EP0127694A1 - Maschine mit Schwenkkolben und -kammern - Google Patents

Maschine mit Schwenkkolben und -kammern Download PDF

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Publication number
EP0127694A1
EP0127694A1 EP83105524A EP83105524A EP0127694A1 EP 0127694 A1 EP0127694 A1 EP 0127694A1 EP 83105524 A EP83105524 A EP 83105524A EP 83105524 A EP83105524 A EP 83105524A EP 0127694 A1 EP0127694 A1 EP 0127694A1
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EP
European Patent Office
Prior art keywords
machine according
eccentric
chamber
central pivot
shaft
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
EP83105524A
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English (en)
French (fr)
Other versions
EP0127694B1 (de
Inventor
Roger Bajulaz
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.)
Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to DE1983105524 priority Critical patent/DE127694T1/de
Priority to DE8383105524T priority patent/DE3376578D1/de
Priority to EP19830105524 priority patent/EP0127694B1/de
Publication of EP0127694A1 publication Critical patent/EP0127694A1/de
Application granted granted Critical
Publication of EP0127694B1 publication Critical patent/EP0127694B1/de
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
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C9/00—Oscillating-piston machines or engines
    • F01C9/005—Oscillating-piston machines or engines the piston oscillating in the space, e.g. around a fixed point

Definitions

  • the present invention relates to a piston machine with non-linear movements which can be used, inter alia, as an internal combustion engine, as a compressor, as a pump, etc. suppressing rectilinear movements of movable organs.
  • the object of the present invention is to provide a simple and robust construction machine, in which the problems of tightness, wear and maintenance are easy to master.
  • the pistons being driven in a rotational movement relative to the chambers in which they move, only the spherical shape is usable. These relative movements which are not carried out only in one direction, cause sealing difficulties between the pistons and their chambers.
  • the present invention therefore also aims to achieve such a machine in which the pistons do not do not rotate on themselves during the operating cycle and have a simple angular movement relative to their chambers and in which the pressures between pistons and chambers, due to compressions and explosions, are eliminated.
  • the oscillating chamber and piston machine according to the present invention is distinguished by the characteristics listed in claim 1.
  • FIGS. 1 to 6 comprises a single active unit for the simplicity of the illustration and of its description. It is obvious that in practice, a machine could comprise several active units, four, six or more for example, coupled together.
  • This machine comprises a through shaft 1 journalled on a frame 2 in two bearings 3.
  • a cylindrical central bearing 4 is carried by the shaft 1, the axis xx of this central bearing 4 is perpendicular to the axis of the shaft 1
  • This bearing 4 is made integral with the shaft 1 angularly using a key 5 and axially using a screw 6.
  • This cylindrical central bearing 4 serves as an articulation to a central pivot 7 whose longitudinal axis intersects the axis of the through shaft 1 at 0.
  • This central pivot 7 is therefore angularly and axially integral with the through shaft 1, but can perform relative to the latter, oscillations in a plane defined by the axis of said central pivot 7 and that of the through shaft 1.
  • the axis of the central pivot 7 can thus tilt relative to the axis of the traversing tree 1.
  • the through shaft 1 simultaneously constitutes a member for controlling the central pivot 7 to which it is mechanically connected.
  • the unitary machine illustrated further comprises two chambers 8, 9 each formed by a first external shell 10 and a second internal shell 11, the upper and lower ends of which are adjusted to one another and connected together as well as at the ends. of the central pivot 7 by means of latches 12 made integral with the central pivot by screws 13.
  • Each external shell 10 has a cylindrical boss 14 whose axis passes through the intersection O of the axes of the central pivot 7 and of the through shaft 1 and is perpendicular to these two axes.
  • a circular distribution ring 15 surrounds the two outer shells 10 and has two recesses receiving the bosses 14 of these shells 10. This distribution ring 15 is thus angularly integral with the shells 10 and therefore with the central pivot 7 and the through shaft 1 .
  • Seals are provided between the shells 10 and the distribution ring.
  • a passage 16 is made in the cylindrical bosses 14 of the external shells 10 connecting the chamber 8 respectively 9 to a recess 17, respectively 18 practiced in the distribution ring 15. These recesses 17,18 communicate, as will be seen below, by a passage 19.20 with lights 21 made in the frame 2, these lights being themselves connected to the suction or discharge pipes respectively of the machine, as well as to the ignition device of the machine .
  • Seals are provided between the distribution ring 15 and the frame 2.
  • the unitary machine illustrated also comprises two double pistons 22,23, each having two active faces 24,24a, respectively 25,25a evolving freely in chambers 8 and 9.
  • These active faces 24,25 of the pistons consist of added parts 26 on the pistons 22,23.
  • These inserts 26 can slide in their plane relative to the pistons so as to ensure self-centering of the latter in the chambers 8, 9.
  • These inserts 26 include sealing elements, for example in the form of segments, ensuring a tight seal. perfect tee between their edges and the internal walls of the chambers 8,9 formed by the shells 10,11.
  • the pistons 22, 23 each have a recess 27 giving passage to the through shaft 1 and comprise arms 28 at their upper and lower ends respectively. These arms 28 carry guide shoes 29 sliding in a bowl 30 formed in the ends of the central pivot 7. In this way the pistons are held in a fixed axial position relative to the central pivot 7 and are pivoted concentrically to this pivot, on this one.
  • the unitary machine illustrated also includes eccentrics 31, 32 journalled in the example illustrated concentrically with the through shaft 1 and whose active parts 33, 34 have axes which meet at the point O of intersection of the axes of the central pivot 7 and of the through shaft 1. These active parts of the eccentrics rotate in housings 35,36 formed in the pistons 22,23. It should be noted that each of the active parts of the eccentrics 33, 34 is traversed right through by the through shaft 1, which allows a construction in which these eccentrics are large while ensuring a large angle between the axes of these eccentric and the axis of the through shaft 1, allowing a large angular displacement of the pistons relative to each other.
  • This unitary machine also includes kinematic means imposing a relative rotation between at least one of the eccentrics 31,32 and the through shaft 1.
  • the two eccentrics 31,32 are dragged in rotation relative to the through shaft 1.
  • a first kinematic link connects the eccentric 31 to the through shaft 1 and a second kinematic link connects the eccentric 32 also to this through shaft 1.
  • the kinematic connection between the eccentric 31 and the through shaft 1 comprises a toothed pinion 37 integral with the eccentric 31 and concentric with the through shaft 1, meshing with a satellite pinion 38 pivoted idly on an axis 39 integral with a connecting rod 40 itself secured to the through shaft 1 using a key 48 and a screw 49.
  • This idler satellite pinion 38 also meshes with a toothed ring 41 rigidly fixed on the frame 2.
  • the ratio of reduction of this kinematic connection is such that the eccentric 31 rotates around the through shaft 1 at a speed V2 always greater than the speed of rotation V1 of the through shaft 1 and in the same direction as the latter.
  • the kinematic link connecting the eccentric 32 to the through shaft 1 comprises a pinion 42 secured to the eccentric and concentric to the through shaft 1 meshing with a first satellite pinion 43 pivoted idly on an axis 44 secured to a connecting rod 45 itself secured to the through shaft 1 using a key and a screw.
  • This connecting rod 45 carries a second axis 46 on which is journalled for a second satellite pinion 43a engaged, on the one hand, with the first satellite 43, and on the other hand, with a toothed crown 47 secured to the frame 2.
  • each piston 22, 23, performs inside the corresponding chamber 8, 9, two alternations for a revolution of the through shaft 1.
  • the reduction ratio of the kinematic connections is 1: 2.
  • the upper edge of the outer shell 10 is placed on a shoulder formed in the upper edge of the inner shell 11.
  • the latches 12 come to cap these two shells 10,11 to keep them in an axial position relative to the pivot 7 and simultaneously thanks to the external shoulder of the lock, the latter also blocks the radial position of the shells 10, 11 relative to the central pivot 7. This fixing also makes it possible to ensure sealing between the edges in contact with the shells.
  • FIG. 3 shows a variant in which the chambers 8, 9 have a rectangular section. This is without other possible, owing to the fact that compared to these chambers 8,9 the pistons 22,23 carry out a simple angular movement constituted only by a rotation around the central pivot 7 whose chambers are integral and concentric.
  • the axis of the pistons describes a cone, the apex of which coincides with the point O of intersection of the axes of the central pivot 7 and of the through shaft 1, without, however, the pistons turning on them- same, because of the sliding between these and their eccentrics.
  • the central pivot 7 performs an angular oscillation, causing in it the chambers 8,9 and the shells 10,11 which are integrally connected to it, around the cylindrical central bearing 4, causing a modification of the inclination the axis of this central pivot 7 relative to the axis of the central shaft 1.
  • a rotational movement takes place between the active parts of the eccentrics 33,34 and the respective pistons 22,23, so that these pistons do not rotate on themselves, although the eccentrics 31,32 do rotate around them of the axis of the through shaft 1.
  • the chambers do not necessarily have to be spherical, but can have any shape as far as the external and internal surfaces of these cham bres are surfaces of revolution having as axis, the axis of the central pivot 7. It is thus possible to design chambers whose external or internal generator is curvilinear, in an arc of a circle, broken, rectangular, etc.
  • the active parts of the eccentrics 33,34 can be very large without limiting the opening angle between two active faces of the two pistons 22,23 thanks to the fact that these eccentrics are placed very close to the center of the unit and that they can move inside the rooms 8,9. This arrangement is possible, due to the large opening of the pistons allowing them to move around the transverse axis 1.
  • the distribution ring 15 rotates at the same speed and in the same direction as the through shaft 1, these elements can be rigidly connected to each other, for example by a casing.
  • This casing would replace the connecting rods 40,45 and would carry the satellites 38,43 and 43a. This makes it possible to stiffen the entire construction and not to transmit all the torque through the shaft 1, but to take over part of it through this distribution ring 15 and the casing. It is thus possible to produce a very compact motor comprising a ring of dis outside contribution, but of small diameter all the same which is important for high speeds of rotation.
  • the pistons exert no force against the walls of the chambers, other than those due to the sealing rings. This greatly limits wear on the pistons and chambers.
  • the active surfaces of the pistons are self-centered.
  • the machine is well balanced owing to the fact that the two chambers are integral with the central pivot and that the imbalances formed by the pistons and the eccentrics can be easily compensated by balancing weights.
  • the pistons only carry out a pivoting movement around the axis of the central pivot 7 and an oscillation corresponding to that of this central pivot.
  • the chambers 8, 9 only oscillate on themselves around the bosses 14.
  • FIG. 10 A second embodiment of the machine is illustrated in FIG. 10.
  • This machine also includes a single active unit to simplify the description and its representation.
  • This machine comprises a fixed frame 70 containing all the moving parts of the machine.
  • This machine also comprises two pistons 71, 72, each having two active faces 73, 74; 73a, 74a formed, as in the first embodiment described by attached parts which can move relative to the pistons parallel to the active faces 73, 74 to ensure self-centering of these in the chambers 75, 76.
  • These pistons 71, 72 are, as in the first embodiment, guided axially and radially on a central pivot 77.
  • the external surface of this central pivot 77 constitutes the internal surface of the chambers 75, 76.
  • the external surfaces of these chambers 75, 76 are here also produced by shells 78 integral with the central pivot and having pins 79 coaxial and perpendicular to the axis of the machine and to the axis of the central pivot 77 and passing through the point of intersection O of these two axes.
  • These pins 79 have passages 80 and are engaged in housings made in a distribution box 81 comprising passages 82 communicating on the one hand with the passages 80 and on the other hand with intake ports 82a and exhaust, as well as an ignition member in the case of an internal combustion engine, practiced in, or fixed to the frame 70.
  • the machine also comprises two eccentrics 83, 84 whose active parts constituted by pins 85, 86 are housed in corresponding bearings pra stitched in the pistons 71, 72.
  • the eccentric 84 is journalled on a shaft 87 rigidly fixed to the frame 70 and extending coaxially to the longitudinal axis of the machine.
  • This eccentric 84 comprises a pinion 88 coaxial with the fixed shaft 87 kinematically connected to a ring gear 89 by means of two satellites 90, 91 pivoted idly on axes integral with the distribution box 81.
  • the other eccentric 83 is journalled on a control member, here formed by a motor shaft 92, pivoted in the frame coaxially with the longitudinal axis of the machine.
  • This motor shaft 92 is rigidly fixed on the distribution box 81.
  • the eccentric 83 carries a pinion 93 kinematically connected to a ring gear 94 secured to the frame 70 using a satellite 95 pivoted idly on an axis secured to the housing distribution 81.
  • the kinematic connections 93, 94, 95 connecting the eccentric 83 to the distribution box 81 and 88, 89, 90, 91 connecting the eccentric 84 to this same distribution box 81 have relationships such as with respect to this distribution box 81, the eccentrics rotate at the same relative speed, but in opposite directions.
  • the machine does not have a through shaft and the central pivot is only held by the distribution box 81 by means of the shells 78 of which it is integral.
  • the third embodiment of the machine illustrated in FIG. 11 is a machine comprising several active units, four in the example illustrated.
  • This machine comprises two groups of two units mounted in parallel on a drive shaft 100. Each of the groups comprises two units mounted in series on a through shaft 101.
  • each active unit comprises an oscillating central pivot 102 rotatably mounted on a through shaft 101.
  • This central pivot 102 is rigidly connected, as in the embodiments previously described, to two chambers constituted by shells 103 integral in rotation with the distribution box 104 around the through shaft 101.
  • a distribution box 104 cooperates with two active units.
  • this distribution box 104 cooperates with the fixed frame 105 and alternately connects the chambers of the active units to the inlet l06 and exhaust 106a ports formed in this frame 105.
  • Channels 107 of the distribution box 104 and 107a shells 103 are provided for this purpose.
  • each active unit also comprises two pistons 108, 109 whose active surfaces move inside the chambers 110, 111. These pistons are guided on the ends of the central pivots 102 as in the forms of previous execution.
  • pistons 108, 109 are mounted rotating on the active parts of eccentrics 112, 113, the axes of which intersect at the points of intersection of the axes of the central pivots 102 and of the through shaft 101.
  • each active unit is here integral with the through shaft 101, while the other eccentric 113 of each active unit is journalled concentrically with the through shaft and is connected by a kinematic link to the distribution box 104, which constitutes in this execution the control member.
  • This kinematic link comprises a pinion 114 integral with the eccentric 113, coaxial with the through shaft 101, meshing with a satellite pinion 115 idly pivoted on an axis carried by the distribution box 104 and simultaneously engaged with a toothed ring 116 integral of the fixed frame 105.
  • This kinematic connection is such that the eccentric l13 rotates around the through shaft 101 in the same direction as the distribution box 104, but at higher speed.
  • the distribution box 104 constitutes the control member of two coaxial active units.
  • One of the eccentrics 113 carries a pinion 117 coaxial with the through shaft 101 and meshing with a toothed wheel l18 secured to the motor shaft 100.
  • this drive shaft 100 further comprises a pinion 119 engaged with a satellite pinion 120 journalled idly on an axis integral with the fixed frame 105.
  • This satellite 120 meshes with a toothed wheel 121 integral with the through shaft 101.
  • the ratios of the various kinematic connections described are always such that the relative speeds of rotation of the eccentrics 112, 113 relative to the control member, here the distribution box 104, are equal, but in opposite directions.
  • the ratio between the toothed wheel 118 and the pinion 117 is 1.5: 1, that between the pinion 119 and the gear 121 of 1: 2 and that between the eccentric 113 and the distribution box 104, i.e. the kinematic link 114, 115, 116, of 1: 2.
  • the eccentric 113 when the distribution box 104 rotates in one direction, the eccentric 113 performs, relative to the housing 104, two rotations in the same direction and the eccentric 112, integral with the through shaft 101, performs two rotations in the opposite direction.
  • one revolution of the distribution box 104 corresponds to three revolutions in the same direction of the eccentrics 113 and to one revolution in the opposite direction of the eccentrics 112.
  • one turn of the motor shaft 100 corresponds to 1/2 turn of the distribution box 104, that is to say an opening and a closing of the pistons 108, 109.
  • This third embodiment of the machine is very compact, it allows the coupling of several groups of active units in a limited space, grouped around a single motor shaft.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP19830105524 1983-06-04 1983-06-04 Maschine mit Schwenkkolben und -kammern Expired EP0127694B1 (de)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE1983105524 DE127694T1 (de) 1983-06-04 1983-06-04 Maschine mit schwenkkolben und -kammern.
DE8383105524T DE3376578D1 (en) 1983-06-04 1983-06-04 Engine with oscillating pistons and chambers
EP19830105524 EP0127694B1 (de) 1983-06-04 1983-06-04 Maschine mit Schwenkkolben und -kammern

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19830105524 EP0127694B1 (de) 1983-06-04 1983-06-04 Maschine mit Schwenkkolben und -kammern

Publications (2)

Publication Number Publication Date
EP0127694A1 true EP0127694A1 (de) 1984-12-12
EP0127694B1 EP0127694B1 (de) 1988-05-11

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EP19830105524 Expired EP0127694B1 (de) 1983-06-04 1983-06-04 Maschine mit Schwenkkolben und -kammern

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EP (1) EP0127694B1 (de)
DE (2) DE127694T1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PT105954A (pt) * 2011-10-21 2013-04-22 Jorge De Heredia Motor rotativo de combustão interna
US12186222B2 (en) 2019-12-05 2025-01-07 Vision Quest Industries Incorporated Orthopedic device having wrap and single strap

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2094143A (en) * 1935-08-29 1937-09-28 Linley Corp Pumping apparatus
US2197959A (en) * 1937-06-02 1940-04-23 Roland Stanley Quartermaine Rotary prime mover, pump, compressor, and the like
FR85753E (fr) * 1963-02-07 1965-10-08 Procédé de génération d'une capacité périodiquement variable et machine volumétrique à fluide de travail qui en constitue l'application
US3895610A (en) * 1974-05-17 1975-07-22 Robert H Wahl Rotary Nutating engine
FR2316433A1 (fr) * 1975-07-03 1977-01-28 Bajulaz Roger Machine a piston spherique
FR2322282A1 (fr) * 1975-08-26 1977-03-25 Etienne Charles Mouvement mecanique spherotatif
GB2054043A (en) * 1979-07-23 1981-02-11 Sacchi G Semi-rotary hydraulic pump

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2094143A (en) * 1935-08-29 1937-09-28 Linley Corp Pumping apparatus
US2197959A (en) * 1937-06-02 1940-04-23 Roland Stanley Quartermaine Rotary prime mover, pump, compressor, and the like
FR85753E (fr) * 1963-02-07 1965-10-08 Procédé de génération d'une capacité périodiquement variable et machine volumétrique à fluide de travail qui en constitue l'application
US3895610A (en) * 1974-05-17 1975-07-22 Robert H Wahl Rotary Nutating engine
FR2316433A1 (fr) * 1975-07-03 1977-01-28 Bajulaz Roger Machine a piston spherique
FR2322282A1 (fr) * 1975-08-26 1977-03-25 Etienne Charles Mouvement mecanique spherotatif
GB2054043A (en) * 1979-07-23 1981-02-11 Sacchi G Semi-rotary hydraulic pump

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PT105954A (pt) * 2011-10-21 2013-04-22 Jorge De Heredia Motor rotativo de combustão interna
PT105954B (pt) * 2011-10-21 2014-10-27 Jorge De Herédia Motor rotativo de combustão interna
US12186222B2 (en) 2019-12-05 2025-01-07 Vision Quest Industries Incorporated Orthopedic device having wrap and single strap

Also Published As

Publication number Publication date
DE127694T1 (de) 1985-03-14
DE3376578D1 (en) 1988-06-16
EP0127694B1 (de) 1988-05-11

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