Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
  • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
  • F01B3/0005—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having two or more sets of cylinders or pistons
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
  • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F01B3/02—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis with wobble-plate
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
  • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F01B3/0082—Details
  • F01B3/0094—Driving or driven means
• • 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
  • F02B75/26—Engines with cylinder axes coaxial with, or parallel or inclined to, main-shaft axis; Engines with cylinder axes arranged substantially tangentially to a circle centred on main-shaft axis
• • 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
  • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
  • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
  • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two

Definitions

• This invention relates to power transmission apparatus for converting linear reciprocating motion into rotational motion and an axial motor using such an apparatus.
• the linear reciprocating motion can come from pistons, or the like, arranged in a circular configuration.
• Axial motors include an engine block in which the cylinders and pistons are arranged evenly in a circular configuration about a central axis of the engine block, rather than in the inline, "V" or horizontally opposed configurations of traditional engines.
• the reciprocal motion of the pistons in such a motor can be transferred to rotational motion of an output shaft by way of a wobble plate and z crank configuration such as that disclosed in NZ 221336, or by some other suitable transfer means.
• opposed pistons are used to increase the thrust on the transmission means.
• connecting rods couple the pistons to the wobble plate to transfer thrust from the pistons to the z crank, or other means, to drive the output shaft.
• the connecting rods do not remain in a vertical orientation throughout the entire cycle due to the motion of the wobble plate, and this can create side thrust on various components of the engine, including the pistons.
• the present invention may be said to consist in an axial motor including: a plurality of reciprocating thrust means arranged as opposed pairs in a substantially circular array about a central axis, a connecting rod for each thrust means pair connecting the thrust means in that pair, each connecting rod coincident with an axis extending through the respective thrust means pair it connects, a z crank coupled between the ends of an output shaft extending substantially coincident with the central axis, a power transmission apparatus coupled to the z crank, a plurality of reciprocating couplings, each connected to or integrated with the transmission apparatus, and also connected to a corresponding connecting rod to transfer thrust from the corresponding thrust means to the z crank, wherein during operation, to reduce side thrust on thrust means, the reciprocating couplings move to compensate for movement in the transmission apparatus to retain each connecting rod substantially aligned with the axi
• the present invention may be said to consist in a power transfer apparatus adapted for transferring thrust from reciprocating thrust means arranged axially in opposed pairs to a z crank of an axial motor, the apparatus including: a z crank coupling for connecting the apparatus to a z crank, a plurality of coupling support arms extending radially from the z crank coupling, a plurality of reciprocating couplings, each reciprocating coupling disposed in a respective coupling support arm and adapted to oscillate within the respective support arm, wherein upon installation of the apparatus in an axial motor, each reciprocating coupling is adapted for connection to a connecting rod extending between one pair of opposed thrust means in the axial motor, and during operation of the motor, each reciprocating coupling is adapted to reduce side thrust on the thrust means pair, by oscillating to compensate for movement in the apparatus to retain each connecting rod substantially aligned with an axis extending through the respective thrust means pair it connects.
• the reciprocating motion can be provided by a number of internal combustion cylinder/piston arrangements, solenoid or hydraulic rams, or any other suitable power thrust means that operates in a reciprocal motion.
• the piston may be assembled in a modular fashion from carbon components.
• Figures 1 and 2 show in plan, elevation, left/right side elevation and isometric views, a preferred embodiment of an axial motor with opposed pistons and a power transmission apparatus,
• Figures 3 and 4 show elevation, plan and perspective views of a coupling support, couplings and a lower gear restraint of the transmission apparatus
• Figure 5 a is an elevation view of the power transmission apparatus (with upper gear restraint removed for clarity), z crank and output shaft, Figure 5b is an elevation view of the power transmission apparatus, z crank and output shaft showing the upper and lower gear restraint
• Figure 6 is an elevation cross-sectional view of the power transmission apparatus (with both gear restraints removed for clarity), z crank and output shaft shown in Figures 5a and 5b, Figure 7a shows a pivot axle of a connecting rod installed in a knuckle joint with details of the power transmission apparatus removed for clarity,
• Figure 7b shows a pivot axle of a connecting rod installed in a knuckle joint
• Figure 8 a is a plan cross-sectional view (taken through C-C as shown in Figure 3) of the power transmission apparatus showing telescopic arms (wobble sliders) of the coupling support
• Figure 8b is a cross sectional view of one wobble slider in further detail
• Figure 8c is a cross sectional view of one wobble slider showing bearing surfaces
• Figures 8d to 8g are elevation views of a cut away portion of the coupling support showing, one wobble slider and the bearing surfaces,
• Figures 8h and 8i are plan views showing the bearing surfaces
• Figure 9 is an exploded isometric view of a carbon piston
• Figures 10a and 10b are elevation and plan cross-sectional views (taken through A-A and B-B as shown in Figure 12 respectively) of the assembled piston including a bearing, and a little end of a connecting rod,
• Figures 11a and lib are plan, elevation and isometric views of the assembled piston
• Figures 12a, 12b and 12c full and cross-sectional elevation views of a carbon liner for installation in a cylinder bore of the engine block
• Figures 13a and 13 b are elevation and isometric views of the engine block respectively showing detail of the cylinder bores and a turbo charger cavity
• Figure 14 is a cross-sectional view (taken through B-B as shown in Figure 1) of the assembled piston, upper part of an oil pump and connecting rod,
• Figure 15 is an elevation cross-sectional view (taken through B-B as shown in Figure 1) of the axial motor, showing one set of opposed pistons and connecting rods coupled to a respective wobble slider, and Figure 16 shows further detail of the coupling point in Figure 15.
• an axial motor according to the invention and a power transmission apparatus according to the invention for use in an axial motor, may be implemented in various forms.
• the following embodiments are given by way of example only.
• Figures 1 and 2 show various views of a preferred embodiment of an axial internal combustion motor 100, including a preferred embodiment of a power transmission apparatus 300 for converting linear reciprocal motion of pistons 101a-105b into rotational motion of an output shaft 115a, 115b.
• the cylinder block 124 of the motor has been omitted from some of the views for clarity.
• the engine block 124 is described in detail with reference to Figures 13a and 13b.
• the invention will be described in relation to converting the reciprocal motion from an internal combustion cylinder/piston arrangement, however the power transmission device or apparatus 300 (wobble means) is not limited just to use with internal combustion engine applications.
• the invention can be adapted for converting any linear reciprocal motion power source or thrust means, a circular array of solenoid or hydraulic rams being other examples.
• the power transmission apparatus 300 is shown by itself in Figures 3 and 4 for clarity.
• the apparatus 300 includes coupling support 306 and a main coupling (also termed a z crank coupling) 117 for attachment to a z-crank 114, which in turn is attached between ends 115a and 115b of an output shaft.
• Reference to the power transmission apparatus 300 can include the coupling support 306/coupling 117 by itself only, or the entire coupling support 306/coupling 117, z crank 114 and/or output shaft arrangement 115a, 115b.
• the axial motor 100 includes a plurality of pistons 101a-105b with a corresponding connecting rod 106-110 extending between the base of each respective opposed piston pair.
• pistons 101a- 105b arranged in five inline opposed pairs 101a, 101b; 102a, 102b; 103a, 103b; 104a, 104b and 105a, 105b disposed in a circular array about a central axis of the motor 100 each connected by a respective connecting rod 106-110.
• Each piston is housed iri a corresponding cylinder in the cylinder block 124, of which cylinders 111b, 112b, 113b corresponding to pistons 101b, 102b, 103b are visible in Figure 2.
• the cylinders and pistons are described in relation to Figures 9-13.
• the cylinder blocks can also include an internal turbo charger arrangement, such as that described in WO 00/11330.
• the up and down motion of the pistons is transferred to the output shaft 115a, 115b by way of the power transmission apparatus 300 or wobble means.
• This motion is coupled to the apparatus 300 by locating a pivot axle eg 700 (visible in Figures 7a, 7b) of each connecting rod 106-110 in a corresponding coupling 118-122, such as a knuckle joint, disposed on a corresponding telescopic arm or wobble slider (not visible) retained in coupling support 306 of the apparatus 300.
• Detail of the pivot axles eg 700 and knuckle joints 118-122 will be described with reference to Figures 6a and 6b.
• Detail of the wobble sliders will be described with reference to Figures 8a-8i.
• Each axle can pivot in a corresponding knuckle joint eg 118 to allow the corresponding connecting rod to remain in a substantially vertical orientation throughout the reciprocating stroke cycle of the respective piston.
• the coupling support 306, which is more clearly visible in Figure 3 and 4, extends radially from the main shaft coupling 117 of the power transmission device to provide a means to hold respective wobble sliders with knuckle joints 118-122 in a substantially semi-circular arrangement about a longitudinal axis of the main shaft 117.
• the coupling support 306 comprises five arms 301-305 integrally formed with the main shaft coupling 117 and extending radially.
• the coupling support 306 is not restricted to radially extending arms and could comprise, for example, a plate or annular ring attached to the main shaft 117 which receives wobble sliders. In this way the reciprocal motion of the pistons can be transferred to the main shaft 117 which in combination with the z crank 114 rotates the output shaft 115a, 115b in a manner to be described later.
• the transmission apparatus 300 also includes a lower gear restraint 307 comprising an annular ring which supports a plurality of teeth.
• the lower restraint 307 surrounds the main shaft coupling 117 and is attached by way of a plurality of support arms 308-312 which are integrally formed with the main shaft 117 and are bolted, or otherwise attached to, or integrally formed with the annular gear restraint 307 as can be seen in Figure 4.
• the teeth are adapted to mesh with a corresponding upper gear restraint 500 (visible in Figure 5b), which is anchored to a support structure, such as a motor chassis, and remains stationary, independent from the movement of the power transmission apparatus 300.
• the coupling support 306, wobble sliders, couplings 118-122, and connecting rods 106-110 do not extend radially beyond the annular gear restraints 500, 307, but rather remain inside the annular boundary.
• the main shaft coupling 117 of the transmission apparatus 300 is adapted to be rotatably mounted or coupled on a crankshaft 616 of the z crank 114.
• the main shaft coupling 117 is integrally formed as, or includes a coupling sleeve for the crankshaft 616.
• the main shaft includes another type of suitable coupling which is adapted for attachment on the crankshaft 616.
• the z crank 114 has two crank pin webs 116a, 116b rotatably mounted at each distal end of the crankshaft 616.
• Each crank pin web 116a, 116b is adapted to rotatably connect to a respective end of the output shaft 115a, 115b at an angle such that the transmission apparatus 300 and crankshaft 616 lie inclined at an angle with respect to the longitudinal axis of the output shaft 115a, 115b (as shown in Figure 1).
• the preferred angle is between 17° and 18° from vertical, with a particularly preferred angle of substantially 17.5°, although it will be appreciated by somebody skilled in the art that the inclination can fall within a greater range of angles.
• Figures 5b shows detail of the lower gear restraint 307 on the transmission apparatus 300 which meshes with a corresponding annular upper gear restraint 500 attached to a support structure such as the motor chassis.
• the upper gear restraint 500 is omitted from Figure 5a to show obscured detail.
• the respective gear restraints 500, 307 mesh at the point 502 at which one of the upper pistons is at the top of its stroke.
• the cycle for each pair of opposed pistons 101a, 101b; 102a, 102b; 103a, 103b; 104a, 104b and 105a, 105b is staggered such that the top dead centres (TDCs) for the upper pistons 101a-105a occur sequentially in a circular manner.
• TDCs top dead centres
• the TDCs may occur clockwise viewed from above as shown by the arrow 130 in Figures 1, 5 a, 5b, although it could occur counterclockwise.
• This sequential piston movement wobbles the power transmission apparatus 300 and lower gear restraint 307 such that the mesh point 502 of the gear restraints 500, 307 moves in a corresponding circular manner (shown by arrow 130 in Figure 1) about the central axis of the motor 100.
• the gear restraint mechanism 500, 307 prevents or limits the main shaft 117 of the transmission apparatus 300 and the z crank from spinning around crankshaft 616 of the z crank 114.
• the annular gear restraints 307, 500 have a diameter large enough such that the connecting rods 106-110 operate within the annular gear restraints.
• This larger diameter enables more teeth to be provided on the gear restraints 307, 500 than if the connecting rods operated outside the restraint mechanism.
• the increased number of teeth reduces the individual loading on each tooth, due to the thrust of the pistons. Reducing the per tooth thrust is particularly advantageous in the case where opposed pistons are used, as the thrust is double that of a similar motor using non opposed pistons.
• This enables a lighter composite material to be used for the gear restraints 307, 500, rather than a heavier metallic construction, which would usually be required to cope with the increased thrust generated in an opposed piston motor.
• the larger diameter upper gear restraint 500 also enables the restraint to be securely fixed to the support structure.
• FIG. 6 shows a cross sectional view through the longitudinal axis of the transmission apparatus 300 shown in Figures 5a, 5b.
• An upper sleeve 608 slides over a cylindrical protrusion 600 on the upper crank pin web 116a.
• the protrusion 600 includes a threaded blind bore 609 for attachment to the upper output shaft 115a (not shown) by way of a bolt or the like.
• the web 116a also includes a semi cylindrical body 601 with a hollowed portion corresponding to a protruding end of the crankshaft 616.
• the hollowed portion is installed on the crankshaft and then clamped in place by way of two flanges 602 (one of which is visible) which are bolted together. Another bolt is inserted through aligned bores 607 in the web 116a and the crankshaft 616 to prevent the web 116a spinning around the crankshaft 114.
• the semi-cylindrical body 601 includes a recessed portion 610 which enables the web 116a to rotate with the crankshaft about the exterior of the coupling sleeve 117.
• the crankshaft 616 extends through the coupling sleeve and protrudes from either end. It rotates on bearings 604 disposed within an inner surface of the coupling sleeve 117.
• the crankshaft 616 includes a larger diameter bore 605 that tapers into a smaller diameter bore 606.
• the lower crank pin web 116b includes a semi-cylindrical body 615 and a protrusion 612 with a sleeve 613.
• the protrusion 612 includes a blind threaded bore 614 for attachment to the lower portion of the output shaft 115b (not shown in Figure 6) by way of a bolt, or the like.
• the web 116b includes a hollow portion 620 that is mounted on the crankshaft 616. Also visible in Figure 6 is an internal structure of one of the telescopic wobble arms eg 806 that will be described in detail with reference to Figures 8a and 8b.
• FIGS 7a and 7b show the manner in which the pivot axle eg 700 of each connecting rod 106-110 engages with a respective knuckle joint 118-122.
• the pivot axle/knuckle joint arrangement will be described with reference to connecting rod 106 corresponding to pistons 101a, 101b by way of example. This description also relates to the other piston/axle/connecting rod arrangements.
• the pivot axle 700 is located halfway along the connecting rod 106 and comprises two oppositely arranged cylindrical protrusions 705, 706. Each protrusion 705, 706 is integrally formed with and extends substantially horizontally from the connecting rod 106.
• the corresponding knuckle joint 118 comprises a substantially u-shaped bearing cradle comprising a base 701, curved inner face 709 (visible in Figure 5) and two pairs of protrusions 702a, 702b and 703 a (703b is not visible).
• the protrusions 705, 706 of the axle 700 are located in the bearing cradle.
• a corresponding pair of cradle clamps 704 (one clamp being omitted from Figures 7a, 7b for clarity) with a semicircular internal bearing face 708 is bolted to each respective cradle protrusion pair (for example, 703 a, 703b in Figures 7a, 7b) to retain the pivot axle 700 in position.
• Each knuckle joint 118 is connected to a respective telescopic arm 806 (also called a wobble slider) which reciprocates within a respective arm 301 of the coupling support 306.
• the wobble sliders enable slidable coupling of the connecting rods 106-110 to the z crank.
• FIG 8a shows detail of the internal portions of radial arms 301-305 that form the coupling support 306.
• Each arm 301-305 comprises a base portion that receives a telescopic extension arm portion, or wobble slider, that slides within the base portion.
• the wobble sliders form reciprocating couplings for connection to the connecting rods 106-110.
• Figure 8b and 8c show one of the arms in further detail, wherein bearing surfaces 820 and 821 have been omitted from Figure 8b for clarity.
• the slider mechanism will be described in relation to arm 301 however it will be appreciated that this description relates to each of the remaining arms 302-305.
• the base portion 800 includes an outer cylinder 801 that is preferably integrally formed with the main shaft 117 of the transmission apparatus 300.
• a pump piston 802 with an internal cylinder 803 extends through the interior of the outer cylinder 801 to provide an annular interior within the base portion 800.
• An O-ring is embedded in the base of the pump 816.
• a bearing means 805, and sleeve 804 are disposed on the inner surface of the outer cylinder 801.
• the telescopic extension arm 806, or wobble slider includes an integrated knuckle joint 118 and elongated body 808 with a cylindrical outer surface.
• the diameter of the body 808 is dimensioned to fit within the outer cylinder 801 and bearing means 804.
• the body has an inner sleeve 809 that includes a cylindrical bore 810 dimensioned to receive the pump piston 802.
• the wobble slider 806 is housed in the base portion 800 such that the outer surface of the body 808 comes into contact with the bearing means 805 and sleeve 804 and the piston 802 resides in the cylindrical bore 810.
• the wobble slider 806 is able to slide relative to the base portion 800.
• the wobble means 300 wobbles in a manner such that the radial distance between the centre of the wobble means 300 and the position of the pivot axle on the connecting rod varies between a minimum and maximum displacement.
• the wobble slider 806 extends from and retracts into the base portion 800 to compensate for the radial displacement to enable the connecting rod to remain in a substantially vertical orientation (when the motor is supported in a vertical orientation). It will be appreciated therefore, that in the general case, the wobble slider 806 retains the connecting rod in a substantially aligned or coincident relationship with an axis 131 (visible in Figure 1) extending between the opposed pistons 101a, 101b of the pair.
• the reciprocating motion of the wobble slider 806 takes place on two annular bearing surfaces, the first 821 at the base of the wobble slider 806, and the second 820 on the internal base of the outer cylinder 801.
• the bearing surfaces will be described in more detail with respect to Figures 8d to 8i.
• Figures 8d and 8f show a cut away portion of one arm of the coupling support revealing detail of the wobble slider and surface bearings.
• Figures 8e and 8g are close ups showing more detail, while Figures 8h and 8i show plan views of the two bearing surfaces 820, 827. It should be noted that the bearing surfaces shown in these Figures are not to scale, but rather are shown oversized to illustrate detail.
• the second bearing surface 820 comprises two wave formed annular ramps 823, 824 disposed diametrically opposite on the internal base of the outer cylinder 801, and interspersed between flat annular surfaces 825, 826.
• the first bearing surface comprises two wave formed annular ramps 827, 828 disposed diametrically opposite on the base of the wobble slider 806. The ramps 827, 828 are interspersed between annular flat plateau portions 829, 830 and annular troughs 831, 832, 833, 834.
• the ramps 827, 828 slide up opposing faces 836, 837 of second bearing ramps 823, 824, until they reach the peak of ramps 823, 824 as shown in Figures 8d, 8e. This corresponds to the maximum upward travel of the connecting rod.
• the wobble slider 806 extends out of the outer cylinder 801 retaining the connecting rod 106 in a substantially vertical orientation. As the connecting rod 106 reverses its movement downward 835b, the wobble slider 806 continues rotating so that the ramps 827, 828 slide down corresponding reverse faces 838, 839 of ramps 824, 825 until the connecting rod 106 reaches the centre point of its travel again.
• the piston 802 arrangement is damped by hydraulic fluid, for example damping oil.
• hydraulic fluid for example damping oil.
• the inner cylinder 803 of the piston 802 is in fluid communication with hydraulic fluid in the z crank 114 through opening 851.
• hydraulic fluid that resides in the cylinder 803 is compressed in the upper part of the cylindrical bore 810 to provide a damping function.
• the hydraulic fluid is expelled, as shown by the arrows, via channels 811,
• the fluid is also expelled via another channel 815 into the knuckle joint to provide lubrication.
• the damping fluid from the z crank 114 enters the respective wobble sliders in coupling support arms 301-305, through openings 851-855 (all visible in Figure 8a).
• the openings 851-855 each move in and out of alignment with a corresponding bore.
• opening 851 in the z crank aligns with inner cylinder 803 to allow damping fluid to flow into the wobble slider 806.
• the opening 851 is in alignment with cylinder 803 when the wobble slider is at its full extension.
• the z crank 114 moves laterally due to the general action of apparatus.
• each opposed piston pair imparts either an upward or downward thrust, this is transferred to the z crank 114 via the corresponding knuckle joint wobble slider and radial arm coupling support 306.
• the gear restraint mechanism enables the z crank 114 to rotate in the desired manner, while still substantially preventing the transmission apparatus spinning about the longitudinal axis of the z crank 114 and sleeve 117. It will be appreciated that the power transmission apparatus could be adapted for use with any other suitable number of axially arranged pistons, either opposed or otherwise.
• Figure 9 shows an exploded isometric of a preferred embodiment of a modular piston, which can be used in an axial motor, each of the components being manufactured from carbon composites.
• the piston includes a piston head or crown 900 seated on a little end bearing formed from an upper socket 901 and a lower socket 902.
• the crown 900 and bearing assembly is seated or otherwise retained in a piston skirt housing formed from two semi-cylindrical halves 903a, 903b which are joined by way of bolts or the like.
• the piston crown 900 is of generally cylindrical construction with a hollowed interior
• the crown 900 has a circular recess 904 in the top surface to provide a swirling motion to assist fuel/air mixing.
• the crown 900 also includes upper 905 and lower 906 annular recesses in the outer surface.
• the crown 900 further includes an annular rim
• the upper socket 901 has a generally tapered cylindrical outer surface 907, with a partially spherical protrusion 908 on the upper surface which corresponds with the hollow interior 1002 of the crown 900.
• the internal portion of the upper socket 901 is a substantially hemispherical hollow to match the spherical nature of a top portion of a little end of a connecting rod.
• the lower socket 902 of the bearing means comprises a frustohemispherical socket 909, that is a hemispherical socket in which the apex has been removed to leave a base portion with an opening in the top.
• a flange 910 extends from the base edge of the socket 909.
• a bottom annular edge 1001 of the upper socket 901 rests on the flange 910 of the lower socket 902, the matching inner hemispherical portions of each socket forming a spherical socket for a bearing at the little end of the connecting rod.
• Each half of the outer skirt 903a, 903b includes a semi-annular lip on the top edge 915a, 915b and an internal semi-annular shelf 912a, 912b with a profiled top surface.
• the shelves 912,a, 912b form an annular shelf adapted for seating the flange 910 of the lower socket 902 and the annular rim 1001 of the upper socket 901.
• the profiled shelf includes a recess 913 with a ledge and side adapted for seating the flange 910 such that the lower socket 902 is retained by the skirt in an upside down manner in which the frustohemispherical portion protrudes downwardly through the annular shelf 912a, 912b.
• the profiled shelf also includes a bevelled 914 edge about the recess 913.
• the profiled shelf 912a, 912b also includes a plurality of recesses, eg 916, for weight reduction purposes.
• the lower half of each skirt 903 a, 903b which extend below the profiled shelf form a lower cavity 917 of the piston.
• Figures 10a and 10b show elevation and plan cross-sectional views respectively of the assembled carbon piston.
• the crown 900 is seated on the upper bearing socket 901 such that the annular recess 1004 in the annular rim 1003 of the underside of the crown is seated on an annular portion 1005 of the top surface of the upper socket 901.
• the lower annular rim 1001 of the upper socket 901 is seated on the flange 910 of the lower socket 902 to form the spherical bearing socket 1006.
• the outer skirt halves 903a, 903b are then clamped around the crown 900 and socket 901, 902 assembly.
• the flange 910 is seated in an upside down manner on the annular recess ledge 913, the lower surface of the upper socket 901 sits on the flange 910and the annular lip 915a, 915b engages in the annular recess 906 in the crown 900 thus retaining all components of the piston in a secure manner.
• the two skirt halves 903 a, 903b are clamped or otherwise fastened together by way of bolts or the like.
• the outside of the assembled piston is visible in Figures 11a and 1 lb.
• Figures 12a, 12b and 12c show various views of a carbon composite liner 1200 for insertion into the engine block 124, shown in Figures 13a and 13b.
• the carbon liner 1200 provides a cylinder eg 111b in which a respective piston eg 101b reciprocates.
• the liner 1200 has an outer profile 1201 including an annular flange 1202 which sits in a surface recess eg 1301 at the entrance to a corresponding cylinder bore eg 1300 in the block 124.
• the liner 1200 can be secured in the bore 1300 by fastening the annular flange 1202 (shown in more detail in Figure 12b) in the recess by way of bolts or the like which screw into respective openings eg 1303, positioned around the bore 1300.
• the liner 1200 includes various transfer ports 1203 and exhaust ports 1204 that communicate with ducting in the block 124 (not visible) for inlet of combustion fuel/gases and outlet of exhaust gases. Details of this will be known to those skilled in the art, and openings relevant to an internal turbo charger (if used) are described in WO 00/11330.
• the block 124 may also include the required cavity 1303 and ducting for an internal turbo charger.
• An annular flange 1205 on the outer profile includes a machined groove 1206 for an O-ring.
• Figure 14 shows the piston, cylinder and connecting rod assembly, with Figure 15 showing detail of the full arrangement including wobble means, while Figure 16 shows detail of the connecting rod/ knuckle joint coupling.
• the assembled piston resides in the cylinder liner that comprises an outer body 1400 and inner carbon liner sleeve 1200 that is adapted for a sliding fit with the piston.
• a bearing 1402 is installed in the bearing socket 1006 with a lower portion of the bearing 1402 protruding through the opening in the lower bearing socket 902.
• the protruding portion includes a blind bore 1403 for receiving the little end 1404 of a connecting rod 106.
• the diameter of the little end 1404 is smaller than that of the connecting rod 106 itself and is dimensioned to engage in the blind bore 1403.
• the wobble slider arrangement also reduces the amount by which the connecting rod circulates, which happens in existing arrangements. This in turn can reduce movement of the bearing 1402, leading to reduced friction. This can reduce the need for lubrication of the bearing 1402 in the socket 902, especially if carbon components are used.
• the connecting rod 106 extends through a central bore 1416 of a bearing support and pump cylinder 1406 that houses an upper portion of the connecting rod 106.
• the pump cylinder has an elongated cylindrical outer body with a first diameter 1407 which extends through a cylindrical head portion 1408 with a larger second diameter.
• the head portion 1408 is adapted to engage in a sealed manner with the bottom of the cylinder outer body 1400 and inner sleeve 1200 to form the cylinder enclosure. More
• the head portion 1408 includes an exterior annular shelf 1409 with an annular wall 1410 that engage with a corresponding annular profile 1411 in the inner sleeve 1200.
• a top end 1412 of the wall 1410 has a width which extends beyond the width of the inner sleeve to provide a shelf which provides a lower limit for movement of the piston.
• An annular interior 1413 is formed between the wall 1410 and top end of the elongated body 1407 of the pump cylinder 1406. The interior 1413 in combination with the lower piston cavity 917 form an enclosed cavity.
• the upper end of the connecting rod includes an outer sleeve with an annular splayed end which forms a connecting rod pump piston 1414.
• a bush 1415 sits on the splayed end.
• An annular channel 1418 is formed in central bore 1416 of the connecting rod pump cylinder 1406 for the passage of oil or other suitable lubricating fluid in the connecting rod/bore interface to the piston cavity, if required.
• the connecting rod moves linearly upwards and downwards within the central bore 1416 the splayed end of the pump piston 1404 and bush 1415 force hydraulic fluid through the channel 1418 and into the cavity and back again. This action provides lubricating fluid to both the connecting rod/bore interface and the piston/cylinder interface.
• the connecting rod also includes a central bore 1419 which provides a channel for transfer of lubricating fluid between the knuckle joint and the little end bearing 1402/ bearing socket 1006 interface, if it is required. As the wobble slider action provides lubricating fluid into the knuckle joint, this is also transferred to the connecting rod bore 1419. The lubricating fluid flows through the bore into the little end bearing and into the bearing/ bearing socket interface via openings 1420 in the bearing 1402.
• the lower end of the elongated pump cylinder 1402 has a hemispherical recess 1421 in its bottom face.
• a pump piston cover 1422 with a corresponding hemispherical recess 1423 is attached to the pump piston by couplings 1424, 1425 to form a spherical bearing socket for a connecting rod bearing 1426.
• the connecting rod bronze bearing or bush 1426 takes any residual side thrust, and also assists sealing of the piston/cylinder from the crankcase. This assists in preventing lubrication fluid going into the piston/cylinder if this is not desired, and also assists in preventing combustion gases entering the crankcase. It also prevents the piston going into the crankcase.
• each connecting rod bearing and seal e.g. 1426, 1417, seals the respective piston/cylinder from the z crankcase to prevent lubricant entering the piston/cylinder, and to prevent exhaust gases entering the crankcase. Without the seals (1417 being the main seal, with bearing 1426 providing some assistance sealing), lubricant on the connecting rods could enter the respective cylinders.
• the seals are possible by virtue of the connecting rods being retained in a substantially vertical orientation during operation (or in the general case, in-line with the axis through the pistons).
• Existing engines have circulating connecting rods that are far more difficult to seal under operating conditions.
• the seal/bearing 1426 bears any residual side thrust from the respective connecting rod, further reducing any side thrust experienced by the piston/cylinder arrangement. Again, bearing the load of the connecting rods in this way would be difficult if they are not kept substantially inline with the pistons during operation.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
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• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Transmission Devices (AREA)
• Pistons, Piston Rings, And Cylinders (AREA)
• Hydraulic Motors (AREA)
• Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
• Surgical Instruments (AREA)
• Knitting Machines (AREA)
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• 2001
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• 2002
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  • 2002-07-23 KR KR10-2004-7001133A patent/KR20040032866A/ko not_active Withdrawn
  • 2002-07-23 JP JP2003515753A patent/JP2004536991A/ja active Pending
  • 2002-07-23 ES ES02763132T patent/ES2276952T3/es not_active Expired - Lifetime
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