of machines or pumps with 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
    • F01B3/02—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis with wobble-plate
    • 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
    • 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
    • F02B75/26—Engines with cylinder axes coaxial with, or parallel or inclined to, main-shaft axis; Engines with cylinder axes arranged substantially tangentially to a circle centred on main-shaft axis
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • 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
    • F16H23/00—Wobble-plate gearings; Oblique-crank gearings
    • F16H23/04—Wobble-plate gearings; Oblique-crank gearings with non-rotary wobble-members
    • F16H23/08—Wobble-plate gearings; Oblique-crank gearings with non-rotary wobble-members connected to reciprocating members by connecting-rods
    • 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
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • F16H1/321—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear the orbital gear being nutating
    • 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

  • Such engines or compressors are constituted by cylinders, the axes of which are substantially parallel, and equidistant to each other and about a central axis.
  • the axes of the cylinders are substantially parallel to the central axis, or converge slightly towards the latter.
  • Certain solutions include an inclined disk fixed on the central shaft and rotating together therewith. This results in substantial frictions, since the peripheral speed of the disk is high.
  • the main object of the invention is to provide a system of transformation having a pivoting swash-plate, wherein the stresses on the driving or driven crank are of the same order as in a conventional engine provided with piston, connecting-rod and crankshaft, while the friction of the real pivot is almost non-existent, any jamming condition being removed.
  • a volumetric machine for compressors or engines of the axial or barrel type, includes an inclined pivoting swash-plate, and is characterized in that the pivoting swash-plate drives the crank of a driving or driven shaft, the pivoting of said swashplate being defined by a two-nappe frustum of cone integral with the swash-plate and rolling, without sliding, on a stationary two-nappe frustum of cone angularly integral with the frame of the machine, the twoctwonappe frustums of cone having as their common generatrix the bisectrix of the obtuse angle defined by the axis of the machine and the axis of the swash-plate.
  • the four frustums of cone coupled by twos are each split up into a conical gear for rotative positioning, the pitch cone of which is the cone concerned, on the one hand, and a frustum of cone for the bearing and the positioning of the apex, with an apex angle definitely smaller than that ofthe cone concerned, on the other hand, the surface ofsaid bearing frustum of cone projecting beyond either side of the frustum of cone concerned.
  • the two fixed elements disposed coaxially and held fast in the frame of the machine carry each a positioning gear for the rotation and a bearing frustum of cone with a smooth surface and an acute apex angle.
  • the assembly of the two coaxial elements fixed in rotation can be moved and adjusted in position with respect to the fixed frame of the machine, which allows varying the rate of compression of each piston in the cylinder thereof, the strokes of the pistons remaining, besides, constant, as defined by the angle of inclination of the pivoting swash-plate.
  • FIG. 1 is a diagram illustrating the principle of the kinematics of a volumetric machine according to the invention.
  • FIG. 2 shows the arrangement of the cones which roll on each other without sliding.
  • FIG. 3 is an axial section showing the principle of an embodiment of the machine.
  • FIG. 4 is an axial section of the machine along line IVIV of FIG. 5.
  • FIG. 5 is a transverse section along line VV of FIG. 4.
  • FIG. 6 is a transverse section along line VIVI of FIG. 41
  • FIG. 7 is a longitudinal section of the piston, connecting-rod, connecting-rod linking, swash-plate, and pivot assembly when the piston lies at its uppermost dead point.
  • FIG. 8 shows the path of the centre of the connecting-rod/swashplate connection, as projected onto a transverse plane.
  • FIG. 9 corresponds to FIG. 7 when the piston lies at its lowermost dead point.
  • FIG. 1 illustratesthe principle of the kinematics of the pivoting of an axial machine according to the invention.
  • the two cones considered are tangent to each other along their common generatrix AB (which is always in the plane of xx-yy).
  • the nappe ASA of the cone formed about xx is tangent to the nappe ASA" of the cone forme about yy along the half-straight line SA
  • the nappe BSB of the cone formed about xx is tangent to the nappe 858 of the cone formed about yy along the half-straight line SB.
  • a first feature of the invention is to use this kinematic arrangement to obtain the frictionless pivot for the swash-plate intended for transforming the motion of a barrel device.
  • the barrel defines cylinders, not shown, within each of which a piston slides, said piston being connected to the swash-plate 5 by a connecting-rod l (FIG. 3
  • a second feature of the invention is to remove the interferences of those surfaces which are not conjugated, so as to be able to materialize all the useful surfaces. To this end, said surfaces are truncated at the suitable locations, so that only frusto-conical surfaces remain (FIG. 3).
  • the stationary nappe ASA is limited by the two circles cc and dd, traces of two cylinders having xx as axis. Said nappe ASA defines thus a material solid limited by the inner and outer cylindrical surfaces of the annulus and by the frustum of cone cd-cd. cd-cd.
  • the second stationary nappe BSB is likewise limited to the frustum of cone ef-ef defining a material solid together with the cylindrical surfaces ee andff having xx as axis.
  • the frustum of cone cd is carried by the plate 1 and the column 2, which cannot rotate and are temporarily held fast as regards translation.
  • the frustum of cone ef is carried by the plate 3 and the column 4 concentric with the column 2.
  • the first rolling nappe ASA conjugate of the stationary nappe ASA, is limited to the frustum of cone glz defining a material solid together with the cylindrical surfaces gg and I111 having yy as axis (FIG. 3).
  • the second rolling nappe BSB conjugate of the stationary nappe B88, is likewise limited to the frustum of cone jl defining thus a material solid together with the cylindrical surfaces jj and I] having yy as axis.
  • the piece 5 is completed by the plate 6, the latter carrying a crankpin 7 which cooperates with the crank 8 of the driving or driven shaft 9.
  • One of the two pieces 5 or 6, say, 6, has a number of arms which is equal to the number of driving or driven cylinders.
  • Each arm Carries a joint 0, which can be spherical, which joint cooperates with the corresponding connectingrod 10.
  • the invention is characterized in the third place by the combination of the means (described hereinafter) used for constantly maintaining the coincidence at S of the apices of the two two-nappe cones, and preventing, on the other hand, said two cones from sliding on each other, whatever may by the loads and inertias generated in the system.
  • the invention is characterized in the fourth place by the combination of the means (described hereinafter) used for cancelling all the plays of the contacting rolling surfaces, and even maintaining some initial prestress between said surfaces.
  • a fifth feature of the invention is the combination of the means (described hereinafter) used for allowing the whole assembly illustrated in FIG. 3 to move axially along xx with respect to the fixed supporting frame and the cylinders (not shown), the axes of which are parallel, or substantially parallel to xx.
  • This feature enables varying the volumetric ratio of the barrel engine considered according to a principle known per se either voluntarily, or automatically, as a function of the load, the ambient temperature, or the nature of the fuel.
  • a sixth feature of the invention is the limitation of the driving or driven crankshaft to the shaft 9 and the crank 8.
  • any central extension along xx which would pass through the mechanisms corresponding to the preceding features, is excluded.
  • Said shaft 56 receives its motion through spur gears on the shaft 9, preferably between the two bearings 22 and 23. It passes between the branches of the star and between the cylinders (FIG. 4).
  • This shaft 56 which terminates above the cylinderhead of the engine, carries the earns 58 required for ensuring the valve timing in a four stroke engine, whether the number of cylinders is even or odd (while the valve timing through a central shaft would require an odd number of cylinders).
  • Said shaft 56 carries also the gears required for driving a short central shaft 61 carrying the flywheel 63, which runs at the speed of the engine, and constituting at the same time the axis of a rotor 66 for a mixer or a compressor.
  • FIG. 4 materializes more completely the diagrammatic FIG. 3.
  • the frustoconical surface gh (FIG. 3) is replaced by a conical gear 11 having the same apex S, and by a smooth frustum of cone 12 which has its apex S on yy and extends beyond either side of the imaginary surface of the frustum of cone g/z.
  • the smooth frustum of cone 12 (angle different from that of the toothed cone 1]) is preferably interior with respect to the conical gear 11, but it could be exterior with respect thereto. These two elements are carried by the swash-plate 5 and fixed thereon by means which are not shown.
  • the frustoconical surface ed (FIG. 3) is likewise replaced by a conical gear 13 having the same apex S, and by a smooth frustum of cone 14 which has its apex S on .rx' and extends beyond either side of the imaginary surface of the frustum of cone cd.
  • These two elements are carried by the column 2 and rotatively blocked with respect thereto by the key 15.
  • the two conical gears 1 1 and 13 mesh with each other, and have the same numbers of teeth.
  • the smooth frustums of cone l2 and 14 have always a common generatrix along 8'8 and, although their apex half-angles differ by a, they have equal diameters at the level of their respective intersections with the frustums of cone gh and cd.
  • the frustoconical surface jl is likewise replaced by a conical gear 16 having the same apex S, and by a smooth frustum of cone 17 which has its apex S' on yy and extends beyond either'side of the imaginary surface of the cone jl.
  • the gear 16 is exterior with respect to the frustum of cone 17, but the opposite position is equivalent as far as the invention is concerned.
  • the frustoconical surface ef of FIG. 3 is likewise replaced by a conical gear having the same'apex S, and by a smooth frustum of cone 19, which has its apex S on xx and extends beyond either side of the imaginary surface of the frustum of cone ef.
  • These two elements are carried by the plate 3 and by the column 4 concentrical with the column 2. They are fixed to said plate 3 by means which are not shown.
  • the two conical gears 16 and 18 mesh .with each other and have the same number of teeth.
  • the smooth frustums of cone l7 and 19 have always a common generatrix along 8 S and, although their apex half-angles differ by a, they have equal diameters at the level of their respective intersections with the frustums of cone jl and ef.
  • the cylindrical portion of the swash-plate 5 is closed by the plate 6 which carries the crankpin 7.
  • This crank-' pin carries a bearing 20 axially xx locked by the nut 21.
  • the bearing 20 is housed in the'crank 8, which rotates about the driving or driven shaft 9, the latter being carried by the bronze bushes or the rolle' r or needle bearings 22 and 23 in a manner such that it is capable of sliding lengthwise alon'g'xx.
  • the bearing 20 is illustrated as'a self-aligning roller bearing. lt might be replaced by a transverse double row ball bearing mounted in a spherical bush, or by two oppositely disposed tapered roller bearings mounted in a spherical sleeve.
  • the p'ositionof the' centre D of the bearing on the crankpin 7 can be determined by washers 24.
  • the conical pairs 11-13 and 1 6-8 define by their meshings two common points of the generatrix AB and ensure that the two two-nappe cones rotate on each other without sliding.
  • the general keying against rotation of the assembly of the two columns with respect to the fixed frame is obtained through the tenons 31 on the column 4, the tenon 32 on the frame 33, the screws 34 and the locknuts 35 thereof.
  • the frame 33 receives thus the reaction torque transmitted by the gears.
  • the two colums 2 and 4 are axially keyed to. each other by two screws 36, the locking means of which are not shown. Tightening the screws 36 causes the lifting of the column z alongg, and the lowering of the column 4 along xx. Through the agency of the, pairs of smooth cones 12-14 and 17-19, this would tend to reduce the angle a, but this is prevented by the bearing 20 and the crank 8. This tightening results thus in cancelling the plays of the smooth cones 12-14 and 17-19 and the plays of the bearings 20, 22 and 23 simultaneously, and even xx in giving to all said rolling surfaces a certain initial pre-stress by using the extension, compression, bending and torsional elasticity of all the parts of the system. v
  • the column, 4 (that is, from theforegoing, the assembly of 'the two columns) bears on a central spring 37.
  • Said spring 33 bears on a crown 38 screwed frame 33 by means of the thread 39.
  • the crown 38 is adapted to be rotated by a concentric gear 40, a pinion 41, a spindle 42, and a control means 43 provided with a locating means 44.
  • the control and the locating may At rest, the spring 37 pushes thewhole movable as sembly upwards against a stop 45 carried by the cover 46 connected to the frame 33.
  • the angular keying of the assembly of the movable gear obtained by means of the screws 34 has a slightplay. which allows the slight axial movement of said gear'during the operation under the effect of the equilibriumof the 1.
  • Oil under moderate pressure from the lubricating pump is introduced through the nozzle 67 into the enclosure constituted by the frame 33, the cover 46 and the plate 3. Said oil can only escape by the play of the cylindrical centring means 25 and through the calibrated jets 68, it being understood that between the nozzle 67 and the lubricating pump there is a nonreturn valve which is not shown.
  • the swash-plate is provided with a number of arms 47 which is equal to the number of pistons brought into action. This number can be any number from one (inclusive).
  • the engine may be a four-stroke or two-stroke internal-combustion engine, a controlled ignition engine, a compression ignition en gine, a steam engine, or a hot air engine (Stirlings cycle).
  • the points of articulation O of the connecting-rods on the arms 47 of the swash-plate are all equidistant from S and selected so as to lie substantially along the axes of the engine cylinders. These points might have been disposed within the plane Zz perpendicular to the axis yy at S, in order to obtain a left trajectory of projection in the shape of a symmetrical figure eight, with a minimum amplitude of the movement of O with respect to the axes of the cylinders (FIG. 3). It may be preferable, as shown in FIG.
  • the swash-plate comprises an upper portion 5, and a lower portion 6 which ends in the crankpin 7.
  • the upper portion 5 of the swash-plate carries the gear 11 and the smooth concave cone 12, which are respectively conjugated with the gear 13 and the smooth convex cone 14 carried by the column 2 and the plate 1, respectively.
  • the flutes 15 hold the gear 13 during the rotation.
  • the lower portion 6 of the swash-plate carries the gear 16 and the smooth concave cone 17, which are respectively conjugated with the gear 18 and the smooth convex cone 19. The positions thereof are inverted with respect to those shown in FIG. 4.
  • One of the five arms 47 (for a five cylinder machine) fixed to the swash-plate 6 is shown as carrying a connecting-rod couplin having a theoretical centre O.
  • the axis tr of the corresponding cylinder is parallel to xx, and along said axis the point of articulation of the connecting-rod to the piston is at P.
  • the axis of the connecting-rod is P0.
  • the point O is selected on the swash-plate in the trace plan 12 perpendicular to xx at the point S.
  • said point O describes a trajectory the trace of which inis an arc of a circle 0 0"O such that O S O O S O a, subtended by a subtense 00 which intersects at I the trace nn of the transverse plane of the machine which passes through S, in a manner such that OI IO.
  • the trace of said trajectory is a circle (FIG. 8) having a diameter equal to the deflection distance IO", and a centre U such that U] UO.
  • the axis P0 of the connecting-rod describes a conoid about tt, said conoid having an apex half-angle B.
  • a socket 87 concentric with the socket 83 is fixed on the piece 85 and carries a concave cone 88 which is conjugated with the convex cone 89 cut from the socket 90, the latter being concentric with the rod 81 and being held in position together with said rod on the arm 47 by the nut 91.
  • the axis KK passes through the contact generatrix of the conjugated frustums of cone 88 and 89 and through the contact generatrix of the conjugated frustums of cone 80 and 82, while defining large angles with said generatrices.
  • the connecting-rod will not rotate about its axis during the motion of the swash-plate, nor will the pivot supporting column 2 rotate. But if it is found advantageous (and it is, indeed) that the connecting rod should rotate on its axis, it is easy to make it do so by shifting both the contact segment of 89 towards the apex of its cone and the contact segment of 80 towards the apex of its cone. By shifting both of them in the opposite direction, the connecting-rod is caused to turn on itself in the reverse direction with respect to what has been observed previously.
  • a pinion 54 is keyed on the shaft 9 of the engine, anf follows the possible axial movement of said shaft.
  • a toothed wheel 55 meshes with said pinion, and has preferably a diameter twice that of said pinion, although this is not absolutely necessary according to the invention.
  • Said wheel is keyed on the shaft 56, which has its axis parallel to xx and has no axial movement. To prevent the relative angular keying between the shaft 9 and the shaft 56 from varying, the couple of gears thus defined has straight teeth.
  • the shaft 56 passes through two arms 47 of the swash-plate (FIG. without hampering the movement of the latter. lt passes likewise between two adjacent cylinders.
  • Said shaft 56 controls, through a pair of helical pinions 57, the oil pump, the fuel pump, and the ignition distributor in a controlled ignition engine (these three elements are not shown).
  • the shaft 56 is also able to control the injection pump of a compression ignition motor through means which are also conventional.
  • the shaft 56 emerges from the group of cylinders to enter the cylinderhead, and, by means of cams 58 diagrammatically illustrated, it ensures in a conventional way the valve timing of a four stroke engine.
  • a wheel 59 the diameter of which is equal to that of the wheel 55, said wheel 59 meshing with a pinion 60, the diameter of which is equal to that of the pinion 55.
  • Said pinion 60 is mounted on a shaft 61 coaxial with the shaft 9, running at the same speed and in the same direction as the latter.fandniaintaining the keying desired.
  • the teeth of the couple of gears 59-60 may be helical.
  • flywheels 62 and 63 are mounted on the shafts 9 and 61, respectively, and have unbalancing means 64 and 65 opposed by 180 to compensate for the primary torques of inertia'Thc shaft 61 carries a rotor 66 which ensures the distribution of the fuel mix in the controlled ignition engine, while creating a certain overfeeding in every case.
  • ihefl'ywhe'el 62 is used for controlling the transmission through a clutch (not shown), in spite of its possible slight axial displacement.
  • the reaction F3 of the cone 14 on the cone 12 should be perpendicular to the common generatrix S'S at the point where the latter intersects the generatrix ASB.
  • the angle Ss and A88 is thus selected at best.
  • the bearing 20 works exactly in the same way as a crankpin.
  • the conical bearing 12-14 works much better than a conventional bearing, owing to the low l-lertzian pressures.
  • the forces F 1, F2, F3 remain proportional.
  • the cones 17 and 19 do not produce any reaction: they would sooner tend to lift, so that a pre-stress is advantageous. In the vicinity of the lowermost dead point the pressure stresses on the arms 47 (3) and 47 (4) are very low, and are disregarded.
  • the inertias resulting from the masses of the pistons, connecting-rods, and swashplate become important. They are maximum in the uppermost position 01. when the cylinders are in even number, the inertias of two opposed pistons balance each other, and the resultant thereof is zero along the axis xx.
  • balancing masses (not shown) may be disposed in the hollows of the swashplate, at points such as 69 so as to obtain a resultant equal to zero.
  • the axial displacement of the system is only moderately advantageous, and it is preferred then to replace the spring 37 by shims.
  • a compression ratio of 7/1 at full load (which reduces the nitrogen oxides), and of 14/1 at the start (which ensures a good starting) may be selected, with values which vary continuously between l4/l and 7/1 for all the values of the E.M.P. (which, at reduced loads, ensures both complete combustions without any carbon monoxide or unburnt matters, and a thermal efficiency as good as at full loads).
  • the mechanical efficiency of the assembly described is excellent, the pollution and the mean specific consumption are very reduced.
  • the dampening is carried out by the lubrication oil passing through the enclosure defined by the piston 3 and the frame 33.
  • the selection of the size of the outlet holes 68 allows adjusting the value of such dampening.
  • Displacing the bearing surface 38 of the spring 37 by means of an exterior manual drive 40-41-42-43 allows modifying the average compression ratio one way or the other. This allows using fuels having very different octane numbers and volatility. Thus, in a controlled ignition engine, increasing mean ratios may be used for leadless gasoline, high-grade gasoline, methanol, and even for slightly hydrated methanol. In a compression ignition engine, different adjustments will be ensured for gas, oil and gasoline.
  • Said drive 40-41-42-43 may also be brought under the control of the instruments measuring the atmospheric conditions, and, in particular. the thermometer.
  • a volumetric machine of the so-called barrel or axial piston type including pistons which rest on an oblique pivoting swash-plate, characterized in that the pivoting swash-plate drives the crank of a driving or driven shaft, the pivoting of said swash-plate being defined by a two-nappe frustum of cone integral with the swash-plate and rolling, without sliding, on a stationary two-nappe frustum of cone angularly integral with the frame of the machine, the two two-nappe frustums of cone having as their common generatrix the bisectrix of the obtuse angle defined by the axis of the machine and the axis of the swash-plate.
  • a volumetric machine characterized in that the four frustums of cone coupled by twos are each split up into a conical gear for rotative positioning, the pitch cone of which is the cone considered, and a frustum of cone for the bearing and positioning of the apex, with an apex angle definitely smaller than that of the cone considered, the surface of said bearing frustum of cone extending beyond either side of the frustum of cone considered.
  • a volumetric machine char acterized in that the stationary two-nappe frustrum of cone is comprised of two elements ea h carrying gearing for rotation positioning and an acute bearing frustum of cone, while they are adapted to be rotatingly ad justed with respect to each other so as to remove the play of the gearings, and even create a certain rotation pre-stress, and adjusted, besides, in translation with respect to each other so as to remove the play of the bear ings, and even create a certain bearing pre-stress.
  • a volumetric machine characterized in that the assembly of the two elements coaxial to the frame of the machine is carried by a spring which allow a slight axial displacement thereof, which leads to the same displacement of the swash-plate and the driving shaft, this displacement being created by the value of the mean axial thrust of the pistons, hence the value of the effective mean pressure on the pistons,
  • a volumetric machine characterized in that the axial displacement is dampened by the lubrication oil trapped between the frame and the piston integral with the movable assembly, which oil goes in through a nozzleand a non-return valve, and comes out through calibrated jets to lubricate the mechanisms, the calibres of the jets allowing to adjust the amount of dampening.
  • a volumetric machine characterized in that the base of the bearing spring is adapted to be axially displaced by the rotation of a nut which is remotely controlled from the outside, so as to modify the mean compression ratio ofthe engine, while said drive for the nut may be manual to adapt said ratio I to various fuels having different octane numbers or volatilities, or brought under the control of a thermoinctric device to adapt said ratio to the atmospheric or starting conditions.
  • a volumetric machine characterized in that it includes a flywheel opposed to the driving or driven flywheel and running at the same speed as the latter while carrying masses for balancing the inertia torque.
  • said balancing flywheel being con-- trolled by an intermediate shaft parallel to the driving shaft and running at any speed, while being connected to the two shafts of the two flywheels by pairs of gear- 13 ings having identical gear ratios, said intermediate shaft passing through the gap between two arms of the swash-plate and the gap between the two corresponding cylinders.
  • a barrel or axial piston volumetric machine characterized in that the connection of each piston P to the periphery 47 of the swash-plate is ensured by two pairs of smooth cones (82 and 88 on the rod 93 of the piston P, and 80 and 89 on the swashplate 47) which roll on each other and are mounted in opposition, so that they ensure both the accurate positioning of the theoretical point of articulation O and the transmission through rolling of the all the load and inertia stresses.
  • a volumetric machine characterized in that the two segments of the contact generatrices of the two pairs of frustums of cone straddle the isospeed straight line KK', bisectrix of the angle a of the two basic cones 80, 82 or 88, 89 and defining an angle (90 11/2) with the axis of the cylinder, at being the angle of the axis yy of the swash-plate to the axis xx of the cylinder.
  • a volumetric machine characterized in that the male cones 80 and 89 are both fixed on the swash-plate 47, while the female cones 82 and 88 are both fixed on the connecting rod 93 of the piston P.
  • a volumetric machine characterized in that the two pairs of smooth cones include: one female conical rolling surface 82 integral with the rod 93 and converging towards the piston P;
  • a volumetric machine according to claim 8 characterized in that the two female cones 82 and 88 are fixed to the connecting-rod 93 of the piston P, while the male cones 80 and 89 are both fixed to the swash-plate 47.
  • a volumetric machine characterized in that the female conical rolling surfaces 82 and 88 are coaxial, and axially off-set with respect to each other, the face 82 being nearer to the piston P as the face 88, so as to define between them a gap in which the two conical faces and 89 of the swashplate 47 are housed in opposition.
  • annular frustoconical traclc' defined by the rolling face 82 has an outer diameter lower than the inner diameter of the annular frustoconical track defined by the rolling face 88, which allows housing a socket between said two tracks, said socket being integral with the swash-plate 47.
  • a volumetric machine characterized in that the mean rolling diameters of each pair of cones 80, 82 and 88, 89 are equal, so that the connecting-rod 93 does not turn on itself.
  • a volumetric machine characterized in that the mean rolling diameters of each pair of cones 80. 82 and 88, 89 are unequal, so that the connecting-rod 93 turns slowly on itself.
  • a volumetric machine characterized in that the angle (angle of the actual axis P0 of the rod 81 with respect to the theoretical axis P0" of the cylinder) is lower than, or equal to 3.
  • each piston P is rigidly fixed to its connecting rod 93 which is coaxial thereto, the bearing of the piston P on the cylinder 95 being spherical as well as that of the single compression ring 97, while an oil scraper-ring 99 is carried by a counter-piston which slides within the cylinder 95 and receives, through a spherical joint, the rear face of the oscillating piston P.
  • each piston P is rigidly fixed to its connecting rod 93 which is axial thereto, the bearing of the piston P on the cylinder 95 being conical, while that of its compression ring 97 is spherical, an oil scraper-ring 99 being carried by a counter-piston 100 which slides within the cylinder 95 and receives, through a spherical joint, the rear face of the oscillating piston P.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transmission Devices (AREA)
  • Retarders (AREA)
  • Reciprocating Pumps (AREA)
  • Friction Gearing (AREA)
US382221A 1972-07-25 1973-07-24 Axial piston machine Expired - Lifetime US3901093A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR7227465A FR2194226A5 (enrdf_load_stackoverflow) 1972-07-25 1972-07-25
FR7321387A FR2232951A6 (en) 1973-06-06 1973-06-06 Swash plate engine connecting rod linkage - comprises two sets of low-friction conjugate conical surfaces

Publications (1)

Publication Number Publication Date
US3901093A true US3901093A (en) 1975-08-26

Family

ID=26217244

Family Applications (1)

Application Number Title Priority Date Filing Date
US382221A Expired - Lifetime US3901093A (en) 1972-07-25 1973-07-24 Axial piston machine

Country Status (4)

Country Link
US (1) US3901093A (enrdf_load_stackoverflow)
JP (1) JPS5723142B2 (enrdf_load_stackoverflow)
GB (1) GB1444805A (enrdf_load_stackoverflow)
IT (1) IT991404B (enrdf_load_stackoverflow)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4258590A (en) * 1979-08-03 1981-03-31 U.S. Philips Corporation Wobble plate control for a variable piston displacement machine
US4803964A (en) * 1986-12-11 1989-02-14 Wladyslaw Kurek Internal combustion engine
US6481985B2 (en) * 2000-01-25 2002-11-19 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Maximizing the load torque in a swash plate compressor
US20030017060A1 (en) * 1995-07-25 2003-01-23 Lynn William Harry Fluid pumping apparatus
US20040255881A1 (en) * 2001-07-25 2004-12-23 Shuttleworth Richard Jack Axial motors
US20050076878A1 (en) * 2003-10-10 2005-04-14 Julius Drew Internal combustion engine with novel fuel/air delivery system
CH703399A1 (de) * 2010-07-02 2012-01-13 Suter Racing Technology Ag Taumelscheibenmotor.
US20150167547A1 (en) * 2013-12-09 2015-06-18 Joachim Horsch Internal combustion engine

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2403449A1 (fr) * 1977-09-20 1979-04-13 Screb Perfectionnements aux machines volumetriques axiales
GB2239304B (en) * 1989-12-22 1994-06-01 Jaguar Cars Torque transfer or reacting mechanism
JP3570628B2 (ja) * 2001-10-05 2004-09-29 株式会社東京機械製作所 印刷機用ポンプ
WO2009047838A1 (ja) 2007-10-09 2009-04-16 Fujitsu Limited 締結構造及び締結方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US790374A (en) * 1903-07-13 1905-05-23 Jonathan D Maxwell Explosive-engine.
US1255973A (en) * 1916-02-23 1918-02-12 Almen Crosby Motors Co Inc Engine.
US1300098A (en) * 1917-03-06 1919-04-08 John O Almen Internal-combustion engine.
US3333577A (en) * 1964-03-25 1967-08-01 Mongitore Pietro Rotary engine

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1105891A (en) * 1965-01-28 1968-03-13 Rolls Royce Reciprocating piston fluid displacement device

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US790374A (en) * 1903-07-13 1905-05-23 Jonathan D Maxwell Explosive-engine.
US1255973A (en) * 1916-02-23 1918-02-12 Almen Crosby Motors Co Inc Engine.
US1300098A (en) * 1917-03-06 1919-04-08 John O Almen Internal-combustion engine.
US3333577A (en) * 1964-03-25 1967-08-01 Mongitore Pietro Rotary engine

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4258590A (en) * 1979-08-03 1981-03-31 U.S. Philips Corporation Wobble plate control for a variable piston displacement machine
US4803964A (en) * 1986-12-11 1989-02-14 Wladyslaw Kurek Internal combustion engine
US20030017060A1 (en) * 1995-07-25 2003-01-23 Lynn William Harry Fluid pumping apparatus
US6733248B2 (en) * 1995-07-25 2004-05-11 Thomas Industries Inc. Fluid pumping apparatus
US6481985B2 (en) * 2000-01-25 2002-11-19 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Maximizing the load torque in a swash plate compressor
US20040255881A1 (en) * 2001-07-25 2004-12-23 Shuttleworth Richard Jack Axial motors
US7117828B2 (en) 2001-07-25 2006-10-10 Shuttleworth Axial Motor Company Limited Axial motors
US20050076878A1 (en) * 2003-10-10 2005-04-14 Julius Drew Internal combustion engine with novel fuel/air delivery system
US6904878B2 (en) * 2003-10-10 2005-06-14 Julius Drew Internal combustion engine with novel fuel/air delivery system
CH703399A1 (de) * 2010-07-02 2012-01-13 Suter Racing Technology Ag Taumelscheibenmotor.
US20150167547A1 (en) * 2013-12-09 2015-06-18 Joachim Horsch Internal combustion engine
US9453459B2 (en) * 2013-12-09 2016-09-27 Joachim Horsch Internal combustion engine

Also Published As

Publication number Publication date
GB1444805A (en) 1976-08-04
JPS5723142B2 (enrdf_load_stackoverflow) 1982-05-17
DE2337554A1 (de) 1974-02-07
DE2337554B2 (de) 1976-08-12
JPS4954058A (enrdf_load_stackoverflow) 1974-05-25
IT991404B (it) 1975-07-30

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