WO2013110700A1 - A reciprocating piston mechanism - Google Patents

A reciprocating piston mechanism Download PDF

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Publication number
WO2013110700A1
WO2013110700A1 PCT/EP2013/051333 EP2013051333W WO2013110700A1 WO 2013110700 A1 WO2013110700 A1 WO 2013110700A1 EP 2013051333 W EP2013051333 W EP 2013051333W WO 2013110700 A1 WO2013110700 A1 WO 2013110700A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
crank member
auxiliary
reciprocating piston
crankshaft
Prior art date
Application number
PCT/EP2013/051333
Other languages
French (fr)
Inventor
Lambertus Hendrik De Gooijer
Original Assignee
Sleper, Joannes, Jacobus, Josephus
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 Sleper, Joannes, Jacobus, Josephus filed Critical Sleper, Joannes, Jacobus, Josephus
Priority to KR1020147023200A priority Critical patent/KR102074649B1/en
Priority to EP13701256.3A priority patent/EP2828501A1/en
Priority to BR112014017873-9A priority patent/BR112014017873B1/en
Priority to US14/373,470 priority patent/US10234006B2/en
Priority to JP2014552664A priority patent/JP6305347B2/en
Priority to CA2861277A priority patent/CA2861277C/en
Priority to RU2014129394A priority patent/RU2623136C2/en
Priority to CN201380009329.8A priority patent/CN104204455B/en
Publication of WO2013110700A1 publication Critical patent/WO2013110700A1/en

Links

Classifications

    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/12—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
    • F16H37/124—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types for interconverting rotary motion and reciprocating motion
    • 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
    • F02B75/048—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable crank stroke length
    • 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
    • F16H21/22—Crank gearings; Eccentric gearings with one connecting-rod and one guided slide to each crank or eccentric
    • 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
    • F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
    • F02B41/02—Engines with prolonged expansion
    • F02B41/04—Engines with prolonged expansion in main cylinders
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18208—Crank, pitman, and slide

Definitions

  • the present invention relates to a reciprocating piston mechanism.
  • a reciprocating piston mechanism is described in an earlier application PCT/EP2009/059040 of the applicant.
  • the present invention aims to provide a further improved reciprocating piston mechanism.
  • the reciprocating piston mechanism comprises the features as defined in claim 1.
  • the bearing portion is eccentrically disposed with respect to the crankpin. This provides the opportunity to influence the bottom and top dead centre of the piston. Particularly, in case the mechanism is applied in an internal combustion engine it is advantageous to be able to adjust the compression ratio in terms of efficiency.
  • the gear ratio between the crank member gear and the auxiliary gear may be two.
  • the crank member rotates in the same direction as the crankshaft and at half speed thereof if the auxiliary gear has a fixed angular position with respect to the crankcase.
  • the mechanism may be provided with a drive means for turning the auxiliary gear with respect to the crankcase about the crankshaft axis.
  • the drive means may comprise a stop block, which is adapted to fix the auxiliary shaft at different angular
  • the stop block may comprise a control ring which is fixed to the auxiliary shaft and is provided with a plurality of recesses, and an actuator including a controlled displaceable pin that fits in each of the
  • the drive means is provided with a spring that is fixed to the auxiliary shaft and the crankcase. If the mechanism is applied in an internal combustion engine the actual combustion forces caused by the combustion stroke may force the auxiliary shaft to turn in angular
  • the control ring may be rotated in opposite direction by selecting an engine load at which the spring force is higher than the actual rotational force of the auxiliary shaft on the spring.
  • the drive means is provided with a spring that is fixed to the auxiliary shaft and the crankcase without a locking member for fixing the angular position of the auxiliary shaft.
  • the angular position of the auxiliary shaft is automatically balanced on the basis of the actual force of the auxiliary shaft onto the spring and the actual spring force onto the auxiliary shaft.
  • the stop block may comprise a control ring which is fixed to the auxiliary shaft in rotational direction thereof, and an electromagnet may be present for fixing the control ring to the crank case, wherein the mechanism is preferably provided with a spring that is fixed to the auxiliary shaft and the crankcase.
  • auxiliary shaft can be locked with respect to the crank case at various angular positions continuously.
  • this may function in the following manner. If a different compression ratio is desired the electromagnet is switched-off such that the auxiliary shaft is rotatable with respect to the crankcase. If the engine is operated at a higher engine load, in which a lower compression ratio is desired, the actual
  • the control ring including the auxiliary shaft is locked to the crankcase. If the engine is operated at a lower engine load, in which a higher compression ratio is desired, the electromagnet is switched-off and the control ring will be turned in the opposite direction since the actual rotational force of the auxiliary shaft on the spring at the corresponding relatively low engine load is smaller than the spring force. The control ring can then be locked in its new position by means of switching-on the electromagnet .
  • the drive means may comprise a drivable worm meshing with a worm gear which is fixed to the auxiliary shaft. This provides the opportunity to vary the angular
  • this embodiment of the mechanism may be provided with a pressure sensor at the worm which is an indication of the combustion pressure.
  • the worm in combination with a pressure sensor is not necessarily related to a mechanism as described hereinbefore; it may also be applied in other reciprocating piston mechanisms in which, for example, the angular position of a central gear is driven by a worm to adapt the compression ratio, for example in the mechanism as described in PCT/EP2009/059040.
  • the invention is also related to a reciprocating piston mechanism according to claim 11.
  • the mechanism provides the opportunity to vary the top dead centre of the piston by means of adjusting the angular position of the auxiliary shaft with respect to the crankcase.
  • the crank member and the auxiliary wheel are driveably coupled to each other by means of a transmission, formed by gears, chains, belts or the like. It is noted that the speed of rotation of the crank member and the crankshaft is defined in respect to the crankcase.
  • crank member gear meshes with at least a further intermediate gear which also meshes with the auxiliary gear, since this distributes forces within the mechanism.
  • the internal diameter of the crank member can be enlarged at an end portion thereof. This means that the internal diameter at the end portion is larger than at its central cylindrical portion where it contacts a cylindrical portion of the crankpin during rotation of the crankshaft. This provides the opportunity to enlarge the diameter of the crankshaft adjacent to a cylindrical portion of the crankpin. In such a case the crank member gear may partly protrude beyond the cylindrical portion of the crankpin in longitudinal direction thereof. This is advantageous in terms of rigidity of the crankshaft and building in a compact manner as seen along the crankshaft axis.
  • the protruding end portion of the crank member is also advantageous if the crankpin is mounted to an adjacent crank arm by means of a press fit, because it provides the opportunity to create a relatively long press fit connection between the crankpin and the crank arm as seen in axial direction of the crankpin.
  • the length of the press fit in axial direction of the crankpin may be larger than 30% of the diameter of the crankpin, and is preferably larger than 40% thereof.
  • the crank member may comprise a second crank member gear for driving at least a further crank member including a further crank member gear, which further crank member is
  • crank member gear and the second crank member gear are located at opposite end portions of the crank member , wherein the second crank member gear meshes with a further auxiliary gear which is fixed to a shaft that extends through an adjacent crank arm and on which shaft another auxiliary gear is fixed which meshes with the further crank member gear, wherein the diameter of the crankpin at the crank member gear is smaller than the diameter of the further crankpin at the further crank member gear.
  • cooperating connecting rod may also be smaller than that of the connecting rod which cooperates with the further crankpin.
  • the diameter of the crank member gear may be smaller than the diameter of the second crank member gear and/or the width of the crank member gear may be smaller than the width of the second crank member gear.
  • Fig. 1 is a perspective view of an embodiment of a reciprocating piston mechanism according to the invention.
  • Figs. 2 and 3 are perspective views of a part of the embodiment of Fig. 1 on a larger scale and seen from different sides .
  • Figs. 4 and 5 are similar to Figs. 2 and 3, but illustrating the part including the crankshaft.
  • Fig. 6 is a perspective view of a part of an alternative embodiment of the part as shown in Figs. 2 and 3.
  • Fig. 7 is a perspective view of a part of an internal combustion engine which is provided with an embodiment of the mechanism according to the invention.
  • Fig. 8 is a comparable view as Fig. 7, but showing an alternative embodiment as seen from a different side.
  • Fig. 9 is a side view of the embodiment as shown in Figs. 4 and 5.
  • Fig. 10 is a side view of the embodiment as shown in
  • Fig. 11 is a similar view as Fig. 1, but showing an alternative embodiment.
  • Fig. 12 is a perspective view of a part of the embodiment of Fig. 11 on a larger scale.
  • Fig. 13 is a perspective view of a multi-cylinder internal combustion engine which is provided with an embodiment of a reciprocating piston mechanism according to the invention.
  • Fig. 14 is a similar view as Fig. 13, but without showing the crankshaft.
  • Fig. 15 is a side view of the embodiment as shown in
  • Fig. 16 is a perspective view of a part of the embodiment as shown in Fig. 13.
  • Figs. 17-20 are similar views as Fig. 4 in which a bracket is eliminated to illustrate positions of different parts under operating conditions.
  • Fig. 21 is a perspective view of an alternative
  • crank member which is suitable for a
  • Fig. 22 is a perspective view of an alternative
  • Fig. 23 is a perspective view of a three-cylinder internal combustion engine which is provided with an alternative embodiment of a reciprocating piston mechanism according to the invention .
  • Fig. 24 is an enlarged view of a part of the embodiment as shown in Fig. 23.
  • Fig. 25 is a side view and a partial sectional view of a part of an alternative embodiment as shown in Fig. 15 on a larger scale.
  • Fig. 26 is a similar view as Fig. 25, but illustrating the press fit connection between the crankpin and the
  • FIG. 1 shows a part of an embodiment of a reciprocating piston mechanism 1 according to the invention, which is suitable for an internal combustion engine.
  • the reciprocating piston mechanism 1 comprises a crankcase 15, which supports a
  • crankshaft 2 by crankshaft bearings 3, see Figs. 4 and 5.
  • the crankshaft 2 includes a crankpin 4 and is rotatable with respect to the crankcase 15 about a crankshaft axis 5.
  • the reciprocating piston mechanism 1 comprises a crank member 6 which is rotatably mounted on the crankpin 4.
  • the crank member 6 is provided with a bearing portion 7 which is disposed eccentrically with respect to the crankpin 4, see Fig. 2.
  • the bearing portion 7 has an outer circumferential wall which bears a big end 8 of a connecting rod 9.
  • the connecting rod 9 is rotatably mounted on the crank member 6 via its big end 8.
  • the connecting rod 9 also includes a small end 10 to which a piston
  • Figs. 2 and 3 show a part of the embodiment of Fig. 1 as seen from different sides.
  • the crankshaft 2 and connecting rod 9 are not shown for clarity reasons.
  • Figs. 4 and 5 show the same part, but including the crankshaft 2.
  • crank member 6 is provided with a crank member gear
  • crank member 6 and the crank member gear 12 may be made of one piece, but the crank member gear 12 may be pressed onto a cylindrical base part of the crank member 6, as well.
  • the intermediate gears 13 are rotatably mounted to the crankshaft 2 and their axes of rotation extend parallel to the crankshaft axis 5.
  • intermediate gears 13 also meshes with an auxiliary gear 14.
  • the auxiliary gear 14 is fixed to an auxiliary shaft 16.
  • auxiliary shaft 16 extends concentrically through the crankshaft 2 and is rotatable with respect to the crankshaft 2 about the crankshaft axis 5.
  • the auxiliary shaft 16 is rotatable about an auxiliary shaft axis which substantially coincides with the crankshaft axis 5.
  • the centre line of the auxiliary gear 14 coincides with the crankshaft axis 5.
  • Figs. 1, 4 and 5 show that the auxiliary gear 14, the intermediate gears 13 and the crank member gear 12 are mounted at the same side of a crank arm 17 of the crankshaft 2. This can also be seen in the side view of Fig, 9.
  • the crank arm 17 and the adjacent crankshaft bearing 3 are integrated such that the auxiliary shaft 16 extends through both.
  • the auxiliary shaft 16 extends within an outer circumference of the crankshaft bearing 3. It can be seen in Fig. 1 that the intermediate gears 13 are disposed at a side of the crankshaft 2 where a
  • crank member gear 12 the intermediate gears 13 and the auxiliary gears 14 may be external gears. Due to this configuration the reciprocating piston mechanism 1 can be built in a compact way and is simpler than those known in the art.
  • the gear dimensions can be selected such that under operating conditions the crank member 6 rotates in the same direction as the crankshaft 2 and at half speed thereof.
  • the direction of rotation is defined with respect to the crankcase.
  • the directions and speeds of rotation are achieved when the gear ratio between the crank member gear 12 and the auxiliary gear 14 is two and the auxiliary shaft 16 is hold at a constant angular position with respect to the crankcase 15.
  • the intermediate gears 13 and the auxiliary gear 14 are located at the same side of the crank arm 17 since in practice the diameter of the auxiliary gear 14 is relatively small, which would lead to a small diameter of the crankshaft 2 at the location of the auxiliary gear 14 if this was mounted rotatably on the
  • crankshaft 2 at the opposite side of the crank arm 17.
  • a function of the intermediate gears 13 is to turn the auxiliary gear 14 in the correct direction of rotation in case of applying a gear transmission between the crank member 6 and the auxiliary shaft 16.
  • the number of teeth of the intermediate gears 13 is not relevant for the transmission ratio between the crank member gear 12 and the auxiliary gear 14.
  • Figs. 17-20 show four different positions of the crankshaft 2 with respect to the crankcase 15.
  • the crank member 6 and the auxiliary gear 14 are provided with marks A, B, see Fig. 17.
  • the direction of rotation of the crankshaft 2 and the crank member 6 with respect to the crankcase 15 are shown by respective arrows.
  • Fig. 17 shows the position of top dead centre.
  • the crankshaft 2 has rotated anti clockwise by 180° with respect to the crankcase.
  • the auxiliary gear 14 has maintained its angular position whereas the crank member gear 12 has also rotated anti clockwise with respect to the crankcase 15, but by an angle of 90°.
  • Figs. 19 and 20 show further steps of rotation of the crankshaft 2 by steps of 180°.
  • Figs. 17-20 show that two full rotations of the crankshaft 2 corresponds to one full rotation of the crank member 6, as defined with respect to the crankcase 2.
  • the reciprocating piston mechanism 1 as shown in Figs.
  • the mechanism 1 provides the opportunity to adjust the top dead centre of the piston 11, hence its compression ratio, by changing the angular position of the auxiliary shaft 16 with respect to the crankcase 15.
  • the mechanism 1 is provided with a torsion spring 18 which is fixed to the auxiliary shaft 16, on the one hand, and to the crankcase 15, on the other hand.
  • a control ring 19 is attached to the auxiliary shaft 16, for example by means of pressing, and provided with recesses 20 which are located at mutual angular distances about the crankshaft axis 5.
  • the mechanism 1 also comprises an actuator 21 which controls a pin (not shown) that fits in each of the recesses 20. Under stable running conditions the pin holds the control ring 19 at a fixed position with respect to the crankcase 15 and the mechanism 1 runs at a fixed compression ratio. It is conceivable to eliminate the actuator 21
  • the auxiliary shaft 16 may vibrate in rotational direction due to the presence of the torsion spring 18, which vibration is initiated by varying combustion forces in case of an internal combustion.
  • the average angular position of the auxiliary shaft 18 is then determined by a natural balance between the actual load of the auxiliary shaft 16 on the torsion spring 18 and the actual spring force of the torsion spring 18 on the auxiliary shaft 16.
  • the action and reaction force between the auxiliary shaft 16 and the torsion spring 18, i.e. the natural balance lies at a higher level.
  • the embodiment as shown in Fig. 3 works as follows. If a different compression ratio is desired the pin is retracted out of the corresponding recess 20 by the actuator 21 at a predetermined engine load. For example, if a lower
  • auxiliary shaft 16 on the torsion spring 18 exceeds the spring force of the torsion spring 18, causing the auxiliary shaft 16 including the control ring 19 to turn in the direction of the resultant force . If the pin is displaced back towards the control ring 19 the pin fits into another recess 20. If the control ring 19 should be turned in the opposite direction in order to obtain a higher compression ratio, i.e. switching to a lower engine load, the actual rotational force of the auxiliary shaft 16 on the spring 18 at the corresponding relatively low engine load is smaller than the spring force of the torsion spring 18, hence turning the control ring 19 to the opposite direction. The control ring 19 can then be fixed with respect to the crankcase 15 by means of inserting the pin into the
  • the actuator 21 may be controlled electrically, hydraulically or the like.
  • the circumferential surface of the control ring 19 may be part of a bearing in order to support the control ring 19 by the crankcase 15.
  • the crankcase 15 may bear the control ring 19 by means of a ball bearing 19a, see Fig. 10, but alternative bearings are conceivable .
  • the angular position of the auxiliary shaft 16 is monitored by a sensor 22, which may be a simple potentiometer.
  • the sensor is mounted to the crankcase 15.
  • the signal from the sensor 22 is an indication of the actual compression ratio.
  • Fig. 22 shows an alternative embodiment of an actuator 38 for locking the control ring 19 at a fixed position with respect to the crankcase 15 such that the mechanism 1 runs at a fixed compression ratio.
  • the control ring 19 is fixed to the auxiliary shaft 16 in rotational direction thereof.
  • the torsion spring 18 is fixed to the auxiliary shaft 16 at location P as indicated in Fig. 22 and to the crankcase 15 close to the sensor 22.
  • the actuator 38 comprises an
  • crank member gear 12 and the auxiliary gear 14 are located next to each other within the same plane.
  • Most piston mechanisms have piston strokes, which may not allow the configuration as shown in Figs. 1-5.
  • the intermediate gears 13 may be lengthened such that they extend beyond the crank member gear 1 in at least one direction thereof, whereas the auxiliary gear 1 meshes with the intermediate gears 13 at the extended portions thereof such that the auxiliary gear 14 partly overlaps the crank member gear 12. This is shown in Fig. 6 where the
  • auxiliary gear 14 is located in front of the crank member gear 12.
  • the sum of the outer diameters of the crank member gear 12 and the auxiliary gear 14 is larger than a piston stroke, whereas the gears 12-14 are located at the same side of the crank arm 17.
  • crank member 6 comprises a second crank member gear 12' for driving further crank members in case of a multi-cylinder reciprocating piston mechanism.
  • the crank member gear 12 and the second crank member gear 12' are located at opposite end portions of the crank member 6.
  • the big end 8 of the connecting rod 9 is disposed between the crank member gear 12 and the second crank member gear 12'.
  • Figs. 13-16 show an embodiment of a multi-cylinder internal combustion engines in which the second crank member gear 12' drives crank member gears that are provided at other crank pins.
  • the second crank member gear 12' meshes with a further auxiliary gear 34 which is fixed to a shaft 35 that extends through an adjacent crank arm 17' and/or crank arms and/or main bearings, and on which shaft 35 another auxiliary gear 36 is fixed which drives a further crank member gear 37 of an adjacent crank pin.
  • Figs. 6 and 13-16 show that the width of the crank member gear 12 is smaller than that of the second crank member gear 12'. This is possible since the crank member gear 12 meshes with two intermediate gears 13, whereas the second crank member gear 12' meshes with only one further auxiliary gear 34.
  • the diameter of the crank member gear 12 that meshes with the intermediate gears 13 may be different from the
  • auxiliary gears 36 it is relevant that identical transmission ratios are applied.
  • Figs. 7 and 8 show a drive means of the auxiliary gear 14 for adjusting the compression ratio of the mechanism 1 in a continuous manner instead of by means of discrete steps as described in relation to the embodiment that is shown in Figs. 3 and 5.
  • the alternative drive means comprises an actuator 23 in the form of an electric motor, which is able to drive the auxiliary gear 14 via a worm 24 and worm gear 25 which is fixed to the auxiliary shaft 16, but other alternative drive means are conceivable.
  • Upon rotation of the worm 24 the top and bottom dead centre of the piston 11 can be influenced.
  • the torsion spring 18 could be omitted.
  • the torsion spring 18 may be appropriate in order to balance the actual force of the worm gear 25 onto the worm 24, hence requiring relatively limited power to drive the worm 24.
  • the actual force of the worm gear 25 onto the worm 24 may be caused by combustion forces in case of an internal combustion engine.
  • An advantage of applying a drive means including the worm 24 is that it provides the opportunity to determine the actual rotational force of the auxiliary shaft 16 on the worm 24. In case of an internal combustion engine this force is directly related to combustion pressure on the piston 11.
  • the force may be measured by a force or pressure sensor at the worm 24, for example a piezo electric element or the like.
  • the sensor may be incorporated in the bearings of the worm 24.
  • the signal may be used for misfire detection, for example.
  • auxiliary shaft 16 provides the opportunity to measure combustion forces in alternative manners, for example by means of measuring torque of the auxiliary shaft 16.
  • Figs. 7 and 8 also show transfer members for driving auxiliary parts in case of an internal combustion engine. Both embodiments in Figs. 7 and 8 have a power take-off gear 26 which is attached to the crankshaft 2.
  • the power take-off gear 26 meshes with a first drive gear 27, for example for driving an oil pump, and a second drive gear 28 , for example for driving a camshaft.
  • the embodiment of Fig. 7 shows that the second drive gear 28 is mounted on a common axis with a sprocket wheel 29 for driving a chain.
  • the embodiment of Fig. 8 shows that the second drive gear 28 is mounted on a common axis with a pulley 30 for driving a belt.
  • the pulley 30 or sprocket wheel 29 may be replaced by a wheel for driving a toothed belt. Since the pulley 30 and the sprocket 29 are located on a shaft that extends parallel to the crankshaft 2 the mechanism 1 can be built compact in the longitudinal direction of the crankshaft 2, despite the presence of parts of the drive means for turning the auxiliary gear 14 at the end of the crankshaft 2.
  • Such a structure is also shown in the embodiment of the mechanism 1 of a three-cylinder internal combustion engine as depicted in Fig. 23.
  • the power take-off gear 26 meshes with the first drive gear 27 that is now mounted to a balance shaft 41, together with the pulley 30. It is noted that this structure is applicable to engines that have a different number of cylinders.
  • the diameter of the crank member gear 12 is smaller than that of the second crank member gear 12' and the further crank member gears 37. This provides the opportunity to arrange the gears 12-14 within a common plane, which is shown in Fig. 24.
  • the width of the crank member gear 12, however, is greater than that of the second crank member gear 12' and the further crank member gears 37.
  • the diameter of a portion of the crankpin 4 at the crank member gear 12 is smaller than at a portion of the crankpin 4 at the second crank member gear 12' and the diameter of the crankpin 4 at the further crank member gears 37.
  • crankpin 4 at both the crank member gear 12 and the second crank member gear 12' is the same but smaller than that of the crankpin 4 at the further crank member gears 37. If the diameter of the bearing portion 7 of the crank member 6 is also relatively small the big end of its cooperating connecting rod may also be smaller than that of the other connecting rods .
  • connection between the crankpin 4 and the crank arm 17 can be relatively less strong, which might cause a problem since the connection is intended to be a press fit. However, in practice this is not a problem for the following reasons.
  • the crankshaft 2 as shown in Fig. 23 is made by three press fits; two of them can be seen in Fig. 23 and are indicated by X and Y, respectively, where the respective crank pins 4 are pressed into respective holes of the corresponding crank arms 17.
  • the portion of the crankshaft 2 between the press fits X and Y can be made of one piece.
  • Fig. 23 shows that the diameter of the crankpin 4 at the press fit X has a smaller diameter than the crankpin 4 at the press fit Y.
  • the force that is guided through the crankshaft 2 at the press fit X is smaller than at the press fit Y since a load take-off, or flywheel, of the internal combustion engine is located at the end of the crankshaft 2 opposite to the pulley 30.
  • the press fit X guides the force to the balance shaft 41 and to the pulley 30,
  • crankpin 4 at the crank member 6 has a smaller diameter than the other crankpins .
  • Fig. 9 shows a side view of the embodiment as shown in Figs. 4 and 5. It can be seen that the gears 12-14 are partly located in a recess of the crank arm 17. This provides the opportunity to minimize the length of the mechanism 1 as seen along the crankshaft 2.
  • Fig. 10 shows a side view of the embodiment as shown ii Fig. 7. It can be seen that in this embodiment the gears 12-14 are not located within a common plane as explained in relation to the embodiments of Figs. 6 and 24.
  • the auxiliary gear 14 partly overlaps the crank member gear 12 as seen in a direction along their centre lines.
  • intermediate gears 13 are rotatable to respective intermediate shafts 13a via plain bearings, needle bearings or the like (not shown) , which intermediate shafts 13a are pressed in a bracket 31.
  • the intermediate shafts 13a fit in respective holes in the crank arm 17 and are fixed to the crankshaft 2.
  • the intermediate gears 13 are mounted onto the intermediate shafts 13a, after which the bracket 31 is pressed onto the intermediate shafts 13a and fixed to the crank arm 17 through a bolt 32.
  • the bracket 31 also prevents
  • bracket 31 has a different shape. It is fixed to the crank arm 17 through two bolts 32.
  • Figs. 11 and 12 show an alternative embodiment of the mechanism 1 according to the invention. Parts that are similar to those in the embodiments as described hereinbefore are indicated by corresponding reference signs.
  • the crank member gear 12 and the auxiliary gear 14 are replaced by respective wheels 12a and 14a for driving a toothed belt 33.
  • This transmission may also be an alternative belt or a
  • Fig. 21 shows an alternative crank member 6 which is suitable for a reciprocating piston mechanism having a V
  • crank member gears 12 Furthermore, the crank member 6 is provided with two bearing portions 7, which are angled with respect to each other about the centreline of the crank member 6. Due to this configuration the corresponding pistons reach their respective top dead centres at different angles of the crankshaft.
  • Fig. 25 shows a part of the crankshaft of a multi- cylinder engine which is comparable to the embodiment as shown in Fig. 15.
  • Two other auxiliary gears 136 mesh with respective further crank member gears 137 of the corresponding crank member 106 that is rotatably mounted to the corresponding crank pin 104.
  • the internal diameter of the crank member 106 is enlarged at an end portion thereof. This means that the further crank member gears 137 partly protrude beyond the cylindrical portion of the crankpin 104 in longitudinal direction thereof which contacts the big end of the cooperating connecting rod.
  • crank member 106 is provided with central cavities 140 at end portions thereof for receiving transition portions of the crankshaft 2 that are located between the respective crank arms 17 and the cylindrical portion of the crankpin 104, which transition portions have a larger diameter than the cylindrical portion of the crankpin 104.
  • crank member 4 may be enlarged at an end portion thereof, such that an outer
  • crank member gear 12 at least partly protrudes beyond the cylindrical portion of the crankpin 4 in longitudinal direction thereof.
  • crank member gear 12, 137 is also advantageous to maximize the length of the press fit connection between the adjacent crank arm 17 and the crankpin 4, 104 , which is illustrated in Fig. 26 at the left side of the crankpin 104.
  • the length of the press fit in axial direction of the crankpin is preferably larger than 40% of the diameter of the cooperating crankpin.
  • the invention provides a relatively simple reciprocating piston mechanism which provides the possibility of designing a compact embodiment of the mechanism.
  • the reciprocating piston mechanism may be extended to larger mechanisms having more pistons than the embodiments as described hereinbefore.
  • the crank member may be cylindrical instead of eccentrical, which appears to result in lower

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Transmission Devices (AREA)

Abstract

A reciprocating piston mechanism (1) comprises a crankcase (15) and a crankshaft (2) which has at least a crankpin (4). The crankshaft (2) is supported by the crankcase (15) and rotatable with respect thereto about a crankshaft axis (5). The mechanism further comprises at least a connecting rod (9) including a big end (8) and a small end (10), a piston (11) which is rotatably connected to the small end (10), and a crank member (6) which is rotatably mounted on the crankpin (4). The crank member (6) comprises at least a bearing portion (7) and has an outer circumferential wall which bears the big end (8) of the connecting rod (9) such that the connecting rod (9) is rotatably mounted on the bearing portion (7) of the crank member (6) via the big end (8). The crank member (6) is provided with a crank member gear (12). The crank member gear (12) is an external gear, which meshes with at least an intermediate gear (13). The intermediate gear (13) is an external gear, which also meshes with an auxiliary gear (14). The auxiliary gear (14) is an external gear, which is fixed to an auxiliary shaft (16) that extends concentrically through the crankshaft (2). The crankshaft (2) and the auxiliary shaft (16) are rotatable with respect to each other.

Description

A reciprocating piston mechanism
The present invention relates to a reciprocating piston mechanism.
A reciprocating piston mechanism is described in an earlier application PCT/EP2009/059040 of the applicant.
The present invention aims to provide a further improved reciprocating piston mechanism.
For this purpose the reciprocating piston mechanism comprises the features as defined in claim 1.
The advantage of this mechanism is that the number of gears is minimized. The applicant has discovered that an engine comprising the reciprocating piston mechanism according to the invention has lower friction losses than a conventional engine without the crank member and gear transmissions.
In a practical embodiment the bearing portion is eccentrically disposed with respect to the crankpin. This provides the opportunity to influence the bottom and top dead centre of the piston. Particularly, in case the mechanism is applied in an internal combustion engine it is advantageous to be able to adjust the compression ratio in terms of efficiency.
The gear ratio between the crank member gear and the auxiliary gear may be two. In this case the crank member rotates in the same direction as the crankshaft and at half speed thereof if the auxiliary gear has a fixed angular position with respect to the crankcase. When the bearing portion is
eccentrically disposed with respect to the crankpin, this provides the opportunity to change the compression ratio upon adjusting the angular position of the auxiliary gear.
The mechanism may be provided with a drive means for turning the auxiliary gear with respect to the crankcase about the crankshaft axis. The drive means may comprise a stop block, which is adapted to fix the auxiliary shaft at different angular
positions with respect to the crankcase.
More specifically, the stop block may comprise a control ring which is fixed to the auxiliary shaft and is provided with a plurality of recesses, and an actuator including a controlled displaceable pin that fits in each of the
respective recesses. Preferably, the drive means is provided with a spring that is fixed to the auxiliary shaft and the crankcase. If the mechanism is applied in an internal combustion engine the actual combustion forces caused by the combustion stroke may force the auxiliary shaft to turn in angular
direction against the spring force, when the pin is retracted from the corresponding recess. At a desired angular position of the auxiliary shaft the pin can be moved back to the control ring such that the pin fits in another recess. The control ring may be rotated in opposite direction by selecting an engine load at which the spring force is higher than the actual rotational force of the auxiliary shaft on the spring.
It is also possible that the drive means is provided with a spring that is fixed to the auxiliary shaft and the crankcase without a locking member for fixing the angular position of the auxiliary shaft. In such a case the angular position of the auxiliary shaft is automatically balanced on the basis of the actual force of the auxiliary shaft onto the spring and the actual spring force onto the auxiliary shaft.
The stop block may comprise a control ring which is fixed to the auxiliary shaft in rotational direction thereof, and an electromagnet may be present for fixing the control ring to the crank case, wherein the mechanism is preferably provided with a spring that is fixed to the auxiliary shaft and the crankcase. The advantage of this embodiment is that the
auxiliary shaft can be locked with respect to the crank case at various angular positions continuously. In case of applying the mechanism including the spring in an internal combustion engine this may function in the following manner. If a different compression ratio is desired the electromagnet is switched-off such that the auxiliary shaft is rotatable with respect to the crankcase. If the engine is operated at a higher engine load, in which a lower compression ratio is desired, the actual
relatively high rotational force of the auxiliary shaft on the spring exceeds its spring force, causing the auxiliary shaft including the control ring to turn in the direction of the resultant force. When switching-on the electromagnet the control ring including the auxiliary shaft is locked to the crankcase. If the engine is operated at a lower engine load, in which a higher compression ratio is desired, the electromagnet is switched-off and the control ring will be turned in the opposite direction since the actual rotational force of the auxiliary shaft on the spring at the corresponding relatively low engine load is smaller than the spring force. The control ring can then be locked in its new position by means of switching-on the electromagnet .
Alternatively, the drive means may comprise a drivable worm meshing with a worm gear which is fixed to the auxiliary shaft. This provides the opportunity to vary the angular
position of the auxiliary gear in a continuous manner.
Furthermore, this embodiment of the mechanism may be provided with a pressure sensor at the worm which is an indication of the combustion pressure. It is noted that, the worm in combination with a pressure sensor is not necessarily related to a mechanism as described hereinbefore; it may also be applied in other reciprocating piston mechanisms in which, for example, the angular position of a central gear is driven by a worm to adapt the compression ratio, for example in the mechanism as described in PCT/EP2009/059040.
The invention is also related to a reciprocating piston mechanism according to claim 11. The mechanism provides the opportunity to vary the top dead centre of the piston by means of adjusting the angular position of the auxiliary shaft with respect to the crankcase. In practice the crank member and the auxiliary wheel are driveably coupled to each other by means of a transmission, formed by gears, chains, belts or the like. It is noted that the speed of rotation of the crank member and the crankshaft is defined in respect to the crankcase.
In a preferred embodiment the crank member gear meshes with at least a further intermediate gear which also meshes with the auxiliary gear, since this distributes forces within the mechanism.
The internal diameter of the crank member can be enlarged at an end portion thereof. This means that the internal diameter at the end portion is larger than at its central cylindrical portion where it contacts a cylindrical portion of the crankpin during rotation of the crankshaft. This provides the opportunity to enlarge the diameter of the crankshaft adjacent to a cylindrical portion of the crankpin. In such a case the crank member gear may partly protrude beyond the cylindrical portion of the crankpin in longitudinal direction thereof. This is advantageous in terms of rigidity of the crankshaft and building in a compact manner as seen along the crankshaft axis.
The protruding end portion of the crank member is also advantageous if the crankpin is mounted to an adjacent crank arm by means of a press fit, because it provides the opportunity to create a relatively long press fit connection between the crankpin and the crank arm as seen in axial direction of the crankpin. The length of the press fit in axial direction of the crankpin may be larger than 30% of the diameter of the crankpin, and is preferably larger than 40% thereof.
The crank member may comprise a second crank member gear for driving at least a further crank member including a further crank member gear, which further crank member is
rotatable mounted to a further crankpin, wherein the crank member gear and the second crank member gear are located at opposite end portions of the crank member , wherein the second crank member gear meshes with a further auxiliary gear which is fixed to a shaft that extends through an adjacent crank arm and on which shaft another auxiliary gear is fixed which meshes with the further crank member gear, wherein the diameter of the crankpin at the crank member gear is smaller than the diameter of the further crankpin at the further crank member gear. This provides the opportunity to apply a crank member gear that has a relatively small diameter. In a practical embodiment, the diameter of the crankpin is smaller than the diameter of the further crankpin. As a consequence, the big end of the
cooperating connecting rod may also be smaller than that of the connecting rod which cooperates with the further crankpin.
Alternatively or additionally, the diameter of the crank member gear may be smaller than the diameter of the second crank member gear and/or the width of the crank member gear may be smaller than the width of the second crank member gear.
The invention will hereafter be elucidated with reference to the schematic drawings showing embodiments of the invention by way of example.
Fig. 1 is a perspective view of an embodiment of a reciprocating piston mechanism according to the invention.
Figs. 2 and 3 are perspective views of a part of the embodiment of Fig. 1 on a larger scale and seen from different sides .
Figs. 4 and 5 are similar to Figs. 2 and 3, but illustrating the part including the crankshaft.
Fig. 6 is a perspective view of a part of an alternative embodiment of the part as shown in Figs. 2 and 3.
Fig. 7 is a perspective view of a part of an internal combustion engine which is provided with an embodiment of the mechanism according to the invention.
Fig. 8 is a comparable view as Fig. 7, but showing an alternative embodiment as seen from a different side.
Fig. 9 is a side view of the embodiment as shown in Figs. 4 and 5. Fig. 10 is a side view of the embodiment as shown in
Fig. 7.
Fig. 11 is a similar view as Fig. 1, but showing an alternative embodiment.
Fig. 12 is a perspective view of a part of the embodiment of Fig. 11 on a larger scale.
Fig. 13 is a perspective view of a multi-cylinder internal combustion engine which is provided with an embodiment of a reciprocating piston mechanism according to the invention.
Fig. 14 is a similar view as Fig. 13, but without showing the crankshaft.
Fig. 15 is a side view of the embodiment as shown in
Fig. 14.
Fig. 16 is a perspective view of a part of the embodiment as shown in Fig. 13.
Figs. 17-20 are similar views as Fig. 4 in which a bracket is eliminated to illustrate positions of different parts under operating conditions.
Fig. 21 is a perspective view of an alternative
embodiment of a crank member, which is suitable for a
reciprocating piston mechanism in ¥ arrangement.
Fig. 22 is a perspective view of an alternative
embodiment of an actuator.
Fig. 23 is a perspective view of a three-cylinder internal combustion engine which is provided with an alternative embodiment of a reciprocating piston mechanism according to the invention .
Fig. 24 is an enlarged view of a part of the embodiment as shown in Fig. 23.
Fig. 25 is a side view and a partial sectional view of a part of an alternative embodiment as shown in Fig. 15 on a larger scale.
Fig. 26 is a similar view as Fig. 25, but illustrating the press fit connection between the crankpin and the
cooperating crank arm. Fig. 1 shows a part of an embodiment of a reciprocating piston mechanism 1 according to the invention, which is suitable for an internal combustion engine. The reciprocating piston mechanism 1 comprises a crankcase 15, which supports a
crankshaft 2 by crankshaft bearings 3, see Figs. 4 and 5. The crankshaft 2 includes a crankpin 4 and is rotatable with respect to the crankcase 15 about a crankshaft axis 5.
The reciprocating piston mechanism 1 comprises a crank member 6 which is rotatably mounted on the crankpin 4. The crank member 6 is provided with a bearing portion 7 which is disposed eccentrically with respect to the crankpin 4, see Fig. 2. The bearing portion 7 has an outer circumferential wall which bears a big end 8 of a connecting rod 9. Thus, the connecting rod 9 is rotatably mounted on the crank member 6 via its big end 8. The connecting rod 9 also includes a small end 10 to which a piston
11 is rotatably connected.
Figs. 2 and 3 show a part of the embodiment of Fig. 1 as seen from different sides. The crankshaft 2 and connecting rod 9 are not shown for clarity reasons. Figs. 4 and 5 show the same part, but including the crankshaft 2.
The crank member 6 is provided with a crank member gear
12 which meshes with two intermediate gears 13. The crank member 6 and the crank member gear 12 may be made of one piece, but the crank member gear 12 may be pressed onto a cylindrical base part of the crank member 6, as well. The intermediate gears 13 are rotatably mounted to the crankshaft 2 and their axes of rotation extend parallel to the crankshaft axis 5. Each of the
intermediate gears 13 also meshes with an auxiliary gear 14. The auxiliary gear 14 is fixed to an auxiliary shaft 16. The
auxiliary shaft 16 extends concentrically through the crankshaft 2 and is rotatable with respect to the crankshaft 2 about the crankshaft axis 5. Thus, the auxiliary shaft 16 is rotatable about an auxiliary shaft axis which substantially coincides with the crankshaft axis 5. As a consequence, the centre line of the auxiliary gear 14 coincides with the crankshaft axis 5. Figs. 1, 4 and 5 show that the auxiliary gear 14, the intermediate gears 13 and the crank member gear 12 are mounted at the same side of a crank arm 17 of the crankshaft 2. This can also be seen in the side view of Fig, 9. The crank arm 17 and the adjacent crankshaft bearing 3 are integrated such that the auxiliary shaft 16 extends through both. Thus, the auxiliary shaft 16 extends within an outer circumference of the crankshaft bearing 3. It can be seen in Fig. 1 that the intermediate gears 13 are disposed at a side of the crankshaft 2 where a
counterweight is located which creates a compact structure.
In the embodiment as shown in Figs. 1-5 the crank member gear 12, the intermediate gears 13 and the auxiliary gears 14 may be external gears. Due to this configuration the reciprocating piston mechanism 1 can be built in a compact way and is simpler than those known in the art.
The gear dimensions can be selected such that under operating conditions the crank member 6 rotates in the same direction as the crankshaft 2 and at half speed thereof. The direction of rotation is defined with respect to the crankcase. The directions and speeds of rotation are achieved when the gear ratio between the crank member gear 12 and the auxiliary gear 14 is two and the auxiliary shaft 16 is hold at a constant angular position with respect to the crankcase 15. In order to achieve the desired gear ratio it is relevant that the intermediate gears 13 and the auxiliary gear 14 are located at the same side of the crank arm 17 since in practice the diameter of the auxiliary gear 14 is relatively small, which would lead to a small diameter of the crankshaft 2 at the location of the auxiliary gear 14 if this was mounted rotatably on the
crankshaft 2 at the opposite side of the crank arm 17.
It is noted that a function of the intermediate gears 13 is to turn the auxiliary gear 14 in the correct direction of rotation in case of applying a gear transmission between the crank member 6 and the auxiliary shaft 16. The number of teeth of the intermediate gears 13 is not relevant for the transmission ratio between the crank member gear 12 and the auxiliary gear 14.
In order to illustrate the functioning of the mechanism under operating conditions Figs. 17-20 show four different positions of the crankshaft 2 with respect to the crankcase 15. For illustrative reasons the crank member 6 and the auxiliary gear 14 are provided with marks A, B, see Fig. 17. The direction of rotation of the crankshaft 2 and the crank member 6 with respect to the crankcase 15 are shown by respective arrows. Fig. 17 shows the position of top dead centre. In the position as shown in Fig. 18 the crankshaft 2 has rotated anti clockwise by 180° with respect to the crankcase. It can be seen that the auxiliary gear 14 has maintained its angular position whereas the crank member gear 12 has also rotated anti clockwise with respect to the crankcase 15, but by an angle of 90°. Figs. 19 and 20 show further steps of rotation of the crankshaft 2 by steps of 180°. Figs. 17-20 show that two full rotations of the crankshaft 2 corresponds to one full rotation of the crank member 6, as defined with respect to the crankcase 2.
The reciprocating piston mechanism 1 as shown in Figs.
1-5 provides the opportunity to adjust the top dead centre of the piston 11, hence its compression ratio, by changing the angular position of the auxiliary shaft 16 with respect to the crankcase 15. In Figs. 1-5 and more specifically in Fig. 3 it can be seen that the mechanism 1 is provided with a torsion spring 18 which is fixed to the auxiliary shaft 16, on the one hand, and to the crankcase 15, on the other hand. A control ring 19 is attached to the auxiliary shaft 16, for example by means of pressing, and provided with recesses 20 which are located at mutual angular distances about the crankshaft axis 5. The mechanism 1 also comprises an actuator 21 which controls a pin (not shown) that fits in each of the recesses 20. Under stable running conditions the pin holds the control ring 19 at a fixed position with respect to the crankcase 15 and the mechanism 1 runs at a fixed compression ratio. It is conceivable to eliminate the actuator 21
including the pin, which means that the auxiliary shaft 16 is not lockable to the crankcase 15. In that case, under operating conditions the auxiliary shaft 16 may vibrate in rotational direction due to the presence of the torsion spring 18, which vibration is initiated by varying combustion forces in case of an internal combustion. The average angular position of the auxiliary shaft 18 is then determined by a natural balance between the actual load of the auxiliary shaft 16 on the torsion spring 18 and the actual spring force of the torsion spring 18 on the auxiliary shaft 16. At a higher load due to increased combustion forces, the action and reaction force between the auxiliary shaft 16 and the torsion spring 18, i.e. the natural balance, lies at a higher level. This means that the torsion spring 18 will be compressed and the auxiliary shaft 16 is turned by a certain angle with respect to the crankcase 15. At a lower load the opposite effect is achieved. As a consequence, an automatic adjustment of the angular position of the auxiliary shaft 16 is attained.
In case of applying the mechanism 1 in an internal combustion engine the embodiment as shown in Fig. 3 works as follows. If a different compression ratio is desired the pin is retracted out of the corresponding recess 20 by the actuator 21 at a predetermined engine load. For example, if a lower
compression ratio is desired, i.e. switching to a higher engine load, the actual relatively high rotational force of the
auxiliary shaft 16 on the torsion spring 18 exceeds the spring force of the torsion spring 18, causing the auxiliary shaft 16 including the control ring 19 to turn in the direction of the resultant force . If the pin is displaced back towards the control ring 19 the pin fits into another recess 20. If the control ring 19 should be turned in the opposite direction in order to obtain a higher compression ratio, i.e. switching to a lower engine load, the actual rotational force of the auxiliary shaft 16 on the spring 18 at the corresponding relatively low engine load is smaller than the spring force of the torsion spring 18, hence turning the control ring 19 to the opposite direction. The control ring 19 can then be fixed with respect to the crankcase 15 by means of inserting the pin into the
corresponding recess 20.
It is noted that the actuator 21 may be controlled electrically, hydraulically or the like. Furthermore, the circumferential surface of the control ring 19 may be part of a bearing in order to support the control ring 19 by the crankcase 15. The crankcase 15 may bear the control ring 19 by means of a ball bearing 19a, see Fig. 10, but alternative bearings are conceivable .
The angular position of the auxiliary shaft 16 is monitored by a sensor 22, which may be a simple potentiometer. The sensor is mounted to the crankcase 15. The signal from the sensor 22 is an indication of the actual compression ratio.
Fig. 22 shows an alternative embodiment of an actuator 38 for locking the control ring 19 at a fixed position with respect to the crankcase 15 such that the mechanism 1 runs at a fixed compression ratio. In this embodiment the control ring 19 is fixed to the auxiliary shaft 16 in rotational direction thereof. The torsion spring 18 is fixed to the auxiliary shaft 16 at location P as indicated in Fig. 22 and to the crankcase 15 close to the sensor 22. The actuator 38 comprises an
electromagnet 39 which is attached to the crankcase 15 and covered by a magnet cover 40. Upon turning-on the electrical current through the electromagnet 39 the control ring 19 is pulled against the magnet cover 40 such that the control ring 19 including the auxiliary shaft 16 is hold at a fixed position with respect to the crankcase 15. The cooperating contact surfaces of the magnet cover 40 and the control ring 19 may be provided with friction matter. The axial distance between the cooperating contact surfaces in case the electromagnet is not activated is very small, for example smaller than 0.2 mm such that the axial displacement of the control ring 19 with respect to the auxiliary shaft 16, or of the control ring 19 including the auxiliary shaft 16 with respect to the crankcase 15 is very small. It is noted that switching between high and low-load and high and low compression ratios by means of the torsion spring 18 can be performed in a similar way as explained hereinbefore in relation to the embodiment according to Figs 1-5.
In the embodiment as shown in Figs. 1-5 the crank member gear 12 and the auxiliary gear 14 are located next to each other within the same plane. Most piston mechanisms have piston strokes, which may not allow the configuration as shown in Figs. 1-5. In such a case the intermediate gears 13 may be lengthened such that they extend beyond the crank member gear 1 in at least one direction thereof, whereas the auxiliary gear 1 meshes with the intermediate gears 13 at the extended portions thereof such that the auxiliary gear 14 partly overlaps the crank member gear 12. This is shown in Fig. 6 where the
auxiliary gear 14 is located in front of the crank member gear 12. In this embodiment the sum of the outer diameters of the crank member gear 12 and the auxiliary gear 14 is larger than a piston stroke, whereas the gears 12-14 are located at the same side of the crank arm 17.
Furthermore, Fig. 6 shows that the crank member 6 comprises a second crank member gear 12' for driving further crank members in case of a multi-cylinder reciprocating piston mechanism. The crank member gear 12 and the second crank member gear 12' are located at opposite end portions of the crank member 6. The big end 8 of the connecting rod 9 is disposed between the crank member gear 12 and the second crank member gear 12'. Figs. 13-16 show an embodiment of a multi-cylinder internal combustion engines in which the second crank member gear 12' drives crank member gears that are provided at other crank pins. The second crank member gear 12' meshes with a further auxiliary gear 34 which is fixed to a shaft 35 that extends through an adjacent crank arm 17' and/or crank arms and/or main bearings, and on which shaft 35 another auxiliary gear 36 is fixed which drives a further crank member gear 37 of an adjacent crank pin. Figs. 6 and 13-16 show that the width of the crank member gear 12 is smaller than that of the second crank member gear 12'. This is possible since the crank member gear 12 meshes with two intermediate gears 13, whereas the second crank member gear 12' meshes with only one further auxiliary gear 34.
The diameter of the crank member gear 12 that meshes with the intermediate gears 13 may be different from the
diameter of the second crank member gear 12' and the further crank member gears 37. This may be desired for packaging reasons at the crank arm 17. In such a case a relatively small crank member gear 12 may be pressed onto the cylindrical base part of the crank member 6. In respect of the second crank member gear 12' and the further crank member gears 37 and the other
auxiliary gears 36 it is relevant that identical transmission ratios are applied.
Figs. 7 and 8 show a drive means of the auxiliary gear 14 for adjusting the compression ratio of the mechanism 1 in a continuous manner instead of by means of discrete steps as described in relation to the embodiment that is shown in Figs. 3 and 5. The alternative drive means comprises an actuator 23 in the form of an electric motor, which is able to drive the auxiliary gear 14 via a worm 24 and worm gear 25 which is fixed to the auxiliary shaft 16, but other alternative drive means are conceivable. Upon rotation of the worm 24 the top and bottom dead centre of the piston 11 can be influenced. In the
embodiment as shown in Figs. 7 and 8 the torsion spring 18 could be omitted. However, the torsion spring 18 may be appropriate in order to balance the actual force of the worm gear 25 onto the worm 24, hence requiring relatively limited power to drive the worm 24. The actual force of the worm gear 25 onto the worm 24 may be caused by combustion forces in case of an internal combustion engine. An advantage of applying a drive means including the worm 24 is that it provides the opportunity to determine the actual rotational force of the auxiliary shaft 16 on the worm 24. In case of an internal combustion engine this force is directly related to combustion pressure on the piston 11. The force may be measured by a force or pressure sensor at the worm 24, for example a piezo electric element or the like. The sensor may be incorporated in the bearings of the worm 24. The signal may be used for misfire detection, for example.
It is noted that the auxiliary shaft 16 provides the opportunity to measure combustion forces in alternative manners, for example by means of measuring torque of the auxiliary shaft 16.
Figs. 7 and 8 also show transfer members for driving auxiliary parts in case of an internal combustion engine. Both embodiments in Figs. 7 and 8 have a power take-off gear 26 which is attached to the crankshaft 2. The power take-off gear 26 meshes with a first drive gear 27, for example for driving an oil pump, and a second drive gear 28 , for example for driving a camshaft. The embodiment of Fig. 7 shows that the second drive gear 28 is mounted on a common axis with a sprocket wheel 29 for driving a chain. The embodiment of Fig. 8 shows that the second drive gear 28 is mounted on a common axis with a pulley 30 for driving a belt. In an alternative embodiment the pulley 30 or sprocket wheel 29 may be replaced by a wheel for driving a toothed belt. Since the pulley 30 and the sprocket 29 are located on a shaft that extends parallel to the crankshaft 2 the mechanism 1 can be built compact in the longitudinal direction of the crankshaft 2, despite the presence of parts of the drive means for turning the auxiliary gear 14 at the end of the crankshaft 2.
Such a structure is also shown in the embodiment of the mechanism 1 of a three-cylinder internal combustion engine as depicted in Fig. 23. In this case the power take-off gear 26 meshes with the first drive gear 27 that is now mounted to a balance shaft 41, together with the pulley 30. It is noted that this structure is applicable to engines that have a different number of cylinders.
In the embodiment as shown in Fig. 23 the diameter of the crank member gear 12 is smaller than that of the second crank member gear 12' and the further crank member gears 37. This provides the opportunity to arrange the gears 12-14 within a common plane, which is shown in Fig. 24. The width of the crank member gear 12, however, is greater than that of the second crank member gear 12' and the further crank member gears 37. Furthermore, the diameter of a portion of the crankpin 4 at the crank member gear 12 is smaller than at a portion of the crankpin 4 at the second crank member gear 12' and the diameter of the crankpin 4 at the further crank member gears 37. It is also conceivable that the diameter of the crankpin 4 at both the crank member gear 12 and the second crank member gear 12' is the same but smaller than that of the crankpin 4 at the further crank member gears 37. If the diameter of the bearing portion 7 of the crank member 6 is also relatively small the big end of its cooperating connecting rod may also be smaller than that of the other connecting rods .
Due to the relatively small diameter of the crankpin 4 at the crank member gear 12, the connection between the crankpin 4 and the crank arm 17 can be relatively less strong, which might cause a problem since the connection is intended to be a press fit. However, in practice this is not a problem for the following reasons.
The crankshaft 2 as shown in Fig. 23 is made by three press fits; two of them can be seen in Fig. 23 and are indicated by X and Y, respectively, where the respective crank pins 4 are pressed into respective holes of the corresponding crank arms 17. The portion of the crankshaft 2 between the press fits X and Y can be made of one piece. Fig. 23 shows that the diameter of the crankpin 4 at the press fit X has a smaller diameter than the crankpin 4 at the press fit Y. In practice, the force that is guided through the crankshaft 2 at the press fit X is smaller than at the press fit Y since a load take-off, or flywheel, of the internal combustion engine is located at the end of the crankshaft 2 opposite to the pulley 30. The press fit X guides the force to the balance shaft 41 and to the pulley 30,
optionally including auxiliary devices. Therefore, it is
allowable that the crankpin 4 at the crank member 6 has a smaller diameter than the other crankpins .
Fig. 9 shows a side view of the embodiment as shown in Figs. 4 and 5. It can be seen that the gears 12-14 are partly located in a recess of the crank arm 17. This provides the opportunity to minimize the length of the mechanism 1 as seen along the crankshaft 2.
Fig. 10 shows a side view of the embodiment as shown ii Fig. 7. It can be seen that in this embodiment the gears 12-14 are not located within a common plane as explained in relation to the embodiments of Figs. 6 and 24. The auxiliary gear 14 partly overlaps the crank member gear 12 as seen in a direction along their centre lines.
Referring to the embodiment as shown in Fig. 4 it can be seen that the intermediate gears 13 are rotatably mounted to the crank arm 17 of the crankshaft 2. In this case the
intermediate gears 13 are rotatable to respective intermediate shafts 13a via plain bearings, needle bearings or the like (not shown) , which intermediate shafts 13a are pressed in a bracket 31. The intermediate shafts 13a fit in respective holes in the crank arm 17 and are fixed to the crankshaft 2. Upon assembly of the mechanism 1 the intermediate shafts 13a are pressed into the crankshaft 2 , then the intermediate gears 13 are mounted onto the intermediate shafts 13a, after which the bracket 31 is pressed onto the intermediate shafts 13a and fixed to the crank arm 17 through a bolt 32. The bracket 31 also prevents
displacement of the auxiliary gear 14 in a direction away from the crank arm 17. In the embodiment as shown in Fig. 24 it can be seen that the bracket 31 has a different shape. It is fixed to the crank arm 17 through two bolts 32.
Figs. 11 and 12 show an alternative embodiment of the mechanism 1 according to the invention. Parts that are similar to those in the embodiments as described hereinbefore are indicated by corresponding reference signs. In this case the crank member gear 12 and the auxiliary gear 14 are replaced by respective wheels 12a and 14a for driving a toothed belt 33. This transmission may also be an alternative belt or a
combination of sprocket wheels and a chain.
Fig. 21 shows an alternative crank member 6 which is suitable for a reciprocating piston mechanism having a V
arrangement, for example a V--engine . The crank member 8
comprises two crank member gears 12. Furthermore, the crank member 6 is provided with two bearing portions 7, which are angled with respect to each other about the centreline of the crank member 6. Due to this configuration the corresponding pistons reach their respective top dead centres at different angles of the crankshaft.
Fig. 25 shows a part of the crankshaft of a multi- cylinder engine which is comparable to the embodiment as shown in Fig. 15. Two other auxiliary gears 136 mesh with respective further crank member gears 137 of the corresponding crank member 106 that is rotatably mounted to the corresponding crank pin 104. In order to keep the crankshaft 2 as strong as possible and to build in a compact way, the internal diameter of the crank member 106 is enlarged at an end portion thereof. This means that the further crank member gears 137 partly protrude beyond the cylindrical portion of the crankpin 104 in longitudinal direction thereof which contacts the big end of the cooperating connecting rod. In fact, the crank member 106 is provided with central cavities 140 at end portions thereof for receiving transition portions of the crankshaft 2 that are located between the respective crank arms 17 and the cylindrical portion of the crankpin 104, which transition portions have a larger diameter than the cylindrical portion of the crankpin 104.
It is noted that in the embodiments as described hereinbefore the internal diameter of the crank member 4 may be enlarged at an end portion thereof, such that an outer
circumferential portion of the crank member gear 12 at least partly protrudes beyond the cylindrical portion of the crankpin 4 in longitudinal direction thereof.
An axially protruding crank member gear 12, 137 is also advantageous to maximize the length of the press fit connection between the adjacent crank arm 17 and the crankpin 4, 104 , which is illustrated in Fig. 26 at the left side of the crankpin 104. In general, the length of the press fit in axial direction of the crankpin is preferably larger than 40% of the diameter of the cooperating crankpin.
It is noted that different features of the embodiments as described hereinbefore may be combined.
From the foregoing, it will be clear that the invention provides a relatively simple reciprocating piston mechanism which provides the possibility of designing a compact embodiment of the mechanism.
The invention is not limited to the embodiments shown in the drawings and described hereinbefore, which may be varied in different manners within the scope of the claims and their technical equivalents. For example, the reciprocating piston mechanism may be extended to larger mechanisms having more pistons than the embodiments as described hereinbefore. In an alternative embodiment the crank member may be cylindrical instead of eccentrical, which appears to result in lower
friction losses than in a conventional mechanism having no crank member and gear transmission for driving the crank member.

Claims

1. A reciprocating piston mechanism (1) comprising a crankcase (15);
a crankshaft (2) having at least a crankpin (4), said crankshaft (2) being supported by the crankcase (15) and rotatable with respect thereto about a crankshaft axis (5);
at least a connecting rod (9) including a big end (8) and a small end (10);
a piston (11) being rotatably connected to the small end ( 10 ) ;
a crank member (6) being rotatably mounted on the crankpin (4), and comprising at least a bearing portion (7) having an outer circumferential wall which bears the big end (8) of the connecting rod (9) such that the connecting rod (9) is rotatably mounted on the bearing portion (7) of the crank member (6) via the big end (8);
wherein the crank member (6) is provided with a crank member gear (12), being an external gear, which meshes with at least an intermediate gear (13), being an external gear, which intermediate gear (13) also meshes with an
auxiliary gear (14) being an external gear, wherein the
auxiliary gear (14) is fixed to an auxiliary shaft (16) which extends concentrically through the crankshaft (2), wherein the crankshaft (2) and the auxiliary shaft (16) are rotatable with respect to each other.
2. A reciprocating piston mechanism (1) according to claim 1, wherein the gear ratio between the crank member gear (12) and the auxiliary gear (14) is two.
3. Ά reciprocating piston mechanism (1) according to claim 1 or 2, wherein the bearing portion (7) is
eccentrically disposed with respect to the crankpin (4) .
4. A reciprocating piston mechanism (1) according to one of the preceding claims, wherein the crank member gear (12) meshes with at least a further intermediate gear (13) which also meshes with the auxiliary gear (14).
5. A reciprocating piston mechanism (1) according to one of the preceding claims, wherein the mechanism (1) is provided with a drive means (18-21, 23-25) for turning the auxiliary gear (14) with respect to the crankcase (15) about the crankshaft axis (5).
6. Ά reciprocating piston mechanism (1) according to claim 5, wherein the drive means comprises a stop block, which is adapted to fix the auxiliary shaft (16) at different angular positions with respect to the crankcase (15) .
7. A reciprocating piston mechanism (1) according to claim 6, wherein the stop block comprises a control ring (19) which is fixed to the auxiliary shaft (16) and provided with a plurality of recesses (20), and an actuator (21) including a controlled displaceable pin that fits in each of the respective recesses (20), wherein the mechanism (1) is preferably provided with a spring (18) that is fixed to the auxiliary shaft (16) and the crankcase (15) .
8. A reciprocating piston mechanism (1) according to claim 6, wherein the stop block comprises a control ring (19) which is fixed to the auxiliary shaft (16) in rotational direction thereof, and wherein an electromagnet is present for fixing the control ring (19) to the crank case (15), wherein the mechanism (1) is preferably provided with a spring (18) that is fixed to the auxiliary shaft (16) and the crankcase (15) .
9. A reciprocating piston mechanism (1) according to claim 5, wherein the drive means comprises a drivable worm (24) meshing with a worm gear (25) which is fixed to the auxiliary shaft (16).
10. A reciprocating piston mechanism (1) according to one of the preceding claims, wherein the intermediate gear
(13) extends beyond the crank member gear (12) in at least one longitudinal direction thereof, wherein the auxiliary gear (14) meshes with the intermediate gear (13) such that the auxiliary- gear (14) partly overlaps the crank member gear (12) .
11. A reciprocating piston mechanism (1) comprising a crankcase (15) ;
a crankshaft (2) having at least a crankpin (4), said crankshaft (2) being supported by the crankcase (15) and rotatable with respect thereto about a crankshaft axis (5) ;
at least a connecting rod (9) including a big end (8) and a small end (10);
a piston (11) being rotatably connected to the small end (10) ;
a crank member (6) being rotatably mounted on the crankpin (4), and comprising at least a bearing portion (7) having an outer circumferential wall which bears the big end
(8) of the connecting rod (9) such that the connecting rod (9) is rotatably mounted on the bearing portion (7) of the crank member (6) via the big end (8);
wherein the crank member (6) is driveably coupled to an auxiliary wheel (14, 14a) which is fixed to an auxiliary shaft (16) that extends concentrically through the crankshaft (2), wherein the crankshaft (2) and the auxiliary shaft (16) are rotatable with respect to each other, wherein the auxiliary wheel (14, 14a) is disposed at the same side of an adjacent crank arm (17) as the crank member (6), wherein the mechanism (1) is adapted such that under operating conditions the crank member (6) rotates in the same direction as the crankshaft (2) and at half speed thereof, whereas the auxiliary shaft (16) has a substantially fixed angular position with respect to the crankcase (15) .
12. A reciprocating piston mechanism (1) according to claim 11, wherein the crank member (6) comprises a crank member wheel (12a) which is driveably coupled to the auxiliary wheel (14a) by means of a toothed belt (33) .
13. A reciprocating piston mechanism (1) according to claim 11, wherein the crank member (6) comprises a crank member sprocket and the auxiliary wheel is formed by an
auxiliary sprocket, wherein the crank member sprocket is drivable by means of a chain.
14. Ά reciprocating piston mechanism (1) according to claim 11, wherein the crank member (6) is provided with a crank member gear (12), and the auxiliary wheel is formed by an auxiliary gear (14) being an external gear, wherein the crank member gear (12) and the auxiliary gear (14) are driveably coupled to each other by at least an intermediate gear (13), being an external gear (14), which meshes with the auxiliary gear (14) and the crank member gear (12) .
15. A reciprocating piston mechanism (1) according to claim 5, wherein the drive means (18-21, 23-25) is provided with a spring (18) that is fixed to the auxiliary shaft (16) and the crankcase (15).
16. A reciprocating piston mechanism (1) according to one of the preceding claims, wherein the internal diameter of the crank member (6) is enlarged at an end portion thereof.
17. A reciprocating piston mechanism (1) according to one of the preceding claims, wherein the crank member (6) comprises a second crank member gear ( 12 ' ) for driving at least a further crank member including a further crank member gear (37), which further crank member is rotatable mounted to a further crankpin, wherein the crank member gear (12) and the second crank member gear (12') are located at opposite end portions of the crank member (6), wherein the second crank member gear (12') meshes with a further auxiliary gear (34) which is fixed to a shaft (35) that extends through an adjacent crank arm (17') and on which shaft (35) another auxiliary gear
(36) is fixed which meshes with the further crank member gear
(37) , wherein the diameter of the crankpin (4) at the crank member gear (12) is smaller than the diameter of the further crankpin at the further crank member gear (37) .
18. A reciprocating piston mechanism (1) according to one of the preceding claims, wherein the crank member (6) comprises a second crank member gear (12') for driving at least a further crank member including a further crank member gear (37), which further crank member is rotatable mounted to a further crankpin, wherein the crank member gear (12) and the second crank member gear ( 12 ' ) are located at opposite end portions of the crank member ( 6) , wherein the second crank member gear (12') meshes with a further auxiliary gear (34) which is fixed to a shaft (35) that extends through an adjacent crank arm (17') and on which shaft (35) another auxiliary gear
(36) is fixed which meshes with the further crank member gear
(37) , wherein the diameter of the crank member gear (12) is smaller than the diameter of the second crank member gear (12') and/or wherein the width of the crank member gear (12) is smaller than the width of the second crank member gear (12') .
19. A reciprocating piston mechanism (1) according to one of the preceding claims, wherein the crankpin (104) is mounted to an adjacent crank arm (17) by means of a press fit, wherein the length of the press fit in axial direction of the crankpin (104) is larger than 30% of the diameter of the crankpin (104), and preferably larger than 40% thereof.
PCT/EP2013/051333 2012-01-24 2013-01-24 A reciprocating piston mechanism WO2013110700A1 (en)

Priority Applications (8)

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KR1020147023200A KR102074649B1 (en) 2012-01-24 2013-01-24 A reciprocating piston mechanism
EP13701256.3A EP2828501A1 (en) 2012-01-24 2013-01-24 A reciprocating piston mechanism
BR112014017873-9A BR112014017873B1 (en) 2012-01-24 2013-01-24 ALTERNATIVE PISTON MECHANISM
US14/373,470 US10234006B2 (en) 2012-01-24 2013-01-24 Reciprocating piston mechanism
JP2014552664A JP6305347B2 (en) 2012-01-24 2013-01-24 Reciprocating piston mechanism
CA2861277A CA2861277C (en) 2012-01-24 2013-01-24 A reciprocating piston mechanism
RU2014129394A RU2623136C2 (en) 2012-01-24 2013-01-24 Piston unit with reciprocating motion
CN201380009329.8A CN104204455B (en) 2012-01-24 2013-01-24 A kind of reciprocating-piston mechanism

Applications Claiming Priority (2)

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EP12152309.6 2012-01-24
EP12152309.6A EP2620614B1 (en) 2012-01-24 2012-01-24 A reciprocating piston mechanism

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JP (1) JP6305347B2 (en)
KR (1) KR102074649B1 (en)
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Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140360292A1 (en) 2012-01-24 2014-12-11 Joannes Jacobus Josephus SLEPER Reciprocating piston mechanism
EP2873834A1 (en) 2013-11-13 2015-05-20 Gomecsys B.V. A method of assembling and an assembly of a crankshaft and a crank member
EP2905449A1 (en) 2014-02-11 2015-08-12 Gomecsys B.V. An internal combustion engine including variable compression ratio and a method of operating the engine
EP2907986A1 (en) 2014-02-18 2015-08-19 Gomecsys B.V. A four-stroke internal combustion engine with variable compression ratio
EP2930329A1 (en) 2014-04-08 2015-10-14 Gomecsys B.V. An internal combustion engine including variable compression ratio
CN105156620A (en) * 2015-07-24 2015-12-16 李云峰 Reciprocation-rotation conversion mechanism
WO2016181046A1 (en) * 2015-05-11 2016-11-17 Peugeot Citroen Automobiles Sa Eccentric component for a system for varying the compression ratio of a combustion engine
EP3103986A1 (en) 2015-06-08 2016-12-14 Gomecsys B.V. A four-stroke internal combustion engine including variable compression ratio and a vehicle
WO2017068257A1 (en) * 2015-10-22 2017-04-27 Peugeot Citroen Automobiles Sa Heat engine comprising a system for varying the compression ratio
WO2017211727A1 (en) 2016-06-09 2017-12-14 Gomecsys B.V. Heat engine provided with an improved system for varying the compression ratio
US10557409B2 (en) 2015-10-22 2020-02-11 Gomecsys B.V. Heat engine comprising a system for varying the compression ratio
EP3719339A1 (en) 2019-04-05 2020-10-07 Gomecsys B.V. An apparatus including an adjusting system for adjusting a rotational position of a shaft with respect to a shaft holding member
EP3726023A1 (en) 2019-04-17 2020-10-21 Gomecsys B.V. An internal combustion engine
EP3808955A1 (en) 2019-10-15 2021-04-21 Gomecsys B.V. An internal combustion engine with variable compression ratio
DE102021103790A1 (en) 2021-02-18 2022-08-18 Bayerische Motoren Werke Aktiengesellschaft Adjusting device for setting a variable compression ratio of a reciprocating engine, motor vehicle and method
EP4086443A1 (en) 2021-05-05 2022-11-09 Gomecsys B.V. An internal combustion engine and a method of operating the internal combustion engine

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BR112012000948A2 (en) * 2009-07-15 2016-03-15 Joannes Jacobus Josephus Sleper reciprocating piston mechanism
EP2902603A1 (en) * 2014-01-31 2015-08-05 Gomecsys B.V. An internal combustion engine including variable compression ratio
FR3022299A1 (en) * 2014-06-12 2015-12-18 Peugeot Citroen Automobiles Sa INTERNAL COMBUSTION ENGINE WITH VARIABLE COMPRESSION RATIO
DE102014216533A1 (en) * 2014-08-20 2016-02-25 Schaeffler Technologies AG & Co. KG Device for changing a compression ratio of a cylinder unit of a reciprocating internal combustion engine
CN104832279B (en) * 2015-01-08 2018-01-02 武汉富国发动机科技有限公司 New energy-saving IC engine
FR3035681B1 (en) * 2015-04-28 2017-04-28 Peugeot Citroen Automobiles Sa ECCENTRIC PIECE FOR A COMPRESSION RATE SYSTEM OF A THERMAL ENGINE
FR3035682B1 (en) * 2015-04-28 2017-04-28 Peugeot Citroen Automobiles Sa INTERNAL COMBUSTION ENGINE OF A MOTOR VEHICLE WITH A SYSTEM OF VARIATION IN THE RATE OF COMPRESSION
MX2018000493A (en) * 2015-07-21 2018-04-30 Nissan Motor Internal combustion engine.
DE102015112690B4 (en) * 2015-08-03 2023-04-20 Ovalo Gmbh Actuator system, in particular for coupling to the adjustment shaft of an internal combustion engine for setting the expansion stroke and/or the compression ratio
FR3043720B1 (en) 2015-11-17 2019-11-08 MCE 5 Development VARIABLE VOLUMETRIC RATIO ENGINE
CN105605081A (en) * 2016-03-18 2016-05-25 蔡建龙 Engine crankshaft
CN105673795A (en) * 2016-03-23 2016-06-15 刘有双 Accelerator
FR3050234B1 (en) * 2016-04-19 2021-01-15 Peugeot Citroen Automobiles Sa KIT FOR THERMAL ENGINE COMPRESSION RATE VARIATION SYSTEM
US10119463B2 (en) * 2016-12-09 2018-11-06 Mark Albert Sokalski Infinitely variable compression ratio and single stroke length mechanism or dual stroke length mechanism of reciprocating 2-cycle or 4-cycle internal combustion engine
JP2018105159A (en) * 2016-12-22 2018-07-05 いすゞ自動車株式会社 engine
DE102017200918B4 (en) 2017-01-20 2022-10-06 Bayerische Motoren Werke Aktiengesellschaft Crank mechanism for a reciprocating internal combustion engine
JP7101459B2 (en) * 2017-04-26 2022-07-15 Ntn株式会社 Electric actuator
US10801591B2 (en) * 2017-06-23 2020-10-13 Crown Packaging Technology, Inc. System and method for converting rotating motion into linear motion
DE102018201988B3 (en) 2018-02-08 2019-05-29 Audi Ag Connecting rod for an internal combustion engine and corresponding internal combustion engine
EP3540270A1 (en) 2018-03-12 2019-09-18 Gomecsys B.V. A gear train and an internal combustion engine
EP3608523A1 (en) * 2018-08-09 2020-02-12 Gomecsys B.V. An eccentric member and a v-type internal combustion engine
DE102018128524B4 (en) 2018-11-14 2022-09-22 Bayerische Motoren Werke Aktiengesellschaft Compression ratio changing device, reciprocating internal combustion engine and working device
RU2716521C1 (en) * 2019-07-30 2020-03-12 Общество с ограниченной ответственностью "Завод дозировочной техники "Ареопаг" Piston device of pump
CN111022603B (en) * 2020-01-07 2021-07-20 重庆大学 Staggered planetary roller screw speed reducer
US11131240B1 (en) * 2020-05-15 2021-09-28 GM Global Technology Operations LLC Engine assembly including a force splitter for varying compression ratio using an actuator
GEP20227367B (en) * 2020-08-06 2022-03-25 Ramzan Goytemirov Engine having compression ratio control mechanism
CN112504054A (en) * 2020-11-24 2021-03-16 重庆钧顶机械制造有限公司 Timing gear meshing runout degree gauge for crank link mechanism
US11255374B1 (en) * 2021-03-04 2022-02-22 VenTec LLC Engine crank

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE164819C (en) * 1904-08-02 1905-11-16
DE329861C (en) * 1918-04-12 1920-12-04 Motorenfabrik Oberursel A G Elevation control for rotary engines of aircraft
FR986605A (en) * 1943-11-23 1951-08-02 Device for varying, in operation, the compression ratio of an engine
EP0184042A2 (en) * 1984-11-23 1986-06-11 Politechnika Warszawska Crank mechanism of the internal combustion piston engine with variable crankthrow
WO2009018863A1 (en) * 2007-08-09 2009-02-12 Gomecsys B.V. A reciprocating piston mechanism

Family Cites Families (74)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR636243A (en) * 1928-04-04
DD242077A (en)
US460642A (en) * 1891-10-06 Variable crank-motion
DE181913C (en)
US1207429A (en) * 1916-01-04 1916-12-05 James Currie Morison Means for equalizing piston displacement.
GB150291A (en) * 1917-12-13 1921-11-18 Clerget Blin & Cie Improvements in or relating to explosion engines with variable compression
GB173252A (en) 1920-07-19 1921-12-19 Charles Kane Salisbury Improvements in internal combustion engines
US1553009A (en) 1923-07-23 1925-09-08 Stuke Ernest Engine
DE488059C (en) 1925-05-16 1929-12-18 Louis Damblanc Internal combustion engine with variable piston stroke
US1767352A (en) 1927-03-26 1930-06-24 Damblanc Louis Crank shaft
US1964096A (en) * 1931-11-21 1934-06-26 Emmitt M Tucker Connecting rod mounting
FR861611A (en) 1939-07-29 1941-02-13 Internal combustion engine with variable displacement and automatic compression ratio
US2271766A (en) 1940-05-06 1942-02-03 Harry A Huebotter Engine
US2369747A (en) * 1942-07-30 1945-02-20 Elvin R Munn Engine
FR1014314A (en) 1946-04-10 1952-08-13 Variable displacement internal combustion engine
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
US3686972A (en) * 1970-05-28 1972-08-29 Edward M Mcwhorter Internal combustion engine variable throw crankshaft
JPS5247093B2 (en) * 1972-05-10 1977-11-30
US3861239A (en) * 1972-06-05 1975-01-21 Edward M Mcwhorter Internal combustion engine combustion control crankshaft
US3886805A (en) * 1974-04-09 1975-06-03 Ivan Koderman Crank gear for the conversion of a translational motion into rotation
US4152955A (en) * 1975-01-02 1979-05-08 Mcwhorter Edward M Engine compound crankshaft
US4073196A (en) * 1976-08-13 1978-02-14 Gilbert T. Hendren, Jr. Cranking system of varying radius
DE2720284C3 (en) 1977-05-05 1981-05-27 Huf, Franz, Prof. Dipl.-Ing., 7750 Konstanz Slider crank system series
US4179942A (en) * 1978-01-09 1979-12-25 Matthews Leslie C Variable ratio crank assembly
DE2947882A1 (en) 1979-11-28 1981-07-23 Volkswagenwerk Ag, 3180 Wolfsburg Piston engine crank drive without connecting rod - includes stationary surface formed by wheel concentric to lengthwise axis
AU7857681A (en) 1980-12-16 1982-06-24 Charles Radcliff Furlonger Internal combustion engine
JPH0627969B2 (en) 1984-06-29 1994-04-13 キヤノン株式会社 Character processor
JPS61187931A (en) 1985-02-18 1986-08-21 Asahi Chem Ind Co Ltd Adsorbent of arsenic in aqueous solution
WO1986007115A1 (en) 1985-05-24 1986-12-04 Robert Alan Cooper Crankshaft crank
JPH0443620Y2 (en) * 1985-12-28 1992-10-15
DE3634536A1 (en) 1986-10-10 1987-02-19 Toan Dat Tran Crankshaft drive with doubled piston strokes
DE3642681A1 (en) 1986-12-13 1988-06-23 Michael Schenk Crankshaft, particularly for reciprocating-piston combustion engines
US4860702A (en) 1988-03-21 1989-08-29 Doundoulakis George J Compression ratio control in reciprocating piston engines
EP0345366A1 (en) 1988-06-08 1989-12-13 Alfredo Buffoli Eight cycle or diesel type internal combustion engine
JPH0361135A (en) 1989-07-31 1991-03-15 Masateru Maruyama Transmission method of signal indicator connected with switch in operating section of vehicle such as car and ship and will signal to same signal indicator
JPH0422717A (en) * 1990-05-17 1992-01-27 Mitsubishi Motors Corp Compression ratio varying device of internal combustion engine
GB2258271A (en) * 1991-08-01 1993-02-03 Ford Motor Co Variable compression ratio i.c.engine.
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
US5265566A (en) 1991-12-23 1993-11-30 General Motors Corporation Assembled seal disc for a crankshaft
US5133314A (en) * 1991-12-23 1992-07-28 Langstroth Steven W Linkage arms for minimizing piston wobble
US5170757A (en) 1991-12-24 1992-12-15 Damien Gamache Variable horsepower output gearing for piston engine
SE513061C2 (en) 1992-06-30 2000-06-26 Fanja Ltd Method and apparatus for changing the compression ratio in an internal combustion engine
SE501331C2 (en) 1993-05-28 1995-01-16 Saab Automobile Structural inclusion of internal combustion engine in order to reduce engine noise
US5482015A (en) 1994-07-11 1996-01-09 Fish; Robert D. Device for coupling reciprocating and rotating motions
RU2053391C1 (en) * 1994-03-18 1996-01-27 Евгений Иванович Воронкин Internal combustion engine with extended working stroke
CZ289670B6 (en) 1995-02-28 2002-03-13 Tk Design Ag Reciprocating piston type internal combustion engine with variable compression ratio
GB9611135D0 (en) 1996-05-29 1996-07-31 Gang Nail Systems Limited Connector
JP2829287B2 (en) 1996-10-23 1998-11-25 ロングウェルジャパン株式会社 Crank device
AUPO885297A0 (en) * 1997-09-01 1997-09-25 Bresland, Claude Neil Compression engine
US5927236A (en) * 1997-10-28 1999-07-27 Gonzalez; Luis Marino Variable stroke mechanism for internal combustion engine
NL1009211C2 (en) * 1998-05-19 1999-11-22 L H De Gooijer Holding B V Crank-connecting rod mechanism.
US6453869B1 (en) * 2001-01-04 2002-09-24 Mooremac, Llc Internal combustion engine with variable ratio crankshaft assembly
PT1360403E (en) * 2001-01-24 2004-12-31 Hasan Basri Ozdamar ENGINE WITH ROTARY CONNECTED BOLT
ITRM20010038A1 (en) 2001-01-26 2002-07-26 Foggia Andrea Di DEVICE FOR THE TRANSFORMATION OF THE ALTERNATE STRAIGHT MOTORCYCLE INTO A ROTARY AND VICEVERSA MOTORCYCLE, EQUIPPED WITH ONE OR MORE S-MOUNTED SATELLITES
JP2002286020A (en) 2001-03-26 2002-10-03 Shinko Denki:Kk Crank mechanism of reciprocating engine
US20030183026A1 (en) 2002-03-29 2003-10-02 Korniyenko Alexsandr Y. Apparatus for converting rotary to reciprocating motion and vice versa
EP1507956A1 (en) 2002-05-17 2005-02-23 Normand Beaudoin Retro-mechanical, post-mechanical, bi-mechanical traction engines
DE10230425A1 (en) 2002-07-06 2004-01-22 Bayerische Motoren Werke Ag Bearing bush for IC engine crankshaft is made up of two halves which fit together with butt joints and have end flanges, halves being held together by clips across butt joints
DE10230426A1 (en) 2002-07-06 2004-01-22 Bayerische Motoren Werke Ag Bearing bush for IC engine crankshaft comprises two halves which fit together with butt joints and have end flanges, halves being held together by collars in shape of part of circle which fit across butt joints
WO2005059330A2 (en) * 2003-12-11 2005-06-30 Dow Glendal R Variable crankshaft
RU2280771C2 (en) * 2004-05-19 2006-07-27 Владимир Александрович Ворогушин Motion converting device
US7185557B2 (en) 2004-06-29 2007-03-06 Thomas Mark Venettozzi Epitrochoidal crankshaft mechanism and method
JP2007113471A (en) 2005-10-19 2007-05-10 Toyota Motor Corp Internal combustion engine
EP1959112A1 (en) 2007-02-16 2008-08-20 Gomecsys B.V. A reciprocating piston mechanism, a method of assembling this, and an internal combustion engine
EP1983215A1 (en) 2007-04-20 2008-10-22 Gomecsys B.V. Reciprocating piston machine and internal combustion engine
JP2009036030A (en) 2007-07-31 2009-02-19 Fuji Heavy Ind Ltd Crankshaft structure of high expansion ratio engine
US20090133653A1 (en) 2007-11-26 2009-05-28 Thomas Duzzie Spur gear drive for an internal combustion engine
US8001948B2 (en) 2008-01-30 2011-08-23 Chuy-Nan Chio Kinetic energy generation apparatus having increased power output
WO2009100759A1 (en) * 2008-02-13 2009-08-20 Gomecsys B.V. A reciprocating piston mechanism and a method of increasing internal egr in an internal combustion engine
BR112012000948A2 (en) * 2009-07-15 2016-03-15 Joannes Jacobus Josephus Sleper reciprocating piston mechanism
DE102011085647A1 (en) 2011-11-03 2013-05-08 Bayerische Motoren Werke Aktiengesellschaft Divided bearing shell i.e. eccentric cam shell, for use in crank drive of piston-internal combustion engine, has mounting unit comprising tension rod with tension head, where cross-section of tension head is larger than that of tension rod
EP2620614B1 (en) 2012-01-24 2016-11-09 Gomecsys B.V. A reciprocating piston mechanism
WO2013160501A1 (en) 2012-04-23 2013-10-31 Garcia Sanchez Eduardo Kinematic chain for positioning eccentric bearings which rotate on the crankpins of the crankshaft of an engine with a variable compression ratio
WO2014005258A1 (en) 2012-07-02 2014-01-09 Qualcomm Incorporated Methods and apparatuses for enabling fast early termination of voice frames on the uplink

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE164819C (en) * 1904-08-02 1905-11-16
DE329861C (en) * 1918-04-12 1920-12-04 Motorenfabrik Oberursel A G Elevation control for rotary engines of aircraft
FR986605A (en) * 1943-11-23 1951-08-02 Device for varying, in operation, the compression ratio of an engine
EP0184042A2 (en) * 1984-11-23 1986-06-11 Politechnika Warszawska Crank mechanism of the internal combustion piston engine with variable crankthrow
WO2009018863A1 (en) * 2007-08-09 2009-02-12 Gomecsys B.V. A reciprocating piston mechanism

Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10234006B2 (en) 2012-01-24 2019-03-19 Gomecsys B.V. Reciprocating piston mechanism
US20140360292A1 (en) 2012-01-24 2014-12-11 Joannes Jacobus Josephus SLEPER Reciprocating piston mechanism
US10233966B2 (en) 2013-11-13 2019-03-19 Gomecsys B.V. Method of assembling and an assembly of a crankshaft and a crank member
EP2873834A1 (en) 2013-11-13 2015-05-20 Gomecsys B.V. A method of assembling and an assembly of a crankshaft and a crank member
EP2873835A1 (en) 2013-11-13 2015-05-20 Gomecsys B.V. A method of assembling and an assembly of a crankshaft and a crank member
EP2905449A1 (en) 2014-02-11 2015-08-12 Gomecsys B.V. An internal combustion engine including variable compression ratio and a method of operating the engine
WO2015121254A1 (en) * 2014-02-11 2015-08-20 Gomecsys B.V. An internal combustion engine including variable compression ratio and a method of operating the engine
WO2015124565A1 (en) * 2014-02-18 2015-08-27 Gomecsys B.V. A four-stroke internal combustion engine with variable compression ratio
US10100726B2 (en) 2014-02-18 2018-10-16 Gomecsys B.V. Four-stroke internal combustion engine with variable compression ratio
EP2907986A1 (en) 2014-02-18 2015-08-19 Gomecsys B.V. A four-stroke internal combustion engine with variable compression ratio
US10145299B2 (en) 2014-04-08 2018-12-04 Gomecsys B.V. Internal combustion engine including variable compression ratio
EP2930329A1 (en) 2014-04-08 2015-10-14 Gomecsys B.V. An internal combustion engine including variable compression ratio
WO2016181046A1 (en) * 2015-05-11 2016-11-17 Peugeot Citroen Automobiles Sa Eccentric component for a system for varying the compression ratio of a combustion engine
FR3036146A1 (en) * 2015-05-11 2016-11-18 Peugeot Citroen Automobiles Sa ECCENTRIC PIECE FOR A COMPRESSION RATE SYSTEM OF A THERMAL ENGINE
WO2016198349A1 (en) 2015-06-08 2016-12-15 Gomecsys B.V. A four-stroke internal combustion engine including variable compression ratio and a vehicle
US10605178B2 (en) 2015-06-08 2020-03-31 Gomecsys B.V. Four-stroke internal combustion engine including variable compression ratio and a vehicle
EP3103986A1 (en) 2015-06-08 2016-12-14 Gomecsys B.V. A four-stroke internal combustion engine including variable compression ratio and a vehicle
CN105156620B (en) * 2015-07-24 2018-04-17 李云峰 A kind of crankmotion switching mechanism
CN105156620A (en) * 2015-07-24 2015-12-16 李云峰 Reciprocation-rotation conversion mechanism
FR3042815A1 (en) * 2015-10-22 2017-04-28 Peugeot Citroen Automobiles Sa THERMAL MOTOR PROVIDED WITH A SYSTEM OF VARIATION OF THE COMPRESSION RATE
US10557409B2 (en) 2015-10-22 2020-02-11 Gomecsys B.V. Heat engine comprising a system for varying the compression ratio
WO2017068257A1 (en) * 2015-10-22 2017-04-27 Peugeot Citroen Automobiles Sa Heat engine comprising a system for varying the compression ratio
WO2017211727A1 (en) 2016-06-09 2017-12-14 Gomecsys B.V. Heat engine provided with an improved system for varying the compression ratio
EP3719339A1 (en) 2019-04-05 2020-10-07 Gomecsys B.V. An apparatus including an adjusting system for adjusting a rotational position of a shaft with respect to a shaft holding member
WO2020201099A1 (en) 2019-04-05 2020-10-08 Gomecsys B.V. An apparatus including an adjusting system for adjusting a rotational position of a shaft with respect to a shaft holding member
EP3726023A1 (en) 2019-04-17 2020-10-21 Gomecsys B.V. An internal combustion engine
EP3808955A1 (en) 2019-10-15 2021-04-21 Gomecsys B.V. An internal combustion engine with variable compression ratio
DE102021103790A1 (en) 2021-02-18 2022-08-18 Bayerische Motoren Werke Aktiengesellschaft Adjusting device for setting a variable compression ratio of a reciprocating engine, motor vehicle and method
EP4086443A1 (en) 2021-05-05 2022-11-09 Gomecsys B.V. An internal combustion engine and a method of operating the internal combustion engine
WO2022233690A1 (en) 2021-05-05 2022-11-10 Gomecsys B.V. An internal combustion engine and a method of operating the internal combustion engine

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US10234006B2 (en) 2019-03-19
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CN104204455A (en) 2014-12-10
RU2623136C2 (en) 2017-06-22
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CN104204455B (en) 2018-03-27
RU2014129394A (en) 2016-03-20
KR20140113737A (en) 2014-09-24
CA2861277C (en) 2020-06-16
BR112014017873A8 (en) 2017-07-11
JP6305347B2 (en) 2018-04-04
BR112014017873B1 (en) 2022-10-18
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CA2861277A1 (en) 2013-08-01
EP2620614B1 (en) 2016-11-09

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