EP0035867A2 - Transmission à plateaux oscillants - Google Patents

Transmission à plateaux oscillants Download PDF

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Publication number
EP0035867A2
EP0035867A2 EP81300895A EP81300895A EP0035867A2 EP 0035867 A2 EP0035867 A2 EP 0035867A2 EP 81300895 A EP81300895 A EP 81300895A EP 81300895 A EP81300895 A EP 81300895A EP 0035867 A2 EP0035867 A2 EP 0035867A2
Authority
EP
European Patent Office
Prior art keywords
crankshaft
wabbler
carrier
ball
crankcase
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP81300895A
Other languages
German (de)
English (en)
Other versions
EP0035867A3 (en
EP0035867B1 (fr
Inventor
Joseph Scalzo
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Scalzo Joseph
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0035867A2 publication Critical patent/EP0035867A2/fr
Publication of EP0035867A3 publication Critical patent/EP0035867A3/en
Application granted granted Critical
Publication of EP0035867B1 publication Critical patent/EP0035867B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • 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
    • 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
    • F01B3/10—Control of working-fluid admission or discharge peculiar thereto
    • F01B3/101—Control of working-fluid admission or discharge peculiar thereto for machines with stationary cylinders
    • F01B3/102—Changing the piston stroke by changing the position of the swash plate

Definitions

  • This invention relates to wabbler plate engine mechanisms and has as its aim to introduce a variable displacement facility thereto which is simple in operation and preserves the stability of the mechanism. Such mechanisms are useful in internal and external combustion engines and in pumps.
  • Wabbler plate engine mechanisms broadly comprise a plurality of piston/cylinders arranged around a crankshaft axis, and coupled to arms of a wabbler plate rotatably mounted on a wabbler carrier, which is obliquely mounted on a crankshaft. As the crankshaft rotates, each piston is forced to reciprocate in its cylinder, and vice versa.
  • These mechanisms are known for example from U.S.Patent No.2 258 127 to Almen.
  • the mechanism described in that Patent resolved a number of problems inherent in wabbler plate mechanisms, particularly that of stabilizing the mechanism while permitting the wabbler plate arms to oscillate relative to each piston in a plane perpendicular to the axis thereof.
  • Almen describes the provision of ball races on curved surfaces of the wabbler plate and crankcase which confine a ball at the intersection thereof. As these races are only in alignment at the top dead centre and bottom dead centre positions of the pistons, the ball can never become displaced.
  • the Almen mechanism is quite satisfactory for fixed displacement but is not adapted to variable displacement.
  • a mechanism according to the invention comprises a crankcase having a crankshaft rotatable therein; a wabbler carrier obliquely mounted on the crankshaft; and a wabbler plate rotatably mounted on the carrier; a plurality of cylinders arranged around the crankshaft with pistons reciprocally moveable therein along axes substantially parallel to the rotational axis of the crankshaft, the wabbler plate having arms extending radially therefrom to bearings coupling each arm to a piston, each bearing permitting lateral movement of the respective arm relative to the axis of the piston; and a stabilizer mechanism operating between the wabbler plate and the crankcase comprising ball races formed in juxtaposed curved surfaces of the wabbler plate and a ball carrier on the crankcase, and a ball confined at the intersection of the ball races.
  • means are provided for shifting the rotational axis of the wabbler plate along the axis of the crankshaft, and the ball carrier on the crankcase parallel thereto, while simultaneously altering the angle between the crankshaft axis and the wabbler carrier to vary the stroke of the engine mechanism. Further, the effective lengths of the ball races of the stabilizer mechanism are variable to accommodate the alteration of said angle.
  • the crankshaft is slidably coupled to an output shaft, the shifting means being operable to shift the crankshaft relative to the output shaft.
  • the carrier is coupled by a flexible linkage to a connection fixed axially in relation to the crankcase, the linkage causing alteration of said angle as the shafts are shifted relative to one another.
  • One such linkage comprises links pivotally mounted on the connection and pivotally coupled to the wabbler carrier at a position eccentrically located with respect to the rotational axis of the crankshaft.
  • Another such linkage comprises a body integral with the wabbler carrier defining a slot extending substantially parallel to the rotational axis of the wabbler plate on the carrier, the fixed connection slidably engaging the slot to cause alteration of said angle upon relative axial movement of the body and the connection.
  • This arrangement is better suited to larger mechanisms, primarily for the reason that the crankshaft must normally be slotted to permit the connection to be mounted on the output shaft while engaging the slot in the body on the wabbler carrier.
  • the shifting means may take a number of forms, and various suitable systems are referred to herein.
  • the means may if desired be coupled to the output shaft to obviate the need for an auxiliary power source to effect the change, or for purely manual operation.
  • the mechanisms described herein can also be adjusted while they are operating, which is also facilitated by some form of automatic operation.
  • an engine embodying the invention can be adjusted to minimum displacement, while the effective capacity can be increased for high speed motoring. In this way, optimum fuel economy can be achieved. Adjustment can also be made while a vehicle is in motion, to match the engine to the vehicle road load requirements.
  • a crankshaft 2 is mounted in bearings 4 on a crankcase 6 and slidably coupled to an anchor member 8.
  • the anchor member is mounted in radial and thrust bearings 10 on the crankcase 6.
  • the crankshaft 2 supports a wabbler carrier 12, pivotally mounted on trunnion pins 14.
  • An annular wabbler plate 16 is mounted in thrust and radial bearings 18 on the carrier 12 and includes a plurality of arms 20 (in this embodiment five) extending radially therefrom.
  • a plurality of cylinders 22 are arranged around the crankshaft 2, with their axes parallel thereto, and a piston 24 is reciprocally movable in each cylinder.
  • each piston At the bottom of each piston is formed a pocket bore 26 having an open end directed radially inwards towards the crankshaft axis.
  • This bore 26 slidably receives a bearing piston 28 to which an arm 20 is coupled by means of a little end bearing on a wrist pin 30.
  • each arm 20 will describe a lemniscate, (a figure of eight on the surface of a sphere) and this movement is accommodated by the radial freedom afforded by the bearing piston 28 in bore 26, and the tangential freedom afforded by the designed end float on wrist pin 30, best shown in Figure 3.
  • the bearing piston 28 and wrist pin 30 assembly has the effect of transferring the engine torque reaction equally to all cylinders 22 from pistons 24 and to crankcase 6, with the exception of the frictional torque generated by the bearing surfaces.
  • a stabilizer mechanism is included. This mechanism consists of ball races 32, 34 formed in juxtaposed curved surfaces of the wabbler plate 16 and a ball race carrier 36 mounted on the crankcase 6 diametrically opposite one of the arms 20.
  • the race 34 in the ball race carrier 36 and the axis of the crankshaft 2 have a common plane, but the race 34 is concave with respect thereto, defining the arc of a circle with its centre at the intersection of the crankshaft axis and the axis of the trunnion pins 14.
  • the race 32 on the wabbler plate 16 defines a similar arc, but because of the rotation of the crankshaft 2 and wabbler carrier 12, the two races will only be aligned when the engine mechanism is at its top (TDC) or its bottom (BDC) dead centre position. At all other times the races will be mutually inclined and the stabilizer mechanism is completed by a ball 38 confined between the two races 32, 34 where they intersect or, in the extreme positions, overlap.
  • means are provided for shifting the crankshaft 2 axially with respect to the crankcase 6, and for simultaneously altering the angle between the wabbler carrier 12 and the crankshaft axis.
  • the latter alteration changes the stroke of the pistons 24 while the former shifts the oscillatory motion of the pistons 24 such that their respective top dead centre positions are properly located.
  • the shifting means in the embodiment of Figures 1 to 3 operates as follows:
  • the wabbler carrier 12 is pivotally mounted on the crankshaft 2 by trunnion pins 14.
  • the anchor member 8 carries a connection 62 to which a two piece link 64 is pivotally connected at one end. At its other end the link 64 is pivotally connected to a pin 66 mounted on the wabbler carrier 12.
  • An identical linkage will normally be provided on the opposite side of the wabbler carrier 2.
  • the ball race carrier 36 is slidably mounted in the crankcase 6 on rails 68 and coupled to the crankshaft 2 by a bearing member 70.
  • the bearing member 70 receives the rim 72 of a bearing ring 74 fixed on the crankshaft 2.
  • the bearing ring 74 is part of a counterweight assembly for preserving dynamic balance of the mechanism, which includes a counterweight 76.
  • each leaf spring 78 will be fully extended in the TDC or BDC position, while at minimum displacement, as shown in Figure 2, only a minimal flexure (if any) of the leaf springs is required in the TDC or BDC positions to prevent the ball 38 from moving to a seizure location in the races 32, 34.
  • the stabilizing forces are predominantly perpendicular to the plane of the ball race 34 the walls of the races 32, 34 provide the requisite resistance and the leaf springs 78 are not required to exert any force. Accordingly, their , stiffness can be very low but the spring rates of diagonally opposed pair of springs must be substantially equal.
  • the springs 78 play a secondary role while the engine is in motion at less than maximum displacement, but they become essential when the engine is stationary and the ball races 32 and 34 are aligned.
  • the stiffness of the springs 78 is a function of the size and weight of ball 38.
  • Axial shifting of the anchor member 8 has the effect of increasing or decreasing the stroke of the mechanism without compensation to the unswept volume (i.e. head volume). For example, if the stroke is slightly increased without changing the position of trunnion pins 14, the unswept volume is decreased by half or additional swept volume, and in combination with the increased swept volume the compression ratio is increased. Decrease of stroke will decrease the compression ratio.
  • Stabilizer ball races 32 and 34 must be increased in length to accept the additional piston stroke as too must cylinders 22 accept the additional piston stroke.
  • crankshaft 2 is in the form of a cylinder slidably mounted by means of splines 55 on an output shaft 56 that extends the length of the crankcase 6 supported in bearings 4 and 4'.
  • the shifting means for the crankshaft comprises a clutched gearbox 88 driven by a gear 90 fixed on the output shaft 56, and driving a member 92 axially fixed in relation to the crankcase 6 and the output shaft 56 by bearings 94 and 96.
  • the member 92 has external screw thread mating with a complementary internal screw thread on the crankshaft 2.
  • the gearbox 88 has a layshaft 98 supporting a gear 100 in permanent mesh with the gear 90 and a clutch gear 102 movable axially on the layshaft 98.
  • the clutch gear l02 is in mesh with a gear l04 on the member 92, the ratio between the gear 100 and the gear 90 being the same as that between the clutch gear 102 and the gear 104, thereby preventing relative rotation between the member 92 and the crankshaft 2 and fixing their relative axial position.
  • the clutch gear l02 is shifted so that it disengages from the gear 104 and one of the cone clutches 106 mates respectively with one of the gears l08 and 110, normally rotating freely on the layshaft 98, which are in permanent mesh with gears 112 and 114 on the member 92.
  • the gears 108, 110, 112 and 114 are so sized that movement of the clutch gear 102 to the right as shown in the figure causes relative rotation of the member 92 in one sense with respect to the crankshaft 2, and movement to the left in the other. Such relative rotation causes the crankshaft 2 to shift to the left or the right as shown.
  • the carrier 12 In order to simultaneously alter the angle of the wabbler carrier 12 to the crankshaft axis, the carrier 12 has abody 116 fixed thereto with a slot 118 formed therein and extending therefrom in a direction generally perpendicular to the plane of the carrier 12.
  • a pin 120 fixed with respect to the output shaft 56 engages the slot 118, sliding therealong as the crankshaft 2 is shifted, and forcing the angle to change.
  • the position of the slot 118 and pin 120 will be chosen to produce the desired characteristic, and the slot may be non-linear in certain circumstances.
  • a similar arrangement to that shown and described will normally be provided on the opposite side of the wabbler carrier 12.
  • the stabilizer mechanism in the embodiment of Figure 5 is similar to that of Figures 1 to 3 in that ball races 32 and 34 are provided on the wabbler plate 16 and a ball race carrier 36 but the means for varying the effective length of the races is different.
  • the length of race 32 is defined by stops 122 running in guides 124, the stops being continuously urged to the centre of the race by springs'126. Similar means might be employed on the ball race carrier 36, but a more definitive device is employed in this example.
  • the effective length of the race 34 is determined by stops 128, but the position of these stops is determined directly by a mechanical coupling to the movement of the crankshaft 2.
  • the ball race carrier 36 moves with the crankshaft, but this movement simultaneously rotates a double threaded shaft 130 through a non-locking screw and nut drive 132.
  • Followers 134 to the shaft 130 drive stops 128 via pins and shaped slots 136 to shorten or lengthen the ball race 34 in accordance with the sense of rotation of the shaft 130.
  • Mechanisms of the invention also have the ability tobe used in tandem, with two or more mechanisms being aligned and coupled to a common output shaft transmission system.
  • successive mechanisms may be mounted on a single shaft 56.
  • successive crankshafts and output shafts can be slidably coupled.
  • the mechanisms may also be coupled in a horizontally opposed arrangement, with cylinders 22 being aligned with their couterparts in another similar mechanism.
  • the ignition system would be incorporated between opposed cylinders, and it will be noted that by adapting the means for altering the angle of the wabbler carrier in one mechanism to be capable of making that angle 90°, that mechanism may be rendered inoperative, to provide greater reduction in the displacement ratio.
  • each of the adjustments referred to can be made while the mechanism is operated, and for a motor vehicle, even while the vehicle is in motion.
  • Such an application of the invention permits variation of engine capacity and compression ratio according to demand in a manner which can easily be effected between for example town use, motorway driving and acceleration.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transmission Devices (AREA)
EP19810300895 1980-03-11 1981-03-04 Transmission à plateaux oscillants Expired EP0035867B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
GB8008264 1980-03-11
GB8008264 1980-03-11
GB8038546 1980-12-02
GB8038546 1980-12-02

Publications (3)

Publication Number Publication Date
EP0035867A2 true EP0035867A2 (fr) 1981-09-16
EP0035867A3 EP0035867A3 (en) 1982-09-08
EP0035867B1 EP0035867B1 (fr) 1985-07-31

Family

ID=26274774

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19810300895 Expired EP0035867B1 (fr) 1980-03-11 1981-03-04 Transmission à plateaux oscillants

Country Status (3)

Country Link
EP (1) EP0035867B1 (fr)
AU (1) AU545777B2 (fr)
DE (1) DE3171533D1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0081205A1 (fr) * 1981-12-04 1983-06-15 Dieter Lehmann Moteur à combustion interne à plateau oscillant
EP0219298A3 (en) * 1985-10-11 1988-01-27 Sanden Corporation Variable displacement wobble plate type compressor
AU580579B2 (en) * 1984-02-18 1989-01-19 Ludwig Wenker Internal-combustion engine
RU2121589C1 (ru) * 1998-04-01 1998-11-10 Конюхов Виталий Алексеевич Способ регулирования мощности двигателя внутреннего сгорания методом изменения хода поршня и числа работающих цилиндров и двигатель внутреннего сгорания (варианты)
WO2003002893A1 (fr) * 2001-06-27 2003-01-09 Stuard Daevys Ensembles plaque oscillante
ES2937207A1 (es) * 2021-09-23 2023-03-24 Moran Emiliano Fernandez Bomba de pistones axiales

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4688439A (en) * 1984-04-17 1987-08-25 S. V. Engine Co. Pty. Ltd. Wabble plate engine mechansim

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR392320A (fr) * 1908-07-15 1908-11-24 Louis Renault Changement de vitesse hydraulique progressif avec débrayage et frein
FR432183A (fr) * 1910-09-28 1911-11-30 Temple Du Changement de vitesse hydraulique
DE540055C (de) * 1923-11-07 1931-12-07 Ludwig Le Bret Taumelgetriebe mit veraenderlichem Hub
DE636557C (de) * 1932-08-23 1936-10-12 Guenther Schneggenburger Dipl Schiefscheibengetriebe
GB463543A (en) * 1935-06-27 1937-03-30 Emil Goelz Improvements in or relating to hydraulic power transmission gears
DE669350C (de) * 1935-11-16 1938-12-23 Guenther Schneggenburger Dipl Taumelringgetriebe mit umlaufender Schiefscheibe
CH218712A (fr) * 1937-10-01 1941-12-31 Variable Speed Gear Limited Machine à pistons.
US2465638A (en) * 1945-05-24 1949-03-29 Samuel B Eckert Stroke varying mechanism for swash plate engines
FR57971E (fr) * 1948-01-28 1953-09-18 Applic Mecanique Automobile Et Transmission hydraulique et variateur de vitesse
AT175754B (de) * 1949-06-25 1953-08-10 Heinrich Dr Ing Ebert Stufenlos einstellbares Flüssigkeitskolben-Untersetzungs- oder Übersetzungsgetriebe, insbesondere für Werkzeugmaschinen
US2718758A (en) * 1949-07-15 1955-09-27 Borg Warner Variable ratio hydrostatic transmission
DE971177C (de) * 1949-10-20 1958-12-18 Karl Bauer Hydrostatischer Drehmomentwandler
US2908151A (en) * 1956-09-25 1959-10-13 Gunnar A Wahlmark Constant speed drive
GB906357A (en) * 1960-01-04 1962-09-19 New York Air Brake Co Hydraulic engine
FR1355385A (fr) * 1963-05-07 1964-03-13 Suzuki Motor Co Dispositif de transmission d'énergie hydrostatique
US3357209A (en) * 1965-12-13 1967-12-12 Gen Motors Corp Universal joint for a hydrostatic transmission
GB1204021A (en) * 1968-04-26 1970-09-03 Johannes Neukirch Power-branching hydraulic axial piston type transmission
DE2107729A1 (de) * 1971-02-18 1972-08-31 Hestermann G Taumelscheibengetriebe
DE2206101A1 (de) * 1972-02-09 1973-08-30 Franz Riedl Stufenlos regelbares getriebe mit einem taumelscheibenartig gelagerten glied
GB1502425A (en) * 1975-05-07 1978-03-01 Lucas Industries Ltd Stroke control apparatus for a variable stroke hydraulic pump

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0081205A1 (fr) * 1981-12-04 1983-06-15 Dieter Lehmann Moteur à combustion interne à plateau oscillant
AU580579B2 (en) * 1984-02-18 1989-01-19 Ludwig Wenker Internal-combustion engine
EP0219298A3 (en) * 1985-10-11 1988-01-27 Sanden Corporation Variable displacement wobble plate type compressor
RU2121589C1 (ru) * 1998-04-01 1998-11-10 Конюхов Виталий Алексеевич Способ регулирования мощности двигателя внутреннего сгорания методом изменения хода поршня и числа работающих цилиндров и двигатель внутреннего сгорания (варианты)
WO2003002893A1 (fr) * 2001-06-27 2003-01-09 Stuard Daevys Ensembles plaque oscillante
ES2937207A1 (es) * 2021-09-23 2023-03-24 Moran Emiliano Fernandez Bomba de pistones axiales

Also Published As

Publication number Publication date
EP0035867A3 (en) 1982-09-08
AU545777B2 (en) 1985-08-01
AU6827481A (en) 1981-09-17
DE3171533D1 (en) 1985-09-05
EP0035867B1 (fr) 1985-07-31

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