EP0874948A1 - Adaptive motor mechanism - Google Patents

Adaptive motor mechanism

Info

Publication number
EP0874948A1
EP0874948A1 EP96901158A EP96901158A EP0874948A1 EP 0874948 A1 EP0874948 A1 EP 0874948A1 EP 96901158 A EP96901158 A EP 96901158A EP 96901158 A EP96901158 A EP 96901158A EP 0874948 A1 EP0874948 A1 EP 0874948A1
Authority
EP
European Patent Office
Prior art keywords
beeing
crank
motion
interior
satellite
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.)
Withdrawn
Application number
EP96901158A
Other languages
German (de)
French (fr)
Inventor
Liviu Grigorian Giurca
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
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 EP0874948A1 publication Critical patent/EP0874948A1/en
Withdrawn legal-status Critical Current

Links

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
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/047—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft with rack and pinion
    • 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
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F01B9/023—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft of Bourke-type or Scotch yoke
    • 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
    • F02B75/047—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of variable crankshaft position
    • 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
    • F16H21/00—Gearings comprising primarily only links or levers, with or without slides
    • F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
    • F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
    • F16H21/18—Crank gearings; Eccentric gearings
    • F16H21/36—Crank gearings; Eccentric gearings without swinging connecting-rod, e.g. with epicyclic parallel motion, slot-and-crank motion
    • F16H21/365—Crank gearings; Eccentric gearings without swinging connecting-rod, e.g. with epicyclic parallel motion, slot-and-crank motion with planetary gearing having a ratio of 2:1 between sun gear and planet gear

Definitions

  • the present invent ion relat es t o an adapt iv mot or me ⁇ chanism which achieves the t ransformat ion of the alt erna ⁇ t ive mot ion of t ranslat ion in rot at ion mot ion and conver ⁇ sely, concomitant ly with the cont inuous adj ustment of the stroke .
  • This mechanism is useful - for thermic and hydrauli c machines, for machine t ools and for other struct ure .
  • the most used mechanism for thermic and hydraulic ma ⁇ chines is that one with connecting rod and crankshaft. Although it is a simple mechanism.it has many desadvan- tages.lt produces a considerable pressing force between piston and cylinder which has negative effects as to the durability.lt has a fixed stroke of the piston and that means for the engines a fixed compression ratio and a great dependence on the fuel sort.
  • the fixed compression ratio has a negative effect as to the super-charging pro ⁇ cess becose is necessary to reduce the air pression for certain conditions.
  • the diesel engines have a great com ⁇ pression ratio fixed for starting conditions but that is not adequate for the fuel economy and for the size of the engines.For gasoline engines the fixed compression ratio has a negative influence as to the volumetrical efficiency for little ana partial load.With this mechanism is very difficult to achieve a working interruption for certain cylinders to the little and partial load while other cy ⁇ linders work on.
  • the fixed stroke means an invariable flow.
  • a adaptiv motor mechanism having, in a first instance,at least one piston jointed with a connecting rod which transmits its alternative motion of transla ⁇ tion to a crank pin.
  • at least one piston in solidarity with a push rod,transmits its al ⁇ ternative motion of translation to a crank pin,using a slide which can oscilate inside a guide.
  • the crank pin belongs to a crank shaft which contains too a crank and a satellite which engages with an interior geared plate, consi ⁇ erated fixed for the same adjustment,the crank and the satellite having a planetary motion inside a main shaft which turns inside a crankcase.
  • the radial position of the interior geared plate can be changed using a gea ⁇ red sector ,situated at the external side of the inter ⁇ ior geared plate,this geared segment engaging with a worm.
  • the worm is drived,in a first variant, y a step- y- step motor or, in a second variant,
  • the ⁇ daptiv motor mechanism offers certain adventges. o the maximum stroke position the force between piston and cylinder is zero and in other positions is much diminiched. This mechanism can achieve a continuous variation of 5 the stroke and that means the continuous variation of the compression ratio and certainly of the capacity. That means for engines a very good adaption of the combustion parameters to the necessites and means too a maximalize of the effective efficiency.Other conse- 10 quence is that one as the same engine can use many types of fuel.This mechanism can achieve a stroke equal with zero and that means for engines the possi ⁇ bility of the working interuption for certain cylin ⁇ ders to the little and partial load while other cy- 5 linders work en.
  • variable capacity means for hydraulic machines a variable flow.
  • Fig.l is ⁇ naxial section through the adaptiv motor mechanism with connecting rods;
  • Fig.2 is a section in accordance to the tract A-A from Fig.l;
  • Fig.3 is a section in accordance to the tract B-B from Fig.l;
  • Fig.4 is anaxial section through the adaptiv motor mechanism with slide
  • Fig. is a section in accordance to the tract C-C p from Fig. .
  • the first mode of carrying out is represented in 5 Fig.l,2 and 3.
  • This mechanism uses two pistons 1 which transmit either i s alternative motion of translation to a connecting rod 2 using a bolt 3.
  • the connecting rods 2 are jointed to the other end with a crank pin a_ which belongs to a crank shaft 4.
  • the crank pin a is in solida ⁇ rity with a crank b, having a circular forme, and which is in solidarity too with a satellite £.
  • the satellite £ engages with an interior geared plate 5 » considerat ⁇ d fixe ⁇ for the same adjustment .
  • the crank shaft 4 has too a journal d in prolongation of the satellite £.
  • the crank b,the satellite c and the journal d have together ⁇ pla- netary motion inside a main shaft 6.
  • crank pin ⁇ a is forced to have a linear motion and the main shaft 6 is forced to have a rotation motion in ⁇ side a case 7.
  • he main shaft 6 has a breach £ whereby emerges that portion of the satellite £ which engages with the interior geared plate 5.
  • the radial position of the interior geared plate 5 can be changed using a gea ⁇ red segment f situated to the external side of the inter ⁇ ior geared plate 5 t which engages with a worm 8.
  • the worm 8 has a axle £ which is actuated by a step-by-step motor 9.
  • the rotation motion of the step-by-st ⁇ p motor 9 is con- troled by an electronic unit 10 which receives informa ⁇ tions from certain specific sensors 11 and from a selec ⁇ tor switch 12 which has many posit ions.
  • the selector switch 12 transmits the option of the user.
  • the interior geared plate 5 is hindered to have axial motion by a cover 13 fixed in the c ⁇ 3 ⁇ 7.
  • the secon ⁇ mode of carrying out is represented in Fig. 4 and 5.
  • This mechanism uses two pistons 1 solidarizated by a push rod 14 which has , in the idle zone, a guide h. T e ensemble maked up the pistons 1 and the push rod 14 transmits its alternative motion of translation to a slide 15 which can oscilate inside the guide h and which is jointed to the crank pin a.
  • the push rod 14 takes its alternative motion of translation as two guides 16, fixed in the case 7.
  • the rest of this mechanism is sirailary with that describet in the first instance exepting the driving of the.
  • the axle £ has a gear i t processed on it,which engages with a gear rack 17.
  • the gear rack 17 is drivit in linear motion by an actuator 18 which is controled by the electronic unit 10.
  • the both variants can operate only with one piston l,but with two pistons 1 the mechanism is more effi ⁇ ciently.
  • the worm 8 is turned with a certain angle the interior geared plate 5 what brings about the rotation with the same angle of the translation axis of the crank pin a,termed Y.
  • the stroke of the pistons 1 is diminished after a cosine law.
  • the connecting rods 2,past the translation motion will have too a swinging motion.
  • the slide 15 will have,past the translation motion after the axis X,a translation motion after an axis which coincides with the axis of the guide £,termed Z,which is perpendiculry on the axis X.
  • the specific sensors 11 transmit to the electro ⁇ nic unit 10 the informations about the charge of the engine,the rotation speed,the temperature of the cooling liquide,the temperature of the environment,the pression of the air in the intake manifoild,the contents of oxy ⁇ gen into the burned gases and about the ⁇ knocking.
  • the selector switch 12 serves for the transmission of the option of the user which can resolve a certain variant of programme memorized by the electronic unit 10,such as: -The engine will furnich the maximum power for all the working loads. hat means as the compression ratio will be regulate to the knocking limits for all . the working loads. -The engine will operate in the most economical mo ⁇ dality.That means as the compression ratio will , .be re ⁇ gulate so as to the effective efficiency to be maximum for all the working loads.
  • the engine will operate in the most reduced polu- tting modality.That means as the compression ratio will be regulate so as to the contents of harmful components to be at minimum in all the working loads.
  • the specific sensors 11 transmit to the electronic unit 10 the informations about the outlet pressure of the wor ⁇ king oil,the rotation speed of the main shaft 6, the inlet pressure of the working oil,etcetera.
  • he selector switch 12 serves for the transmisson of the option of the user which can resolve the value of the flow or the intteruption of the working of the pump while the dri- ving motor works on (only for the second constructive variant).
  • the worm 8 is possible to be actuated,for simple applications,using a kinematical chain directly by the user (without electronic unit,sensors,etcetera). These mechanisms can be used for other machines if the pistons 1 are replaced with certain specific tools.

Abstract

The present invention relates to an adaptive motor mechanism which achieves the transformation of the alternative motion of translation in rotation motion and conversely, concomitantly with the continuous adjustment of the stroke. This mechanism has two pistons (1) which drive, using two connecting rods (3), a crank shaft (4) which turns inside a main shaft (6). The crank shaft (6) includes a satelitte (c) which engages with an interior geared plate (5), considered fixed for the same adjustment. The interior geared plate (5) has to the external side a geared segment (f) engaging with a worm (8) which can change the radial position of the interior geared plate (5) and therefore the stroke of the pistons (1). This mechanism can be used for thermic and hydraulic machines or for any mechanical structure having need of variable stroke.

Description

ADAPTIVE MOTOR MECHANISM
TE CHNICAL FIELD
The present invent ion relat es t o an adapt iv mot or me¬ chanism which achieves the t ransformat ion of the alt erna¬ t ive mot ion of t ranslat ion in rot at ion mot ion and conver¬ sely, concomitant ly with the cont inuous adj ustment of the stroke . This mechanism is useful - for thermic and hydrauli c machines, for machine t ools and for other struct ure .
BACKGROUND ART
The most used mechanism for thermic and hydraulic ma¬ chines is that one with connecting rod and crankshaft. Although it is a simple mechanism.it has many desadvan- tages.lt produces a considerable pressing force between piston and cylinder which has negative effects as to the durability.lt has a fixed stroke of the piston and that means for the engines a fixed compression ratio and a great dependence on the fuel sort.The fixed compression ratio has a negative effect as to the super-charging pro¬ cess becose is necessary to reduce the air pression for certain conditions.The diesel engines have a great com¬ pression ratio fixed for starting conditions but that is not adequate for the fuel economy and for the size of the engines.For gasoline engines the fixed compression ratio has a negative influence as to the volumetrical efficiency for little ana partial load.With this mechanism is very difficult to achieve a working interruption for certain cylinders to the little and partial load while other cy¬ linders work on.
For the hydraulic pumps which use this mechanism, the fixed stroke means an invariable flow.
OBJECT OF THE INVENTION
It is therfore an object of the present invention to provide auch a continuous variable stroke of the piston is operated most efficiently in the thermic and hydrau¬ lic machines.
DISCLOSURE OF THE INVENTION
This object is attained according to the instant in¬ vention in a adaptiv motor mechanism having, in a first instance,at least one piston jointed with a connecting rod which transmits its alternative motion of transla¬ tion to a crank pin.In the second instance at least one piston, in solidarity with a push rod,transmits its al¬ ternative motion of translation to a crank pin,using a slide which can oscilate inside a guide.The crank pin belongs to a crank shaft which contains too a crank and a satellite which engages with an interior geared plate, consiάerated fixed for the same adjustment,the crank and the satellite having a planetary motion inside a main shaft which turns inside a crankcase.The radial position of the interior geared plate can be changed using a gea¬ red sector ,situated at the external side of the inter¬ ior geared plate,this geared segment engaging with a worm.The worm is drived,in a first variant, y a step- y- step motor or, in a second variant, y an actuator which is controled by an electronic unit receiving informations from certain specific sensors and from a selector switch which transmits the option of the user.The variation of a radial position of the interior geared plate brings about the change of the piston's stroke.For the good working of this mechanism is necessary that the distance between the rotation axis of the crank and the axis of the crank pin to be equal to the pitch radius of the satellite and equal to the half pitch radius of the interior geared plate.
ADVANTAGEOUS EFFECTS
The βdaptiv motor mechanism,according to the present invention offers certain adventges. o the maximum stroke position the force between piston and cylinder is zero and in other positions is much diminiched. This mechanism can achieve a continuous variation of 5 the stroke and that means the continuous variation of the compression ratio and certainly of the capacity. That means for engines a very good adaption of the combustion parameters to the necessites and means too a maximalize of the effective efficiency.Other conse- 10 quence is that one as the same engine can use many types of fuel.This mechanism can achieve a stroke equal with zero and that means for engines the possi¬ bility of the working interuption for certain cylin¬ ders to the little and partial load while other cy- 5 linders work en.
The variable capacity means for hydraulic machines a variable flow.
BRIEF DESCRIPTION OF THE DRAWINGS 0
Fig.l is βnaxial section through the adaptiv motor mechanism with connecting rods;
Fig.2 is a section in accordance to the tract A-A from Fig.l; 5 Fig.3 is a section in accordance to the tract B-B from Fig.l;
Fig.4 is anaxial section through the adaptiv motor mechanism with slide;
Fig. is a section in accordance to the tract C-C p from Fig. .
BEST MODES OF CARRYING OUT
The first mode of carrying out is represented in 5 Fig.l,2 and 3.This mechanism uses two pistons 1 which transmit either i s alternative motion of translation to a connecting rod 2 using a bolt 3. The connecting rods 2 are jointed to the other end with a crank pin a_ which belongs to a crank shaft 4. The crank pin a is in solida¬ rity with a crank b, having a circular forme, and which is in solidarity too with a satellite £.The satellite £ engages with an interior geared plate 5»consideratβd fixeα for the same adjustment .The crank shaft 4 has too a journal d in prolongation of the satellite £.The crank b,the satellite c and the journal d have together α pla- netary motion inside a main shaft 6. In the same time the crank pin ιa is forced to have a linear motion and the main shaft 6 is forced to have a rotation motion in¬ side a case 7. he main shaft 6 has a breach £ whereby emerges that portion of the satellite £ which engages with the interior geared plate 5. The radial position of the interior geared plate 5 can be changed using a gea¬ red segment f situated to the external side of the inter¬ ior geared plate 5twhich engages with a worm 8. The worm 8 has a axle £ which is actuated by a step-by-step motor 9. The rotation motion of the step-by-stβp motor 9 is con- troled by an electronic unit 10 which receives informa¬ tions from certain specific sensors 11 and from a selec¬ tor switch 12 which has many posit ions. The selector switch 12 transmits the option of the user. The interior geared plate 5 is hindered to have axial motion by a cover 13 fixed in the cβ3β 7.
The seconα mode of carrying out is represented in Fig. 4 and 5. This mechanism uses two pistons 1 solidarizated by a push rod 14 which has , in the idle zone, a guide h. T e ensemble maked up the pistons 1 and the push rod 14 transmits its alternative motion of translation to a slide 15 which can oscilate inside the guide h and which is jointed to the crank pin a. The push rod 14 takes its alternative motion of translation as two guides 16, fixed in the case 7. The rest of this mechanism is sirailary with that describet in the first instance exepting the driving of the. worm a.The axle £ has a gear i tprocessed on it,which engages with a gear rack 17.The gear rack 17 is drivit in linear motion by an actuator 18 which is controled by the electronic unit 10. The both variantes can operate only with one piston l,but with two pistons 1 the mechanism is more effi¬ ciently.
For the good working of these mechanisms is ne¬ cessary that the distance between the center of the crank b_ and the crank pin a.,termed L,to be equal to the pitch radius of the satellite £,termed M and equal to the pitch radius of the interior geared plate 5. ermed N,diminished to one half.Therefore:
L β M =- Other condition is that as the rotation axis of the main shaft 6 to pass through the geometrical center of interior geared plate 5«
When these mechanisms work to the maximum stroke (equal with 2xN) the translation axis of the crank pin a coincides with the translation axis of the pistons 1, termed X.In this position the connecting rods 2, res¬ pectively the slide 15, ill have only a translation mo¬ tion after axis X.
Using the worm 8 is turned with a certain angle the interior geared plate 5 what brings about the rotation with the same angle of the translation axis of the crank pin a,termed Y.The stroke of the pistons 1 is diminished after a cosine law.In this case,for the first construc¬ tive variant,the connecting rods 2,past the translation motion,will have too a swinging motion.For the second constructive variant the slide 15 will have,past the translation motion after the axis X,a translation motion after an axis which coincides with the axis of the guide £,termed Z,which is perpendiculry on the axis X. If the interior geared platejis turned with 90° given the situation of the maximum stroke position,in the case of the second constructive variant,it is interrup¬ ted the motion of the pistons l.the slide 15 oscillating only after the axis Z which coincides with the symme¬ trical axis of the mechanism.In this position the mecha¬ nism has the function of a coupled clutch because the stroke is equal with zero while the main shaft 6 can turn on.
INDUSTRIAL APPLICABILITY
If these mechanisms are used for internal combustion engines,the specific sensors 11 transmit to the electro¬ nic unit 10 the informations about the charge of the engine,the rotation speed,the temperature of the cooling liquide,the temperature of the environment,the pression of the air in the intake manifoild,the contents of oxy¬ gen into the burned gases and about the ^knocking. The selector switch 12 serves for the transmission of the option of the user which can resolve a certain variant of programme memorized by the electronic unit 10,such as: -The engine will furnich the maximum power for all the working loads. hat means as the compression ratio will be regulate to the knocking limits for all . the working loads. -The engine will operate in the most economical mo¬ dality.That means as the compression ratio will , .be re¬ gulate so as to the effective efficiency to be maximum for all the working loads.
-The engine will operate in the most reduced polu- tting modality.That means as the compression ratio will be regulate so as to the contents of harmful components to be at minimum in all the working loads.
If these mechanisms are used for hydrauic pumps the specific sensors 11 transmit to the electronic unit 10 the informations about the outlet pressure of the wor¬ king oil,the rotation speed of the main shaft 6, the inlet pressure of the working oil,etcetera. he selector switch 12 serves for the transmisson of the option of the user which can resolve the value of the flow or the intteruption of the working of the pump while the dri- ving motor works on (only for the second constructive variant).
The worm 8 is possible to be actuated,for simple applications,using a kinematical chain directly by the user (without electronic unit,sensors,etcetera). These mechanisms can be used for other machines if the pistons 1 are replaced with certain specific tools.
BIBLIOGRAPHY
l.SRUNWALD,Jβrtold,MTeoria,calculul gi constructia motoarelor pentru autovehicule rutiβre", Editura Di- actica gi pedagogicδ,Bucuregt i,1980.
2. MARIN, Virgil, MOSCOVICI, Rudolf, ENESLAV.Dumitru, "Sistβme hidraul^ce", Editura Tβhnica,Bucuregt i,1981.

Claims

1.An adaptiv motor mechanism which uses a crank shaft (4) beeing characterized in that this crank shaft (4) includes a crank pin (a) in solidarity with a crank (b),having circular forme but not obligatory, with a satellite (c) and with a journal (d),the satellite (c) engaging with an interior geared plate (5), considerat ed fixed for the same adjustment,the satellite (c),the crank (b) and the journal (d) having together a plnetary motion inside a main shaft (6) which is forced to turn inside a case (7) while the crank pin (a) has a linear motion, and in that the distance between the rotation axis of the crank (b) and the axis of the crank pin (a), termed L, is equal to the pitch radius of the satellite (c), termed M,and equal to the pitch radius of the interior geared plate (5), termed N, diminished to one hβlF, the relation between them beeing ,the rota
tion axis of the main shaft (6) passing through the geometrical center of the interior geared plate (5).
2.The mechanism defined in the claim 1 beeing characterized in that the crank pin (a) is connected, in a first constructive variant,with at least one piston (1) using a connectig rod (2) and a bolt (3), the piston (1) having a alternative motion of translation.
3.The mechanism defined in the claim 1 beeing characterized in that the crank pin (a) has attached on it, in a second constructive variant, a slide (15) which can oscilate inside a guide (h) included in a push rod (14) which has an alternative motion of translation on at least a guide (16), fixed in the case (7), the push rod (14) beeing solidarizated with at least one piston (1) or other working device.
4.The mechanism defined in the claim 1 beeing cha- racterized in that the interior geared plate (5) can change its radial position using a geared segment (f) which engages with a worm (8), solidarizated with a axle (g) and which can transmit a rotation motion to the interior geared plate (5).
5.The mechanism defined in the claims 1 and 4 beeing characterizated in that the axle (g) is drived, in a first constructive variant, by a step-by-step motor (9).
6.The mechanism defined in the claims 1 and 4 beeing characterizated in that the axle (g) includes, in a second constructive variant, a gear (i) engaging with a gear rack (17) which is drived by an actuator (18).
7.The mechanism defined the claims 1,2,3,4,5 and 6 beeing characterizated in that the adjustment of the step-by-step motor (9) respectively of the actuator (18) is controled by an electronic unit (10) which can decide to change the radial position of the interior geared plate (5) and therefore the stroke of the piston (1), the electronic unit (10) receiving informations from certain specific sensors (11) and from a selector switch (12), with many positions, which transmits the option of the user for a certain programme.
EP96901158A 1995-11-02 1996-01-18 Adaptive motor mechanism Withdrawn EP0874948A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
RO9501911 1995-11-02
RO95-01911A RO114370B1 (en) 1995-11-02 1995-11-02 Adaptive motor mechanism
PCT/RO1996/000002 WO1997016625A1 (en) 1995-11-02 1996-01-18 Adaptive motor mechanism

Publications (1)

Publication Number Publication Date
EP0874948A1 true EP0874948A1 (en) 1998-11-04

Family

ID=20102654

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96901158A Withdrawn EP0874948A1 (en) 1995-11-02 1996-01-18 Adaptive motor mechanism

Country Status (3)

Country Link
EP (1) EP0874948A1 (en)
RO (1) RO114370B1 (en)
WO (1) WO1997016625A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2421415Y (en) * 2000-05-08 2001-02-28 徐丁成 Driver for rotary motion and reciprocating straight motion
GB2371845B (en) * 2001-02-02 2005-01-12 Wymbs Engineering Ltd Movement output apparatus
FR2824121B1 (en) * 2001-04-27 2003-07-25 Renault DEVICE FOR DRIVING A CRANKSHAFT AND RECIPROCATING PISTON MOTOR
FR2825756B1 (en) * 2001-06-11 2004-03-12 Roger Lecal SYSTEM FOR MODIFYING THE P.M.H. OF A CONNECTING / CRANK MECHANISM

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Publication number Priority date Publication date Assignee Title
DE800264C (en) * 1948-10-02 1950-10-25 Maschf Augsburg Nuernberg Ag Stepless control of the deflection of a back and forth movement, especially for printing machines
GB1094649A (en) * 1963-12-16 1967-12-13 Henry Eddington Roberts Improvements in or relating to machines having a reciprocating member coupled to a rotatable member
FR2034244A1 (en) * 1969-02-28 1970-12-11 Touya Gilbert
DE3116851A1 (en) * 1981-04-28 1982-11-11 Hilti AG, 9494 Schaan DRILL AND CHISEL HAMMER
US4485768A (en) * 1983-09-09 1984-12-04 Heniges William B Scotch yoke engine with variable stroke and compression ratio
US4887560A (en) * 1988-06-20 1989-12-19 Heniges William B Crankshaft assembly for variable stroke engine for variable compression
FR2680402A1 (en) * 1991-08-12 1993-02-19 Bes Jean Paul Mechanism for reversible conversion of a uniform rotational movement into a sinusoidal (simple harmonic) reciprocating rectilinear motion of variable stroke, and engine including such a mechanism

Non-Patent Citations (1)

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Title
See references of WO9716625A1 *

Also Published As

Publication number Publication date
RO114370B1 (en) 1999-03-30
WO1997016625A1 (en) 1997-05-09

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