WO2009120715A1 - Mécanisme de transformation de mouvements - Google Patents

Mécanisme de transformation de mouvements Download PDF

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Publication number
WO2009120715A1
WO2009120715A1 PCT/US2009/038133 US2009038133W WO2009120715A1 WO 2009120715 A1 WO2009120715 A1 WO 2009120715A1 US 2009038133 W US2009038133 W US 2009038133W WO 2009120715 A1 WO2009120715 A1 WO 2009120715A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
crankshaft
drive
axis
journal
Prior art date
Application number
PCT/US2009/038133
Other languages
English (en)
Inventor
Christopher L. Cook
Original Assignee
Efficient-V, Inc.
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 Efficient-V, Inc. filed Critical Efficient-V, Inc.
Priority to US12/497,497 priority Critical patent/US8375919B2/en
Publication of WO2009120715A1 publication Critical patent/WO2009120715A1/fr

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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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C7/00—Connecting-rods or like links pivoted at both ends; Construction of connecting-rod heads
    • F16C7/02—Constructions of connecting-rods with constant length
    • F16C7/023—Constructions of connecting-rods with constant length for piston engines, pumps or the like
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/22—Cranks; Eccentrics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H21/00—Gearings comprising primarily only links or levers, with or without slides
    • F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
    • F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
    • F16H21/18—Crank gearings; Eccentric gearings
    • F16H21/36—Crank gearings; Eccentric gearings without swinging connecting-rod, e.g. with epicyclic parallel motion, slot-and-crank motion
    • F16H21/365—Crank gearings; Eccentric gearings without swinging connecting-rod, e.g. with epicyclic parallel motion, slot-and-crank motion with planetary gearing having a ratio of 2:1 between sun gear and planet gear

Definitions

  • This application concerns machines that convert rotating motion to reciprocating motion, and vice-versa, and more particularly, but not exclusively, to reciprocating piston machines.
  • a conventional slider-crank mechanism includes a crank-arm that rotates about a proximal end and a distal end of the crank-arm pivotally engages (e.g., using a pin-type connection) a connecting rod at the proximal end of the connecting rod.
  • the connecting rod pivotally engages a reciprocable slider (e.g., piston) at the distal end of the connecting rod. Consequently, as the crank-arm rotates, the slider reciprocates.
  • crankshaft and bearing apparatus comprise a crankshaft defining at least one crankshaft drive having a crankshaft drive axis-of-rotation and at least one piston-journal defining a longitudinal axis radially spaced from the at least one crankshaft drive axis-of- rotation.
  • crankshaft drive having a crankshaft drive axis-of-rotation and at least one piston-journal defining a longitudinal axis radially spaced from the at least one crankshaft drive axis-of- rotation.
  • These embodiments also comprise a corresponding at least one piston engaging the at least one piston-journal, and a drive member defining a central axis- of-rotation.
  • the drive member defines a crankshaft drive receiving region for receiving the corresponding crankshaft drive.
  • the apparatus also comprises an internal ring gear, and the crankshaft comprises a pinion matingly engageable with the ring gear such that the longitudinal axis of each at least one piston-journal reciprocates along a respective substantially linear hypocycloidal path as the crankshaft orbits about the central-axis-of-rotation.
  • the at least one piston can comprise at least a first piston and a second piston.
  • the at least one piston-journal comprises at least a first piston-journal pivotably engageable with the first piston, and a second piston-journal pivotably engageable with the second piston.
  • Each of the piston-journals define a respective longitudinal axis being radially spaced from the crankshaft drive axis-of- rotation.
  • the first piston-journal and the second-piston-journal can be angularly separated from each other by a first angle relative to the crankshaft drive axis-of- rotation.
  • the at least one piston comprises at least a first piston, a second piston, a third piston and a fourth piston.
  • the at least one piston-journal can comprise at least a first piston-journal pivotably engageable with the first piston and defining a corresponding longitudinal axis, a second piston-journal pivotably engageable with the second piston and defining a corresponding longitudinal axis, a third piston-journal pivotably engageable with the third piston and defining a corresponding longitudinal axis, and a fourth piston-journal pivotably engageable with the fourth piston and defining a corresponding longitudinal axis.
  • the longitudinal axis of the first piston-journal and the longitudinal axis of the second piston-journal can reciprocate in respective first and second planes as the crankshaft orbits about the central-axis-of-rotation.
  • the first plane and the second plane can be angularly separated by a second angle measuring one-half of the first angle.
  • the disclosed crankshaft and bearing apparatus can comprise a block defining a first piston cylinder having a corresponding first cylinder axis.
  • the first piston cylinder can be configured to slidably receive at least a portion of the first piston.
  • the block can also define a second piston cylinder having a corresponding second cylinder axis.
  • the second piston cylinder can be configured to slidably receive at least a portion of the second piston.
  • An angle between the first cylinder axis and the second cylinder axis can correspond to the first angle.
  • the first angle measures between about 0-degrees and about 180-degrees.
  • the first angle can measure between about 60- degrees and about 150-degrees, such as, for example, between about 75-degrees and about 135-degrees.
  • the first angle measures between about 85-degrees and about 100-degrees.
  • the second angle measures between about 40-degrees and about 85-degrees, such as, for example, about 45 -degrees.
  • the second angle measures between about 0-degrees and about 180-degrees, such as, for example, between about 20-degrees and about 150-degrees. In some embodiments, the second angle measures between about 40- degrees and about 80-degrees, such as, for example, about 45-degrees.
  • the at least one piston can comprise a single piston, and a corresponding block can define a single piston cylinder.
  • the piston cylinder can have a corresponding cylinder axis and be configured to slidably receive the single piston.
  • the internal ring gear is a first internal ring gear and the pinion is a first pinion. Such embodiments can also comprise a second internal ring gear.
  • the crankshaft can comprise a second pinion matingly engageable with the second ring gear.
  • One or more of the pistons can comprise an elongate body having a length extending from a proximal region to a distal region.
  • the body can define a bearing surface extending over more than about 25%, such as more than about 33%, and in some instances more than about 50%, of the length of the elongate body for slidably engaging a portion of a block, crankcase or cylinder wall.
  • the drive member can comprise an armature. At least one of the pistons can reciprocate along a stroke length measuring four times the distance extending between the longitudinal axis of the at least one piston-journal and the at least one crankshaft drive axis-of-rotation.
  • crankshaft and bearing apparatus can comprise a block having defined therein a longitudinal crankcase, a drive-member receiving region that defines a central-axis-of-rotation, and at least first and second cylinders.
  • the first and second cylinders define respective cylinder axes being disposed at a first angle of other than about 90- degrees and other than about 180-degrees, such as, for example, between about 20- degrees and about 150-degrees. In some embodiments, this first angle measures between about 40-degrees and about 80-degrees, such as, for example, about 45- degrees.
  • At least first and second pistons can be slidably disposed within the respective first and second cylinders and can have respective first and second crankshaft-bearing regions.
  • Such apparatus can also comprise a crankshaft defining a crankshaft-drive and at least first and second piston-journals. The first and second crankshaft-bearing regions can pivotally engage the respective first and second piston-journals.
  • Such apparatus can also comprise a drive-member rotatably engageable with the crankshaft-drive. The first and second pistons can reciprocate within the respective first and second cylinders as the crankshaft orbits the central- axis-of-rotation.
  • crankshaft and bearing apparatus further comprise a ring gear
  • the crankshaft comprises a pinion matingly engaging the ring gear
  • crankshaft and bearing apparatus further comprise a housing fixedly attached to the block and defining an aperture through which a portion of the drive-member extends.
  • crankshaft and bearing apparatus can include a crankshaft, at least a first piston and a drive-member.
  • the crankshaft can define at least one crankshaft-drive having a crankshaft-drive axis-of-rotation, and at least one radially extending piston-journal spaced from the at least one crankshaft-drive.
  • the crankshaft can define a piston-journal longitudinal axis spaced from the crankshaft- drive axis-of-rotation.
  • the first piston can have a crankshaft-bearing-region at a proximal end, a piston head at a distal end and an elongate body connecting the crankshaft-bearing- region and the piston head.
  • the crankshaft-bearing-region is pivotally engageable with the at least one piston-journal of the crankshaft.
  • the piston head can have a substantially cylindrical shape and define a piston head diameter.
  • the body has a width substantially equal to the head diameter along at least about 25% of a length of the body between the piston head and the crankshaft- bearing-region. In some embodiments, the width is substantially equal to the head diameter along at least about 33%, and in some embodiments at least about 50%, of a length of the body.
  • the body also has a thickness less than the width. The piston can be thusly configured to be slidably received in a piston-cylinder.
  • the drive-member defines a central-axis-of-rotation and can be rotatably engageable with the crankshaft-drive.
  • a moment applied to the drive-member can urge the crankshaft- drive axis-of-rotation along a circular orbit about the central-axis-of-rotation, thereby urging the piston-journal to reciprocate along a substantially linear stroke with respect to a fixed frame-of-reference.
  • the elongate body is fixedly attached to the piston head.
  • the width of the elongate body can be substantially uniform over the length of the body between the piston head and the crankshaft-bearing-region.
  • the width of the elongate body can be less than the piston head and/or spaced from a corresponding wall of a crankcase or cylinder, e.g., to reduce friction.
  • a moment applied to the drive-member can urge a region of the crankshaft along a hypocycloidal path.
  • Some embodiments also include a block.
  • the block can have a first recess that defines a drive-member receiving region sized to pivotally receive the drive- member.
  • the block also can have a second recess sized to slidably receive the piston and define a piston-cylinder.
  • the second recess has an outer portion sized to receive the piston head and piston width, and in some embodiments, a narrowed inner portion sized to slidably receive the proximal end of the piston.
  • the linear stroke of the longitudinal axis of the at least one piston-journal is approximately four times as large as a radius defined by the circular orbit of the longitudinal axis of the crankshaft-drive about the central-axis- of-rotation.
  • a distance between the crankshaft-drive axis-of-rotation and the piston- journal longitudinal axis can be substantially equal to a radius of the circular orbit of the longitudinal axis of the crankshaft-drive about the central-axis-of-rotation.
  • Some disclosed embodiments also include a second piston defining a crankshaft-bearing-region at a proximal end, a head at a distal end and an elongate body connecting the crankshaft-bearing-region and the head.
  • the head of the second piston can have a substantially cylindrical shape defining a piston head diameter.
  • the body of the second piston can have a substantially uniform width, in some instances being substantially equal to the head diameter, and a thickness substantially less than the head diameter.
  • the second piston can be configured to be slidably received in a piston-cylinder.
  • the at least one piston- journal is a first piston-journal that further includes a radially extending second piston-journal being longitudinally spaced apart from the first piston-journal.
  • the second piston-journal can define a longitudinal axis and the crankshaft-bearing- region of the second piston can be pivotally engageable with the second piston- journal.
  • first and second piston- journals are typically parallel and can be angularly offset from each other relative to the crankshaft-drive axis-of-rotation.
  • the angular offset between the respective longitudinal axes of the first and the second piston-journals can range from about zero-degrees to about 180-degrees, such as between about 60-degrees and about 15- degrees.
  • the respective longitudinal axes of the first and second piston-journals can be co-planar with the crankshaft-drive axis-of-rotation.
  • the first piston and the second piston can be configured to reciprocate out of phase relative to each other.
  • a distance between the respective longitudinal axes of the first piston-journal and the second piston-journal is substantially equal to a diameter of the circular orbit of the longitudinal axis of the crankshaft-drive about the central-axis-of-rotation.
  • the linear stroke of the respective longitudinal axes of the first and second piston-journals is approximately twice the diameter of the orbit.
  • Some embodiments that include two or more pistons also include a block having a first recess that defines a drive-member receiving region sized to rotatably receive the drive-member.
  • the block can also have a second recess sized to slidingly receive the first piston and defining a first piston-cylinder extending in a first cylinder direction and a third recess sized to slidingly receive the second piston and defining a second piston-cylinder extending in a second cylinder direction.
  • An angle between the first cylinder direction and the second cylinder direction can range from about zero-degrees to about 180-degrees.
  • Some embodiments include a balance shaft rotatably engaged with the drive-member. In some embodiments, a moment applied to the drive-member urges the first and second pistons to reciprocate within the first and second piston-cylinders, respectively.
  • crankshafts include an intermediate member configured to cause two or more pistons to reciprocate out of phase with each other.
  • Some crankshaft-drives include one of a pinion gear and a journal bearing surface.
  • Some drive-members pivotally engage the journal bearing surface of the crankshaft-drive.
  • Reciprocating-piston apparatus include a block, at least first and second pistons, a crankshaft, and a drive-member. Such blocks have defined therein a longitudinal crankcase, a drive-member receiving region that defines a central-axis-of-rotation, and at least first and second cylinders.
  • the first and second cylinders define respective cylinder axes disposed at an angle measuring between about 0-degrees and about 180-degrees relative to each other and are longitudinally offset along the central-axis-of-rotation.
  • the first and second cylinders each have a substantially cylindrical top-portion defining a diameter and a narrowed central-portion with a first dimension perpendicular to the central-axis-of- rotation and substantially the same as the diameter, and a second dimension along the central-axis-of-rotation substantially less than the diameter.
  • the crankshaft defines a crankshaft-drive and at least first and second piston- journals and is disposed in the longitudinal crank-bore.
  • the at least first and second pistons are slidably disposed within the respective first and second cylinders and have respective first and second crankshaft-bearing regions.
  • the first and second crankshaft-bearing regions pivotally engage the respective first and second piston-journals.
  • the drive-member rotatably engages the crankshaft-drive and is pivotally disposed relative to the drive-member receiving region of the block. In some instances, the drive -member is pivotally disposed at least partially within the drive- member receiving region of the block.
  • reciprocating piston apparatus also include a balance shaft rotatably engaged with the drive-member.
  • Some embodiments include a housing fixedly attached to the block and defining an aperture through which a portion of the drive-member extends.
  • the drive-member can be pivotally disposed at least partially within the housing.
  • the housing can further include a bearing that pivotally engages the portion of the drive-member extending through the aperture to provide support thereto.
  • Some blocks are substantially one-piece. Some one-piece blocks include a cylinder sleeve disposed in one or more of the cylinders to promote wear resistance. Other blocks have removable piston cylinders, or other removable features.
  • a moment applied to the drive-member can urge the crankshaft-drive to orbit the central-axis-of-rotation, thereby urging the first and second pistons to reciprocate along respective substantially linear strokes in the respective first and second cylinder-bores. Urging the first and second pistons to reciprocate in the respective first and second cylinder-bores can urge the crankshaft-drive to orbit the central-axis-of- rotation, thereby urging rotation of the drive-member.
  • the respective pistons and cylinder-bores are configured to promote combustion of a fuel and air mixture for releasing chemical energy of the fuel and forming products of combustion capable of performing work on at least one of the pistons.
  • crankshaft-drive include one of a pinion gear and a journal.
  • the drive-member receiving region of the block includes an internal gear configured to receive the crankshaft-drive pinion gear.
  • the drive-member includes a region defining a bore configured to receive the crankshaft-drive journal.
  • Disclosed pistons can include one or more oil pathways configured to deliver oil to one or more bearing regions, at least partially in response to reciprocation of the pistons within the cylinders.
  • Drive-members for shaft and bearing apparatus can include a driveshaft, a crankshaft-drive receiving area and a prismatic sector defining a body.
  • the prismatic sector defining a body has first and second ends, a sidewall that extends between the ends, and a central-axis-of-rotation perpendicular to each end and substantially parallel to the sidewall.
  • the driveshaft defines a first longitudinal axis that substantially aligns with the central-axis-of-rotation.
  • the crankshaft-drive receiving region is configured to receive a crankshaft-drive and defines a longitudinal-axis-of-symmetry parallel to and spaced from the central-axis-of- rotation.
  • the prismatic sector spans less than approximately 180-degrees about the central-axis-of-rotation. In other embodiments, the prismatic sector spans more than about 180-degrees about the central-axis-of-rotation. For example, the prismatic sector can span about 360-degrees, thereby forming a substantially cylindrical body.
  • the body also defines one or more recessed regions disposed symmetrically about a plane that includes the central-axis-of-rotation.
  • Some drive-members include a longitudinally extending member contiguous with the body that is configured to provide balance to a rotating crankshaft and bearing assembly.
  • the crankshaft-drive receiving region can include a journal or an internal gear configured to receive a pinion gear.
  • the sidewall can include a journal.
  • the driveshaft can include a journal, a pinion, a pulley, a sprocket, spline, keyway, or drive flange.
  • rotation of the body about the central-axis-of-rotation causes the longitudinal-axis-of- symmetry of the crankshaft-drive receiving region to orbit the central-axis-of-rotation.
  • the sidewall can be configured to pivotally engage a block and the crankshaft-drive receiving region can be configured to receive a crankshaft-drive.
  • Planetary crankshafts that include a first end and a second end, at least a first crankshaft-drive and at least first and second radially extending piston journals.
  • the at least first crankshaft-drive is configured to rotatably engage a first drive-member.
  • the at least first crankshaft-drive defines a first longitudinal axis and is disposed on the first end.
  • the at least first and second radially extending piston journals are each configured to pivotally engage a corresponding crankshaft- bearing-region of respective first and second pistons.
  • the first piston journal defines a second longitudinal axis and the second piston journal defines a third longitudinal axis.
  • the first, second, and third longitudinal axes are substantially parallel to and spaced from each other, and can be substantially coplanar.
  • the respective piston journals can be angularly separated by an angle measuring from about 0-degrees to about 180-degrees (e.g., about 60-degrees to about 150-degrees).
  • Pistons for reciprocating-piston apparatus can include a substantially cylindrically shaped head configured to be reciprocally received in a piston-cylinder and an elongate body.
  • the elongate body can be configured to pivotally engage a crankshaft journal and to be reciprocally received in a piston cylinder.
  • the body can extend from the head.
  • the body is sized to be spaced from a corresponding crankcase wall or cylinder wall.
  • more than about 25%, such as more than about 33%, and in some instances, more than about 50%, of the body can have a substantially uniform width that is substantially the same as the head diameter.
  • the body also can have a thickness substantially less than the piston diameter.
  • the body has a substantially uniform width over a majority of the body that is substantially the same as the head diameter. In other embodiments, the body has a width being narrower than the head diameter.
  • Elongate bodies that are configured to pivotally engage a crankshaft journal can include a bearing configured to engage the crankshaft journal.
  • Elongate bodies that include a bearing can also include a separable bearing cap defining a concave region and an end distal from the head configured to engage the separable bearing cap. The distal end defines a concave region, wherein the concave region of the bearing cap and the concave region of the end are together configured to substantially enclose the crankshaft journal when the end engages the bearing cap to substantially form the bearing configured to engage the crankshaft journal.
  • the elongate body and the piston head define at least one oil pathway configured to distribute oil among the crankshaft journal and the piston cylinder.
  • Bearing caps can define at least one oil pathway configured to distribute oil among the crankshaft journal and the piston cylinder.
  • Pistons can also include one or more oil pathways configured to distribute oil to the piston head to promote cooling of the piston head during use.
  • Blocks for reciprocating-piston apparatus include a body of unitary construction, a longitudinal crankcase, a drive-member receiving region and at least first and second cylinders.
  • the drive-member receiving region can be in communication with the crankcase and can define a central-axis-of-rotation.
  • the at least first and second cylinders are in communication with the crankcase and have respective longitudinal axes disposed at an angle measuring between about 0- degrees and about 180-degrees relative to each other and longitudinally offset along the central-axis-of-rotation.
  • the unitary body can define the crankcase, the drive- member receiving region, and the first and second cylinders.
  • the first and second cylinders each include a substantially cylindrical top-portion that defines a diameter and a narrow central-portion having a first width perpendicular to the central-axis- of-rotation.
  • the first width can be substantially the same as the diameter along the central-portion's length, or just part of the length (e.g., about 25% of the length, about 33% of the length, or more than about 50% of the length).
  • a second width along the central-axis-of-rotation is substantially less than the diameter.
  • the longitudinal axes of the first and second cylinders are longitudinally spaced along the crankcase by less than or equal to the diameter of the top-portion.
  • the reciprocating-piston apparatus comprises an internal combustion engine for converting chemical energy of a fuel, in part, to mechanical work.
  • the reciprocating-piston apparatus comprises a positive displacement pump for pumping a fluid.
  • a crankshaft and bearing apparatus can include a crankshaft, at least a first piston, a drive member and an internal ring gear.
  • the crankshaft defines at least one crankshaft drive having a crankshaft drive axis-of-rotation and at least one piston- journal radially spaced from the at least one crankshaft drive.
  • the piston journal defines a piston-journal longitudinal axis spaced from the crankshaft drive axis-of- rotation.
  • the drive member defines a central axis-of-rotation and a crankshaft drive receiving region for engaging the crankshaft drive.
  • the piston engages the piston journal.
  • the crankshaft drive has a corresponding pinion for engaging the ring gear.
  • the crankshaft drive axis-of- rotation orbits the central axis of rotation and urges the piston to linearly reciprocate.
  • the ring gear is stationary.
  • the spacing between the crankshaft drive axis-of-rotation and the piston-journal longitudinal axis is about one-quarter the stroke of the piston.
  • Some embodiments include a block defining at least one cylinder bore for slidably receiving the at least one piston.
  • the at least one piston can define an elongate surface that cooperates with a wall of the cylinder bore to guide the piston as it reciprocates.
  • the elongate surface provides a bearing surface.
  • the block houses the ring gear.
  • the ring gear is fixedly attached to the block.
  • the at least one piston includes at least two pistons.
  • the crank includes at least two piston journals, each having a longitudinal axis.
  • a first piston-journal longitudinal axis is radially spaced from the crankshaft drive axis-of-rotation.
  • a second piston-journal longitudinal axis is radially spaced from the crankshaft drive axis-of-rotation and angularly offset from the longitudinal axis of the first piston journal by a first angle.
  • the pinion has a radius substantially equal to the radial spacing between the crankshaft drive axis-of-rotation and one or both of the piston journal longitudinal axes.
  • the at least one cylinder bore can include at least two cylinder bores for receiving the at least two pistons.
  • the two cylinder bores are angularly offset from each other by a second angle, about one-half of the first angle.
  • the first angle ranges up to about 180-degrees
  • the second angle ranges up to about 90-degrees.
  • the first angle is between about 90-degrees and about 180-degrees
  • the second angle is between about 45- degrees and about 90-degrees.
  • the first angle is about 144- degrees and the second angle is about 72-degrees.
  • the at least one piston includes at least four pistons. In some instances, the at least one piston includes at least six pistons. The at least one piston can include at least eight, at least ten or at least twelve pistons.
  • FIG. 1 illustrates geometric and spatial relationships concerning hypocycloid motion.
  • FIG. 2 illustrates additional geometric and spatial relationships concerning hypocycloid motion.
  • FIG. 3 a schematic timing diagram illustrating various positions of a pair of circles, in sequence, undergoing hypocycloid motion.
  • FIG. 4 illustrates a linkage representation of an embodiment similar to that shown in FIG. 9 at various sequential positions.
  • FIG. 5 is a schematic timing diagram illustrating various positions of another pair of circles in sequence during hypocycloid motion.
  • FIG. 6 is a schematic timing diagram illustrating various positions of a third pair of circles in sequence during hypocycloid motion.
  • FIG. 7 is an exploded view of one embodiment of a machine configured to convert motion from rotation to reciprocation, and vice-versa.
  • FIG. 8A illustrates a side elevation of an alternative embodiment of a machine configured to convert motion from rotation to reciprocation, and vice-versa.
  • FIG. 8B illustrates a front elevation of the embodiment shown in FIG. 8 A.
  • FIG. 8C illustrates a plan view of the crankshaft of the embodiment of FIGS. 8A and 8B having piston journals angularly offset by other than 180-degrees.
  • FIG. 8D illustrates an end elevation of the crankshaft shown in FIG. 8C.
  • FIG. 9 illustrates a perspective view of a third embodiment of an assembled machine configured to convert motion from rotation to reciprocation, and vice-versa.
  • FIG. 10 illustrates an exploded, perspective view of the embodiment shown in FIG. 9.
  • FIG. 11 illustrates a partial cross-sectional, perspective view of the embodiment shown in FIG. 9.
  • FIG. 12 illustrates a top plan view of the block in the embodiment shown in
  • FIG. 13 illustrates a perspective view of the block shown in FIG. 12.
  • FIG. 14 illustrates a front elevation view of the block shown in FIG. 12.
  • FIG. 15 illustrates a cross-sectional view of the block shown in FIG. 12 taken along line 15-15 of FIG. 14.
  • FIG. 16 illustrates an exploded view of a piston configured to engage a planetary crankshaft according to the embodiment of FIG. 9.
  • FIG. 17 illustrates a side elevation of the piston of FIG. 16 assembled to the bearing cap, also shown in FIG. 16, with internal features shown in relief.
  • FIG. 18A illustrates another side elevation of the piston of FIG. 16, with internal features shown in relief.
  • FIG. 18B illustrates a cross-sectional view of the piston of FIG. 16 taken along line 18B-18B of FIG. 18 A.
  • FIG. 18D illustrates an end view of the piston of FIG. 16 along line 18D-18D of FIG. 18 A.
  • FIG. 18C illustrates a side elevation of the bearing cap of FIG. 16, with internal features shown in relief.
  • FIG. 18E illustrates an end view of the bearing cap of FIG. 16 along line 18E-18E ofFIG. 18C.
  • FIG. 18F illustrates a top plan view of the bearing cap of FIG. 16 along line 18F-18F ofFIG. 18C.
  • FIG. 19 illustrates a perspective view of a planetary crankshaft configured according to the embodiment of FIG. 9.
  • FIG. 19A illustrates a plan view of the crankshaft of FIG. 19 from above.
  • FIG. 19B illustrates an end elevation view of the crankshaft of FIG. 19 showing hidden features in relief.
  • FIG. 19C illustrates a side elevation view of the crankshaft of FIG. 19 showing hidden features in relief.
  • FIG. 20 illustrates a perspective view of a drive-member configured according to the embodiment of FIG. 9.
  • FIG. 2OA illustrates a top plan view of the drive-member of FIG. 20 showing hidden features in relief.
  • FIG. 2OB illustrates a front elevation view of the drive-member of FIG. 20 showing hidden features in relief.
  • FIG. 21 illustrates a top plan view of the assembly of FIG. 9 showing internal features in relief.
  • FIG. 21A illustrates a cross-sectional view taken along line 21A-21 A in FIG. 21.
  • FIG. 2 IB illustrates a cross-sectional view taken along line 21B-21B in FIG.
  • FIG. 22 illustrates a front elevation view of the embodiment of FIG. 9 showing internal features in relief.
  • FIG. 22A illustrates a cross-sectional view of the embodiment of FIG. 9 taken along line 22A-22A in FIG. 22.
  • FIG. 22B illustrates a cross-sectional view of the embodiment of FIG. 9 taken along line 22B-22B in FIG. 22.
  • FIG. 23 illustrates a perspective view of an alternative embodiment for converting motion from rotation to reciprocation, and vice-versa.
  • FIG. 23 A illustrates a front elevation view of the alternative embodiment of FIG. 23, showing internal features in relief.
  • FIG. 23B illustrates a cross-sectional view taken along line 23B-23B of FIG. 23 A.
  • FIG. 23C illustrates a cross-sectional view taken along line 23C-23C of FIG. 23A.
  • FIG. 24 illustrates a plot showing piston bore location relative to crankshaft angular displacement for an embodiment similar that of FIG. 10 compared to piston bore location relative to crankshaft angular displacement for a Ford 302 cubic inch engine.
  • FIG. 25 illustrates an exploded perspective view of an embodiment similar to that of FIG. 23 incorporating a balance shaft.
  • FIG. 26 illustrates a perspective view of an embodiment similar to that of FIG. 10 incorporating a balance shaft and weighted drive-member. Selected internal features are shown in relief.
  • FIG. 26B illustrates a plan view of the embodiment of FIG. 26 from above, showing selected internal features in relief.
  • FIG. 26A illustrates a front elevation view of the embodiment of FIG. 26.
  • FIG. 26C illustrates a side elevation view of the embodiment of FIG. 26.
  • FIG. 26D illustrates an exploded perspective view of the embodiment of FIG. 26.
  • FIG. 27 illustrates an exploded view of a single-cylinder embodiment of a machine configured to convert reciprocation to rotation, and vice-versa. Selected features are shown in relief.
  • FIG. 28 illustrates an exploded view of another single-cylinder embodiment of a machine configured to convert reciprocation to rotation, and vice-versa. Selected features are shown in relief.
  • FIG. 29 illustrates an exploded, partial cross-sectional view of a four- cylinder embodiment of a machine for converting motion from rotation to reciprocation, and vice-versa. Selected features are shown in relief.
  • FIG. 29A illustrates a detailed view of the region encompassed by the circle 29A ofFIG. 29.
  • FIG. 30 illustrates a perspective view of another piston embodiment.
  • FIG. 3OA illustrates a plan view of the piston of FIG. 30.
  • FIG. 3OB illustrates a front elevation view of the piston of FIG. 30.
  • FIG. 30C illustrates a side elevation view of the piston of FIG. 30.
  • FIG. 31 illustrates an exploded perspective view of a drive-member and crankshaft assembly configured according to the alternative embodiment of FIG. 23.
  • FIG. 32 illustrates a plan view from above of another alternative embodiment of a machine for converting motion from rotation to reciprocation, and vice-versa, using a four piston-cylinder configuration, with internal features shown in relief.
  • FIG. 33 illustrates a perspective view of the intermediate shaft that places pairs of pistons out of phase in the embodiment illustrated in FIG. 32.
  • FIG. 33A illustrates a top plan view of the intermediate shaft of FIG. 33.
  • FIG. 33B illustrates an end elevation view of the intermediate shaft of FIG. 33, with hidden features shown in relief.
  • FIG. 34 illustrates a front elevation view of a third alternative embodiment, which uses an eight cylinder configuration to convert motion from rotation to reciprocation, and vice-versa, with internal features shown in relief.
  • FIG. 34A illustrates a cross-sectional view along line 34A-34A of FIG. 34.
  • FIG. 34B illustrates a cross-sectional view along line 34B-34B of FIG. 34.
  • FIG. 35 illustrates a perspective view of another alternative embodiment for a drive-member.
  • FIG. 35A illustrates a plan view of the drive -member of FIG. 35 from above showing hidden features in relief.
  • FIG. 35B illustrates a front elevation view of the drive-member of FIG. 35 showing hidden features in relief.
  • FIG. 36 illustrates a perspective view of yet another alternative embodiment for a drive -member.
  • FIG. 36A illustrates another side elevation view of the drive-member of FIG. 36, showing hidden features in relief.
  • FIG. 36B illustrates a side elevation of the drive-member of FIG. 36, showing hidden features in relief.
  • FIG. 36C illustrates a front elevation of the drive-member of FIG. 36, showing hidden features in relief.
  • FIG. 37 illustrates a perspective view of an embodiment of a shaft-mountable balance weight for a drive-member.
  • FIG. 37A illustrates a front elevation view of the shaft mounted balance weight of FIG. 48.
  • FIG. 37B illustrates a plan view of the shaft-mountable balance weight of FIG. 37 from above, showing hidden features in relief.
  • FIG. 38 is a perspective exploded view illustrating a multi-part crankshaft having piston journals angularly offset by other than 180-degrees and being configured to reciprocate pairs of pistons out of phase with each other.
  • a hypocycloid refers to any of a family of curves that results from following a single point on a circumference of a first circle as the first circle rolls around the interior of a second circle of larger diameter. If the diameter of the first circle is half that of the second circle, resulting hypocycloids are straight lines that span the second circle. This geometric relationship forms the basis of motion of machines described herein.
  • two points 6702 and 6706 located on a circumference of a circle 6703 are each spaced from the center 6704 of the circle by a distance of .25X.
  • the angle 2V e.g., 180-degrees in the example shown in FIG. 1, angularly separates the points 6702 and 6706 relative to the center 6704 of the circle 6703.
  • the circle 6703 has a diameter of length 0.5X.
  • the outer circle defines a diameter of length X.
  • FIGS. 3(A)-3(I) as the circle 6703 rolls around the interior of the circle 6701, the center 6710 of the outer circle 6701 remains positioned on the circumference of the inner circle 6703.
  • the points 6702 and 6706 also translate along the axes 6802 and 6804, respectively.
  • the axes 6902 and 6804 intersect at the center 6710 of the outer circle.
  • the angular separation V of the axes 6802 and 6804 relative to the center 6710 is one-half of the angular separation 2 V between the points 6702 and 6706.
  • the angle V measures about 90-degrees.
  • the axes 6802 and 6804 have lengths X and define the stroke length, X, of the reciprocation of the points 6702 and 6706 along the axes.
  • generation of a pair of linear hypocycloids is illustrated as a first circle 6703 rolls about the interior of a second, larger circle 6701 with a diameter twice that of the first circle.
  • the smaller circle 6703 rotates counter-clockwise about its center 6704 as it orbits about the central axis of rotation 6710, which coincides with the center of the larger circle.
  • the smaller circle 6703 has a diameter 6708 equal to the radius of the larger circle 6701.
  • points on the circumference of the smaller circle 6703 such as points 6702 and 6706, trace linear hypocycloids, such as the hypocycloids 6804 and 6802.
  • the resulting hypocycloids will be disposed at 90-degrees relative to each other. If the ratio of the large circle's diameter to that of the small circle is not equal to 2-to-l, then the resulting hypocycloids will not be linear. As more fully described below, if the angular separation 2V between the points 6702 and 6706 is less than aboutl80- degrees (as in FIG. 2), the angle V can measure less than about 90-degrees. As described above concerning the geometric relationships shown in FIG. 1, varying the diameter X of the outer circle 6701 varies the length of the stroke through which the points 6702 and 6706 travel.
  • FIG. 2 shows a pair of circles 24, 25 similar to the circles 6701, 6703 shown in FIG. 1.
  • Points 20, 21 located on the circumference of the inner circle 24 are angularly separated by an angle 2V relative to the center 22 of the circle 25, such as, for example, by about 120-degrees (or 2V being about 240-degrees).
  • the diameter of the outer circle 24 has a length X and the diameter of the inner circle 25 has a length half as long, i.e., 0.5X.
  • the points 20, 21 are spaced from the center 22 of the inner circle 25 by 0.25X.
  • rolling the inner circle 25 around the inner circumference of the outer circle 24 reciprocates the points 20 and 21 along the axes 70 and 29, respectively.
  • the axes 29, 70 intersect at the center 23 of the outer circle 24 and form an angle V corresponding to the angle 2 V (or in some embodiments, the angle 2V).
  • the angular separation V between the two points 6702 and 6706 located at opposing ends of the diameter of, and on the circumference of, the inner circle 6703 relative to the center 6704 of the inner circle measures 180-degrees.
  • the selected two points 6702 and 6706 on the inner circle 6703 correspond to respective longitudinally extending crank-pin axes (e.g., the axes 502 and 506 shown in FIG. 19B), and the center 6704 of the inner circle 6703 corresponds to the crankshaft-drive axis (e.g., the axis 504 shown in FIG. 19B).
  • the angle V shown in FIG. 1 represents the angular separation of the axes 6802 and 6804 traced by the points 6702 and 6706 located on the circumference of the inner circle 6703 as the inner circle rolls within the outer circle 6701.
  • the axes 6802 and 6804 correspond to longitudinal axes of respective piston-cylinder bores (e.g., the longitudinal axes 150, 152 of the respective cylinder bores 110, 112 shown in FIG. 10).
  • the center 6710 of the outer circle 6701 corresponds to the central axis of rotation 114, about which the crankshaft 116 orbits and the drive member 104 turns.
  • the circle 6703 has a diameter of length 0.5X and the circle 6701 has a diameter of length X.
  • the diameter 0.5X of the inner circle 6703 is about equal to a circular pitch diameter of a crankshaft drive pinion gear 670, 671.
  • the diameter X of the outer circle 6701 corresponds to a circular pitch diameter of the ring gear(s) 660 and 661.
  • the hypocycloid motion and MTM architecture just described can result from, or be schematically represented by, a pair of pinned (e.g., pivotally connected) linkages, as shown by FIGS. 4(A)-(I).
  • the first linkage 5802 pivotally couples at its proximal end 5806 to a fixed reference frame, forming a central axis of rotation.
  • the first linkage 5802 is also pinned at its distal end 5808 to, and bisecting, the second linkage 5804.
  • the second linkage 5804 is twice as long as the first linkage 5802. As the first linkage 5802 rotates clockwise about the central axis of rotation, the second linkage 5804 rotates counter-clockwise.
  • FIGS. 4(A)-(I) illustrate a series of relative positions of the pair of linkages
  • a linkage mechanism for converting motion from rotation to reciprocation, and vice-versa can use a slidable piston pivotally coupled to the opposing ends 5810 and 5812 of the second linkage 5804, as described in more detail below.
  • FIG. 58FIG. 4(A) illustrates the relative positions of the linkages 5802 and 5804 with the first linkage 5802 at zero-degrees of rotation (e.g., a starting position). At this position, the second linkage 5804 is aligned with the first axis 5814 and the first end 5812 is at its Top Dead Center (TDC) location. The second end 5810 is aligned with the central axis of rotation.
  • TDC Top Dead Center
  • FIG. 4(B) illustrates relative positions of the linkages 5802 and 5804 with the first linkage 5802 rotated clockwise by 45-degrees.
  • the second linkage 5804 has rotated 45-degrees counter-clockwise relative to its starting position.
  • the first end 5812 has translated along the first axis 5814 toward the central axis of rotation 114.
  • the second end 5810 has translated along the axis 5816 toward its Bottom Dead Center (BDC) position.
  • BDC Bottom Dead Center
  • FIG. 4(C) illustrates relative positions of the linkages 5802 and 5804 with the first linkage 5802 rotated clockwise by 90-degrees.
  • the second linkage 5804 has rotated counter-clockwise by 90-degrees relative to its starting position, placing the first and second linkages 5802 and 5804, respectively, in alignment.
  • the end 5812 coaxially aligns with the central axis of rotation.
  • the second end 5810 is at BDC along the second axis 5816.
  • FIG. 4(D) illustrates relative positions of the linkages 5802 and 5804 with the first linkage 5802 rotated clockwise by 135-degrees.
  • the second linkage 5804 has rotated 135-degrees counter-clockwise relative to its starting position.
  • the first end 5812 has translated along the first axis 5814 past the central axis of rotation 114.
  • the second end 5810 has translated along the axis 5816 from BDC toward TDC.
  • FIG. 4(E) illustrates relative positions of the linkages 5802 and 5804 with the first linkage 5802 rotated clockwise by 180-degrees.
  • the second linkage 5804 has rotated counter-clockwise by 180-degrees relative to its starting position, placing the first and second linkages 5802 and 5804, respectively, in alignment.
  • the end 5812 is at BDC and the second end 5810 aligns with the central axis of rotation.
  • FIG. 4(F) illustrates relative positions of the linkages 5802 and 5804 with the first linkage 5802 rotated clockwise by 225-degrees.
  • the second linkage 5804 has rotated 225-degrees counter-clockwise relative to its starting position.
  • the first end 5812 has translated along the first axis 5814 from its BDC location toward the central axis of rotation 114.
  • the second end 5810 has translated along the axis 5816 past the central axis of rotation and toward its TDC position.
  • FIG. 4(G) illustrates relative positions of the linkages 5802 and 5804 with the first linkage 5802 rotated clockwise by 270-degrees.
  • the second linkage 5804 has rotated counter-clockwise by 270-degrees relative to its starting position, placing the first and second linkages 5802 and 5804, respectively, in alignment. At this position, the end 5812 coaxially aligns with the central axis of rotation. The second end 5810 is at TDC along the second axis 5816.
  • FIG. 4(H) illustrates relative positions of the linkages 5802 and 5804 with the first linkage 5802 rotated clockwise by 315-degrees.
  • the second linkage 5804 has rotated 315-degrees counter-clockwise relative to its starting position.
  • the first end 5812 has translated along the first axis 5814 past the central axis of rotation 114.
  • the second end 5810 has translated along the axis 5816 from TDC toward BDC.
  • FIG. 4(H) corresponds to the position of the respective geometric relationships shown in FIG. 1.
  • the diameter of the inner circle 6703 is .5X, or equal to the radius of circle 6701, and corresponds to a revolved diameter of the piston crankpin axes 5810 and 5812 shown in FIG. 4(H) (e.g., for crankshafts having piston crankpin axes separated by 180-degrees).
  • the revolved diameter of the piston crankpin axes defines one-half of a piston stroke for a corresponding piston.
  • the center 6704 of the inner circle 6703 shown in FIG. 1 corresponds to the central axis 5808 about which a planetary crankshaft (e.g., the linkage 5804) revolves.
  • the axis 5808 is coaxially located relative to the crankshaft-drive (e.g., the crankshaft-drive 140 and 141 shown in FIGS. 19 - 19C) and a corresponding crankshaft-drive receiving region of a drive member (e.g., the crankshaft-drive receiving region 138 and 139 shown in FIGS. 10 and 11).
  • the illustrated linkage 5802 between the central axis of rotation 5806 and the axis of revolution 5808 corresponds to a drive member (e.g., the drive member 104 shown in FIG. 10).
  • FIG. 4(1) illustrates relative positions of the linkages 5802 and 5804 with the first linkage 5802 rotated clockwise by 360-degrees.
  • the second linkage 5804 has rotated counter-clockwise by 360-degrees relative to its starting position, placing the first and second linkages 5802 and 5804 in their respective starting positions.
  • the second linkage 5804 of FIGS. 4(A)-(I) forms a class 2 lever, with loads transmitted at its midpoint to and/or from the first linkage 5802, and with opposing ends 5812 and 5810 pivo tally and slidably constrained.
  • the first linkage 5802 can be functionally described as a crank-arm that rotates about a central axis of rotation, and that transmits class 3 lever loads to the second linkage 5804 and class 2 lever loads from the second linkage 5804.
  • FIGS 4(A)-(I) illustrate that reciprocation of the opposing ends 5812 and 5810 along the axes 5814 and 5816, respectively, drives rotation about a central axis of rotation, or conversely, that rotation about the central axis of rotation drives reciprocation.
  • FIG. 2 illustrates an exemplary hypocycloid geometry having an angular separation 2V measuring less than 180-degrees, such as for example, about 120- degrees, between two points 20, 21 (relative to a center 22 of the inner circle 25).
  • the inner circle 25, like the inner circle 6703 in FIG. 1, has a radius of 0.25X and a corresponding diameter of 0.5X.
  • the outer circle 24, like the outer circle 6701 in FIG. 1, has a diameter X being twice that of the inner circle 25.
  • FIGS. 2 and 5(A)-5(I) by revolving the circle 25 within the circle 24, the points 20 and 21 trace axes 70 and 29, respectively.
  • Each of these axes 29 and 70 bisect the outer circle 24, and intersect at the outer circle's center 23.
  • the angular separation V of the axes 29 and 70 relative to the center 23 measures one-half of the angular separation 2V between the points 20 and 21, e.g., about 60- degrees for the example shown in FIG. 1.
  • the angle 2V can be used to characterize the angular separation between the points 20, 21.
  • the axes would then be said to be oriented at an angle V (measuring one-half of the angle 2V).
  • Varying the angle 2 V separating the points 20, 21 varies the angle V separating the axes 29 and 70.
  • some exemplary pairs of angles 2V and V are 90-degrees and 45-degrees, 144-degrees and 72-degrees, and 240-degrees and 120-degrees.. Please refer to FIGS. 6(A)-6(I), 7 and 8A-8D and the corresponding description below for further exemplary pairs of angles 2V and V.
  • the points 20, 21 can correspond to longitudinally extending axes of respective crank-pins (or piston-journals) of a crankshaft, such as, for example, the crankshaft 616 shown in FIG. 7.
  • crankshaft 616 shown in FIG. 7.
  • Such a single-point example of hypocycloid motion can represent a single-cylinder MTM architecture.
  • FIGS. 5(A)-(I) and 6(A)-(I) schematic timing diagrams are shown for various sequential positions of respective pairs of circles undergoing hypocycloid motion.
  • the sequence shown in FIGS. 5(A)-5(I) corresponds with the geometry described above and shown in FIG. 2.
  • the points 20, 21 on the inner circle 25 are separated by an angle 2Vmeasuring less than 180-degrees and greater than about 90-degrees (e.g., about 120-degrees) relative to the center 23.
  • the axes 29, 70 are angularly offset from each other by an angle V measuring one-half of the angle 2 V measured between the points 20, 21 relative to the center 23 of the circle 25.
  • the corresponding axes of reciprocation 29, 70 are offset by angle V measuring one-half of about 144-degrees (e.g., about 72-degrees).
  • a crankshaft 9 can have longitudinal axes 14, 15 of respective piston journals 12, 13 offset by an angle 2V measuring about 144- degrees.
  • the respective axes 5, 6 of the piston cylinders 3, 4 (shown in FIG. 8B) are angularly offset by an angle V measuring one-half of the angle 2V (e.g., about 72- degrees).
  • the points 20, 21 can be separated (and, with reference to, for example, FIG. 8D, the corresponding longitudinal axes 14, 15 of piston journals 12, 13 can be offset), generally, by an angle measuring from zero to 360-degrees.
  • the corresponding axes of reciprocation e.g., the axes 5, 6 shown in FIG 8B
  • the corresponding axes of reciprocation can be offset by one-half the angle between the points 20, 21 (and the axes 5, 6), or from zero- to 180-degrees.
  • Some blocks have cylinders angularly offset by as much as 180-degrees, as in a "boxer" configuration.
  • cylinders that are longitudinally offset along the central axis-of-rotation without being angularly offset (as with an "inline” configuration).
  • a pair of corresponding pistons are angularly offset by about 180- degrees, but not longitudinally offset along the central axis-of-rotation.
  • a piston head such as the piston head 142 (see FIG. 10), can be positioned at opposing ends of a single elongate piston body.
  • FIGS. 6(A)-6(I) illustrate a progression of hypocycloid positions similar to that shown in FIGS. 5(A)-5(I), except that the points 30, 31 are angularly offset by about 90-degrees relative to the center 32 of the inner circle 35.
  • FIGS. 6(A)-6(I) are numbered similarly to features shown in FIGS. 5(A)-5(I), except that the reference numerals in FIGS. 6(A)-6(I) are incremented by ten.
  • the points 30, 31 in FIGS. 6(A)-6(I) are similar to the points 20, 21.
  • the resulting reciprocation of the points 30, 31 occurs along lines 80, 39, which are offset by one- half of the offset between the points 30, 31 (e.g., about 45-degrees).
  • FIG. 7 illustrates an exploded view of one exemplary embodiment of a reciprocating piston machine incorporating MTM architecture.
  • the piston-cylinders 610 and 612 of the cylinder block 602 are angularly displaced relative to the central axis of the crankcase 618 by an angle V measuring approximately 45-degrees.
  • the planetary crankshaft 616 comprises crankpins 626, 628 being angularly offset relative to the crankshaft drives 640, 641 by an angle 2V measuring approximately 90-degrees.
  • the pistons 606 and 608 respectively comprise piston heads 642 and 643, piston-ring receiving regions 609 and 609A, and elongate bodies 644 and 645 being narrower than a major diameter of the respective piston-ring receiving region.
  • the proximal end of each elongate body 644, 645 defines a respective recessed region 621, 624.
  • Each end-cap 620, 620A (also referred to herein as a "bearing cap”) defines a respective recessed region 622, 625 and is configured to engage a proximal end of a corresponding elongate body 644, 645 for pivotably capturing the crankpins 628 and 626 of the crankshaft 616 between opposing recessed regions 621, 622 and 624, 625.
  • Each piston 606, 608 is slidably disposed in a corresponding piston- cylinder bore 610, 612.
  • Ring-gear receiving regions 619 and 619A defined by the crankcase 618 can receive respective internal ring gears 660 and 661.
  • Pinions 670 and 671 defining corresponding pinion bores 674, 675 can be coaxially affixed (as by, for example, press fitting, welding) to respective crankshaft-drives 640 and 641 located at opposing ends of the crankshaft 616.
  • Each of the illustrated ring gears 660, 661 define respective drive-member receiving regions 664, 665 for receiving a corresponding drive -member 604, 605 in a concentric relationship with the respective drive-member sidewall 634, 635.
  • Each ring gear 660, 661 also comprises an internal ring gear cog region 667, 668 for matingly engaging corresponding cogs 672, 673 of a respective pinion 670, 671.
  • the internal ring gear cogs 667 and 668, and crankshaft-drive pinion cogs 673 and 672 can be left and right handed helical pitch cogs. Such cog configurations can provide axial spacing of the crankshaft.
  • double helix (herringbone) pinion and internal ring gear cogs at one of the respective crankshaft ends e.g. cogs 668 and 672 can provide axial spacing of the crankshaft.
  • Helical gears also provide more silent operation.
  • Each drive-member 604, 605 defines a crankshaft-drive receiving region 639 (visible in FIG. 7 only on the drive-member 605) for receiving a corresponding crankshaft-drive 640, 641.
  • Each drive -member 604, 605 also defines a corresponding driveshaft 636 (visible in FIG. 7 only on the drive-member 604).
  • the drive shaft can be received in a bearing housing (not shown) positioned coaxially relative to the crankcase 618 and the central axis of rotation about which the planetary crankshaft 616 orbits, as supported by a bearing housing (not shown). As described above with reference to the sequence of positions shown in FIGS.
  • the inner circle 35 "rolls" within the outer circle 34 such that the center 32 of the inner circle 35 orbits the center 33 of the outer circle 34 in a clockwise direction.
  • the center 33 of the outer circle 34 is analogous to a central axis of rotation about which the crankshaft 616 shown in FIG. 7 orbits and about which the drive member 604 turns.
  • the center 32 of the small circle 35 is analogous to a crankshaft axis-of- revolution (not shown) about which the crankshaft 616 revolves as it orbits the central-axis-of-rotation 614.
  • the piston-cylinders 610 and 612 are substantially cylindrical in shape and in the illustrated example are not narrowed to correspond to the shape of the elongate bodies 644, 645 of the pistons. Also by way of example, the illustrated cylinders 610, 612 do not transect the crankcase, as in other disclosed exemplary embodiments. These are among many features that can reduce friction.
  • the illustrated elongate bodies 644 and 645 are narrowed in at least one dimension with respect to the diameter of the piston heads 642 and 643. In such embodiments, respective "swept areas" of sliding contact between each respective piston 606, 608 and piston-cylinder 610, 612 is thus reduced compared to a piston having an elongate body in sliding contact with a portion of the piston cylinder.
  • pistons, crankshafts, drive-members and blocks are described with reference to FIGS. 1-6, 8A-8D, and 38.
  • FIGS. 8 A and 8B illustrate an alternative embodiment of a motion translation mechanism 10 incorporating MTM architecture.
  • the planetary crankshaft 9 (shown in FIGS. 8C and 8D) includes one or more pinions 8 for rotatably engaging a ring gear 7, as described above.
  • the longitudinal axes 14, 15 of the piston journals 12, 13 radially spaced from the crankshaft-drive axis-of- rotation 17 and angularly offset from each other by an angle 2 V.
  • crankshaft 9 includes pinions 8 positioned adjacent the crankshaft drive 16, the pinions 8 can be located at various other locations along the crankshaft 9.
  • the crankshaft drive 16 can be configured as described herein.
  • the radius of the pinion 8 e.g., a circular pitch radius
  • the ring gear 7 can be stationary relative to the block 10. In some instances the ring gear 7 is allowed to rotate relative to the block 10, such as to drive power take off devices.
  • the ring gear 7 comprises at least a portion of a drive-member, such as a portion of a drive-member receiving region.
  • the stationary ring gears 7 of FIGS. 8A and 8B are fixedly attached to the block 11 in a region adjacent the drive- member receiving region and independent of the drive-member (not shown).
  • the ring gear 7 can be disposed wholly or partially within a corresponding drive-member receiving region, and can be independent of, or integrated with, the respective drive-member.
  • the block 11 defines a pair of piston cylinders, or cylinder bores, 3, 4 similar to those described above.
  • Each cylinder bore defines a longitudinal axis 5, 6 along which corresponding pistons (not shown) reciprocate.
  • the cylinders 3, 4 in the block 10 are longitudinally spaced along the central axis-of-rotation and angularly offset from each other by an angle, V. In other words, cylinders 3, 4 in the block 10 should be angularly offset by about one -half the angle between the longitudinal axes 14, 15 of the corresponding crankshaft piston journals 12, 13.
  • the crankshaft has one piston journal, and the block defines one corresponding piston cylinder.
  • the pinion and ring gear engagement and drive-member provides lateral support to the crankshaft.
  • crankshaft defines more than two piston journals, each with a corresponding piston.
  • Blocks can define a corresponding cylinder for each of the pistons.
  • crankshafts that have piston journals angularly offset by other than 180-degrees can be coupled using an intermediate shaft to provide out-of-phase piston reciprocation.
  • the crankshaft 530 illustrated in FIG. 38 is one such embodiment.
  • the crankshaft 530 has a first crankshaft portion 531 and a second crankshaft portion 533 coupled to each other by the intermediate shaft 532.
  • the respective first crankshaft drives 581, 542 engage corresponding openings 534, 535 in the intermediate shaft 532, and the respective second crankshaft drives 547, 548 are configured to engage corresponding drive-members (not shown) in a manner such as those described above.
  • the first and second crankshaft portions 531, 533 each have features similar to crankshafts described in detail above.
  • the first crankshaft portion 531 defines a pair of piston journals 551, 552.
  • the second crankshaft portion 533 similarly defines a pair of piston journals 549, 550.
  • Each piston journal defines a longitudinal axis 554, although only the longitudinal axis 554 of the piston journal 550 is illustrated.
  • the piston journals 549, 550 of the second crankshaft portion 533 are angularly offset by an angle ranging up to 180-degrees.
  • the piston journals 551, 552 of the first crankshaft portion 531 are angularly offset by a similar angle.
  • the piston journals, and hence the corresponding pistons reciprocate along longitudinal axes offset by about one-half the angle between the piston journals 549, 550 and 551, 552, similar to other hypocycloid based mechanisms.
  • the pairs of piston journals 549, 550 and 551, 552 reciprocate out of phase.
  • Each portion 531, 533 includes a pair of pinions 583, 546 for coupling the crankshaft 530 to the block (not shown).
  • Corresponding ring gears 537, 588 with internal cogs 540, 539 are configured to engage the pinions 583, 546.
  • the ring gears 537, 588 are fixedly attached to the block, and in others, the ring gears 537, 588 are allowed to rotate relative to the block.
  • intermediate shafts define a pinion, such as the pinion 536 for engaging secondary devices, with balance shafts and synchronization shafts being examples.
  • crankshaft and bearing apparatus configured to convert motion from rotation to reciprocation, and vice- versa.
  • the embodiment incorporates aspects of the hypocycloid-based motion just described.
  • FIGS. 9-11 provides a drive-member 104 that functions similarly to the first linkage 5802 and a planetary crankshaft 116 that functions similarly to the second linkage 5804.
  • the embodiment of FIGS. 9-11 also incorporates first and second pistons 106 and 108 coupled to the crankshaft 116 at locations similar to the opposing ends 5812 and 5810 of the second linkage 5804.
  • the block 102 houses the crankshaft and bearing apparatus configured for hypocycloid based motion.
  • the embodiment of FIG. 9 includes first and second pistons, 106 and 108, respectively, coupled to the drive-member 104.
  • the block 102 defines first and second piston-cylinders 110 and 112, respectively, that slidably receive the respective first and second pistons, 106 and 108 and constrain the pistons 106 and 108 to substantially linear motion.
  • the first and second pistons 106 and 108 engage a crankshaft 116 that engages the drive-member 104.
  • the first and second pistons 106 and 108 are substantially similar to each other. Each includes a respective, substantially cylindrically shaped head 142 and 143, elongate body 144 and 145, crankshaft-bearing-region 121 and 124, and bearing cap 120 and 120A.
  • the first and second piston-cylinders 110 and 112 are also similar to each other and slidably receive the respective first and second pistons 106 and 108.
  • the first and second piston-cylinders 110 and 112 each define respective, substantially cylindrical top-portions 210 and 212 (see, e.g., FIGS. 11-15, 21, 21A, 22A and 22B) and respective narrow central-portions 202 and 207.
  • the proximal end 422 (FIG. 16) of the elongate body 144 of the first piston 106 forms a concave crankshaft bearing region 121 corresponding to the first piston journal 126 of the crankshaft 116.
  • a bearing cap 120 that attaches to the elongate body 144 also forms a concave region 122 corresponding to the first piston journal 126.
  • the elongate body 144 in combination with the bearing cap 120 pivotally engages the piston journal 126 through journaling surfaces, or alternatively, through a bearing race or bearing inserts (not shown).
  • FIG. 9 provides these features without using conventional connecting rods or wrist pins common in conventional slider- crank mechanisms.
  • the second piston 108 engages the second piston journal 128 in a similar fashion as shown in, for example, FIG. 10.
  • Embodiments similar to that of FIG. 9 include independent drive-members 104 and 105, although some embodiments include only a single drive-member.
  • crankshaft 116 defines crankshaft-drives 140 and 141 at each end.
  • the illustrated crankshaft-drives 140 and 141 pivotally engage the drive-members 104 and 105, although in some embodiments, the crankshaft-drives 140 and 141 can rotatably engage the drive-members 104 and 105.
  • pivotally engaging means that one body can pivot relative to another body such that contacting surfaces of the two bodies are able to effectively slip or slide relative to each other during a pivoting movement.
  • rotatably engaging means that two coupled bodies are able to rotate relative to each other. Accordingly, as used herein, all pivotally engaging bodies are also rotatably engaging, but not all rotatably engaging bodies are pivotally engaging.
  • a simple pin connection such as, for example, a pair of journaling surfaces, a journal surface and bearing race, among other configurations, provides both rotating and pivoting movement between two connected bodies.
  • a pinion engaging an internal gear does not provide a pivoting movement but does provide a rotating movement.
  • both the pin connection and the pinion/internal gear are examples of rotatably engaging bodies.
  • the pin connection is also pivotally engaging, but the pinion/internal gear connection is not.
  • each drive-member 104 and 105 is pivotally disposed in a corresponding drive-member receiving region 118 and 119 (see FIG. 11) defined by the block 102.
  • a housing for example the housing 700, pivotally engages the driveshaft 136 through a bearing portion, such as, for example, the journal surface 702 illustrated in FIG. 11.
  • the drive-member 104 is substantially supported by the housing 700, which is fixedly attached to the block 102 using a plurality of bolts 704.
  • the block 102 defines a recessed region for partially receiving the housing 700 and supporting the circumference of the housing 700, thereby reducing excessive and non-uniform shear loads on the bolts 704.
  • the drive-members 104 and 105 pivotally engage the drive-member receiving regions 118 and 119.
  • Journaling surfaces can provide engagement between either or both drive members 104 and 105 and the corresponding drive-member receiving regions 118 and 119.
  • a bearing race can provide the pivotal engagement between one or both drive- members 104 and 105 and the corresponding drive-member receiving regions 118 and 119. (Some alternative embodiments provide rotatable engagement between the block 102 and the drive members 104 and 105.)
  • a force applied to the first piston journal 126 urging reciprocation will impart a moment to the planetary crankshaft 116.
  • a force applied to the first piston journal 126 can result in a moment applied to the crankshaft 116.
  • a moment so applied will urge the crankshaft 116 to rotate.
  • the respective first and second crankshaft-drives 140 and 141 rotatably engage the respective first and second drive-members 104 and 105 the moment applied to the crankshaft 116 will urge the crankshaft-drives 140 and 141 against the drive members 104 and 105.
  • crankshaft-drives 140 and 141 against the drive members 104 and 105 will urge the drive members 104 and 105 to rotate, thereby urging the respective first and second crankshaft-drives, 140 and 141, to orbit the central-axis- of-rotation 114.
  • a moment applied to the drive-members 104 and 105 will urge the pistons 106 and 108 along a reciprocating path.
  • configurations similar to the embodiment of FIG. 9 eliminate conventional main bearings that support the crankshaft.
  • the block 102 orients the longitudinal axes 150 and 152 of the respective piston cylinders 110 and 112 at 90-degrees relative to each other and longitudinally spaces the piston cylinders 110 and 112 along the central- axis-of-rotation 114.
  • FIGS. 19, 19A-19C which illustrate the crankshaft 116 shown by FIG. 10, the radially extending first and second piston journals 126 and 128 oppose each other relative to the longitudinal axis of the crankshaft-drive 504.
  • the longitudinal axes 502 and 506 of the respective first and second piston journals 126 and 128 are spaced by a crankpin separation distance, X.
  • a crankshaft and bearing apparatus including a pair of pistons disposed at 90-degrees relative to each other and coupled together through a crankshaft with radially opposing piston-journals will provide a piston stroke twice the distance between the longitudinal axes of the opposing piston-journals. Accordingly, the embodiment of FIG. 9 will provide a stroke for each piston 106 and 108 of twice the crankpin separation distance, X.
  • the longitudinal axis 504 will undergo a circular orbit about the central-axis-of-rotation 114, where the radius of the orbit is approximately half the crankpin separation distance, X.
  • the planetary crankshaft 116 functions similarly to a class 2 lever with a fulcrum located alternately along longitudinal axis 502 or 506 (FIGS. 19A- 19C) of the crankshaft, and the effort applied alternately along axis 502 and 506, and the load applied along axis 504 similar to the second linkage 5804 of FIGS. 4(A)-4(I). Accordingly, if a force is applied to the first piston 106 (e.g., a gas expanding against the piston head 142 (see FIG. 10), the force will urge the piston 106 to slide in the cylinder 110, which in turn urges the crankshaft 116 to undergo motion similar to that of the second linkage 5804 illustrated in FIGS. 4(A)-4(I).
  • a force is applied to the first piston 106 (e.g., a gas expanding against the piston head 142 (see FIG. 10)
  • the force will urge the piston 106 to slide in the cylinder 110, which in turn urges the crankshaft 116
  • embodiments described herein provide mechanical arrangements for converting reciprocation to rotation and efficient transmission of linear forces to moments, and vice-versa.
  • principles just described can be applied to various other embodiments, several of which are described below.
  • the block 102 of FIG. 9 defines first and second piston cylinders 110 and 112 disposed at 90-degrees relative to each other and a crankcase 204, which defines a longitudinal axis substantially coincident with the central-axis-of-rotation 114 and transects the cylinders 110 and 112.
  • Each piston cylinder 110 and 112 defines a substantially cylindrical top portion, e.g., the cylindrical top portions 210 and 212 of the first and second piston cylinders 110 and 112, respectively.
  • the top portions slidably receive the piston heads 142 and 143.
  • Each piston cylinder 110 and 112 also defines a narrow central portion 202 and 207 that slidably receives the elongate bodies 144 and 145.
  • the narrow central portions 202 and 207 are defined by concave walls with a radius of curvature corresponding to that of the arcuate walls 416 of the elongate bodies 144 and 145. As described above, in some embodiments the radius of curvature of the arcuate walls 416 is the same as the radius of the piston heads 142 and 143. In such an embodiment, the narrow central- portions 202 and 207 have a first width corresponding to the diameter of the piston heads 142 and 143 and a second width, transverse to the first width (e.g., along the central-axis-of-rotation), substantially less than the diameter of the piston heads 142 and 143.
  • the elongate bodies 144 and 145 of the corresponding pistons When installed in a piston cylinder so formed, the elongate bodies 144 and 145 of the corresponding pistons are oriented substantially perpendicular to the central-axis-of-rotation 114.
  • the walls of the narrow central portions 202 and 207 provide guide surfaces for the corresponding elongate bodies 144 and 145. Notably, the guide surfaces distribute eccentric loads and reduce wear of the rings and cylinder walls near the piston head.
  • each piston cylinder 110 and 112 further defines a cylinder access disposed below the narrow central portion 202 and 207, i.e., opposite the cylindrical top-portion.
  • a cylinder access 208 of the second piston cylinder 112 is illustrated, but each cylinder provides a similar cylinder access.
  • the cylinder access 208 provides an opening that can be used to access the lower end of the cylinder, for example, for assembling the bearing caps 120 and 120A to the corresponding elongate bodies 144 and 145 of the pistons 106 and 108.
  • the block 102 can be formed of a unitary body, such as results from a casting process. Casting processes can be particularly desirable in view of the ability to form internal passageways and other cavities or through-holes without secondary machining operations.
  • the cylinders and crankcase can be cast with dimensions that approximate their final desired dimensions.
  • features such as flanges 306 and 308 (FIG. 13) for attaching an oil sump can be cast into the block 102.
  • the cylinders, each with a cylindrical top portion, narrow central portion and cylinder access, can be rough-cast in the unitary body. Following casting, surfaces that require a high degree of dimensional accuracy can be machined, for example using a milling, a boring, a honing or a similar process.
  • crankcase walls can be used as-cast, or they can be cast and bored. Cylindrical top portions, narrow central portions and cylinder access regions can be bored and honed to a desired dimension.
  • the block deck surface 302 and 304 can be machined to a desired flatness, for example, to provide a surface against which a cylinder head (not shown) can seal.
  • an oil galley (not shown) can provide pressurized, filtered oil from a pump and filter (not shown) to the piston-cylinders 110 and 112.
  • the piston- cylinders 110 and 112 so provided with pressurized oil can deliver oil to various oil pathways e.g., 402, 403, 403A, 404, 404A, and 428 (oil squirts for piston head cooling) (See FIGS. 16-18F, 21A and 21B), provided in the pistons 106 and 108.
  • an oil galley can provide oil to the drive-members 104 and 105, the crankshaft 116 and other intermediate shafts. Oil can be provided using any conventional oil delivery method, such as, for example, wet or dry sump pressure oiling. For a more detailed description, refer to the Lubrication section below.
  • FIG. 16 illustrates an exploded view of a piston and bearing cap configured to engage a planetary crankshaft according to the embodiment of FIG. 9.
  • FIG. 17 illustrates a side elevation of the piston of FIG. 16 assembled to the bearing cap. Internal features are shown in relief.
  • a bearing cap 120 can fixably attach to the proximal end 422.
  • the substantially cylindrical piston head 142 has an axis-of- symmetry substantially aligned with the longitudinal axis 408 of the piston 106.
  • the piston 106 can include any of a variety of piston head and piston ring configurations.
  • the illustrated piston head 142 includes a piston ring-carrier structure 424, extending longitudinally from the distal end of the piston head 142 to form a substantially cylindrically shaped wall circumferentially extending around a distal portion of the elongate body 144.
  • the conventional piston skirt (not shown) is replaced by the arcuate walls 416 of the elongate body 144.
  • Other embodiments can also include a more conventional piston skirt.
  • piston head 16 and 17 defines a plurality of circumferentially extending grooves 410 and 412 for engaging compression rings and oil scraper rings, respectively.
  • the illustrated piston head also defines a substantially flat distal surface.
  • the piston head 142 defines a convex distal surface, while other configurations of the piston head 142 define a concave distal surface.
  • some embodiments of the piston head 142 will provide more or fewer circumferentially extending grooves than the embodiment of FIG. 16.
  • the piston head 142 and/or the piston ring- carrier structure 424 can provide oil pathways in fluid connection to an oil reservoir (not shown) to enhance cooling of the piston head 142, the piston ring-carrier structure 424, and the piston rings during operation.
  • Oil squirt features 428 can also be provided to supply pressurized squirts of oil to the underside of the piston head for cooling of the piston head.
  • Oil return holes 406 can be provided under the groove 412 to return oil from an oil scraper ring.
  • the elongate body 144 longitudinally extends from the piston head 142, and piston ring-carrier structure 424 having a width that extends substantially across the diameter of the head 142 and a thickness substantially less than the diameter.
  • the width of the elongate body 144 is substantially the same as the diameter for between about 25% and about 50% of the length of the body 144.
  • the width of the elongate body 144 is substantially constant over its length, as illustrated.
  • the width of the elongate body 144 is slightly less than or greater than the diameter of the head 142, e.g., from about 0.000 inches to about 0.010 inches, such as about 0.001 inches to about 0.004 inches.
  • piston rings (not shown) fitted to piston ring grooves 410 and 412 may usefully be configured with reduced ring tension bearing against piston- cylinder walls 110 and 112 for reduced operational friction. See the detailed description of bearing and journaling features below.
  • the elongate body 144 defines arcuate walls 416 longitudinally extending from the circumference of the piston ring-carrier structure 424 and disposed on each transverse side of the elongate body 144. Accordingly, the arcuate walls 416 have a radius of curvature substantially similar to the radius of the piston head 142 and the piston ring-carrier structure 424. In addition, the arcuate walls 416 can be slidably received in a corresponding region of a piston-cylinder, e.g., first and second piston cylinders 110 and 112. See e.g., FIG. 11. Also FIG. 23B shows a cylinder wall 2504 that partially defines a narrowed central region of the piston cylinder 2312 corresponding to the elongate body of the piston 2308.
  • Each arcuate wall 416 can also define an oil pathway 402 for providing lubricant to surfaces that slide relative to each other in a slidable engagement, such as, for example, between a piston-cylinder and the elongate body 144.
  • the elongate body 144 can define a recessed region extending between the arcuate walls 416, forming an I-beam-like web member 414 having a reduced thickness relative to a chord between opposing sides of the arcuate walls 416.
  • the reduced thickness provides a lower piston mass, resulting in lower inertial forces during reciprocation of the piston 106.
  • a narrowed profile relative to the piston head 142 provides operational clearance between adjacent piston-cylinders, as well as between the elongate body 144 and walls of the crankshaft 116 that flank the piston journal 126.
  • the web member 414 can also define one or more lightening holes. Alternatively, the web member 414 can be substantially eliminated for further mass reduction.
  • the faces 430 and 430A of the piston 116 and the bearing cap 120 respectively, can also define a thrust bearing face, or can receive an insert bearing defining a thrust bearing face.
  • the proximal end 422 forms a plurality of recesses that define attachment features 426 with longitudinal axes of symmetry aligned parallel to the longitudinal axis 408 of the piston 106.
  • the attachment features 426 can define internal threads for engaging corresponding external threads of bolts extending through corresponding apertures 420 formed in the bearing cap 120.
  • Still another alternative configuration of the attachment features 426 provides studs (not shown) that extend from the proximal end 422.
  • the studs can be configured to engage corresponding features formed in the bearing cap 120.
  • the studs can define external threads to engage a corresponding nut.
  • dowels or "Fractured Cap” technology can provide alignment between the bearing cap 120 and the proximal end 422.
  • the illustrated proximal end 422 also forms a recess defining a crankshaft bearing region 121 for pivotally engaging the corresponding first piston journal 126. See, e.g., FIG. 10.
  • the crankshaft bearing region 121 can define one or more oil pathways 404 for providing lubricant to the pivotal engagement between the piston 106 and the crankshaft 116.
  • the bearing cap 120 can form a concave region 122 that defines crankshaft engagement features corresponding to the crankshaft bearing region 121 formed by the proximal end 422.
  • the bearing cap 120 can define one or more oil pathways 403 A, corresponding to the oil pathway 403 disposed in the arcuate wall 416 of the elongate body 144.
  • the crankshaft bearing regions 121 and 122 can receive insert shell bearings or bearing races.
  • pistons can be of substantially unitary construction (not shown).
  • no removable bearing cap is employed, and a "built- up” (e.g., "pressed together") crankshaft can be used to facilitate assembly of pivotal couplings between the pistons and the crankshaft.
  • pistons are formed using composite construction, e.g., different features are formed of different materials.
  • the ring-carrier structure 424 and/or the piston head 142 can be formed of an alloy of steel or iron to provide heat and wear resistance
  • the elongate body can be formed of an alloy of aluminum.
  • Such a composite piston provides for a long wearing, heat resistant, and light weight piston.
  • a composite MTM piston can, for example, join the piston head and elongate body with a pin, as is commonly practiced in joining a connecting rod and piston in a conventional slider crank piston mechanism assembly
  • FIGS. 30-30C illustrate one embodiment of an MTM piston 870.
  • the piston 870 comprises a piston head 892 located distally from a proximal end defining a crankpin-bearing bore 872 in a central region of the elongate body. Extending outwardly from the central region toward opposing sides of the elongate body are two respective piston-cylinder bearing regions 894 for slidably engaging a piston-cylinder defined by a block. A narrowed region 895 is located between the proximal end and the piston head 892.
  • an oilway 899 circumscribes a portion of the crankpin bearing bore 872 and an oilway 898 extends outwardly therefrom toward each opposing bearing region 894 to an opening 896 for placing the oilway in fluid communication with a film of lubrication (not shown) in the region of sliding engagement between the bearing region 894 and a corresponding cylinder wall.
  • a piston ring region 897 and the piston- cylinder bearing region 894 are approximately the same diameter. Narrowing of the elongate piston body in region 895 reduces the swept piston to cylinder surface area reduces friction losses arising from sliding contact between the bearing region 894 and a corresponding cylinder wall.
  • a crankshaft generally engages one or more pistons along the crankshaft's longitudinally extending length and engages or provides an externally accessible driveshaft.
  • the crankshaft 116 shown in FIG. 10 includes first and second crankshaft-drives 140 and 141 disposed on each end of the crankshaft.
  • Corresponding crankshaft-drive receiving regions 138 and 139 are formed in the drive-members 104 and 105 for coupling the driveshaft 136 to the crankshaft 116.
  • the illustrated embodiment provides pivotal engagement between the journaling surfaces of the crankshaft-drives 140 and 141 and the corresponding crankshaft- drive receiving regions 138 and 139.
  • the illustrated crankshaft 116 also includes radially extending piston journals 126 and 128 disposed 180-degrees from each other relative to, for example, the longitudinal axis 504 of the crankshaft-drive.
  • the piston journals 126 and 128 are physically joined with the crankshaft drives 140 and 141 by flanking walls formed by the crankshaft.
  • the piston journals 126 and 128 define respective longitudinal axes 502 and 506 that extend parallel to and spaced apart from the longitudinal axis 504 of the crankshaft drives 140 and 141.
  • Each piston journal 126 and 128 forms a crankpin for pivotally engaging a corresponding crankshaft-bearing-region of a piston, such as, for example, the first and second pistons 106 and 108.
  • Some embodiments of the crankshaft 116 include thrust faces 161, 162, 163, and 164 corresponding to the piston and bearing cap faces 430 and 430A shown in FIGS. 16-18F.
  • Some crankshafts include thrust faces 160 and 165 corresponding to the drive-member ends 132 and 133 (see FIG. 10).
  • crankshaft 270 includes first and second crankshaft drives 2706 and 2708 disposed at each end, and radially extending piston journals 2702 and 2704 disposed 180- degrees from each other.
  • crankshaft drives 2706 and 2708 each form a recessed region 2502 for pivotally engaging a corresponding drive -member, e.g., the shaft 2714 extending from the drive-member 271.
  • the recessed regions 2502 define an axis of symmetry radially offset from the piston journals 2702 and 2704.
  • crankshaft-drive defines a pinion configured to engage a corresponding gear defined by the drive-member's crankshaft-drive receiving region.
  • the crankshaft-drive receiving region forms an internal gear ring around the center of which the pinion can orbit.
  • crankshaft configurations dispose the piston journals at angles other than 180-degrees from each other relative to a longitudinal axis of the crankshaft-drive.
  • the above described embodiments of crankshafts are substantially one-piece bodies.
  • FIGS. 32-33B illustrate one embodiment 2800 of many that incorporates an intermediate shaft 2900 disposed between adjacent crankshaft portions 2801 and 2803 to provide alternative angles between adjacent piston journals relative to a longitudinal axis.
  • the intermediate shaft 2900 defines male drives 2902 and 2904 that pivotally engage corresponding female crankshaft portions 2814 and 2816 adjacent to the intermediate shaft 2900.
  • a drive-member couples a crankshaft to the driveshaft.
  • An exemplary drive-member 104 shown in detail by FIGS. 20-20B, is formed of a substantially cylindrical body defining a first end 130, a second end 132 and a sidewall 134 that extends between the ends 130 and 132.
  • the sidewall 134 is usually configured to pivot within a block in a manner similar to that shown in FIGS. 10 and 11.
  • the first and/or second ends 130 and 132 respectively, each define a thrust bearing face or a feature configured to receive a bearing featuring a thrust face.
  • the longitudinal axis 1502 of the drive-member 104 substantially coincides with the central-axis-of-rotation 114.
  • the crankshaft-drive receiving region 138 defines a longitudinal-axis-of-symmetry 144 parallel to and spaced from the longitudinal axis 1502.
  • FIG. 9 provides for pivoting between the drive-member 104 and the block 102 by journaling or otherwise pivotally supporting a portion or portions of the driveshaft 136.
  • a housing member similar to the housing 700, provides bearing support to the drive-member 104 by journaling a portion or portions of the drive shaft 136 in a bearing arrangement.
  • the housing can provide attachment for a driven or driving device, or may include part of such device.
  • the housing 700 can be fixedly attached to the cylinder block and can provide a bearing region 702 that supports the driveshaft substantially coaxially with the central axis of rotation 114.
  • Such housings can also provide oil to the bearings and journals located at the driveshaft 136 through passages in fluid connection with an oiling system.
  • the sidewall 134 can pivotally engage the block 102 using a journaling engagement between the drive-member 104 and the drive-member receiving region 118.
  • the sidewall 134 can define the exterior body containing a female ring gear, (not shown) where the drive member 104 would pivot between the sidewall 134 and the drive-member receiving region 118.
  • the longitudinal axis 1502 of the drive-member 104 will generally orbit the central-axis-of-rotation 114 and the longitudinal-axis-of- symmetry 144 of the crankshaft-drive receiving region 138 will follow a circular orbit about the longitudinal axis 1502.
  • the drive-member 104 also forms a driveshaft 136 and a crankshaft-drive receiving region 138 configured to receive a crankshaft-drive, such as, for example, the crankshaft-drive 140.
  • the driveshaft 136 of the drive-member 104 can form a pinion to engage cogs of another gear, such as in a transmission (not shown), a pulley for belt-drive systems, a sprocket for chain driven machines and another shaft for direct-drive systems.
  • the driveshaft 136 can define splines or a keyway for engaging a driven or driving apparatus.
  • the driveshaft 136 can be spaced from the central-axis-of-rotation 114, such that the driveshaft 136 will orbit the central axis-of-rotation 114.
  • the driveshaft 136 can be a shaft that extends from the drive-member and is configured to pivotally engage another member or the driveshaft 136 can be a recessed bore formed in the body of the drive-member 104 and configured to receive a shaft.
  • the drive-member 104 can form a crankshaft-drive receiving region 138 configured as a bore to pivotally receive a crankshaft, such as the journaling engagements shown by, for example, FIGS. 10, 11, 20-20B, and 22B.
  • the crankshaft-drive receiving region 138 can include an internal gear (not shown) to receive a pinion gear, for example, on the crankshaft or crankshaft-drive.
  • the crankshaft-drive receiving region can form a shaft, such as the exemplary shaft 2714 in FIG. 31 that extends from the drive- member 271 to pivotally engage a corresponding recessed region formed by a crankshaft drive, e.g., the recessed region 2502 formed by the crankshaft 270.
  • FIG. 23C provides such an arrangement and journals the drive-member 271 such that the sidewall 2701 (FIG. 31) pivotally engages the drive-member receiving region 2316 of the block 2302 providing robust support and low friction.
  • Such journaling can be in addition to journaling of the drive shaft in a drive-member housing as described above.
  • the drive shaft can be supported by a corresponding component, such as, for example, a motor-generator or a transmission.
  • FIGS. 23-31 illustrate assemblies that include a weighted drive-member, e.g., a block 2302 housing first and second pistons 2306 and 2308 in respective first and second cylinders 2310 and 2312.
  • the pistons 2306 and 2308 are coupled to a pair of weighted drive -members 271 through female crankshaft-drives 2502.
  • FIG. 31 shows one example of a weighted drive-member 271 including a prismatic sector 2712 that spans approximately 180-degrees about the longitudinal axis of the drive-shaft 2304.
  • the longitudinal axis of the drive-shaft 2304 substantially coincides with the central-axis-of-rotation for the drive -member 271.
  • the balance weight 2712 provides balance to the drive-member 271 and crankshaft 270 assembly during rotation.
  • the exemplary balance weight 2712 is formed as a partial disc or flange partially disposed around the drive shaft 2304.
  • the balance weight 2712 and the body are of unitary construction with the sidewall 2701.
  • other embodiments of balance weights for example the balance weight 3800 in FIGS. 37-37B, define a drive shaft receiving region 3802 for engaging a driveshaft, such as the driveshaft 136 shown in FIGS. 20-20B.
  • FIGS. 35 -35 B illustrate another embodiment of a weighted drive-member 3500.
  • the weighted drive-member 3500 includes a driveshaft 3536 extending from the first side 3530 and an eccentrically located crankshaft-drive receiving region 3538 formed in the second side 3502.
  • the body 3532 also defines one or more recesses 3504 in the second side 3502 of the drive-member 3500.
  • the recesses 3504 are symmetrically disposed about a plane that includes the central-axis-of-rotation of the drive-member 3500.
  • the longitudinal axis of the drive-shaft 3536 substantially coincides with the central- axis-of-rotation for the drive-member 3500.
  • the drive-member 3500 forms a sidewall 3534 that extends between the first side 3530 and the second side 3502.
  • the sidewall 3534 is configured to pivot relative to a drive-member receiving region defined by a block or a housing.
  • the body that defines the sidewall is one example of a prismatic sector that spans 360- degrees about the central-axis-of-rotation of the drive-member 3500.
  • the sidewall 3534 could alternatively be configured to pivotally engage the block or the housing.
  • FIGS. 36-36C illustrate another embodiment of a weighted drive-member 4400.
  • the weighted drive-member 4400 includes a drive shaft 4402 extending from a first side 4412, a crankshaft receiving region 4410 and one or more recessed regions 4408 defined by the body in the second side 4414.
  • a gear 4416 extends from the sidewall 4406 to engage a corresponding gear 4604 on the balance shafts 40 and 41 (see FIGS. 26-26D).
  • the drive-member 4400 also defines a member that extends longitudinally from the sidewall 4406 to form a partial annular body 4404 centered about the longitudinal axis of symmetry of the driveshaft 4402. In the embodiment of FIGS.
  • the annular body 4404 circumferentially extends about 150-degrees and is disposed opposite the recessed regions 4408.
  • the recesses are symmetrically disposed about a plane that includes the longitudinal axis of the driveshaft 4402.
  • the annular body 4404 is similarly symmetrically disposed about the plane that includes the longitudinal axis of the driveshaft 4402.
  • the longitudinal axis of the driveshaft 4402 substantially coincides with the central-axis-of-rotation for the drive-member 4400.
  • Other embodiments of the annular body can circumferentially extend more or less than about 150-degrees.
  • the annular body 4404 When assembled to a block and/or housing, the annular body 4404 partially fills a volume defined by the crankcase and left unoccupied by an eccentrically located and orbiting crankshaft portion, e.g., the volume 204A of FIG. 11.
  • the drive-members employ a spur gear attached to or formed by the drive member sidewall.
  • Spur gears of this sort can drive or be driven by one or more secondary geared shafts for synchronizing the drive-members and/or intermediate shafts.
  • ancillary components such as balance shafts, camshafts, pumps, or other power take-off devices can be similarly driven.
  • crankshaft 116 into the crankcase 204 through the drive-member receiving region 118.
  • the crankshaft bearing regions 121 and 124 engage the respective first and second piston journals 126 and 128 of the crankshaft 116.
  • crankshaft 116 should be positioned such that a crankshaft bearing region 121 or 124 of one piston 106 or 108 engages a respective piston journal 126 or 128.
  • the drive-member 104 can be disposed in the drive-member receiving region 118 while inserting the crankshaft-drive 140 in the crankshaft-drive receiving region 138 of the drive -member 104.
  • the drive-member 104 can be supported according to a selected drive-shaft support configuration, such as described above.
  • the graph of FIG. 24 illustrates a comparison of piston travel for a reciprocating piston machine employing a hypocycloid configuration that provides a 3 inch piston stroke to piston travel of a production Ford 302 engine with a 3 inch piston stroke.
  • the Ford 302 provides an excellent example of favorable slider-crank based piston kinetics.
  • the solid line (MTM piston location) illustrates positions of a piston journal axis (e.g., journal axis 126 in FIG. 10) throughout one complete revolution of the crankshaft.
  • the dashed line (Ford 302 piston location) illustrates the Ford 302 V-8 piston position throughout one complete revolution of its crankshaft.
  • the difference in piston displacements is plotted as the dotted line (improvement delta (I)) in FIG. 24.
  • the pistons and planetary crankshaft of the exemplary embodiment accelerate at lower rates than the conventional slider-crank based Ford 302 engine.
  • the hypocycloid based reciprocating piston machine provides a configuration that functions substantially equivalent to a conventional slider-crank mechanism with a connecting rod of infinite length. Accordingly, hypocycloid based reciprocating piston machines provide a more compact package than conventional connecting rod arrangements.
  • Lower acceleration and deceleration rates of the reciprocating mass in the exemplary embodiment are further complemented by low reciprocating component mass to further reduce stress during operation.
  • a very beneficial mechanism is provided in the narrowed central-section of cylinder region 202 and 207 for supporting, guiding and bearing of the reciprocating slider (e.g. a piston) received therein.
  • a force can be applied to the piston head 143 (such as by an expanding gas).
  • the force is substantially borne through the piston 108 and transmitted to the planetary crankshaft 116 by the journal 128.
  • a substantially tangential force is transmitted through the crankshaft drives 140 and 141 (see e.g., FIGS. 3-4) to the rotatable drive-members 104 and 105 as discussed in some detail in the Applied Geometry Operational Overview and the Applied Kinematics sections.
  • the narrowed arcuate wall 416 functions as a sliding journal received in a narrowed central region of the piston-cylinder.
  • the piston as received in the cylinder acts as a dynamic crankshaft journaling device which reciprocates to provide a beneficially tangent position for the crankshaft to optimally translate reciprocation to rotation, and vice-versa.
  • Such configurations eliminate conventional main bearings.
  • the elongated bearing surfaces provided by the arcuate walls substantially bear eccentric forces acting on the piston rings.
  • spacing the crankshaft bearing region 121 (FIGS. 16- 18F) from the piston ring carrier region 424 reduces eccentric forces that are detrimental to the piston rings.
  • the piston rings can be configured with less tension against the cylinder wall sealing surfaces, thereby further reducing friction.
  • narrowing of the piston and cylinder provides for a compact and lightweight block (e.g., the block 102) that rigidly supports transverse loads applied to the cylinder structure are rigidly supported.
  • the transverse cylinders create a longitudinal "window" 602 that enables installation of the crankshaft while still providing a substantially unitary cylinder block structure.
  • cylinder and piston narrowing provides for a shorter more rigid, robust, less massive crankshaft, further reducing stress and friction.
  • a light, robust piston is also provided optimized, which reduces friction and provides a long and efficient service life.
  • bearings and journaling described herein are but a few examples.
  • Ball bearings, insert bearings, bushings, needle bearings, full floating turbine bearings, are several other examples of bearings that can be usefully employed.
  • Lubrication Embodiments described herein can use conventional lubrication systems.
  • lubrication can be provided by a dry or wet sump, an oil pump and filtration system to provide a clean pressurized oil supply to an oil galley, and oil passages in fluid connection with bearings and journals.
  • Oil galleys can provide oil to the drive-members 104 and 105, the crankshaft 116 and other intermediate shafts.
  • housings can provide oil passages in fluid connection with an oil galley and thus provide pressurized filtered oil to bearings that journal or portions (e.g., the driveshaft) thereof.
  • Drive- members can define an oil passage in fluid connection with the journaling region(s) of the driveshaft to provide oil lubrication to the drive-member crankshaft receiving regions, such as the regions 138 and 139.
  • oil passages in the crankshaft 116 can fluidly connect the crankshaft drives 140 and 141 and the first and second piston journals 126 and 128 for distribution of pressurized oil therebetween.
  • oil provided to a central passage in a driveshaft e.g., the driveshaft 1366 will benefit from increased pressure at the crankshaft receiving region due to the centrifugal forces imparted by rotation of the drive-member. Similar benefit is imparted to oil similarly conveyed to the oil passages in the crankshaft drive. Rotation of the crankshaft also imparts increased pressure to the oil conveyed to the crankshaft piston journals.
  • one or more oil galleys can provide pressurized, filtered oil from a pump and filter (not shown) to oil ports in the piston-cylinders 110 and 112.
  • Piston-cylinders 110 and 112 so provided with pressurized oil can deliver oil to the oil pathways 402, 403, 403 A, 404, 404A, and oil squirts 428 (for piston head cooling). See FIGS. 16-18F, 21A and 21B.
  • Reciprocating motion of the pistons relative to the piston-cylinders 110 and 112 can provide pumping action for oil.
  • oil provided to an oil pathway such as the oil pathway 402 (FIG.
  • Oil squirt features 428 provide pressurized squirts of oil to the underside of the piston head to provide cooling of the piston head.
  • Oil return holes 406 are provided under the groove 412 to return oil from an oil scraper ring.
  • the piston head 142 and piston ring-carrier structure 424 can provide oil pathways (406 are oil scraper ring return holes) in fluid connection to an oil reservoir (not shown) to enhance cooling of the piston head 142, the piston ring-carrier structure 424, and the piston rings during operation.
  • the oil galley can provide oil to intermediate shafts, and balance shaft bearings and journals using conventional means.
  • the oil galley can provide oil to the drive -members 104 and 105, the crankshaft 116 and other intermediate shafts.
  • oil can be provided using any conventional oil delivery method, such as, for example, wet or dry sump pressure oiling.
  • one or more balance shafts 38 can be positioned at one or more locations 43, such as the lower sides of the cylinder block, between the "V" formed by the cylinders, or in the sump area below the oil sump attachment flange.
  • the balance shaft 38 can be used in conjunction with a weighted drive- member, or without.
  • a balance shaft can be configured with mass appropriate for primary balance purposes, or to balance secondary imbalance if needed.
  • a balance shaft drive can be coupled to the driveshaft(s), and or intermediate shaft(s), using a chain and sprockets, a belt and pulleys, or a gear train to synchronize balance shaft 38 rotational speed with crankshaft rotational speed.
  • the balance shaft 38 can rotate at the same rate as the driveshaft or some faster or slower speed relative to the driveshaft, such as, for example, twice the driveshaft rotational speed.
  • balance shafts are driven by a gear train or a chain engaging a pair of corresponding sprockets coupled to a drive -member and/or an intermediate shaft. Such configurations are particularly useful for driving balance shafts at rotational speeds different from the driveshaft rotation speed, for synchronizing the drive members and intermediate shafts, and for providing one or more additional load paths for power transmission and reduced friction.
  • Balance shafts so configured can also be used to drive of ancillary devices, and for power take-off, e.g., reduction drive for propeller drive.
  • FIGS. 26-26D illustrate another example that incorporates balance shafts 40 and 41 that provide secondary balance to the reciprocating piston machine 4600 and synchronization of the drive-members 4400.
  • the assembly 4600 incorporates drive- members 4400 defining gears 4416 that engage corresponding gears 4604 defined by the balance shafts 40 and 41.
  • the gears 4604 are driven at twice the rotational speed of drive-members 4400, although other embodiments provide different gear ratios that will drive the gears 4604 at different speeds relative to the drive-members 4400.
  • the balance shafts 40 and 41 are retained to the block 4602 with caps 4700 and are received in corresponding journals defined by the caps 4700 and the block 4602.
  • the balance shafts 40 and 41 can incorporate eccentrically mounted weights sized and be located to balance secondary vibrations.
  • a single point on the circumference of the inner circle 6703 reciprocates along a corresponding axis.
  • a selected single point on the circumference of the inner circle 6703, such as the point 6702 can represent a longitudinal axis of a crank-pin for a single-cylinder reciprocating piston machine.
  • FIG. 27 illustrates an exploded view of a single-cylinder embodiment of a reciprocating piston machine incorporating MTM architecture.
  • a planetary crankshaft 816 can have pinions 815, 824 in fixed relationship relative to the crankshaft.
  • pinion bores 828, 829 coaxially engage respective crankshaft drives 840, 841.
  • the block 802 receives the planetary crankshaft 816 through the crankcase aperture 818.
  • the block 802 defines a single piston cylinder 810 and slidably receives a corresponding single piston 806.
  • the piston head 842 slidably mates with the walls of the cylinder 810.
  • the elongate body 844 is narrowed relative to the piston head 842 and, in this example, is not in sliding contact with the walls of the piston cylinder.
  • the narrowed region of the piston 806 is spaced from the walls of the piston cylinder for reducing friction between the walls of the cylinder and the piston.
  • a piston bearing recess 821 can receive the piston crankpin 846 and a piston bearing cap 820 can be affixed to the proximal end of the elongate body 844, capturing the piston crankpin 846 between the recesses 821, 822 in a bearing relationship.
  • crankcase bore 819 receives ring gears 808, 809 on corresponding crankcase-bearing regions 823, 847.
  • the respective internal ring-gear cogs 814, 815 matingly engage respective crankshaft-drive-pinion cogs 826, 827.
  • the drive-member 805 has a crankshaft-drive receiving region 839 that pivotab Iy receives the crankshaft-drive 841, and the crankshaft-drive receiving region (not visible as illustrated) of the drive-member 804 pivotab Iy receives the crankshaft-drive 841 located at an opposing end of the crankshaft from the crankshaft-drive 841.
  • Driveshafts 836 and 837 can be journaled in a bearing relationship with housings (not shown) being positioned coaxially relative to the crankcase and the central-axis-of-rotation.
  • piston to piston- cylinder swept surface area can be reduced by having a narrowed body.
  • the illustrated ring-gear / pinion configuration reduces piston-to- cylinder eccentric forces, reducing overall piston-slider mechanism friction and improving overall efficiency.
  • FIG. 28 shows an exploded view of another single cylinder embodiment incorporating MTM architecture.
  • the illustrated reciprocating piston machine incorporates the piston 870 shown in FIG. 30.
  • the piston 870 is received by the piston-cylinder bore 860 defined by the block 852.
  • the crankshaft drive 876 of the crankshaft 866 fixedly receives a pinion 865 in coaxial relationship with the pinion- gear bore 879.
  • the crankshaft 866 is received through the crankcase aperture 868 and the piston crankpin 887 is pivotably received in the piston crankpin bearing bore 872.
  • the internal ring gear 858 can be fixedly received in the corresponding crankcase bore 869 and positioned coaxially therewith relative to the internal ring gear outer diameter 873.
  • crankshaft drive pinion cogs 877 can matingly engage internal ring gear cogs 864.
  • a drive-member 853 can be received by the crankcase aperture 868 and can receive the crankshaft-drive 876 in the corresponding crankshaft drive-member receiving region 854.
  • the illustrated drive member 853 can provide dynamic balance by incorporating a balance weight 856.
  • the driveshaft 855 can be supported by a housing having, for example, roller bearings (not shown) coaxially aligned relative to the crankcase 868 and the central axis of rotation 851.
  • the driveshaft 855 can, in some embodiments, comprise an electrical armature (also not shown). Such an electrical armature can be used to drive the drive-member 853 through rotation, which in turn can drive the piston 870 through reciprocation (as for use as a positive displacement pump, such as a compressor used in vapor-cycle refrigeration).
  • FIG. 29 illustrates an exploded and cut away view of one exemplary four-cylinder embodiment 900 incorporating MTM architecture.
  • FIG. 29A shows detail within the circled region 29A of FIG. 29.
  • the crankshaft 916 is received in the crankcase 913.
  • Elongate pistons 906, 908, 910 and 912 are received in respective piston-cylinders (e.g., cylinders 907, 909).
  • Piston cylinders 907 and 909 are shown as being cut-away at each respective central bore axis (not shown).
  • the pistons 910 and 912 are shown as being exposed and free from piston- cylinders for clarity of illustration.
  • the illustrated internal ring gear 962 comprises a cylindrically shaped external bearing surface being coaxially received in a crankcase bore (not shown), and internal gear cogs 968 in mating engagement with the illustrated crankshaft- drive pinion cogs 906.
  • the pinion 906 is fixedly attached and coaxially aligned relative to the crankshaft drive 940.
  • the drive- member 904 pivotably receives crankshaft drive 940 in the crankshaft-drive receiving region 905.
  • a balance weight 934 is offset relative to the drive -member receiving region 904, being located opposite the drive-member receiving region relative to a central axis of the driveshaft 936.
  • the piston-cylinder bearing region 994 of each inner piston e.g., the piston
  • each respective piston-cylinder e.g., the cylinder 909
  • the corresponding narrowed region 995 of the piston 908 can be, as shown, spaced from the cylinder wall 996, providing a piston-cylinder clearance.
  • the narrowed region 944 of an adjacent (e.g., outer) piston 906 can also be spaced from the wall of the cylinder bore 907, as shown.
  • Each outer piston-cylinder e.g., cylinder 907 opens to and ends at the crankcase 913.
  • each of the inner piston cylinders e.g., cylinder 909) extends across (or transects) the crankcase 913.
  • the sliding bearing engagement between the bearing region 994 and the corresponding cylinder walls can support lateral forces arising in various portions of the orbit of the crankshaft 916 about the central-axis-of-rotation.
  • the inner pistons 908, 910 can be configured relative to each respective cylinder in a manner similar to that illustrated in, for example, FIG. 22B.
  • Each of the illustrated outer pistons 906, 912 are shown in FIG. 29 as having a narrowed region 911, 944 extending from the respective proximal end near the crankshaft engaging region to a region adjacent the respective piston head (e.g., the head 942) adjacent the distal end of the piston.
  • the narrowed regions 911, 944 are spaced from the cylinder walls. Lateral forces for these pistons can be supported by the ring-gear and pinion.
  • FIG. 32 Another embodiment that provides four cylinders is illustrated in FIG. 32.
  • the four-cylinder machine 2800 provides two pairs of pistons, each pair composed of two pistons oriented at 90-degrees relative to each other, with each pair having a similar orientation.
  • the illustrated embodiment thus provides two horizontal pistons 2804 and 2808 and two vertical pistons 2802 and 2806. Although the two pairs of pistons are aligned with each other, some embodiments will provide pairs of pistons at various angles relative to each other, and some will provide pairs of pistons that oppose each other.
  • the configuration shown in FIG. 32 provides an out of phase configuration for the pistons 2802, 2804, 2806 and 2808.
  • the horizontal pistons 2804 and 2808 are out of phase by about 180-degrees.
  • the vertical pistons 2802 and 2806 are also out of phase by about 180-degrees relative to each other.
  • arrangements that provide out of phase piston configurations offer improved balance, which in turn provides an increase in rotational speed that can be safely achieved.
  • sequential ignition can be used with out-of-phase pistons, which provides smoother and more continuous power than with pairs of pistons that are in phase.
  • the pistons can be configured to operate out of phase using a crankshaft with an intermediate shaft that provides piston journals disposed at various circumferential locations relative to the crankshaft longitudinal axis.
  • the crankshaft of FIG. 32 incorporates an intermediate shaft 2900 disposed between adjacent crankshaft portions 2801 and 2803 to provide out of phase piston reciprocation for pistons 2804 and 2808, and for pistons 2802 and 2806.
  • the embodiment of FIG. 32 includes drive-members 2810 and 2812 for communicating rotational motion to or from the crankshaft.
  • the pistons 2802, 2804, 2806 and 2808 are configured to operate out of phase in the embodiment of FIG. 32, some four cylinder embodiments will provide pairs of pistons that operate in phase.
  • FIGS. 34-34B provides an exemplary eight cylinder configuration 3300, which provides four pairs of pistons, each pair composed of two pistons oriented at 90-degrees relative to each other. Each pair of pistons has nearly the same orientation.
  • the embodiment of FIG. 34 provides four horizontal pistons 3306, 3308, 3310 and 3312 and four vertical pistons 3314, 3316, 3318 and 3320.
  • the four pairs of pistons are substantially aligned with each other, some embodiments will provide pairs of pistons at various angles relative to each other, and some will provide pairs of pistons that oppose each other.
  • the eight cylinder configuration 3300 provides in-phase motion among the horizontal pistons and in- phase motion among the vertical pistons, although the horizontal pistons are out of phase from the vertical pistons.
  • the four horizontal pistons 3306, 3308, 3310 and 3312 will be near top dead center simultaneously and near bottom dead center simultaneously.
  • the four vertical pistons 3314, 3316, 3318 and 3320 will be near top dead center simultaneously and near bottom dead center simultaneously.
  • FIGS. 34- 34B provides in-phase motion among the horizontal pistons and among the vertical pistons
  • some eight cylinder configurations will provide out of phase motion among horizontal pistons and among vertical pistons.
  • Configurations similar to those described above can convert motion from reciprocation to rotation, and vice-versa.
  • Such configurations include pistons capable of performing mechanical work on a fluid, e.g., by compressing the fluid.
  • a fluid e.g., products of combustion, can perform mechanical work on the pistons.
  • the substantially square to oversquare bore diameter to stroke length ratios provide lower accelerations for the movable components, resulting in lower forces and corresponding stresses.
  • embodiments that adopt the above described features can operate at higher cylinder pressures, and at a higher rotational speeds, e.g., RPM, yielding power and efficiency improvements compared to conventional reciprocating piston devices.
  • the improvement in piston "dwell" in the exemplary embodiment provides substantially more time for an expanding gas to act upon a piston head to perform work.
  • crankshafts having a pinion having a pinion
  • substantially undersquare bore-to-stroke ratios i.e., embodiments with a piston stroke in excess of a corresponding bore diameter
  • These embodiments can have larger diameter pinions for facilitating improved piston reciprocation.
  • Embodiments according to the present disclosure can be comparatively simple to assemble and well suited to machining, such as CNC-machining. Embodiments similar to those described also provide improved piston locations as compared to conventional reciprocating piston machines that rely on a slider-crank configuration. See, e.g., FIG. 24.
  • Embodiments of hypocycloid motion translation mechanisms as described above innovatively addresses the need for a robust, compact, lightweight, highly efficient mechanism which may be practically produced, and cost effectively implemented, and which will provide high efficiency in operation, and long reliable service life with little loss of efficiency.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention porte sur des machines qui convertissent un mouvement de rotation en un mouvement alternatif, et inversement, et plus particulièrement, mais non exclusivement, sur des machines de piston à alternatif. Certains modes de réalisation comprennent un vilebrequin définissant un entraînement par vilebrequin et au moins un tourillon de piston s'étendant radialement et espacé de l'entraînement par vilebrequin, et un piston configuré pour engager de façon pivotante le tourillon de piston. Le piston définit une tête cylindrique et un corps allongé. Certains modes de réalisation comprennent en outre un élément d'entraînement définissant un axe de rotation central et qui est apte à se mettre en prise de façon rotative avec l'entraînement par vilebrequin. Certains modes de réalisation comprennent également un bloc définissant un ou plusieurs cylindres destinés à recevoir un ou plusieurs pistons. L'élément d'entraînement tourne lorsque le piston est animé d'un mouvement alternatif, et inversement.
PCT/US2009/038133 2007-01-05 2009-03-24 Mécanisme de transformation de mouvements WO2009120715A1 (fr)

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US12/497,497 US8375919B2 (en) 2007-01-05 2009-07-02 Motion translation mechanism

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US7062108P 2008-03-24 2008-03-24
US61/070,621 2008-03-24

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CN102091723A (zh) * 2010-12-10 2011-06-15 苏州建莱机械工程技术有限公司 行星-连杆驱动装置
EP2789852A3 (fr) * 2013-04-08 2014-10-22 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Compresseur
EP3179116A4 (fr) * 2014-08-07 2018-01-24 Nippon Steel & Sumitomo Metal Corporation Vilebrequin pour moteur à piston alternatif
US9958041B2 (en) 2013-06-03 2018-05-01 Enfield Engine Company, Llc Power delivery devices for reciprocating engines and related systems and methods
US10851877B2 (en) 2013-06-03 2020-12-01 Enfield Engine Company, Llc Power delivery devices for reciprocating engines, pumps, and compressors, and related systems and methods
US11703048B2 (en) 2020-03-04 2023-07-18 Enfield Engine Company, Inc. Systems and methods for a tangent drive high pressure pump

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US3886805A (en) * 1974-04-09 1975-06-03 Ivan Koderman Crank gear for the conversion of a translational motion into rotation
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IT1235199B (it) * 1989-05-18 1992-06-23 Bosso Sergio Manovellismo ipocicloidale in motori alternativi
US7124718B2 (en) * 2003-01-23 2006-10-24 Jorge Artola Multi-chamber internal combustion engine
US20070215093A1 (en) * 2006-03-16 2007-09-20 Achates Power, Llc Opposed piston internal-combustion engine with hypocycloidal drive and generator apparatus

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US2166975A (en) * 1936-10-10 1939-07-25 Sologaistoa Manuel Humbe Perez Mechanical movement
US3886805A (en) * 1974-04-09 1975-06-03 Ivan Koderman Crank gear for the conversion of a translational motion into rotation
US4270395A (en) * 1977-06-30 1981-06-02 Grundy Reed H Motion translating mechanism
IT1235199B (it) * 1989-05-18 1992-06-23 Bosso Sergio Manovellismo ipocicloidale in motori alternativi
US5067456A (en) * 1990-11-16 1991-11-26 Beachley Norman H Hypocycloid engine
US7124718B2 (en) * 2003-01-23 2006-10-24 Jorge Artola Multi-chamber internal combustion engine
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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102091723A (zh) * 2010-12-10 2011-06-15 苏州建莱机械工程技术有限公司 行星-连杆驱动装置
EP2789852A3 (fr) * 2013-04-08 2014-10-22 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Compresseur
US9958041B2 (en) 2013-06-03 2018-05-01 Enfield Engine Company, Llc Power delivery devices for reciprocating engines and related systems and methods
US10436296B2 (en) 2013-06-03 2019-10-08 Enfield Engine Company, Llc Power delivery devices for reciprocating engines and related systems and methods
US10801590B2 (en) 2013-06-03 2020-10-13 Enfield Engine Company, Llc Power delivery devices for reciprocating engines and related systems and methods
US10851877B2 (en) 2013-06-03 2020-12-01 Enfield Engine Company, Llc Power delivery devices for reciprocating engines, pumps, and compressors, and related systems and methods
EP3179116A4 (fr) * 2014-08-07 2018-01-24 Nippon Steel & Sumitomo Metal Corporation Vilebrequin pour moteur à piston alternatif
US10330142B2 (en) 2014-08-07 2019-06-25 Nippon Steel & Sumitomo Metal Corporation Crankshaft for reciprocating engine
US11703048B2 (en) 2020-03-04 2023-07-18 Enfield Engine Company, Inc. Systems and methods for a tangent drive high pressure pump

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