EP0035867B1 - Transmission à plateaux oscillants - Google Patents

Transmission à plateaux oscillants Download PDF

Info

Publication number
EP0035867B1
EP0035867B1 EP19810300895 EP81300895A EP0035867B1 EP 0035867 B1 EP0035867 B1 EP 0035867B1 EP 19810300895 EP19810300895 EP 19810300895 EP 81300895 A EP81300895 A EP 81300895A EP 0035867 B1 EP0035867 B1 EP 0035867B1
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.)
Expired
Application number
EP19810300895
Other languages
German (de)
English (en)
Other versions
EP0035867A3 (en
EP0035867A2 (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

Links

Images

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 US-A-2 258 127.
  • 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.
  • US-A-2 258 127 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 mechanism of US-A-2 258 127 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 movable 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, whereby the ball races of the stabilizer are adapted to limit the movement of the ball therein in accordance with 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 main shaft 2 is slidably axially with respect to the crankcase 6 in the bearings 4 and in the anchor member 8 in a close sliding fit.
  • Thrust bearing rings 40 and 42 are fixed to the crankshaft 2 and are rotatably mounted with respect to a member 44 by means of thrust bearings 46 and 48.
  • the member 44 has an external screw thread 50 which mates with a complementary internal screw thread 52 formed in the crankcase 6. Rotation of the member 44 with respect to the crankcase 6 shifts the crankshaft 2 axially within the engine mechanism.
  • a pinion gear 54 is shown for effecting this movement. Manual, electric, pneumatic or hydraulic mechanisms might be used to achieve this, with or without the use of the pinion gear 54.
  • crankshaft 2 is splined to an output shaft 56, this splined coupling 58 accommodating the axial shift of the crankshaft 2 without displacing a flange 60 on the output shaft 56 for coupling to for example the transmission system of a motor vehicle.
  • the wabbler carrier 12 is pivotally mounted on the crankshaft 2 by trunnion pins 14.
  • the anchor member 8 carries a connection element 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 piston 24 With the alteration of the angle of the wabbler carrier the stroke of each piston 24 is changed, as is the length of the arc required in each of the ball races 32 and 34.
  • means are provided to adapt the races 32 and 34 to limit the movement of the ball 38 when the stroke is reduced. As shown in Figures 1 and 2 a leaf spring 78 extends into each race 32, 34 to resliently urge the ball 38 towards the centre of the respective race.
  • 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 102 is in mesh with a gear 104 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 102 is shifted so that it disengages from the gear 104 and one of the cone clutches 106 mates respectively with one of the gears 108 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 a body 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 nonlinear 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 to be 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 counterparts 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transmission Devices (AREA)

Claims (13)

1. Un mécanisme de moteur à plateau oscillant comprenant un carter (6) de vilebrequin dans lequel est monté à rotation un vilebrequin (2); un support (12) de plateau oscillant monté en oblique sur le vilebrequin (2); et un plateau oscillant (16) monté de façon tournante sur le support (12); plusieurs cylindres (22) répartis autour du vilebrequin (2) et dans lesquels peuvent coulisser alternativement des pistons (24) le long d'axes sensiblement parallèles à l'axe de rotation du vilebrequin (2), le plateau oscillant (16) comportant des bras (20) s'étendant radialement à partir de celui-ci jusqu'à des paliers (30) accouplant chaque bras (20) avec un piston (24), chaque palier (30) permettant un mouvement latéral du bras respectif (20) par rapport à l'axe du piston (24), et un mécanisme stabilisateur opérant entre le plateau oscillant (16) et le carter (6) de vilebrequin et comprenant des voies (32, 34) de roulement de bille formées dans des surfaces incurvées juxtaposées du plateau oscillant (16) et d'un support (36) de voie de roulement de bille du carter de vilebrequin (6), ainsi qu'une bille (38) maintenue à l'intersection des voies de roulement (32, 34), caractérisé en ce que des moyens (44, 92) sont prévus pour faire déplacer l'axe de rotation du plateau oscillant (16) le long de l'axe du vilebrequin (2), et le support (36) de voie de roulement de bille sur le carter (6) de vilebrequin parallèlement à celui-ci, tout en modifiant simultanément l'angle entre l'axe de vilebrequin et le plateau oscillant (12) pourfaire varier la course du mécanisme de moteur, et en ce que les voies (32, 34) de roulement de bille du stabilisateur sont adaptées pour limiter le mouvement de la bille (38) dans celles-ci, en concordance avec ledit angle.
2. Un mécanisme de moteur conforme à la revendication 1, caractérisé en ce que le vilebrequin (2) est accouplé de façon coulissante à un arbre de sortie (56), en ce que les moyens de déplacement sont manoeuvrables de façon à faire déplacer le vilebrequin (2) par rapport à l'arbre de sortie (56); et en ce que le support (12) de plateau oscillant est accouplé par une transmission flexible à un élément de liaison (62, 101) pouvant être fixé axialement par rapport au carter (6) vilebrequin, la transmission produisant une modification dudit angle lorsque les arbres (2, 56) sont déplacés l'un par rapport à l'autre.
3. Un mécanisme de moteur conforme à la revendication 2, caractérisé en outre en ce que la transmission comprend des leviers (64) montés de façon pivotante sur l'élément de liaison (62) et accouplés de façon pivotante au support (12) de plateau oscillant dans une position placée excentriquement par rapport à l'axe de rotation du vilebrequin (2).
4. Un mécanisme de moteur conforme à l'une quelconque des revendications précédentes, caractérisé en ce qu'il comprend un moyen pour modifier additionnellement l'angle entre l'axe de vilebrequin et le support (12) de plateau oscillant, sans faire déplacer axialement l'axe de rotation du plateau oscillant (16) le long de l'axe du vilebrequin (2), pour faire varier la course du mécanisme.
5. Un mécanisme de moteur conforme à la revendication 3 et à la revendication 4, caractérisé en ce que le moyen de modification comprend un élément fileté (80) supportant l'élément de liaison (62) et venant se visser sur un filetage correspondant (84) du carter (6) de vilebrequin; ainsi qu'un moyen pour faire tourner l'élément (80) pour déplacer l'élément de liaison (62) axialement par rapport au vilebrequin (2).
6. Un mécanisme de moteur conforme à la revendication 2, caractérisé en outre en ce que la transmission comprend un corps (116) solidaire du support (12) de plateau oscillant et définissant une fente (118), orientée sensiblement parallèlement à l'axe de rotation du plateau oscillant (16) sur le support (12), l'élément de liaison (120) pouvant être fixé axialement venant coulisser dans la fente (118) pour produire une variation dudit angle lors d'un mouvement axial relatif du corps (116) et de l'élément de liaison (120).
7. Un mécanisme de moteur conforme à l'une quelconque des revendications précédentes, caractérisé en ce que les moyens de déplacement comprennent un élément fileté (14) venant se visser dans un filetage correspondant (52) du carter (6) de vilebrequin autour de l'axe de vilebrequin et accouplé au vilebrequin (2); ainsi qu'un moyen pour faire tourner l'élément (44) de façon à faire déplacer le vilebrequin (2) par rapport au carter (6) de vilebrequin.
8. Un mécanisme de moteur conforme à l'une quelconque des revendications 1 à 6, caractérisé en ce que le vilebrequin (2) est accouplé de façon coulissante à un arbre de sortie (56) et en ce que les moyens de déplacement comprennent une partie filetée tournante qui est fixée sur le vilebrequin (2) et qui vient se visser dans un filetage correspondant d'un élément auxiliaire tournant (92) coaxial à l'arbre de sortie (56) mais en étant axialement fixe par rapport à l'arbre de sortie (56), un moyen étant prévu pour produire une rotation relative du vilebrequin (2) et de l'élément auxiliaire (92) pour engendrer un mouvement axial relatif du vilebrequin (2), par rapport à l'arbre de sortie (56), le moyen d'entraînement en rotation pouvant être sélectivement actionné en fonction de la rotation de l'arbre de sortie (56).
9. Un mécanisme de moteur conforme à la revendication 8, caractérisé en ce que le moyen d'entraînement en rotation comprend un mécanisme à engrenages (88) accouplé entre l'arbre de sortie (56) et l'élément auxiliaire (92), ledit mécanisme à engrenages (88) comprenant un engrenage d'accouplement (102) pouvant être sélectivement actionné pour entraîner l'élément auxiliaire (92) à une vitesse de rotation différente de celle du vilebrequin (2).
10. Un mécanisme de moteur conforme à l'une quelconque des revendications précédentes, caractérisé en ce que les voies (32, 34) de roulement de bille du mécanisme stabilisateur sont définies par des rainures ménagées dans les surfaces respectives, des moyens élastiques (78,122, 178) étant prévus à une extrémité de chaque rainure pour empêcher un libre mouvement de la bille le long des voies de roulement (32,34) quand les voies sont alignées.
11. Un mécanisme de moteur conforme à la revendication 10, caractérisé en outre en ce que les moyens élastiques comprennent des lames élastiques (78).
12. Un mécanisme de moteur conforme à l'une quelconque des revendications 1 à 9, caractérisé en ce que les voies (32, 34) de roulement de bille du mécanisme stabilisateur sont définies par des rainures ménagées dans les surfaces respectives, la longueur effective de la rainure dans le support (36) de bille étant définie par des butées (128) montées de façon mobile dans la rainure, et en ce qu'une transmission mécanique (130, 132) est prévue entre les butées (128) et le vilebrequin (2) pour faire déplacer les butées (122) en synchronisme avec une variation de la cylindrée du mécanisme de moteur.
13. Un mécanisme de moteur conforme à l'une quelconque des revendications précédentes, comprenant un élément à contrepoids (76) accouplé rigidement au vilebrequin (2), caractérisé en ce que le contrepoids (76) est accouplé au moyen de déplacement de façon à conserver son effet d'équilibrage dans le mécanisme pour tous les réglages de cylindrée.
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 EP0035867A2 (fr) 1981-09-16
EP0035867A3 EP0035867A3 (en) 1982-09-08
EP0035867B1 true 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)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3148027C2 (de) * 1981-12-04 1986-07-24 Dieter 6072 Dreieich Lehmann Taumelscheiben-Brennkraftmaschine
DE3405893C2 (de) * 1984-02-18 1986-11-06 Ludwig 8543 Hilpoltstein Wenker Koaxialkolben - Taumelscheiben - Brennkraftmaschine
US4688439A (en) * 1984-04-17 1987-08-25 S. V. Engine Co. Pty. Ltd. Wabble plate engine mechansim
JPS6287678A (ja) * 1985-10-11 1987-04-22 Sanden Corp 斜板式可変容量圧縮機
AUPR592301A0 (en) * 2001-06-27 2001-07-19 Daevys, Stuart Dr A cross head mechanism for swash plate engines, motors and pumps
ES2937207B2 (es) * 2021-09-23 2023-07-31 Moran Emiliano Fernandez Bomba de pistones axiales

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

Also Published As

Publication number Publication date
EP0035867A3 (en) 1982-09-08
AU6827481A (en) 1981-09-17
EP0035867A2 (fr) 1981-09-16
AU545777B2 (en) 1985-08-01
DE3171533D1 (en) 1985-09-05

Similar Documents

Publication Publication Date Title
US4433596A (en) Wabbler plate engine mechanisms
CA2460259C (fr) Dispositif perfectionne de transmission a variation continue
US4077269A (en) Variable displacement and/or variable compression ratio piston engine
US6421903B2 (en) Continuously variable transmission and method of transferring loads in the same
US5113809A (en) Axial cylinder internal combustion engine having variable displacement
US20020043229A1 (en) Apparatus for varying the compression ratio of an internal-combustion engine
EP0453249B1 (fr) Moteur à combustion interne à pistons axiaux
US20110155106A1 (en) Internal combustion engine with variable compression ratio
US6514168B2 (en) Toroidal type continuous variable speed transmission
EP0035867B1 (fr) Transmission à plateaux oscillants
AU2007209223A1 (en) Crankshaft for a variable compression ratio engine
US4270400A (en) Continuously variable traction drive transmission
US5189927A (en) Variable ratio drive transmission
CN101634354A (zh) 一种曲柄圆滑块机构及其内燃机、压缩机
US7213545B2 (en) Reciprocating engine
CN108590849A (zh) 一种可实现米勒循环的曲柄连杆机构及控制方法
US3370510A (en) Barrel engine reciprocating to rotary movement mechanism
CA1209822A (fr) Mecanisme a plateau oscillant dans un moteur
CN208010466U (zh) 一种可实现米勒循环的曲柄连杆机构
US4565103A (en) Connecting rod bearings for a volumetric piston chamber machine
US9447727B2 (en) Variable displacement engine
CN209483480U (zh) 组合式偏心轴及可变压缩比发动机
WO2006061663A1 (fr) Moteur à combustion interne à double bloc de cylindres, avec mécanisme de poussoir à trèfle
CN114198213A (zh) 一种集成无级变速箱的可变排量及可变压缩比发动机
WO1988010382A1 (fr) Transmission mecanique

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): DE FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19830210

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SCALZO, JOSEPH

ITF It: translation for a ep patent filed

Owner name: MODIANO & ASSOCIATI S.R.L.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): DE FR GB IT

REF Corresponds to:

Ref document number: 3171533

Country of ref document: DE

Date of ref document: 19850905

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19890304

GBPC Gb: european patent ceased through non-payment of renewal fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19891130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19891201

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST