WO2018030985A1 - Dispositifs de distribution d'énergie destinés à des moteurs à mouvement alternatif et systèmes et procédés associés - Google Patents

Dispositifs de distribution d'énergie destinés à des moteurs à mouvement alternatif et systèmes et procédés associés Download PDF

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Publication number
WO2018030985A1
WO2018030985A1 PCT/US2016/046033 US2016046033W WO2018030985A1 WO 2018030985 A1 WO2018030985 A1 WO 2018030985A1 US 2016046033 W US2016046033 W US 2016046033W WO 2018030985 A1 WO2018030985 A1 WO 2018030985A1
Authority
WO
WIPO (PCT)
Prior art keywords
component
engine
reciprocating
axis
axis component
Prior art date
Application number
PCT/US2016/046033
Other languages
English (en)
Inventor
Nicholas A. SABDERS
Ryan Thomas Kiley SANDERS
Original Assignee
Enfield Engine Company, Llc
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 Enfield Engine Company, Llc filed Critical Enfield Engine Company, Llc
Priority to PCT/US2016/046033 priority Critical patent/WO2018030985A1/fr
Priority to JP2019507846A priority patent/JP2019530821A/ja
Priority to CN201680089901.XA priority patent/CN109964015A/zh
Priority to EP16912814.7A priority patent/EP3497313A4/fr
Priority to BR112019002562-6A priority patent/BR112019002562A2/pt
Publication of WO2018030985A1 publication Critical patent/WO2018030985A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/047—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft with rack and pinion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/042—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the connections comprising gear transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups

Definitions

  • the output shaft assembly can include a torque transfer gear which transfers torque from the output shaft assembly to the drive gear of the engine drive shaft assembly.
  • the torque transfer gear comprises a sprocket and chain assembly.
  • the base can include a portion of the engine block.
  • the y-axis component can include a linear bearing surface along which the y-axis component slides relative to the base with the reciprocating motion input.
  • the linear bearing surface can limit the y-axis component from moving relative to the base except for in the direction of the reciprocating motion input.
  • the x-axis component can include a linear bearing surface along which the x-axis component slides substantially perpendicularly to the direction of the reciprocating motion input.
  • a pitch diameter of the output pinion gear can be substantially equal to a stroke length of the reciprocating engine and a pitch diameter of the internal ring gear can be substantially equal to two times the stroke length of the reciprocating engine and the sum of respective pitch diameters of the orbital engagement component and the stationary engagement component can be substantially equal to a stroke length of the reciprocating engine.
  • the output shaft assembly can include a torque transfer gear which transfers torque from the output shaft assembly to the drive shaft.
  • the torque transfer gear can include a sprocket and chain assembly.
  • the base can be a portion of an engine block.
  • the base can be a component attached to the engine block.
  • the y-axis component can include a linear bearing surface along which the y-axis component slides relative to the base with the reciprocating motion.
  • the applying the torque moment to the output shaft of the reciprocating engine using the maximum length torque moment arm that remains a substantially constant length can include coupling a translating member to the reciprocating element of the reciprocating engine; and coupling the translating member to the output shaft using the maximum length torque moment arm.
  • the torque moment arm can be substantially perpendicular to a reciprocating axis of the translating member to apply torque to the rotatable power output member.
  • the torque moment arm that remains a substantially constant length can include a rotatable gear device coupled to the power output member and a gear rack coupled to the translating member.
  • a reciprocating engine can include at least one substantially invariant length torque moment arm that remains substantially constant during reciprocation of a reciprocating element and a rotation of an output shaft of the engine.
  • a reciprocating engine can include at least one piston and cylinder, said piston being connected on one end to a crankshaft via a connecting rod, said piston additionally being connected to an output shaft via a substantially invariant length torque moment arm.
  • the moment arm can include a pull rod/gear rack/pinion gear/clutch arrangement.
  • the gear rack can be disposed on the pull rod, the pinion gear is coupled to the output shaft via the clutch, and the gear rack is engageable to the pinion gear to rotate the output shaft.
  • the clutch can include a freewheeling clutch.
  • the clutch can include a sprag clutch.
  • an energy storage device can be positioned between a pull rod and an output shaft, the pull rod configured to couple to a reciprocating member of a
  • an automobile can include a reciprocating engine comprising at least one piston and cylinder, said piston being connected on one end to a crankshaft via a connecting rod, said piston additionally being connected to an output shaft via a substantially invariant length torque moment arm.
  • the automobile can include one or more of light trucks, delivery trucks, fire trucks, over-the-road trucks, motorcycles, and passenger cars.
  • a generator set (e.g., an electric generator set) can include a reciprocating engine having at least one piston and cylinder, said piston being connected on one end to a crankshaft via a connecting rod, said piston additionally being connected to an output shaft via a substantially invariant length torque moment arm.
  • methods of increasing an output power (e.g., an average output power) of an operating reciprocating engine include maintaining a substantially constant length torque moment arm that drives an output shaft of the reciprocating engine.
  • Figure 26A-26I are sequential side view schematics of an example drive mechanism oscillating throughout a power stroke of a reciprocating piston.
  • Figure 31 is a perspective view of an example internal combustion engine using example drive mechanisms in place of a conventional crankshaft mechanism.
  • Figure 32 is another perspective view of the example engine of Figure 31 with the engine block removed for clarity, illustrating connections between the drive mechanism and a drive shaft.
  • Figure 35 is a diagram of example force vectors and torque calculation of a conventional crankshaft connecting rod reciprocating mechanism.
  • a power delivery device can include an output shaft coupled to a reciprocating engine (i.e., reciprocating pistons of the engine) by a clutch device (e.g., a one way clutch) that permits the output shaft to rotate freely in one direction. That is, the clutch device can engage the output shaft only when the piston is in a downward motion.
  • a clutch device e.g., a one way clutch
  • this configuration helps permit the output shaft to rotate at different speeds than the crankshaft of the reciprocating engine to which the power delivery device is coupled.
  • the power delivery device (e.g., the rotatable member of the power delivery device) can additionally or alternatively include a belt system, a pulley system, and/or a chain drive system.
  • a tension device e.g., a belt, cable 206a, chain 206b, or other device able to apply a tensile force
  • a spring return mechanism 212 can also be included to help return the tension device (e.g., cable 206a, belt or chain 206b) upward as the piston 104 moves to the top of the stroke.
  • the example reciprocating engine illustrated in the schematic of Figure 15 can be carried out in any of various suitable configurations and designs.
  • an engine e.g., an IC engine
  • Such specially designed engines can include reduced crankshafts and connecting rods in order to limit power loss that could result from the rotating mass.
  • tension devices connected to the pistons can be coupled to a common output shaft using any of various gearing or pulley configurations to cause consistent rotation of the output shaft.
  • the pull rods 406 include a toothed gear rack 407 that is coupled to an upper region of the pull rod.
  • the gear rack 407 can be coupled to the pull rod 406 so that the gear rack 407 can move slightly along, and
  • the gear rack can be attached to the pull rod using one or more spring elements (e.g., Belleville style springs) 409, which can help perform several functions.
  • the springs can act as an energy storage device 409 for the power delivery device.
  • the pressure within the cylinder and therefore also the force acting on the piston typically has a distinct spike very early during the power stroke and then quickly decays as the piston travels into the cylinder.
  • this can act to slightly smooth the pressure curve and distribute some of the forces throughout the piston power stroke. Additionally or alternatively, the springs can also help limit shock that could be generated as the reciprocating piston translates back and forth.
  • the output shaft is coupled to the engine (e.g., the cylinder head) using mounting devices (e.g., bearing carriers 416) that position the output shaft but permit it to rotate under torque generated by the power delivery device.
  • mounting devices e.g., bearing carriers 416 that position the output shaft but permit it to rotate under torque generated by the power delivery device.
  • a drive mechanism 1000 can include a base 1010, an oscillating assembly 1100 coupled to the base 1010 and configured to interface with a reciprocating element (e.g., a piston), and a rotating output shaft assembly 1300 that engages with the oscillating assembly 1100 to provide a rotational power output, for example, to a drive shaft.
  • a reciprocating element e.g., a piston
  • a rotating output shaft assembly 1300 that engages with the oscillating assembly 1100 to provide a rotational power output, for example, to a drive shaft.
  • the sliding surfaces 1104 can be configured to mate and interface with sliding surfaces 1020 of the base (e.g., of the first base plate 1012). Additionally, the sliding surfaces 1104 and 1020 can individually or together limit the frame 1102 from sliding or otherwise moving along a z-axis direction.
  • the sliding surfaces can be designed and implemented in any of various forms.
  • the sliding surfaces can define smooth and/or surfaces.
  • the sliding surfaces can also define features that help to limit relative motion between components other than in the desired directions. That is, in some cases, the sliding surfaces may permit relative motion in the x and y directions, but limit relative motion along a z-axis (e.g., the z direction) to help keep the drive mechanism assembled and together during use.
  • complementary sliding surfaces can include a protrusion (e.g., flange) on one component and a recess (e.g., a groove) configured to receive the flange along the other component.
  • the drive mechanism 1000 converts purely axial movement (e.g., along the y- direction, in-line with the piston motion) into a movement having an x-direction component and a y-direction component to propel the output shaft with a continuous tangential force. That is, as the x-axis component 1130 travels around the output shaft, the force driving the output shaft can be consistently applied tangentially, regardless of the position of the piston between top dead center and bottom dead center.
  • the idler assembly can be configured and positioned such that an interfacing contact point between the positioning element 1202 and the complementary feature 1204 is opposite an interfacing contact point between the engaging device 1132 and the pinion gear 1304 with respect to a rotational axis of the output shaft 1302.
  • the sizes of the respective positioning element 1202 and complementary feature 1204 can vary. In the case of rollers or gears, the combined diameters (e.g., pitch diameters) of the positioning element 1202 and complementary feature 1204 are typically equal to the diameter of the pinion gear 1304. This sizing can help provide consistent contact force to keep the pinion gear 1304 in contact with the engaging device 1132.
  • FIGS 26A-26I are simplified to schematic views (i.e., the physical idler assembly components are ornmited for clarity), a force caused by the interface between the positioning element 1202 and the complementary feature 1204 is represented in Figures 26A-26I by idler force F . Additionally, the engaging device 1132 orbits with the x-axis component 1130. The circular path of the x-axis component 1130 around the pinion gear 1304 helps to apply a force to the pinion gear 1304 that maintains a consistent moment arm throughout the reciprocation of the piston.
  • the drive mechanism 1000 instantaneous torque is consistently greater than that of the crankshaft mechanism and the overall average torque for the drive mechanism 1000 is about 33% higher than that of the conventional crankshaft connecting rod mechanism.
  • apparent in Figure 37 is the negative impact of the x-axis movement (e.g., away from and towards the central longitudinal axis of the piston) of the connecting rod of the crankshaft mechanism, where it has a negative impact on torque after 90 degrees. This effect of varying x-axis position is not present in the drive mechanism 1000.
  • Drive mechanisms such as those described above as drive mechanism 1000, can additionally or alternatively be implemented to replace conventional crankshaft and connecting rod systems to delivery internal combustion engine power to a rotating drive shaft.
  • the drive mechanism 1000 can be disposed within an engine block 50 between a piston and a drive shaft 1402.
  • a frame 2102 can be coupled directly to a piston 304 within the block 50 of an engine opposite the combustion chamber 75 in place of a conventional connecting rod.
  • the frame 2102 can be designed and structured similar to a connecting rod having a beam- like neck portion 2104 that connects to the piston, for example, using a wrist pin or similar connection.
  • the power delivery devices have generally been described as having a consistent (e.g., constant or invariant) length torque moment arm which has a consistent (e.g., constant or invariant) length that is at its maximum, non-changing length throughout the power stroke, some variation in moment arm length is possible.
  • the power delivery device e.g., the rotating member or the interfacing portion of the pull rod
  • the moment arm length varies slightly as the tension device translates and interfaces with the rotatable member.
  • the moment arm can vary slightly as the gear rack interfaces with a rotating pinion gear or as a chain interfaces with a rotating sprocket.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transmission Devices (AREA)
  • Hydraulic Motors (AREA)
  • Gear Transmission (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Selon certains aspects de l'invention, certains moteurs à mouvement alternatif peuvent comprendre un mécanisme d'entraînement destiné à produire une sortie de mouvement de rotation à partir d'un ensemble à pistons à mouvement alternatif, le mécanisme d'entraînement comprenant un composant d'axe y à translation axiale pour effectuer un mouvement alternatif le long d'un axe y avec l'ensemble à pistons ; un composant d'axe x : i) conçu pour effectuer un mouvement alternatif sensiblement perpendiculairement à l'axe y, ii) doté d'un engrenage annulaire interne, et iii) doté d'un composant d'engagement orbital sensiblement concentrique avec l'engrenage annulaire interne ; un ensemble arbre de sortie doté d'un engrenage à pignon de sortie venant en prise tangentiellement avec l'engrenage annulaire interne ; et un élément d'engagement fixe sensiblement concentrique à l'ensemble arbre de sortie, le composant d'engagement fixe étant en interface avec le composant d'engagement orbital, l'interface entre le composant d'engagement fixe et le composant d'engagement orbital appliquant une force sur le composant d'axe x pour maintenir le contact entre la couronne dentée interne et l'engrenage à pignon de sortie.
PCT/US2016/046033 2016-08-08 2016-08-08 Dispositifs de distribution d'énergie destinés à des moteurs à mouvement alternatif et systèmes et procédés associés WO2018030985A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
PCT/US2016/046033 WO2018030985A1 (fr) 2016-08-08 2016-08-08 Dispositifs de distribution d'énergie destinés à des moteurs à mouvement alternatif et systèmes et procédés associés
JP2019507846A JP2019530821A (ja) 2016-08-08 2016-08-08 レシプロエンジンのための動力伝達装置、関連システム、および方法
CN201680089901.XA CN109964015A (zh) 2016-08-08 2016-08-08 往复式发动机的功率输送装置及相关系统和方法
EP16912814.7A EP3497313A4 (fr) 2016-08-08 2016-08-08 Dispositifs de distribution d'énergie destinés à des moteurs à mouvement alternatif et systèmes et procédés associés
BR112019002562-6A BR112019002562A2 (pt) 2016-08-08 2016-08-08 dispositivos de entrega de energia para motores de movimento alternado e sistemas e métodos associados

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2016/046033 WO2018030985A1 (fr) 2016-08-08 2016-08-08 Dispositifs de distribution d'énergie destinés à des moteurs à mouvement alternatif et systèmes et procédés associés

Publications (1)

Publication Number Publication Date
WO2018030985A1 true WO2018030985A1 (fr) 2018-02-15

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2016/046033 WO2018030985A1 (fr) 2016-08-08 2016-08-08 Dispositifs de distribution d'énergie destinés à des moteurs à mouvement alternatif et systèmes et procédés associés

Country Status (5)

Country Link
EP (1) EP3497313A4 (fr)
JP (1) JP2019530821A (fr)
CN (1) CN109964015A (fr)
BR (1) BR112019002562A2 (fr)
WO (1) WO2018030985A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9897179B2 (en) * 2016-07-07 2018-02-20 Karen Sue Svejkovsky Bearing for supporting a linearly reciprocating structure
CN110454353B (zh) * 2019-09-16 2024-04-09 西南石油大学 复合驱动往复泵

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3886805A (en) * 1974-04-09 1975-06-03 Ivan Koderman Crank gear for the conversion of a translational motion into rotation
US5178038A (en) * 1992-01-28 1993-01-12 Heniges William B Crankshaft balancing mechanism for a variable compression engine
US20020185101A1 (en) * 2001-06-08 2002-12-12 Ralph Shaw Cardioid cycle internal combustion engine
WO2004072441A1 (fr) * 2003-02-04 2004-08-26 Norman Leslie Matthews Moteur a bloc-cylindres rotatif et pistons alternatifs
US20090272259A1 (en) * 2007-01-05 2009-11-05 Efficient-V, Inc. Motion translation mechanism

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2725182A (en) * 1951-02-01 1955-11-29 David L Spriggs Air compressor
JPS5715388Y2 (fr) * 1978-06-30 1982-03-31
JPS59231255A (ja) * 1983-06-14 1984-12-25 Shizuo Yoshida ピストン摺動子式クランク軸回転機構
JP2683218B2 (ja) * 1994-05-10 1997-11-26 ロングウェルジャパン株式会社 クランク装置
WO2012144073A1 (fr) * 2011-04-22 2012-10-26 有限会社タックリサーチ Mécanisme de manivelle à séparation xy, et dispositif d'entraînement équipé de celui-ci
WO2014197487A1 (fr) * 2013-06-03 2014-12-11 Sanders Nicholas A Dispositifs de distribution d'énergie pour moteurs à piston et systèmes et procédés associés
JP6384115B2 (ja) * 2014-05-08 2018-09-05 いすゞ自動車株式会社 エンジン

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3886805A (en) * 1974-04-09 1975-06-03 Ivan Koderman Crank gear for the conversion of a translational motion into rotation
US5178038A (en) * 1992-01-28 1993-01-12 Heniges William B Crankshaft balancing mechanism for a variable compression engine
US20020185101A1 (en) * 2001-06-08 2002-12-12 Ralph Shaw Cardioid cycle internal combustion engine
WO2004072441A1 (fr) * 2003-02-04 2004-08-26 Norman Leslie Matthews Moteur a bloc-cylindres rotatif et pistons alternatifs
US20090272259A1 (en) * 2007-01-05 2009-11-05 Efficient-V, Inc. Motion translation mechanism

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3497313A4 *

Also Published As

Publication number Publication date
JP2019530821A (ja) 2019-10-24
EP3497313A1 (fr) 2019-06-19
EP3497313A4 (fr) 2020-06-24
BR112019002562A2 (pt) 2019-05-21
CN109964015A (zh) 2019-07-02

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