JP2019530821A - Power transmission device, related system and method for reciprocating engine - Google Patents

Abstract

In some aspects, the reciprocating engine is a drive mechanism for generating rotational motion output from the reciprocating piston assembly, the axially moving y-axis component for reciprocating along the y-axis with the piston assembly A drive mechanism and an x-axis component, i) configured to reciprocate substantially perpendicular to the y-axis, ii) having an inner ring gear, and iii) an inner ring gear An output ring assembly having a substantially concentric orbital engagement component, an output ring assembly, an output pinion gear tangentially engaged with the inner ring gear, and an output shaft assembly substantially A concentric fixed engagement component connected to the track engagement component, wherein contact between the fixed engagement component and the track engagement component is: The axial component of force to maintain contact between the inner ring gear and the output pinion gear, and a stationary engaging component. [Selection] Figure 24

Description

RELATED APPLICATIONS This application is a continuation-in-part of US patent application Ser. No. 14 / 294,977 entitled “Power Transmission Device, Related System, and Method for Reciprocating Engines” filed on June 3, 2014, Claims the benefit of the US provisional patent application serial number 61 / 830,456 entitled "Power transmission device, related system and method for reciprocating engines" filed June 3, 2013, both of which The entire contents of the application are incorporated herein by reference.

  The present disclosure relates generally to reciprocating engines, and more particularly to power transmission devices for reciprocating engines, and related systems and methods.

  Reciprocating engines typically use a crankshaft to convert the linear reciprocation of one or more pistons moving within a cylinder into the rotational motion of the crankshaft and vice versa. For example, an internal combustion engine (IC engine) is the most common type of reciprocating engine. Reciprocating engines are generally easier to move (e.g., propel objects) chemical or thermal energy (e.g., energy derived from water vapor) released during combustion of various fuels (such as gasoline). Used to convert kinetic energy (eg mechanical rotational motion) that can be used. Reciprocating engine crankshafts are typically used to drive various devices or vehicles, such as automobiles, generators, trucks, airplanes, welders, ships, bulldozers, motorcycles, boats, etc. Is an engine element connected to

  In some aspects, the reciprocating engine includes an engine block that defines at least one cylinder, at least one piston assembly that reciprocates within the at least one cylinder, and a rotational motion output from a reciprocating motion input of the piston assembly. A drive mechanism for generating a y-axis component that moves in an axial direction, wherein the reciprocating motion input of the piston assembly relative to a base on which the y-axis component is slidably mounted, A y-axis component configured to reciprocate along the y-axis, and an x-axis component slidably coupled and moved along the y-axis to the y-axis component, i) configured to reciprocate substantially perpendicular to the y-axis with respect to the y-axis component; ii) includes an inner ring gear; ii ) An x-axis component including a track engagement component disposed substantially concentric with the inner ring gear, and an output pinion gear rotatably connected to the base and connected and engaged tangentially with the inner ring gear An output shaft assembly having a fixed engagement component coupled to or integrally formed with the base and substantially concentric with the output shaft assembly, wherein the x-axis Connecting and tangentially engaging the track engaging component of the component, and the connection of the fixed engaging component and the track engaging component of the x-axis component drives the engine drive shaft assembly The connection between the inner ring gear and the output pinion gear is such that the inner ring gear circulates and drives the output pinion gear to drive the shaft. To maintain, applying a force to the x-axis component, and a fixed engagement element.

Embodiments may include one or more of the following features.
The reciprocating engine may include an opposed piston multi-cylinder engine, and the axially moving y-axis component may be coupled to two opposing pistons. The fixed engagement component may comprise a rotatable element. The fixed engagement component may include a recess to which the track engagement component is connected. The track engaging component may comprise a gear or a roller. The pitch diameter of the output pinion gear is substantially equal to the stroke length of the reciprocating engine, and the pitch diameter of the inner ring gear is substantially equal to twice the stroke length of the reciprocating engine; And the sum of the pitch diameters of each of the fixed engagement components may be substantially equal to the stroke length of the reciprocating engine. The output shaft assembly may include a torque transmission gear that transmits torque from the output shaft assembly to the drive gear of the engine drive shaft assembly. The torque transmission gear may include a sprocket and chain assembly. The base may constitute a part of the engine block. The y-axis component may comprise a linear bearing surface along which the y-axis component slides relative to the base with the reciprocating input. The linear bearing surface may restrict the y component from moving relative to the base except in the direction of the reciprocating input. A linear bearing surface may be provided that slides along the x-axis component substantially perpendicular to the direction of the reciprocating input.

  In some aspects, a drive mechanism for generating a rotational motion output from a reciprocating input of a piston assembly of a reciprocating engine is on a y-axis of the reciprocating input of the piston assembly relative to a base to which a y-axis component is attached. An axially moving y-axis component configured to reciprocate along, and an x-axis component slidably coupled and moved along the y-axis direction to the y-axis component, i) y A track engagement component configured to reciprocate substantially perpendicular to the y-axis relative to the shaft component, ii) includes an inner ring gear, and iii) is disposed substantially concentrically with the inner ring gear An output shaft assembly having an x-axis component and an output pinion gear rotatably connected to the base and connected to the inner ring gear for tangential engagement A fixed engagement component coupled to or integrally formed with the base, substantially concentric with the output shaft assembly, and the track engagement of the x-axis component The connection between the fixed engagement component and the track engagement component of the x-axis component is such that the inner ring gear is around the output pinion gear. Force the x-axis component to maintain a tangential engagement between the inner ring gear and the output pinion gear so that the drive shaft of the engine is driven by orbiting And a fixed engagement component.

  In some aspects, a drive mechanism for generating a rotational motion output from the reciprocating motion input and / or for generating a reciprocating motion output from the rotational motion input is provided for the base to which the y-axis component is attached. An axially moving y component configured to reciprocate along the y-axis together with the reciprocating input, and an x-axis slidably coupled to the y-axis component and moved along the y-axis direction. A component, i) configured to reciprocate substantially perpendicular to the y-axis relative to the y-axis component, ii) includes an inner ring gear, and iii) substantially concentric with the inner ring gear An output shaft having an x-axis component including a track engagement component disposed on the shaft and an output pinion gear rotatably coupled to the base and connected to the inner ring gear to engage tangentially A assembly, a fixed engagement component, coupled to or formed integrally with the base, and substantially concentric with the output shaft assembly, the track of the x-axis component The connection between the fixed engagement component and the orbital engagement component of the x-axis component is such that the inner ring gear is connected to the output pinion gear. A fixed engagement component that is driven around and that applies force to the x-axis component to maintain tangential engagement between the inner ring gear and the output pinion gear. Yes.

  In some aspects, the reciprocating compressor or pump includes a cylinder block that defines at least one cylinder, at least one piston assembly that reciprocates within the at least one cylinder, and a rotational motion input to the piston assembly. A drive mechanism for generating a reciprocating motion, wherein the drive mechanism is along the y-axis along with the reciprocating motion input of the piston assembly relative to a base on which the y-axis component is slidably mounted. An axially moving y component configured to reciprocate, and an x-axis component that is slidably coupled and moved along the y-axis direction to the y-axis component, i) the y-axis configuration Configured to reciprocate substantially perpendicular to the y-axis relative to the element, ii) includes an inner ring gear, and iii) said inner ring An x-axis component including a track engagement component disposed substantially concentrically with the gear, and an input pinion gear rotatably connected to the base and connected to the inner ring gear in a tangential direction. An output shaft assembly having a fixed engagement component coupled to or integrally formed with the base and substantially concentric with the input shaft assembly; Connecting with the track engagement component of the element and tangentially engaging, the connection between the fixed engagement component and the track engagement component of the x-axis component is achieved by the inner ring gear. An x-axis component for driving around the input pinion gear of the input shaft assembly to maintain tangential engagement between the inner ring gear and the output pinion gear Applying a force, and a fixed engagement element.

Embodiments may include one or more of the following features.
The reciprocating engine may include an opposed piston multi-cylinder engine, and a y-axis component that moves in the axial direction may be coupled to two opposed pistons. The reciprocating engine may include an internal combustion engine. The reciprocating engine may include an in-line multi-cylinder combustion engine. The fixed engagement component may comprise a rotatable element. The rotating element may include a gear, and the fixed engagement component may include a recess to which the track engagement component is joined. The track engagement component may include a gear or a roller. The track engagement component may include a shaft device. The shaft device may be fixedly coupled or integrally formed in the x-axis component. The pitch diameter of the output pinion gear is substantially equal to the stroke length of the reciprocating engine, and the pitch diameter of the inner ring gear is substantially equal to twice the stroke length of the reciprocating engine, the track engaging component and the The sum of the respective pitch diameters with the fixed engagement components may be substantially equal to the stroke length of the reciprocating engine. The output shaft assembly may include a torque transmission gear that transmits torque from the output shaft assembly to the drive shaft. The torque transmission gear may include a sprocket and chain assembly. The base may include a part of the engine block. The base may include components attached to the engine block. The y-axis component may include a linear bearing surface, and the y-axis component may slide relative to the base in the reciprocating motion along the linear bearing surface. The linear bearing surface may limit movement of the y-axis component relative to the base except in the direction of the reciprocating input. The x-axis component may include a linear bearing surface, and the x-axis component may slide substantially perpendicular to the direction of the reciprocating motion input along the linear bearing surface.

  In some aspects, the axial force from the reciprocating input of the reciprocating element is converted to torque applied to the output shaft assembly and / or the torque applied from the output shaft assembly is The method of converting to an axial force for reciprocation is the step of applying an axial force to move the axially moving y-axis component, said y-axis component being slidably mounted. A step configured to reciprocate along the y-axis using the reciprocating input of the piston assembly relative to the base, and slidably coupled to the y-axis component along the y-axis. Transmitting the axial force through a moving x-axis component, wherein the x-axis component i) travels substantially perpendicular to the y-axis with respect to the y-axis component. Configured to move, ii) includes an inner ring gear, and iii) includes a track engagement component disposed substantially concentrically with the inner ring gear, rotatably coupled to the base and joined to the inner ring gear And transmitting the axial force to an output shaft assembly having a tangentially engaged output pinion gear, coupled to the base or integrally formed along the base, the output shaft A fixed engagement component substantially concentric with the assembly joins the fixed engagement component and the orbital engagement component of the x-axis component and tangentially engages, and the x-axis component of the x-axis component The joint between the fixed engagement element and the orbital engagement element is such that the axial force is applied from the inner ring gear to the output as a steadily applied torque and vice versa. Applying a force to the x-axis component so as to maintain a tangential engagement between the inner ring gear and the output pinion gear when transmitted to the pinion gear.

  The fixed engagement component may comprise a rotatable element. The track engagement component may include a gear or a roller. The y-axis component may include a linear bearing surface, and the y-axis component may slide relative to the base in the reciprocating motion along the linear bearing surface. The x-axis component may comprise a linear bearing surface, and the x-axis component may slide substantially perpendicular to the direction of the reciprocating motion input along the linear bearing surface.

  In some aspects, the method of converting the reciprocating axial force from the reciprocating motion of the reciprocating element to the torque applied to the output shaft is axially coupled with the reciprocating motion of the reciprocating element with the reciprocating motion of the reciprocating element. Applying the axial force to the output shaft to slide the moving component, wherein the axial moving component is axially coupled to an inner ring gear engaged with the output shaft; An inner ring gear configured to slide relative to the axially moving component in a direction substantially perpendicular to the reciprocating motion of the reciprocating element; Maintaining contact between the inner ring gear and the output shaft using an idler assembly concentrically secured to the shaft, and the axial movement arrangement When the inner ring gear coupled to the element and the axially moving component slides axially relative to the output shaft, the inner ring gear is against the reciprocating motion of the reciprocating element applied by the idler assembly. Allowing the inner ring gear to circulate around the output shaft to steadily apply the torque to the output shaft during the reciprocating movement of the reciprocating element. And steps.

  Embodiments may include one or more of the following features. Allowing the inner ring gear to slide in a direction substantially perpendicular to the reciprocating motion of the reciprocating element means that the inner ring gear is one or more relative to the axially moving component. Allowing movement along the bearing surface of the. The maintenance of contact between the inner ring gear and the output shaft using the idler assembly uses a fixed engagement component that is substantially concentric with the output shaft, coupled to a base or integrally formed. Applying a force to a track engaging component disposed substantially concentrically with the inner ring gear.

  In some aspects, a method of extracting mechanical work from an operating reciprocating engine includes a maximum long torque moment that maintains a substantially constant length when the reciprocating element of the engine reciprocates and the output shaft rotates. Applying a torque moment to the output shaft of the reciprocating engine using the arm may be included.

Embodiments may include one or more of the following features.
The substantially constant length may be substantially the same as the crankshaft radius of the reciprocating engine crankshaft. Using the maximum length torque moment arm may include coupling the reciprocating element of the engine to the output shaft using a substantially constant length moment arm. The mechanical work extraction may further include increasing the output of the reciprocating engine by applying a torque moment using a maximum length torque moment arm. The maximum length torque moment arm may include a moment arm that maintains its maximum length through rotation of the output shaft. For example, coupling a reciprocating element of an engine to an output shaft can include coupling the output shaft to a rotational torque transmission device that defines a substantially constant torque moment arm, the rotational torque transmission device being an engine The reciprocating element may be configured to be joined. The engine may be an internal combustion engine.

  Applying the torque moment to the output shaft of the reciprocating engine using a maximum length torque moment arm that maintains a substantially constant length may include coupling the moving member to the reciprocating element of the reciprocating engine. The moving member is connected to the output shaft using the torque moment arm of the maximum length. For example, the torque moment arm can be substantially perpendicular to the reciprocating axis of the moving member to apply torque to the rotatable power output member. The torque moment arm that maintains a substantially constant length may include a rotatable gear unit coupled to the power output member and a gear rack coupled to the moving member.

  In some aspects, the reciprocating engine includes at least one substantially constant length torque moment arm that remains substantially constant during reciprocation of the reciprocating element and rotation of the output shaft of the engine. You may go out.

Embodiments may include one or more of the following features.
The substantially constant length torque moment arm may have a length equal to the crankshaft radius of the engine crankshaft. The engine may also include a device for converting the reciprocating motion of the reciprocating element of the engine into the rotational motion of the output shaft using a torque moment arm of substantially invariable length. The engine may also include at least one reciprocating piston disposed within the cylinder, the piston being connected at one end to the engine crankshaft by a connecting rod and further by a torque moment arm of substantially invariable length. Connected to the output shaft. For example, a substantially constant length torque moment arm can be formed, at least in part, by a combination of a rotating device connected to the output shaft and a moving element connected to the reciprocating piston, Defining a universal arm of substantially universal length. The rotating device may include at least one of a pulley, a gear, or a sprocket. The moving element may include at least one of a cable, a chain, a belt, a pull rod, or a gear rack. The engine may also include a clutch device disposed between the reciprocating piston and the output shaft. The engine also includes an energy storage device for temporarily storing energy generated by the reciprocating element of the engine and subsequently releasing energy to the output shaft as the reciprocating element moves through the engine. Also good.

  The substantially constant length torque moment arm may include a torque moment arm that generates torque, i) defined between the rotational axis of the output shaft and the contact between the moving member and the rotating member. Ii) is generally perpendicular to the movement of the moving member, and iii) maintains a substantially constant length during the reciprocating movement of the reciprocating element of the engine.

  In some aspects, a power transmission device for coupling to a reciprocating element of a reciprocating engine includes an axially moving tension member coupled to the reciprocating element, and a moving tension coupled to the power output element. The movable tension member includes a rotatable member joined to the member and applies torque to the power output element during axial movement of the movable tension member using a substantially constant length of torque moment arm. An axial force may be provided.

Embodiments may include one or more of the following features.
A torque moment arm that generates torque is defined between i) the rotational axis of the power output element and the contact between the moving tension member and the rotating member, and ii) is generally perpendicular to the movement of the moving tension member. Iii) maintaining a substantially constant length during the reciprocating motion of the reciprocating element. The rotatable member may be coupled to the output element using a clutch device configured to allow the rotatable member to freely rotate in a second direction relative to the output element. The rotating member may include a gear device, and the moving tension member may include a gear rack connected to the gear device.

  In some embodiments, the reciprocating element may be a reciprocating piston, the power output element may be a rotational power output shaft other than the engine crankshaft, and the moving tension member may be on a reciprocating piston. The pull rod device may be connected and moved based on the reciprocating motion of the piston, and the engine may include a linear gear device coupled to the pull rod to move with the pull rod, and the engine is connected to the output shaft. An output shaft may be included when the engine rotates in a first direction of piston movement toward a crankshaft on which the pinion gear rotates, coupled to and configured to be coupled to a linear gear device. One wake located between the output shaft and pinion gear to engage with It may include a pitch device, when the piston reciprocates within the engine, the rotational axis of the output shaft, the distance between the contact area between the Riniagiya device and the pinion gear remains substantially constant.

  In some aspects, the reciprocating engine can include at least one piston and cylinder, wherein the at least one piston is connected to the crankshaft via a connecting rod at one end and has a substantially invariant torque. Connected to the output shaft via a moment arm, the engine includes an axially moving element coupled to the reciprocating piston and moving with the reciprocating piston, a rotating member coupled to the output shaft and joined to the moving element, the moving element being Providing an axial force on the rotatable member that applies torque to the output shaft during the axial movement of the moving element, wherein the torque moment arm of substantially invariable length comprises: i) the rotating shaft of the output shaft and the moving element; Ii) is generally perpendicular to the movement of the moving element.

Embodiments may include one or more of the following features.
The substantially constant length torque moment arm may remain substantially unchanged during inward movement of the piston toward the crankshaft and outward movement of the piston in a direction away from the crankshaft. The rotatable member may include a gear device, and the axial movement element may include a tensioning device for engaging the gear device. The engine may also include a clutch device for selectively engaging the output shaft based on the direction of motion of the moving element. The at least one piston and cylinder includes four in-line pistons and cylinders, each piston configured to rotate in engagement with the output shaft via a torque moment arm of substantially invariable length. .

  In some aspects, a power transmission device configured to couple to a reciprocating element of a reciprocating engine may include an axially moving tensile member that couples to the reciprocating element and reciprocates. The tension member provides an axial force to the rotating member during the axial movement of the moving tension member, applies torque to the power output element during the axial movement of the moving tension member, and generates a torque moment arm i. ) Defined between the rotational axis of the power output element and the moving tension member and the contact between the rotating member, ii) generally perpendicular to the movement of the moving tension member, and iii) during the reciprocating movement of the reciprocating element; Maintain a substantially constant length.

Embodiments may include one or more of the following features.
The moving tension member may include a pull rod. The rotating member is joined to the moving tension member to engage and rotate the output element when the moving tension member moves in the first direction, and the moving tension member is in a second direction opposite to the first direction. It may be configured to disengage so as to rotate freely with respect to the output element as it moves. The rotatable member can be coupled to the output element using a clutch device configured to allow the rotatable member to freely rotate in the second direction relative to the output element. For example, the clutch device may be a sprag clutch. The rotatable member may be a gear device, and the moving tension member may be a gear rack connected to the gear device. The rotatable member may include a sprocket or pulley and the moving tension member may include a chain or cable element engageable with the sprocket or pulley wheel. The power output element may include a rotary output shaft. The power transmission device may include a seal member for limiting loss of cylinder pressure of the reciprocating engine through an opening connected to the reciprocating element by the power transmission device. The seal member may include a labyrinth seal member. The power transmission device may include an energy storage device that temporarily stores energy generated by the reciprocating element and subsequently releases the energy to the power transmission device as the reciprocating element moves through the engine. . For example, the energy storage device may include a spring element coupled between the moving tension member coupled to the reciprocating motion element and the motion transmission device. The reciprocating element may be a piston configured to reciprocate within a cylinder of a reciprocating engine.

  In some aspects, the reciprocating engine may include at least one reciprocating piston within the cylinder, the at least one reciprocating piston connected to the crankshaft via a connecting rod at one end and the other end substantially Is connected to the output shaft via a torque moment arm of invariant length, wherein the engine includes an axially moving element coupled to and moving with the reciprocating piston, the moving element being Providing an axial force on the rotatable member that applies torque to the output shaft during axial movement, the torque moment arm having a substantially invariable length i) between the rotational axis of the output shaft and the moving element and rotating member; Ii) is generally perpendicular to the movement of the moving element.

Embodiments may include one or more of the following features.
The axial movement element may comprise a pull rod fixed to the piston. The axial movement element may include a linear gear device. The linear gear device may include a gear rack. The rotating member may include a gear for engaging with the linear gear device. The engine may include a clutch device coupled between the output shaft and the axially moving element. The clutch device may include a one-way clutch. The one-way clutch may include a freewheel clutch device. The axially moving element may include a gear rack coupled to the pull rod, the rotatable member includes a pinion gear that engages a gear rack coupled to the output shaft via a clutch device, and the gear rack rotates the output shaft. You may let them. The clutch device may be engaged with the output shaft substantially only during the stroke of the piston descending toward the crankshaft. The clutch device can be engaged with the output shaft when the piston moves inward toward the crankshaft, and can be disengaged from the output shaft when the piston moves outward from the crankshaft. A substantially constant length torque moment arm is defined between the rotational axis of the output shaft and the boundary region between the moving element and the rotating member, and the inward movement of the piston to the crankshaft and the piston It may remain substantially unchanged during the outward movement away from the. The engine may also include an energy storage device disposed between the axially moving element and the output shaft. The at least one reciprocating piston and cylinder may include four in-line pistons and cylinders, each piston engaging and rotating with the output shaft via a torque moment arm of substantially invariable length. It is configured.

  In some aspects, a method for extracting rotatable power from a reciprocating engine may include coupling a moving member to a reciprocating member of the reciprocating engine to apply torque to the rotatable power output member. In addition, the moving member is connected to the rotatable power output member using a moment arm having a substantially constant length perpendicular to the reciprocating axis of the moving member.

Embodiments may include one or more of the following features.
The substantially constant length moment arm may include a rotatable gear unit coupled to the power output member and a gear rack coupled to the moving member. The engine can be an internal combustion engine. The moving member can disengage the rotatable output member as the moving member moves as a result of the outward movement of the reciprocating member. The rotatable power output member (for example, output shaft) may include a rotating shaft other than the crankshaft of the engine.

  In some aspects, a power transmission device configured to couple to a reciprocating piston of a reciprocating engine is connected to a rotary power output shaft other than the engine crankshaft and the reciprocating piston and moves based on the reciprocating motion of the piston. A pull rod device, a linear gear device connected to the pull rod so as to move with the pull rod, a rotatable pinion gear connected to the output shaft and configured to be joined to the linear gear device, and the pinion gear in the piston motion A one-way clutch device disposed between the output shaft and the pinion gear for engaging the output shaft when the crankshaft rotates in the direction of 1 to rotate the crankshaft, and the rotation of the output shaft Contact area between shaft and linear gear unit and pinion gear The piston remains constant substantially reciprocates within the engine.

Embodiments may include one or more of the following features.
The energy storage element may be coupled between the pull rod and the linear gear device. The distance between the rotation axis of the output shaft and the contact area between the linear gear device and the pinion gear may be substantially perpendicular to the movement axis of the linear device. The linear gear device may include a gear rack. The linear gear device may be a chain.

  In some aspects, the method for extracting the rotatable power from the reciprocating engine is to connect the moving gear rack to the reciprocating piston of the reciprocating engine and to connect the rotating pinion gear to a rotating output shaft other than the engine crankshaft. The pinion gear is joined with the gear rack to rotate the pinion gear according to the movement movement of the piston and the gear rack, and the output shaft is connected only when the piston moves to the crankshaft to which the piston is connected. Use of a clutch device to selectively engage the output shaft with the pinion gear to rotate the shaft, and the distance of the torque moment arm between the rotating shaft of the output shaft and the contact surface of the gear rack and the pinion gear is When the piston reciprocates in the engine It is maintained substantially constant.

  In some aspects, the methods herein maintain the output torque of the operating reciprocating engine (e.g., average) by maintaining a substantially constant length of torque moment arm that drives the output shaft of the reciprocating engine. Output torque) can be increased. The engine may be an internal combustion engine. The engine may be an external combustion engine.

  In some aspects, the reciprocating engine can include at least one piston and cylinder, the piston being connected to the crankshaft via a connecting rod at one end, the piston also having a substantially invariant length. It is connected to the output shaft via a torque moment arm. The moment arm may include a pull rod / gear rack / pinion gear / clutch configuration. The gear rack can be disposed on the pull rod, the pinion gear is connected to the output shaft via a clutch, and the gear rack can be engaged with the pinion gear to rotate the output shaft. The clutch may include a freewheel clutch. The clutch may include a sprag clutch.

  In some aspects, the energy storage device can be disposed between the pull rod and the output shaft, the pull rod being configured to couple to a reciprocating member of the reciprocating engine. The energy storage device may include a spring (eg, a disc spring).

  In some aspects, the pull rod pressure seal device can be implemented to limit the pressure loss of the reciprocating engine cylinder through an opening through which the pull rod enters through the cylinder. The pressure seal device may include labyrinth seal means.

  In some aspects, the automobile may include a reciprocating engine with at least one piston and cylinder, the piston being connected to the crankshaft at one end via a connecting rod, and having a substantially constant length. It may be connected to the output shaft via a torque moment arm. The automobile may include one or more of light trucks, delivery trucks, fire trucks, land trucks, motorcycles, and passenger cars.

  In some aspects, an off-road vehicle includes a reciprocating engine with at least one piston and cylinder, the piston is connected to the crankshaft at one end via a connecting rod, and the piston is further substantially unchanged. It may be connected to the output shaft via a torque moment arm of a length of. The off-road vehicle may include one or more of agricultural tractors, construction machinery, trucks, graders, cranes, bulldozers, welders, and pumps.

  In some aspects, the generator set (eg, generator set) can include a reciprocating engine having at least one piston and cylinder, the piston connected to the crankshaft at one end via a connecting rod, May also be connected to the output shaft via a torque moment arm of substantially unchanged length.

  In some aspects, a boat or ship can include a reciprocating engine with at least one piston and cylinder, the piston being connected to the crankshaft at one end via a connecting rod, and further substantially invariant. It is connected to the output shaft through a length torque moment arm.

  In some embodiments, the airplane or helicopter may include a reciprocating engine having at least one piston and cylinder, the piston being connected to the crankshaft via a connecting rod at one end, the piston being further substantially It is connected to the output shaft via a torque moment arm of invariable length.

  In some aspects, the power supply apparatus may be configured to be coupled to the power supply apparatus and configured to be coupled to the power output element via a substantially constant length moment arm. Good.

Embodiments may include one or more of the following features.
The power transmission device may include a pull rod connected to the reciprocating element. The power transmission device can include a rotating member engageable with the pull rod, the rotatable member being configured to rotate the power output element. The rotatable member rotates in engagement with the pull rod substantially only in the first direction and the rotatable member is free to rotate relative to the output element in a second direction opposite to the first direction. It may be configured to allow. The rotatable member may be coupled to the output element using a clutch device configured to allow the rotatable member to freely rotate in a second direction relative to the output element. The clutch device may include a sprag clutch. The rotatable member may include a gear device and the pull rod may include a gear rack engageable with the gear device. The power output element may include an output shaft. The power transmission device may include a seal member for limiting loss of cylinder pressure of the reciprocating engine through an opening through which the power transmission device is coupled to the reciprocating element. The seal member may include a labyrinth seal member. The power supply device may include an energy storage device that temporarily stores the energy generated by the reciprocating element and then releases the energy to the power transmission device as the reciprocating element moves through the engine. . The energy storage device may include a spring element coupled between the pull rod and the motion transmission device. The spring element may include one or more disc springs, and the motion transmission device may include a gear rack engageable with a rotatable gear coupled to the output element. The reciprocating element is a piston configured to reciprocate within the cylinder. In some aspects, the reciprocating engine may include a power transmission device. In some aspects, a kit for a reciprocating engine for increasing the output of a reciprocating engine may include a power transmission device.

  In some aspects, a method for extracting rotatable power from a reciprocating engine includes moving a moving member to a reciprocating member of a reciprocating engine and using a substantially constant maximum length of a moment arm. A step of connecting the member to a rotatable power output member may be included.

Embodiments may include one or more of the following features.
The substantially constant moment arm may include a rotatable gear device connected to the power output member and a gear rack connected to the moving member. The moment arm may include a pull rod / chain / sprocket / clutch configuration. The moment arm may include a pull rod / cable / pulley / clutch configuration.

  In some aspects, a method of increasing the power (eg, average power) of an operating reciprocating engine includes maintaining a substantially constant length torque moment arm that drives the output shaft of the reciprocating engine. It is out.

  In some aspects, a method for increasing the thermal efficiency of an operating reciprocating engine may include maintaining a substantially constant length of torque moment arm that drives an output shaft of the reciprocating engine.

  In some aspects, the power supply apparatus described herein includes a rotation of an output shaft coupled to rotation of a reciprocating engine crankshaft during a downstroke of an engine piston, and the reciprocating engine crankshaft decelerated. Useful by using the stored energy of the rotating output shaft configured to disengage from the piston (eg, using a one-way clutch) so that it will continue to rotate even if (eg, stopped) As a result of both generating power and may be used as a hybrid energy storage system that uses stored rotational energy to generate useful power (eg, mechanical (eg, rotational) power). That is, as will be described later, the output shaft is connected only to the piston during the piston downstroke, but reciprocating engine (e.g., the piston of the engine) so that it can continue to rotate freely during the piston upstroke. ). The stored energy of the power output shaft, which rotates freely when disengaged from the crankshaft, can be used to generate power useful for driving the attached load when the engine is decelerated or stopped.

  As described herein, in some cases, in use, the output shaft may have a rotational speed that is potentially different from the crankshaft of the engine. Thus, the difference in rotational speed between the output shaft and the connection point between the piston and the clutch device (for example, a pulley or sprocket coupled to the outer part of the clutch device (or not directly coupled to the output shaft) Any part of the clutch device)) may be in use. As a result of the reciprocating motion of the piston (ie, the associated pulsation of the outer portion of the clutch device), the output shaft motion resulting from the input from the outer portion of the clutch device is the speed as the reciprocating piston moves through its stroke. And a pulsed rotation in which the torque changes. Thus, in some embodiments, the power supply is connected between the power supply and the system to which the power supply supplies power to reduce (eg, minimize) the adverse effects of such pulsating motion. A coupling (e.g., a fluid coupling (e.g., torque converter)) that can also serve as a torque multiplier (e.g., a torque multiplication torque converter) can be included. For example, the coupling may be connected to the end of the output shaft of the power transmission device and to the driveline shaft of the automobile, the generator input shaft, or other similar system input.

Definitions The following definitions are commonly used in the engineering industry and can be found in many textbooks and Internet sources. These are provided herein for illustrative purposes only and are not intended to limit this disclosure.

  Torque is a torsional force applied to an object such as a wheel or crankshaft. Note that no motion is required due to the presence of torque. For example, when standing on a lug wrench attached to a frozen lug bolt, the bolt is torqued without any movement. For simplicity, the torque herein is measured and described in units of pound-force feet (lbf-ft), which is the equivalent of a given force acting on the end of a foot-length lever. Means in pounds. For example, standing at a weight of 81.6 kg (180 lbs) on a lug wrench with a 10.5 ft long moment arm produces a torque of 1.36 Nm (180 lb force ft). A 40.8 kg (90 lb) child standing on a 21.0-foot lug wrench also applies the same torque.

  The task is to apply distance to the force. Note that the unit used to describe the work is the same as the torque (eg, pound x foot), but the unit of work can be written as ft-lb to distinguish it from the torque value. The practical difference between torque and work is that in this or work, the unit of distance (eg “feet” part) represents the length of travel (eg, feet), and in the case of torque, distance is the moment Represents the length of the arm. If the car is pushed 9.1 m (30 ft) with a force of 45.4 kg (100 pounds), the work done is 4.07 kN · m (3000 ft-lb). A simpler example is lifting a weight (pounds) by a predetermined distance (feet). When using certain mechanical advantages such as winches, the same amount of work is required because the required effort has to be doubled to achieve the same objective by halving the required effort. Will do.

The output is to apply a finite time to the work. A work of 0.75 kN · m (550 ft-lb) per second corresponds to one horsepower (HP).
Therefore, the following description and calculation is used to explain the conversion from torque to horsepower. Pushing the end of a 1 foot moment arm lug wrench with 39.7 kg (87.5 pounds (force)) will apply a torque of 0.12 kN · m (87.5 lbf-ft). Since there is still no movement, neither work nor power has been created. However, if the lug bolt is slightly loosened and begins to rotate, the same 39.7 (87.5 pounds) force is required to keep the wrench rotating. Each turn of the wrench results in a force of 39.7 kg (87.5 lbs) (2 * π * 1 ft) or 1.9 m (6.28 ft) (circle of a hand made by pressing the wrench) Applied over a distance). Thus, a total of 0.75 kN · m (550 ft-lb) of work is generated to rotate the wrench. Work is only performed when the system is actually running. From work calculations, if work is applied fast enough to turn the wrench one revolution per second, 0.75 kN · m (550 ft-lb) work is done per second, and one horsepower output is added. It's easy to say that means.

  By definition, it can be seen that HP is directly proportional to torque and RPM. “Directly proportional” means that a multiplier may be involved. Using the numerical values in the example above and recalling that one revolution per second is 60 RPM, the relationship between HP, torque, and RPM is determined as shown below.

Torque * RPM * constant = hp
87.5 lbs-ft * 60 rev / min * X = 1 hp
X = 1 / (60 * 87.5) = 1/5250
Torque * RPM * 1/5250 = hp
hp = (torque × RPM) / 5250
In an internal combustion engine, torque cannot be generated when the engine is not rotating, so torque is generally applied at a constant RPM. If the engine is operating fast enough to maintain its own operation, the force applied against the load can be measured and the speed at which the engine is rotating can be measured. it can. Thus, the torque (and hence power) value can be determined.

  In some embodiments, the term clutch device, which can include a one-way free wheeling clutch, a bearing clutch such as a sprag clutch (eg, one-way bearing of a CSK model), or other similarly suitable one-way clutch device is When the driven shaft rotates faster than the drive shaft, the drive shaft (ie, the crankshaft of the reciprocating engine described herein) is driven to the driven shaft (ie, the output shaft of the power transmission device described herein). For example, as will be described later, when the reciprocating engine decelerates, the crankshaft decelerates.

Specific Challenges in Conventional Reciprocating Engine Design In continuous operation, a crankshaft type reciprocating engine converts the reciprocating motion of a piston into the rotational motion of a load coupled crankshaft. A reciprocating internal combustion (IC) engine uses a crankshaft to convert explosive energy released into a combustion chamber (eg, a cylinder) via fossil fuel combustion into rotating mechanical energy used to propel the object. Use mechanism. External combustion (EC) engines such as steam engines also use a crankshaft mechanism. Whether the IC engine is 2 or 4 (or more) cycles and / or whether it is gasoline, propane, natural gas, or diesel (or other type of fuel or thermal cycle). Instead, most reciprocating engines use a crankshaft to convert piston reciprocating motion (power) into rotating mechanical motion (output).

  Briefly defined, the systems and methods discussed herein provide a relatively invariant (consistent or constant) maximum that separates reciprocating engine output torque (power) from the crankshaft and generates torque on the output shaft. It relates to supplying the torque (power) with a long moment arm via an alternative power transmission (eg powertrain) path.

Such systems and methods are expected to be advantageous for at least the following reasons.
A typical reciprocating engine crankshaft, as its primary function, returns each of the engine's piston or pistons to their previous position within the respective cylinder during various cycles of the engine. The crankshaft is also used secondary to provide rotational energy to any load to which the engine is coupled. Crankshafts function effectively in returning the pistons to their previous position (eg top dead center), but generally transfer potential torque and power to the engine's applied load. Inefficient. The main cause of this inefficiency is the basic variation of the torque moment arm length as the crankshaft rotates. The length varies from zero to maximum with every half rotation of the crankshaft. Therefore, a power transmission device for a reciprocating engine that generates torque and power for a power output shaft of an engine using a moment arm of a substantially constant maximum length is similar to that using a conventional crankshaft as the power output shaft. It is expected to produce greater (eg, significantly greater) torque and power compared to a sized engine.

  Thus, the systems and methods described herein can be used to create more energy efficient engines, can be designed and manufactured in smaller sizes using smaller components, and are still desirable. Level of power can be generated. In some cases, these efficiency and power increases are expected to directly affect fuel consumption and efficiency, resulting in a more fuel efficient engine. For example, in automotive applications, such fuel efficiency improvements are expected to affect the cost of ownership for driving a vehicle having a power supply with a constant moment arm, as described herein. .

FIG. 1a is a schematic diagram of a conventional reciprocating engine. FIG. 1b is an enlarged schematic view of the reciprocating engine of FIG. 1a showing the moment arm changing as the crankshaft rotates. 1 is a drawing of an exemplary cylinder pressure curve of an internal combustion engine during a power process and corresponding moment arm lengths (eg, conventional moment arm and constant moment arm) used to transmit pressure to drive torque. 3 is another exemplary cylinder pressure curve drawing of an internal combustion engine during a power process. 4 is a table of calculations used to estimate torque generated in a conventional internal combustion engine at various crank angles during a power process. FIG. 4 is a table of calculations used to estimate the torque generated in an internal combustion engine using a constant moment arm to generate torque at various crank angles during the power process. 2 is a drawing of a plurality of exemplary cylinder pressure curves in an internal combustion engine at several different engine loads during a power stroke. It is drawing which shows theoretical increase power and torque output using the power transmission device which has a constant moment arm. It is drawing which shows theoretical increase power and torque output using the power transmission device which has a constant moment arm. It is drawing which shows theoretical increase power and torque output using the power transmission device which has a constant moment arm. It is drawing which shows theoretical increase power and torque output using the power transmission device which has a constant moment arm. It is drawing which shows theoretical increase power and torque output using the power transmission device which has a constant moment arm. It is drawing which shows theoretical increase power and torque output using the power transmission device which has a constant moment arm. It is drawing which shows theoretical increase power and torque output using the power transmission device which has a constant moment arm. It is drawing which shows theoretical increase power and torque output using the power transmission device which has a constant moment arm. 1 is a schematic view of an exemplary reciprocating engine having a power transmission device having a constant moment arm for generating output torque. FIG. FIG. 6 is a cross-sectional side view of another example of a reciprocating engine having a power transmission device having a flexible tensioning device (eg, cable) connected to a piston to generate power. It is a front view of the power output supply apparatus of FIG. 1 is a side view of a power transmission device having a chain and a sprocket system coupled to a power output shaft. FIG. It is a perspective view of another example of the power transmission device which generates an output torque using the constant moment arm attached to the reciprocating piston engine. It is front sectional drawing of the power transmission device of FIG. 19, and a reciprocating piston engine. FIG. 20 is a side cross-sectional view of the power transmission device and reciprocating piston engine of FIG. 19 connected between a seal assembly for limiting pressure loss from the engine cylinder and a pull rod and gear rack of the power transmission device coupled to the reciprocating piston. Energy storage device. It is an expanded sectional view of the engine of FIG. 19 which shows the pull rod of the power transmission device connected with the reciprocating piston. 1 is a cross-sectional view of a sealing device that can be used to limit gas pressure loss from a combustion chamber. FIG. 5 is a perspective view of an exemplary drive mechanism for converting reciprocating motion into output shaft rotation, showing an idler assembly. FIG. 6 is another perspective view of an exemplary drive mechanism showing an output shaft. 26A-26I are schematic side views of an exemplary drive mechanism that vibrates throughout the power stroke of a reciprocating piston. 26A-26I are schematic side views of an exemplary drive mechanism that vibrates throughout the power stroke of a reciprocating piston. 26A-26I are schematic side views of an exemplary drive mechanism that vibrates throughout the power stroke of a reciprocating piston. 26A-26I are schematic side views of an exemplary drive mechanism that vibrates throughout the power stroke of a reciprocating piston. 26A-26I are schematic side views of an exemplary drive mechanism that vibrates throughout the power stroke of a reciprocating piston. 26A-26I are schematic side views of an exemplary drive mechanism that vibrates throughout the power stroke of a reciprocating piston. 26A-26I are schematic side views of an exemplary drive mechanism that vibrates throughout the power stroke of a reciprocating piston. 26A-26I are schematic side views of an exemplary drive mechanism that vibrates throughout the power stroke of a reciprocating piston. 26A-26I are schematic side views of an exemplary drive mechanism that vibrates throughout the power stroke of a reciprocating piston. FIG. 2 is a perspective view of an exemplary drive mechanism coupled to a reciprocating piston of an engine through a respective combustion chamber, showing each drive mechanism coupled to a composite drive shaft. FIG. 28 is another perspective view of the exemplary drive mechanism and engine of FIG. 27, showing the idler assembly portion of each x-axis component. FIG. 6 is a perspective view of an exemplary moving y-axis component showing sliding surfaces and attachment points for connection to a reciprocating piston. FIG. 6 is a perspective view of an exemplary x-axis component showing a sliding surface that oscillates relative to a moving y-axis component. It is a perspective view of an example internal-combustion engine using an example drive mechanism instead of the conventional crankshaft mechanism. FIG. 32 is another perspective view of the example engine of FIG. 31 with the engine block removed for clarity, showing the connection between the drive mechanism and the drive shaft. 1 is a perspective view of an exemplary internal combustion engine having a drive mechanism instead of a conventional crankshaft, each drive mechanism being connected to two opposing reciprocating pistons. FIG. 4 is an exemplary force component vector interacting with a gear pitch diameter in a drive mechanism. FIG. 5 is an exemplary force vector and torque calculation diagram for a conventional crankshaft connecting rod reciprocating mechanism. FIG. 6 is a diagram of an example force component vector of torque applied to an output shaft by the drive mechanism described herein and an example associated torque calculation. 6 is a comparative drawing of the calculated torque output of an exemplary tangential drive mechanism, such as that described herein, compared to a conventional crankshaft connecting rod reciprocating mechanism for the same input pressure (or force) function.

  FIGS. 1 a and 1 b show schematic views of a reciprocating engine 100 having a fixed cylinder 102, a piston 104, a connecting rod 106, and a crankshaft 108. As shown, the piston 104 is moving downward in the cylinder 102 during the power stroke, and the crankshaft 108 is rotating clockwise. A typical power stroke in an IC engine continues from 0 ° crank angle (θ) after top dead center (ATDC) to the lowest position of the piston with a 180 ° ATDC rotation.

The piston normal force applied to the crankshaft of the IC engine (as a result of the combustion pressure in the cylinder) can be written as:
VerticalForce = P (θ) cos α · A Equation 1
Where (θ) is the combustion pressure that is a function of the crank angle (θ) (relative to top dead center), and A is the total projected surface area of the top of the piston approximately perpendicular to the moving axis 110. α is the angle of the connecting rod (relative to the cylinder centerline). Depending on the engine design, the connecting rod may be connected to the piston via an off-axis piston pin (eg, a wrist pin) from the centerline of the piston, which usually affects the angle of the connecting rod. Piston pin offset is a manufacturer's way to reduce the stress of reciprocating parts to enable weight reduction of reciprocating parts, thereby making more efficient manufacturing and reducing engine power loss, And higher rpm performance is obtained. The complementary result of piston pin offset can reduce piston slap due to a more gradual shift from large thrust to small thrust during engine operation.

  The moment arm (or torque arm) that generates the torsional force on the crankshaft (eg, provided as “m” in FIG. 1b) changes as the crankshaft rotates. The moment arm (m) is the rotation axis (3) of the crankshaft main journal (usually located at the piston and / or cylinder centerline 110) and the rotation axis of the crankpin journal where the connecting rod is connected to the crankshaft. The horizontal distance between (2). Accordingly, the changing length of the moment arm can be written as follows with respect to the rotational position of the crankshaft (for example, crank angle θ).

MomentArm = rsinθ Equation 2
Here, r is a radial distance from the center line (for example, rotation axis) (3) of the crankshaft main journal to the center line (for example, rotation axis) (2) of the connecting rod slow arm or crank pin (2) ( That is, the connecting rod is connected to the crankshaft), and thus rsin (θ) is the length of the normal force torque moment arm. Note that the maximum length of the variable torque moment arm occurs at a crank angle of 90 degrees and is equal to the crank radius.

Using the above definitions for various connection pieces, the following equation can be written to represent crankshaft torque (torsional force) (T) as a function of crank angle θ:
T (θ) = VerticalForce (θ) · MomentArm (θ) Equation 3
After combining the above equations, the torque generated by the reciprocating engine during the power process can be expressed as:

T (θ) = P (θ) cos α · rsin (θ) Equation 4
As shown, this torque equation is highly dependent on the crank angle (θ). For a fixed engine design, A and r are constant and α is a function of the moment arm (ie, r sin θ) and the connecting rod length (l). The length (1) of the connecting rod is equal to the distance between the rotation axis (1) of the wrist pin (connecting the connecting rod to the piston) and the rotation axis (2) of the crank pin. Piston pressure P (θ) is also a very strong function of crank angle (θ) and differs for many combustion-related factors (eg, air / fuel ratio, compression ratio, fuel type, and other factors). The pressure P (θ) may be different between the IC engine and the EC engine. Piston pressure may also change with changes in engine speed, which is generally expressed in revolutions per minute (RPM).

  In a typical IC engine, the pressure acting on the top of the piston in the cylinder (e.g., piston pressure) is slightly behind the top dead center (TDC) position of the crankshaft, depending on the specific engine design. At ATDC from 9 ° to 18 °, peaks are reached and varies with engine speed. For example, FIG. 2 shows an exemplary piston pressure 52 and moment arm length 54 of an exemplary IC engine as a function of crank angle (θ). As shown, the piston pressure 52 reaches a maximum value a few degrees after TDC and then decays fairly rapidly as the piston moves toward its bottom position at 180 ° ATDC. The function of moment arm length 54 (rsin θ) starts at zero at 0 ° in TDC (since the connecting point between the connecting rod and the crankshaft is directly above the crankshaft main journal axis of rotation (eg, centerline)), The maximum value is reached at 90 ° (since the rotation axis of the crankpin is right next to the rotation shaft of the main journal of the crankshaft), and at 180 ° (the connecting point between the connecting rod and the crankshaft is the centerline of the crankshaft) Move to 0 ° again (as it returns to just above). As can be seen from this drawing of FIG. 2, when the vertical force of the piston is maximum, near the top of the stroke, the moment arm acting to rotate the crankshaft is very short. This fluctuating moment arm greatly affects and limits the generated torque.

  Also shown in FIG. 2 is when the output power train has a constant length moment arm as described herein having a length that is approximately the maximum length of the moment arm that varies throughout the power process. 2 is an exemplary constant length moment arm 56 found in FIG. As shown and discussed below, having a constant length moment arm to generate torque (ie, especially during maximum pressure in the cylinder) draws more output torque and power from the IC engine Make it possible.

In order to demonstrate the effect of the constant length moment arm on the varying moment arm on the engine output torque and horsepower, a predicted output calculation for two cases for a typical IC engine can be calculated. The first case is a variable moment arm (MomentArm = rsinθ), and the second case is a fixed length moment arm (MomentArm = m).
A simple comparison between a variable moment arm configuration and a constant moment arm configuration can be estimated by comparing the various equations described herein with corresponding values equal in both cases.

  The exemplary pressure curve shown in FIG. 3 (Rakopoulos, C, Michos, C, and Giakoumis, E. Availability analysis of a syngas federation sparking engine edition used in the United States (September 2008), pages 1378-1398, the contents of which are incorporated herein by reference in their entirety) It can be calculated at various crankshaft angles throughout the stroke. In order to simplify the comparison of torque values, the various parameters and dimensions were normalized using several unitless values. In particular, 2 engine strokes (S), 3.14159 piston area (A), 2 engine bores (B), 1 crankshaft radius (r = S / 2), 2.924 connecting The rod length (L) was all used to simplify the calculation. The results of these calculation examples are shown in the table of FIG. As shown, using these exemplary values, a typical IC engine was found to produce an average torque of about 0.122076.

  In the case of a constant-length moment arm IC engine, as described above, the torque equation can be simplified as T (θ) = P (θ) A · m, where P (θ) is the crank angle. Cylinder pressure based (eg, as shown in FIG. 3), where m is the length of the constant moment arm (eg, moment arm (m) = moment arm radius (r) = S / 2). Similar to a typical IC engine having a variable moment arm as described above, the estimated torque value can be calculated at various crankshaft angles throughout the power stroke using the same normalized dimensions as described above. The results of these calculation examples are shown in the table of FIG. As shown, using these exemplary values, a theoretically modified IC engine with a constant moment arm has been found to produce an average torque of about 0.290584. Thus, the average output of an IC engine with a constant moment arm is about 2.38 times the average output of a typical variable moment arm IC engine.

  Additional calculations were also completed, which estimated the increased power and torque performance of the constant moment arm IC engine. For illustrative purposes, the IC engine used to calculate both cases (eg, for the variable moment arm case and the constant moment arm case) is a dual overhead cam (DOHC), 16 valve, 4 cycle gasoline engine. . To calculate the predicted power and torque output for both cases, take a predetermined cylinder pressure curve for several different engine loads (as shown in FIG. 6) and use it to create the torque tables of FIGS. The configuration of the variable moment arm and the constant moment arm was compared using the same calculation as that described above. The pressure curve in FIG. 6 is shown in Martychenko, A .; Park, J .; , Ko, Y. Balin, A .; “A Study on the Possibilities of Estimate of In-Cylinder Pressure by Means of Measurement of Pain 99 Ch. The entirety of which is incorporated herein. As detailed by Martychenko et al., The pressure curve is an example of a typical DOHC, 16-valve, 4-cylinder gas engine, so it can be used to make estimates of torque and power for different engine loads. The calculations used are calculated using a 3.1693 inch piston bore (B) and a 3.1693 inch stroke (S), which is a DOHC, 16-valve, 4-cylinder gas engine described in detail by Martychenko et al. This is a typical example of the type (for example, a 4-cylinder 2300 cc, OHC Hyundai Sonata engine). Torque and power estimates were also calculated for a set engine load (eg, 80.0 Nm (59 lb-ft)) over a range of engine speeds (ie, crankshaft rotational speed).

  In order to determine the output of the moment arm engine of constant maximum length in this case where moment arm (m) = crank radius (r) = 1/2 stroke (S / 2) Is converted into a rotational motion. One exemplary general concept (eg, implementation) that may be employed is shown in FIG. For each rotation of the crankshaft while the connecting point (2) (eg, crankpin) of the connecting rod and crankshaft moves by π * S, the output shaft coupling point (5) (ie, pull rod, tension device Or the point at which a similar component couples the piston to the clutch device (and thus also to the output shaft) is only 2 as the piston moves down the distance of the stroke S and back up the distance of the stroke S. * Move by S. The examples herein are generally described as being only one cylinder for simplicity, and in an exemplary engine having two or more cylinders, each different piston moves downward. Note that the output shaft rotates continuously to produce movement of the output shaft. Therefore, the rotational speed of the output shaft is proportionally slower than the rotational speed of the crankshaft. Thus, to determine the steady state rotational speed of the output shaft for a constant rotational speed of the crankshaft, the rotational speed of the crankshaft is multiplied by (2 / π). During the rotation of the piston, the piston momentarily stops moving vertically at both the top (top dead center (TDC)) and bottom (bottom dead center (BDC)) of the stroke, and the crankshaft rotates. Note that it accelerates and decelerates rapidly between TDC and BDC. Thus, the estimated speed of the output shaft may be the same until the piston starts at 0 at TDC and rises to the average speed of the piston (i.e., the length of the moment arm (e.g., pull rod, tensioning device from the center of the output shaft) , Or the distance to the location where similar components are connected))) to maximum speed and then to zero at BDC. As mentioned above, the output shaft can typically continue to rotate as the piston moves upward from BDC to TDC. Thus, while the piston is moving upward (in the opposite direction to the rotation of the output shaft), the output shaft can be estimated using, for example, the average speed of the piston as it moves upward from BDC to TDC. Can continue to rotate at speed. That is, the piston can reciprocate in two opposite directions, but the speed of the output shaft can be estimated based on the absolute average speed of the piston as it moves between BDC and TDC.

  Further, in an engine having only one cylinder, a device such as a flywheel device is used to move the piston upward (that is, while the movement of the piston does not directly apply a rotational force to the output shaft). It is expected to maintain a portion of the output shaft's rotational speed.

  The results of these calculations are shown in the drawings of FIGS. As shown, the estimated torque and power increases observed for a constant maximum length moment arm engine are generally large in proportion to all of the calculated values. As described above, the rotational speeds of the output shaft and the crankshaft are generally not the same, and the rotational speeds listed in FIGS. 7-14 (eg, 2400 RPM) are the rotational speeds of the crankshaft (ie, not necessarily the output shaft). Is not the rotation speed).

  In addition to the potential increase in torque and power described above, the output device described herein having a constant maximum length of moment arm can provide energy (e.g., power) used when the engine is decelerating. ) Can also be used to accumulate. For example, as detailed herein, the power transmission device is a reciprocating engine (ie, a reciprocating piston of the engine) by a clutch device (eg, a one-way clutch) that allows the output shaft to rotate freely in one direction. ) May be included. That is, the clutch device can be engaged with the output shaft only when the piston is moving downward. As mentioned above, this configuration helps to allow the output shaft to rotate at a different speed than the reciprocating engine crankshaft to which the power transmission is coupled.

  In some aspects, the ability to rotate the output shaft at a different speed than the crankshaft allows the power transmission device to function as a power storage device. For example, in use, the rotational speed of the crankshaft can be reduced by the user (eg, as a result of engine deceleration), which typically results in a decrease in output based on the reduced rotational speed. However, since the output shaft can normally rotate freely in one direction from the crankshaft, the output shaft need not be decelerated when the crankshaft decelerates. Thus, when the crankshaft decelerates, for example when the user decelerates the engine during use, the output shaft may be allowed to continue to rotate at a higher rotational speed and continue to generate power. As described below, the output shaft may include a flywheel useful for generating and maintaining rotational moments and output shaft motion.

  In some cases, this configuration can be used to store or recover energy during engine deceleration. For example, in some embodiments where a reciprocating engine and power transmission are used in an automobile, the output shaft continues to rotate and is used in other systems during crankshaft deceleration (eg, as a result of releasing the accelerator pedal). Power (eg, electrical output or mechanical output) can be generated. Accordingly, in some embodiments, an apparatus including one or more power transmission devices described herein causes a reciprocating engine to be mechanically coupled to rotate an output shaft during an engine power process. Used as a hybrid device that can utilize both the resulting power and stored energy (eg, power) that can be made available by continuous rotation of the output shaft even when the engine is decelerated or stopped it can.

  Also, in some embodiments, the output shaft is a coupling or component of an automatic transmission that allows continuous and consistent rotation of the output shaft (e.g., even after the crankshaft has suddenly decelerated). (For example, a torque converter of a transmission) may be connected, and sudden deceleration helps to supply a constant rotational speed and output to the automatic transmission. As noted above, such couplings (eg, torque converters) may also be used to reduce the effects of pulsating motion of the output shaft that may result from the reciprocating motion of the piston driving the clutch device.

Reciprocating engine with constant moment arm As described above, rotation connected to the reciprocating piston via a torque moment arm having a substantially consistent (eg constant) length (eg constant maximum length) throughout the power stroke. It is theoretically possible to extract more (eg, significantly more) rotational motion power from the reciprocating piston power process by using a powertrain (eg, power transmission). In some embodiments, the substantially consistent length of the torque moment arm is fixed at its set length, which is its maximum length, and its fixed maximum (e.g., constant, invariant, or consistent). May include a torque moment arm that is allowed to vary only slightly. In some cases, a substantially constant length of torque moment arm may change (e.g., slightly) as a result of the contact area moving along or between the connecting sprocket and the chain. .

  For example, as shown in FIG. 15, an exemplary reciprocating engine 100 example is connected to a rotatable crankshaft 108 via a connecting rod 106 and controls cylinders 102 and valves (which control gas entering and exiting the cylinder 102). For example, it has a reciprocating element (for example, piston 104) configured to move up and down in an intake valve and an exhaust valve). Engine 100 is connected to a power transmission device 200 having a separate power output element (eg, power output shaft 202) rotatably coupled to piston 104 via power transmission device 200 having a constant length moment arm 204. be able to. The power output shaft 202 can be any of a variety of devices that can utilize rotational force, including a vehicle driveline (eg, automobile, truck, motorcycle, construction equipment (eg, bulldozer), or other transport equipment such as an airplane or boat. Or a generator, welder, or other device that utilizes rotational force.

  As shown, the power transmission device 200 is configured such that when the piston 104 moves back and forth within the cylinder (eg, moves up and down when the cylinder is vertically oriented as shown in the example of FIG. 15), the pull rod 206 To move in substantially the same way as the piston 104 (eg, substantially the same available axial force (eg external work) at substantially the same travel distance, speed, acceleration as the piston 104). An elongate moving tension device (eg, pull rod) 206 connected to the piston 104. The pull rod 206 can be connected to any desired position on the piston 104. That is, the pull rod can be fixed to the area of the piston or connected to a wrist pin that connects the piston to the connecting rod. The pull rod 206 is typically configured to interact with other components of the power transmission device 200 that are attached to or integrated within the power output shaft 202. For example, in some examples as described below, the pull rod 206 is a rotatable member, such as a substantially circular member (eg, a gear device) of a power transmission coupled to the output shaft 202. A toothed rack configured to contact and engage 208 (eg, an elongated member having one or more rows of teeth) may be included. The portion of the engine that defines an opening 210 (eg, pull rod opening) through which the pull rod 206 passes into a cylinder (eg, cylinder head) typically reduces gas flow and pressure loss in the region between the opening and the pull rod. It includes a sealing device for limiting (eg preventing).

  Although the power transmission device that converts the linear motion of the piston into the rotational motion of the power transmission device is generally described and illustrated as a single toothed rack that connects and engages with a gear device that is connected to an output shaft, Other configurations are possible. For example, in some embodiments, the power transmission device includes one or more additional gear sets that are used to increase or decrease the rotational speed or torque of the output shaft based on the linear speed and force of the reciprocating piston. May be. Additionally or alternatively, the power transmission device properly transmits the linear motion of the piston to the rotational motion of the output shaft while maintaining a substantially consistent (eg, constant) length of moment arm. It may include any of a variety of devices or systems that can. For example, in some embodiments, a power transmission device (eg, a rotating member of the power transmission device) may additionally or alternatively include a belt system, a pulley system, and / or a chain drive system. In some cases, referring to FIGS. 16-18, one end of a tensioning device (eg, belt, cable 206a, chain 206b, or other device capable of applying a tensile force) is attached to the piston and the other end of the tensioning device Can be attached to the piston, and the tensioning device can be connected to the output shaft using pulley 208a or sprocket 208b. A spring return mechanism 212 may also be included to help return the tensioning device (eg, cable 206a, belt or chain 206b) upward as the piston 104 moves to the top of the stroke. In some embodiments, the power transmission device may include other types of power transmission systems including any of a variety of devices.

  Although the movement of the piston 104 alternates back and forth, it is generally desirable to rotate the output shaft 202 in only one direction, so the power transmission device 200 (eg, the rotating member 208 in some cases) typically engages the output. Configured so that the output shaft rotates substantially in one direction so that the output shaft rotates only in one direction (for example, in the case of a two-cycle IC engine, the piston is Only during the power stroke to move to). Note: In the case of a four-cycle engine, the clutch bearing power transmission will be engaged during both the intake downstroke and the power downstroke, but still allow rotation in one consistent direction. Only.

  In some embodiments, a power transmission device (e.g., a rotating member of a power transmission device) is used when the tension device (e.g., pull rod, cable, or sprocket) is pulled into the cylinder by the piston and the piston is at top dead center. When returning to, the pull rod is configured to grip the output shaft only when the output shaft is substantially released when moved out of the cylinder. In some embodiments, the power transmission device 200 includes a reciprocating piston when the tensioning device moves into the cylinder, but the rotational component of the power supply device (eg, a round gear device) moves out of the cylinder. When allowing the output shaft to rotate freely in the opposite direction relative to the output shaft so as to limit (eg prevent) the output shaft from accidentally rotating forward or backward as it moves in the cylinder Only a clutch device 214, such as a one-way clutch, is configured to engage and rotate the output shaft. In some embodiments, the rotating member may include a sprocket, gear, pulley, wheel, clutch device, or any suitable combination of one or more devices.

  In some examples, as further discussed below, the clutch device 214 includes a one-way free wheel clutch, a bearing clutch such as a sprag clutch (eg, a CSK model one-way bearing), or other similarly suitable one-way clutch device. It is out. The clutch bearing can function as a simple ball or roller bearing when rotated in one direction and can limit (eg, prevent) rotation when rotated in the opposite direction. This is accomplished by using a spring loaded sprag that sometimes acts as a wedge between the two bearing races. Clutch bearings are variously known as CSK bearings, one-way bearings, unidirectional bearings, and sprag bearings. The one-way clutch device can be spring loaded to limit backlash when the output shaft is engaged. Alternatively or additionally, the clutch device includes a ratchet mechanism, such as a ratchet clutch that can substantially engage the output shaft only when the power transmission device attempts to rotate the output shaft in one direction. You may go out.

  As shown, as a result of the interface between the pull rod and the power transmission device being separated from the rotational axis of the output shaft by a generally constant distance relative to the reciprocating piston motion axis (ie, Unlike the connection between the connecting rod and the crankshaft), the moment arm of the force that generates the torque acting on the output shaft is substantially constant, steady or unchanged.

As described above, this substantially consistent (eg, substantially constant) length of moment arm is increased (eg, substantially increased) through the output shaft driven by the pull rod. Torque and power output can be extracted. As a result of the extraction of the substantially constant moment arm of the torque generated from the crankshaft reciprocating engine, the engine converts the explosive energy of combustion more easily into mechanical rotational motion, and the engine heat loss is reduced and the entire engine Is expected to decrease. Increases thermal efficiency.

  The illustrated reciprocating piston engine typically includes a crankshaft and a connecting rod, which are used to return the piston to top dead center at least after a power step, but these configurations are based on usable torque. In some cases, both the crankshaft and the connecting rod can be reduced because it is not used to transmit power from the engine. Such a reduction in the size of the crankshaft and connecting rod may be expected to help reduce the amount of parasitic power loss that could otherwise result from additional rotating mass in the engine.

  The exemplary reciprocating engine shown in the schematic diagram of FIG. 15 may be implemented in any of a variety of suitable configurations and designs. As described above, an engine (eg, an IC engine) can be specifically designed to include a separate power transmission and power output shaft that can extract the power generated by the reciprocating piston. Such specially designed engines may include reduced crankshafts and connecting rods to limit the power loss that can result from the rotating mass.

Implementation Example In some embodiments, an existing engine (eg, an existing IC engine) is modified to include a separate power transmission and power output shaft that can extract the power generated by the reciprocating piston. Can be done. For example, FIGS. 19-23 illustrate an improved four-cylinder engine 300 that has been modified to include a separate power transmission 400 and a power output shaft 402. Note that for clarity, the crankshaft, connecting rod, some gas seals, and other parts of the engine are omitted from the drawings.

  As shown, the improved IC engine is a dual overhead cam (DOHC) 4-cylinder, 4-cycle in-line gasoline engine (eg, an improved Toyota 3RZ-FE gasoline engine). For multi-cylinder reciprocating engines (eg, IC engines), it is generally desirable to have a single output shaft, so a simple anticipated configuration is the power of each piston and cylinder with the piston and cylinder aligned with each other. The cylinder can be configured as a single power output shaft, including a line of transmission devices. Therefore, in a 4-cycle IC engine, there is one power stroke for every two rotations of the crankshaft. Therefore, in a 4-cylinder 4-cycle IC engine, there is a power process for every 180 ° rotation of the crankshaft. In the 6-cylinder IC engine, there is a power process for every 120 degrees of rotation of the crankshaft, and in the 8-cylinder IC engine, there is a power process for every 90 degrees of rotation. Regardless of whether it is 4, 6, or 8 cylinders, a single output shaft of the inline IC engine described above is desirable. Although it may be desirable to have a single output shaft, all the benefits of the increased torque and power output of this constant torque arm invention are all power cycles and all mechanical configurations (eg, V6, V8, V12, radial, etc.). In multi-cylinder engine mechanical configurations that are not “in-line”, there may be multiple output shafts. Also, in some embodiments, the V-type engine configuration can be coupled to a power transmission device having a single output shaft. That is, even in the case of an engine having pistons and cylinders that are not all in line with each other, the tensioning device connected to the piston can be one of a variety of gear or pulley configurations to cause consistent rotation of the output shaft. May be coupled to a common output shaft.

  In a DOHC series IC engine, the area above the piston and cylinder centerline is almost unobstructed by various engine components, and it is easy to add a power transmission that is attached to the piston and moves through the cylinder head Become. As shown, the power transmission device 400 includes two pull rods 406 for each cylinder coupled to the piston (eg, via an existing piston pin used to couple the piston to the connecting rod). You may go out. In the illustrated example, two pull rods 406 are used to balance the load on the piston 304 (eg, one on the opposite side of the piston), and the load on each pull rod 406 may be reduced. In some IC engine designs, the connecting rod is connected to the piston slightly off-axis from the piston centerline. Pull rod 406 is disposed through opening 410 on an engine component (eg, cylinder head 302) and is configured to move up and down through opening 410 with the movement of the piston. In the example of the four-cylinder, four-cycle reciprocating engine shown in FIGS. 19 to 22, the two pistons may always be set to move in the same direction and exactly 180 degrees away from the other two pistons. When one cylinder ignites in the power process and drives its piston downward into the cylinder, all four pull rods of the two pistons that move together share the drive load of the power process.

  In some embodiments, the pull rod 406 includes a toothed gear rack 407 coupled to the upper region of the pull rod. In some embodiments, the gear rack 407 can be coupled to the pull rod 406 so that the gear rack 407 can be individually moved along the pull rod. In some cases, as shown, the gear rack can be used with one or more spring elements (eg, Belleville style springs) 409 that can help perform some functions. Can be attached to. For example, the spring can function as an energy storage device 409 for a power supply device. As described above and shown in FIG. 2, the pressure in the cylinder (and hence the force acting on the piston) usually has a well-defined spike at a very early stage of the power process, after which the piston moves into the cylinder. Decays rapidly as Accordingly, as shown in FIGS. 19-21, the spring coupling the gear rack to the pull rod will absorb some of the initial load as the pressure increases rapidly (moving the pull rack slightly downward relative to the gear rack). The energy can be stored by the compression of the spring. Next, when the piston moves into the cylinder and the pressure drops, the spring extends and pushes down the gear rack against the pull rod to release the stored energy. Such spring compression and extension serves to disperse the force spike seen from the piston near top dead center. Figuratively, this can act to make the pressure curve slightly smoother and distribute some of the force throughout the piston power stroke. Additionally or alternatively, the spring also helps limit the impact that can occur when the reciprocating piston moves back and forth.

  Alternatively, the gear rack may be permanently secured to the pull rod (eg, via a fastener or by being integrally formed with the pull rod). The gear rack is coupled to the output shaft 402 for rotating the output shaft and engages and couples with a rotating member (eg, a substantially circular gear 408) coupled to the output shaft 402 for rotating the output shaft. The size is set and configured to As described above, the toothed gear 408 typically uses a clutch (eg, one-way clutch bearing 414) to output shaft 402 to convert the reciprocating linear motion of the pull rod into a substantially one-way rotational motion. It is connected.

  As shown, in some embodiments, the output shaft employs an attachment device (eg, bearing carrier 416) that positions the output shaft but allows the output shaft to rotate under torque generated by the power transmission device. Connected to an engine (for example, a cylinder head).

  Referring specifically to FIGS. 20-23, the cylinder head 302 has an opening 410 through which the pull rod 406 passes that provides adequate clearance so that the pull rod 406 can move freely through the seal member 412. A seal member (eg, a seal such as a labyrinth seal) 412 that can limit pressure loss through is included. As shown in the enlarged view of FIG. 23, the labyrinth seal assembly 412 includes a generally cylindrical body 20 that houses a series of seal discs 21 separated from one another by disc spacers 22. The labyrinth seal assembly 412 also includes a clamp plug 23 for retaining the seal disc 21 and disc spacer 22 within the body 20. A thin nut 24 can be used to couple the clamping plug 23 to the body 20. The cylinder gasket 25 may be disposed at the end of the seal assembly 412 (eg, the end configured to be inserted into the engine cylinder) to help seal the cylinder.

  The inner diameter of the seal disc 21 can be configured to be only slightly larger than the pull rod diameter. The inner diameter of the disk spacer 22 can be larger than the inner diameter of the seal disk 21 by several times the gap distance between the pull rod and the inner diameter of the seal disk, thereby forming a cavity between the seal disks. The series of cavities formed between the seal discs 21 can create a greater resistance to gas flow if more cavities are formed, which can increase resistance to flow. The disk spacer 22 can be somewhat adapted to compensate for the tendency of the seal to loosen. Alternatively, separate compliant parts (eg, springs) can be added to the stack.

  Although some exemplary power transmission mechanisms are described herein and shown in the accompanying drawings, other exemplary devices are used to convert the reciprocating motion of the piston into the rotational motion of the output shaft. May be. In some cases, the mechanisms described herein can be used in addition or alternatively to a typical engine crankshaft.

  For example, referring to FIGS. 24 and 25, the drive mechanism 1000 includes a base 1010, a vibration assembly 1100 coupled to the base 1010 and configured to couple with a reciprocating element (eg, a piston), and a swing assembly 1100. And a rotational output shaft assembly 1300 that provides rotational power output to the drive shaft, for example.

  Base 1010 can serve as a mounting and positioning surface for other components of the drive mechanism, such as rocking assembly 1100 and output shaft assembly 1300. In some cases, the base can be an integral part of the engine, such as a part or region of the engine block or head, or can be a separate component attached to the engine. Base 1010 may include a first base plate 1012 through which output shaft assembly 1300 (ie, output shaft 1302) can rotate. The first base plate 1012 can define a hole or recess that serves as a bearing surface along which the output shaft 1302 can rotate. In some embodiments, the first base plate 1012 may be in the form of a multi-piece assembly formed, for example, from a journal portion 1012A and a cap portion 1012B that can be secured together. In some cases, a bearing can be used between the base plate 1012 and the shaft 1302. For clarity, a portion of the base is shown as transparent in FIGS.

  At least one portion of the base, such as the first base plate 1012, may include a joining surface along which one or more components of the vibration assembly can join. For example, the first base plate 1012 can define a sliding engagement surface 1020 through which the vibration assembly 1100 can move. As described below, the engagement surface 1020 vibrates so that the reciprocating piston moves but is generally coupled in the x-axis direction so that the component can move freely in the axial direction (along the y-axis). The parts of the assembly can be connected. The y-axis is typically the direction of piston reciprocation (or other reciprocating input movement) and the x-axis is substantially perpendicular to the y-axis and reciprocation.

  The vibration assembly 1100 is connected to an axial translational y-axis component (eg, frame) 1102 and the frame 1102 and is configured to move along the x-axis relative to the output shaft assembly 1300. An x-axis component 1130 that engages the portion may be included. For clarity, the x-axis component of FIGS. 24 and 25 is shown as transparent. The frame 1102 can be configured to provide y-axis motion that allows the vibration assembly to move with the reciprocating motion of the engine piston. Thus, the frame 1102 includes one or more sliding surfaces 1104 that couple the frame 1102 along the x-axis, but allow the frame 1102 to move along the y-axis with piston movement. Also good. In some cases, the sliding surface 1104 can be configured to engage and join a base sliding surface 1020 (eg, of the first base plate 1012). Also, the sliding surfaces 1104 and 1020 can restrict the frame 1102 from sliding or otherwise moving along the z-axis direction individually or together.

  The frame 1102 can also include an opening (eg, a hole) 1106 through which the output shaft 1302 can be placed. The opening 1106 can provide clearance for the shaft 1302 when the frame vibrates in the y-axis direction with the movement of the reciprocating piston. The frame 1102 can be coupled to the reciprocating piston in any of a variety of ways. For example, referring briefly to FIG. 29, the frame may include one or more attachment points (eg, threaded holes) 1107 to which a tension member can be connected to drive the frame. In some embodiments, as shown, the frame can have two attachment points 1107 that are balanced on two sides of the frame 1102. As a result of the balanced attachment point, the force applied by the reciprocating piston can be applied evenly to the frame.

  The frame 1102 can be made of any of a variety of structurally suitable materials. For example, the frame 1102 can be a lightweight, high-strength material such as aluminum (eg, alloy; 4032, 7055, 6061, 7068, 5052, 2024, 2618), titanium (eg, alloy; Ti-6242), steel (eg, ASM alloy; 6516, 6414, 6419, 6512, 6425, 6532, 5844), magnesium (eg, ASM alloy; 4429, 4425). The x-axis component 1130 may be made from any of a variety of structurally suitable materials. For example, the x-axis component 1130 can be a lightweight, high-strength material such as aluminum (eg, alloy; 4032, 7055, 6061, 7068, 5052, 2024, 2618), titanium (eg, alloy Ti-6242), steel (Eg, ASM alloy; 6516, 6414, 6419, 6512, 6425, 6532, 5844), magnesium (eg, ASM alloy; 4429, 4425).

  The x-axis component 1130 (also shown in FIG. 30) of the vibration assembly 1100 is configured to move with the frame 1102 as the frame moves along the y-axis. That is, the x-axis component 1130 is coupled to the frame 1102 with respect to the direction of piston movement. However, the x-axis component 1130 can be configured to move relative to the frame 1102 along an x-axis that is substantially perpendicular to the piston motion. For example, the x-axis component 1130 may include one or more sliding surfaces 1133 configured to mate and slide into engagement with one or more sliding surfaces 1108 of the frame 1102. . Sliding surfaces 1133, 1108 that help allow the x-axis component 1130 to move relative to the frame 1102 are substantially relative to the sliding surfaces 1104, 1020 that allow the frame 1102 to move relative to the base 1010. Can be vertical. In some embodiments, the sliding surfaces 1104, 1020 that allow the frame 1102 to move relative to the base 1010 are relative to the frame 1102 where the x-axis component 1130 may be positioned along the x-axis. May be disposed substantially along the y-axis (generally in line with the movement of the piston), which may be substantially perpendicular to the sliding surfaces 1133, 1108, which help to allow movement. For an auxiliary sliding surface that helps to allow the x-axis component 1130 to move in both the y-direction (axial direction) and the x-direction (lateral direction), the x-axis component 1130 is, for example, The output shaft 1302 can be circulated (eg, moved along a substantially circular path). Further, the sliding surfaces 1133 and 1108 can restrict the x-axis component 1130 from sliding or otherwise moving along the z-axis direction, either individually or together.

  The sliding surface can be designed and implemented in any of a variety of forms. For example, the sliding surface can be smooth and / or define a surface. The sliding surface may also define features that help limit relative movement between components other than in the desired direction. That is, in some cases, the sliding surface allows relative movement in the x and y directions, but along the z-axis (eg, the z-direction) to help assemble and keep the drive mechanism together during use. May limit relative movement. For example, the complementary sliding surface includes a protrusion (eg, a flange) on one component and a recess (eg, a groove) configured to receive the flange along the other component. You may go out. In some cases, the flanges and grooves can be placed in the x or y direction to limit relative movement in the z direction. In some embodiments, the sliding surface includes a removable and / or replaceable surface, such as a ball bearing or a rolling bearing slide (eg, a commercially available linear bearing surface such as a Schneeberger type M / V). Also good. As will be appreciated by those skilled in the art, lubricating sliding surfaces including metal-to-metal surfaces as well as bearing and gearing contact surfaces facilitates smooth, low-friction movement, resulting in damage, sticking, galling, and It is important to prevent vibration. This may include forced lubrication of all sliding surfaces with pumped lubricant (eg, lubrication), or sealing system lubrication by sealing lubricant (eg, grease) to the sliding contact area of moving parts, or Includes the application of non-stick surface coatings such as Teflon.

  The circular motion imparted to the x-axis component 1130 by the reciprocating motion of the piston can be used to impart circular motion (eg, rotation) to the output shaft 1302. As a result, the drive mechanism 1000 converts purely axial motion (eg, motion along the y direction consistent with piston motion) into motion with an x-direction component and a y-direction component, and continues the output shaft. To promote with tangential force. That is, when the x-axis component 1130 moves around the output shaft, the force driving the output shaft can always be applied tangentially regardless of the position of the piston between top dead center and bottom dead center. . For example, the x-axis component 1130 is an outer engagement device (eg, an annular power transmission internal ring gear) configured to interface with a meshing device of a rotary output shaft assembly 1300, such as a rotary pinion gear 1304 coupled to the output shaft 1302. 1132 may be included. As a result of the consistent circular motion of the x-axis component 1130 around the rotating pinion gear pinion gear 1304, the x-axis component 1130 has a consistent moment arm length when moving in various directions in the x-axis and y-axis directions. Apply torque force to the pinion gear.

  The outer engagement device 1132 is typically coupled (eg, fixed) to the x-axis component 1130. The outer engagement device 1132 is coupled to the x-axis component 1130 in any of a variety of ways, including a press fit or heat shrink connection, using fasteners, adhesives, or mechanical joints (eg, welding). Can. In some cases, the outer engagement device 1132 and the x-axis component 1130 have a one-piece configuration with features (eg, gear teeth in a joining groove) formed directly on the x-axis component 1130 by machining or casting or other method. Can be manufactured as an element.

  The pinion gear 1304 and the outer engagement device 1132 can be sized and configured based on the mode of the engine in which the drive mechanism is used. For example, the diameter of the outer engagement device 1132 (eg, the pitch diameter for the inner ring gear) can be twice the stroke length of the engine. Forming the outer engagement device to double the stroke length may allow the vibration assembly 1100 to move along the y-axis by the same distance that the piston moves during the stroke. The diameter (eg, pitch diameter) of the pinion gear 1304 is typically approximately equal to the piston stroke length of the engine. As a result, the vibration of the drive mechanism can be more closely coordinated with the reciprocating motion of the piston. The diameters of the pinion gear 1304 and the inner ring gear 1132 configured in this way are such that one complete rotation of the x-axis component around the pinion gear 1304 is achieved during one revolution as the pinion gear moves back from top dead center to bottom dead center. It is configured to allow a 360 degree trajectory.

  The drive mechanism 1000 may also include an idler (eg, engagement) assembly 1200 that can provide force to keep the outer engagement device 1132 in consistent contact with the pinion gear 1304. For example, the idler assembly 1200 can apply a force so that the gear teeth of the outer engagement device 1132 mesh closely with the gear teeth of the pinion gear 1304 over the entire stroke of the piston. In some embodiments, idler assembly 1200 may be offset in the z-direction with respect to drive outer engagement device 1132 and driven pinion gear 1304 and coupled to a track engagement component (eg, coupled to x-axis component 1130). Positioning elements (eg, posts, rollers, pulley wheels, sprockets, or gears) 1202 made or integrally formed therein. That is, the idler assembly 1200 can be on the opposite side of the x-axis component 1130 than the outer engagement device 1132. Positioning element 1202 may be an engagement component (eg, a fixed engagement component (eg, a capture configuration (eg, post, roller, pulley wheel, belt, sprocket, chain, gear, or groove) coupled to base 1010). Or a configuration such as a recess that can be engaged by a track engaging component))) 1204). The positioning element 1202 is typically positioned substantially centrally (eg, concentrically) within the center of the outer engagement device 1132. The complementary configuration 1204 can be aligned with the pinion gear 1304 (eg, coaxially and concentrically). By aligning the positioning element 1202 with the outer engagement device 1132 and the complementary configuration 1204 and the pinion gear 1304, the frame 1102 reciprocates in the y direction and the x-axis component 1130 reciprocates in the x direction. As providing motion and torque to the output shaft, the outer engagement device 1132 moves smoothly around the pinion gear 1304 and continuously engages the pinion gear 1304 to continuously rotate the output shaft 1302. As a result, the drive mechanism 1000 can be more balanced than some other drive devices, such as those in which the output shaft is not aligned with the movement of the piston.

  As shown, in some cases, the positioning element 1202 can be located on the side of the x-axis component 1130 opposite the output shaft 1302. The positioning element 1202 can be rotatably fixed to an x-axis component 1130, such as a fixed gear, and the complementary mechanism 1204 can be a rotatable gear attached from the base. However, in some cases, the positioning element 1202 can be configured to rotate and the complementary feature 1204 can be stationary. In some cases, both positioning element 1202 and complementary mechanism 1204 may be configured to rotate. In some embodiments, as shown, the idler assembly has a joint contact between the positioning element 1202 and the complementary feature 1204 between the engagement device 1132 and the pinion gear 1304 relative to the rotational axis of the output shaft 1302. It may be configured and positioned to be opposite to the junction contact between them. The size of each positioning element 1202 and complementary feature 1204 can vary. In the case of a roller or gear, the combined diameter (eg, pitch diameter) of positioning element 1202 and complementary mechanism 1204 is typically equal to the diameter of pinion gear 1304. This size setting can help provide a consistent contact force to keep the pinion gear 1304 in contact with the engagement device 1132. In some embodiments, the pitch diameters of the various gears may be configured relative to one another so that continuous tangential drive may be achieved. For example, the pitch diameter of the pinion gear 1304 is substantially equal to the piston stroke, and the engagement device (eg, inner ring gear) 1132 is twice the pitch diameter of the pinion gear 1304 and the idler assembly components (as pinion gears). The sum (eg, pitch diameter) of 1202 and the width of complementary mechanism 1204 (as pinion gear) is substantially equal to the pitch diameter of pinion gear 1304.

As shown in the sequential schematics shown in FIGS. 26A-26I, when the reciprocating motion of the piston drives the x-axis component 1130 along a circular path through a set of complementary sliding surfaces, the engagement device ( 1132 (in the form of, for example, an annular gear 1132) rotates the pinion gear 1304 and the output shaft 1302. As will be appreciated by those skilled in the art, FIGS. 26A-26I have been simplified to schematically represent the interaction between the various components of the drive mechanism. Since the movement of the x-axis component and the y-axis component is substantially (eg, purely) sinusoidal in both the x-axis direction and the y-axis direction, the peak axis velocity is typically The point occurs and the minimum axial speed (ie zero) usually occurs at the extremes of each movement. The interface between the positioning element 1202 and the complementary mechanism 1204 helps keep the engagement device 1132 in contact with the pinion gear 1304. 26A-26I are simplified in the schematic (ie, physical idler assembly components have been omitted for clarity), so that the force generated by the interface between positioning element 1202 and complementary feature 1204 It is represented in FIG 26A~26I by idler force _{F I.} Further, the engagement 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 piston reciprocation. In some aspects, engagement device 1132, pinion gear 1304, and positioning element 1202 / complementary mechanism 1204 may be considered as a set of planetary gears where positioning element 1202 is a sun gear and pinion gear 1304 is a planetary pinion. The engagement device 1132 is a fixed outer ring gear. However, instead of the planetary gear and ring gear rotating around the sun gear, in this case the rotating pinion gear 1304 stays in the center and the positioning element 1202 and the engagement device 1132 move around the pinion gear to provide a rotational output. moving.

  The drive mechanism described herein may be used to obtain more power from the internal combustion engine and convert greater linear force from the reciprocating piston into rotational torque than conventional crankshaft systems. Expected to be good. For example, the relationship between the force and torque of the drive mechanism 1000 compared to the relationship between the force and torque of a conventional crankshaft reciprocating mechanism is shown in FIGS. 34, 35, 36 and 37 and will be described below.

FIG. 34 shows various gear pitch diameters (eg, pitch diameter 1501 of engagement device (inner ring gear) 1132, pitch diameter 1503 of pinion gear 1304, pitch diameter 1502 of positioning element 1202, and pitch diameter 1504 of complementary feature 1204. ) Shows the relationship between force vectors on the gears of the exemplary mechanism 1000 as represented by In the exemplary drive mechanism 1000, the pitch diameters 1501 and 1502 are substantially fixed with respect to each other such that one movement corresponds to the other movement and the force applied to one is the force applied to the other. (E.g., inner ring gear 1132 and positioning element 1202 move as one unit). Further, in the exemplary drive mechanism 1000, the pitch diameters 1503 and 1504 are stationary in the xy coordinates and do not move. The pinion gear 1304 associated with the pitch diameter 1503 can rotate. As shown, a normal force F (ie, can be a force from a reciprocating piston) is applied to pitch diameters 1501 and 1502, which simultaneously have two component forces, a normal force component F _N and a tangential component F _T. It is divided into. Normal direction force vector F _N is perpendicular to the tangential force vector F _T, is typically directed through all four gear shaft. At the top dead center position (TDC) of the gear device, the normal force _FN is equal to the total normal force F in the absence of the tangential force _FT component. In the correct TDC position, normal forces typically do not cause rotational movement, and movement through this state is the momentum of the rotating gear and all that is coupled to the gear (eg, drive train, generator, Carried by a pump). This condition at the correct TDC position is substantially the same as that experienced by conventional crankshaft connecting rod mechanisms. The forces on and through the gears of the drive mechanism 1000 and the forces acting on various parts of the gears (eg, the gear faces) are large and continuously changing. This places very high demands on material strength on all gears of the mechanism 1000. The gear unit material can be any high-strength material, and in some cases includes a surface hardened material. Exemplary materials include DIN-EN MnCr steel (eg, 20MnCr5, 20MoCr4, 20CrMo5), DIN-EN NiCrMo steel (eg, 20NiCrMo6-4, 18CrNiMo7-6, 14NiCrMol3-4), including surface hardened steel such as: , 17NiCrMo6-5), or any other material.

FIG. 36 further breaks down the force component into x and y components and shows the mathematical relationship of torque as a function of x and y forces and angular distance from the top of the mechanism stroke. As shown in FIG. 36, the normal force F can be expressed as F = F _y = P (θ) · A. Where P (θ) is the cylinder pressure as a function of angle from TDC, A is the piston area, m = r · sin θ, where r is the radius of pinion gear 1304 (or half of pitch diameter 1503) And represents the length of the torque arm, n = r · cos θ, F _T = F _Y · sin θ; F _x = F _T · cos θ, and F _x = F _Y · sin θ · cos θ. . As a result, the total torque T applied to the output shaft as a result of the two component forces can be expressed as: _{T = F x · n + F} Y · m = F Y · sinθ · cosθ · r · cosθ + F Y · r · sinθ. These representations can be simplified as follows. T = P (θ) · A · r · sin θ · cos ² θ + P (θ) · A · r · sin θ.

FIG. 35 shows the mathematical relationship for torque as a function of x and y forces and angular distance from the top of the stroke for a conventional crankshaft reciprocating mechanism. As shown in FIG. 35, the normal force F can be expressed as F = F _y = P (θ) · A. Where P (θ) is the cylinder pressure as a function of angle from TDC and A is the piston area. sin α = m / l, where α is the angle of the connecting rod and l is the length of the connecting rod. m = r · sin θ, where r is the radius of the crankshaft. n = cos θ. α = sin ⁻¹ ((r · sin θ) / l). F _x = F · sin α. Then, F _Y = F · cos α. As a result, the torque T of the entire applied to the crankshaft can be expressed as _{follows: T = F x · n +} F Y · m = F · sinα · r · cosθ + F · cosα · r · sinθ. Therefore, the torque T is equal to T = F · r (sin α · cos θ) + F · r (cos α · sin θ).

To simplify the equation, T = P (θ) · A · r · (sin α · cos θ) + P (θ) · A · r · (cos α · sin θ).
FIG. 37 is a drawing of an exemplary torque calculation calculated for a tangential drive mechanism 1000 applied to an internal combustion engine, which torque is a conventional crankshaft connecting rod applied to the internal combustion engine represented in FIG. Compared to the exemplary torque of the mechanism is shown in FIG. 36, both using the same pressure (force), the same torque arm length, r = 1.87 inches as a function of angle, and a conventional crankshaft In the case of a connecting rod engine, a typical length value for the connecting rod is used as / = 5.78 inches. Torque values are expressed for both the x and y components and the sum and are represented over the same 180 degree power step. As can be seen from FIG. 37, the instantaneous torque of the drive mechanism 1000 is always greater than the torque of the crankshaft mechanism, and the overall average torque of the drive mechanism 1000 is approximately 33% higher than the torque of the conventional crankshaft connecting rod mechanism. As is apparent from FIG. 37, the torque after 90 ° is caused by the adverse effect of the movement of the connecting rod of the crankshaft mechanism in the x-axis direction (for example, the direction away from the longitudinal center axis of the piston and the direction toward the center) Adversely affect. Every time. This effect of changing the x-axis position does not exist in the drive mechanism 1000.

  Referring back to FIGS. 24-33, the output shaft 1302 can be connected to one or more additional driveline components, depending on the desired implementation or field of use of the drive mechanism. As shown, in some embodiments, the output gear 1306 may be coupled to the output shaft 1302.

  As described herein, a drive mechanism that converts reciprocating axial motion into substantially continuous radial motion can be used in a variety of different applications. For example, the drive mechanism 1000 may be implemented and used in the same manner as the power transmission device 400 to join the internal combustion engine. In some embodiments, a tensioning device (eg, a pull rod) can axially connect the frame 1102 to the reciprocating piston in a manner similar to the pull rod 206 described above. Examples are shown in FIGS. 27 and 28. FIG. For clarity, the example shown in FIGS. 27 and 28 has removed the normally attached complementary mechanism 1204 to provide an unobstructed view of the drive mechanism. However, the base may be manufactured in a separate component attached to the engine, or a structure that couples the drive mechanism 1000 to the engine block.

  As shown in FIGS. 27 and 28, when each output shaft 1302 is mechanically coupled to a composite drive shaft 1402, multiple drive mechanisms 1000 can be used together. The combination drive shaft 1402 can be driven by individual output shafts 1302 using any of a variety of devices such as belts and pulleys, chains and sprockets, gears, and the like. The illustrated example includes a gear set 1303 for connecting a drive mechanism (eg, output gear) 1306 to the composite drive shaft 1402. As described above, while the drive mechanism 1000 and composite drive shaft 1402 can be used to extract power from the engine, the engine can include a crankshaft and a connecting rod, which facilitate piston reciprocation. , Work to return the piston to top dead center. .

  A drive mechanism, such as that described above as drive mechanism 1000, may additionally or alternatively be implemented to replace a conventional crankshaft and connecting rod system to transmit the power of the internal combustion engine to the rotating drive shaft. . As shown in FIGS. 31 and 32, the drive mechanism 1000 is disposed in the engine block 50 between the piston and the drive shaft 1402 instead of being connected to the piston using a pull rod device disposed through the combustion chamber. Can do. For example, the frame 2102 can be connected directly to a piston 304 in the engine block 50 opposite the combustion chamber 75, instead of a conventional connecting rod. As shown, the frame 2102 can be designed and structured similar to a connecting rod having a beam-like neck 2104 that connects to the piston, eg, using a wrist pin or similar connection.

  In some embodiments, the block 50 can function as a base to which the drive mechanism 1000 can be connected (eg, fixed, coupled). Specifically, for example, the complementary mechanism 1204 can be attached to the engine block 50 in the same manner that the crankshaft is attached to a conventional engine, for example using journals and bearings. For clarity, the example of FIG. 31 is shown with a transparent engine block 50 and FIG. 32 is shown without the engine block 50 to clearly show the drive mechanism 1000.

  In these embodiments, the drive mechanism 1000 is located within the engine block 50 so that other top components of the engine such as intake air, heads, valves, fuel injection, and ignition (eg, spark plug or compression ignition) are present. It is possible and remains similar or essentially the same as that used in other conventional internal combustion engines.

  Other embodiments of the drive mechanism are possible. In some embodiments, the improved internal combustion engine may include a drive mechanism that is each coupled to two opposing pistons that reciprocate relative to each other. For example, referring to FIG. 33, the engine can include one or more drive mechanisms that include a frame 2202 that is directly connected to two pistons 304, with the piston and frame motion paths being substantially in line with each other. . For clarity, the engine block of FIG. 33 is shown as transparent. Frame 2202 may include two opposing beam-like neck portions 2104 at both ends that connect to the piston using, for example, a wrist pin or similar connection. The alternating reciprocation of the two pistons 304 connected to the frame 2202 results in a constant alternating movement of the frame 2202 to provide a constant movement of the x-axis component 1130 around the pinion gear 1304 and the piston reciprocating. Helps apply force to the pinion gear 1304 that maintains a consistent moment arm throughout the movement. This type of engine with opposed pistons can sometimes be referred to as a flat engine, a boxer engine, or a horizontally opposed engine. This opposed piston configuration requires only one frame 2202 for two pistons, thus reducing the overall number of parts of the engine.

  In some embodiments, a power transmission device having a substantially steady or constant moment arm for generating increased torque and power is an engine retrofit kit (e.g., engine retrofit) that can be attached to an engine for use. Kit). For example, in some embodiments, the piston and connecting rod and engine upper end components (eg, cylinder head and valve train, ignition system, fuel delivery system, etc.) are left in place and the lower end (eg, separate The engine block (or part of it) and the crankshaft assembly are replaced to install the existing power transmission and power output shaft into the existing engine system. It can be used as a method for increasing.

  A power transmission device generally has a constant (eg, constant or invariable) length of torque moment arm with a constant (eg, constant or invariable) length that is a maximum length that does not vary throughout the power stroke. Then, there is some variation in the length of the moment arm. For example, in some embodiments, a power transmission device (eg, a rotating member or joint of a pull rod) is configured such that the moment arm acting on the output shaft is not completely constant at its maximum value. In some cases, the length of the moment arm changes slightly as the tensioning device moves with the rotating member and contacts the rotating member. For example, the moment arm may change slightly when the gear rack is connected to a rotating pinion gear or when the chain is connected to a rotating sprocket.

  The typical maximum moment arm length of a conventional reciprocating engine would be half the crankshaft radius or engine stroke. However, this can vary with different engine designs. Conventional reciprocating engines typically have a torque moment arm that varies from zero length (at 0 ° and 180 ° ATDC crankshaft angles) to its maximum length (at 90 ° ATDC crankshaft angle). Any moment arm length that has a length and changes less than this range (ie, from 0 to maximum) is expected to be an improvement for torque generation. For example, in some cases, the consistent length-moment arm device described herein provides about 0% to about 50% (eg, from about 0%) of length as the pull rod reciprocates with the piston. About 40%, about 0% to about 30%, about 0% to about 20%, about 0% to about 15%, about 0% to about 10%, about 0% to about 5%, about 0% to about 2 %, About 0% to about 1%, about 0% to about 0.5%, about 0% to about 0.1%, about 0% to about 0.0001%) Can be noticed.

  Note that in this document, these descriptions and geometric relationships are generally described for a substantially vertically aligned cylinder positioned above the centerline (eg, axis) of the crankshaft. I want to be. However, the principles described herein can also be implemented using different configurations of reciprocating engines. That is, presented herein is used to illustrate the difference between power extraction from a crankshaft and power extraction from a separate power transmission device (eg, drive train) having a constant-length moment arm. Although the equation may be adjusted or updated based on the particular engine, it is expected that the constant moment arm engine power increase will be observed on differently configured engines.

  Furthermore, the examples herein relate generally to implementations of drive mechanisms in which they are used to utilize linear motion and convert it to rotational motion of the output shaft, although other examples are possible. It is. For example, in some cases, a drive mechanism such as that described above as drive mechanism 1000 may additionally or alternatively be implemented to replace a conventional crankshaft and reciprocating pump and compressor connecting rod system. As will be appreciated by those skilled in the art, in such a case, the basic components of the drive mechanism 1000 can be used, but the rotational input of the rotating shaft can be converted into a reciprocating motion of the piston assembly.

  Thus, the output assembly described above (eg, output shaft assembly 1300) may function as an input shaft assembly instead. Similarly, the output pinion gear 1304 can function as an input pinion gear. In such a case, increased torque transmission from the drive pinion gear 1304 via the mechanism 1000 to the driven piston assembly tends to increase overall mechanical efficiency.

Although various embodiments have been described herein, they have been presented and described by way of illustration and are not intended to limit the scope of the claims presented with this specification to a particular configuration or structural component. Accordingly, the breadth and scope of the preferred embodiments should not be limited by any of the above-described exemplary structures or embodiments, but should be defined only in accordance with the appended claims and their equivalents. is there.

Claims (42)

In the reciprocating engine,
An engine block defining at least one cylinder;
At least one piston assembly reciprocating within the at least one cylinder;
A drive mechanism for generating a rotational motion output from a reciprocating motion input of the piston assembly, the y-axis component moving in the axial direction, wherein the y-axis component is slidably attached to the base A y-axis component configured to reciprocate along the y-axis by the reciprocating input of the piston assembly;
An x-axis component that is slidably coupled to and moves along the y-axis with the y-axis component, i) substantially perpendicular to the y-axis with respect to the y-axis component An x-axis component configured to reciprocate, ii) includes an inner ring gear, and iii) includes a track engagement component disposed substantially concentrically with the inner ring gear;
An output shaft assembly having an output pinion gear rotatably coupled to a base and tangentially connected and engaged with the inner ring gear;
A fixed engagement component coupled to the base or integrally formed along the base and substantially concentric with the output shaft assembly, the track engagement of the x-axis component Connecting and tangentially engaging a component, wherein the connection between the fixed engagement component and the track engagement component of the x-axis component is configured to drive the drive gear of an engine drive shaft assembly A fixed engagement component that applies a force to the x-axis component to maintain contact between the inner ring gear and the output pinion gear such that the inner ring gear circulates and drives the output pinion gear. Equipped with a reciprocating engine.   The engine of claim 1, wherein the reciprocating engine includes an opposed piston multi-cylinder engine, and the axially moving y-axis component is coupled to two opposed pistons.   The engine of claim 1, wherein the fixed engagement component comprises a rotatable element.   The engine of claim 1, wherein the fixed engagement component comprises a recess to which the track engagement component is connected.   The engine of claim 1, wherein the track engagement component comprises a gear or a roller.   A pitch diameter of the output pinion gear is substantially equal to a stroke length of the reciprocating engine, and a pitch diameter of the inner ring gear is substantially equal to twice the stroke length of the reciprocating engine; The engine of claim 1, wherein a sum of pitch diameters of each of the fixed engagement components is substantially equal to a stroke length of the reciprocating engine.   The engine according to claim 1, wherein the output shaft assembly includes a torque transmission gear that transmits torque from the output shaft assembly to the drive gear of the engine drive shaft assembly.   The engine of claim 7, wherein the torque transmission gear includes a sprocket and chain assembly.   The engine according to claim 1, wherein the base portion constitutes a part of the engine block.   The engine of claim 1, wherein the y-axis component comprises a linear bearing surface along with the reciprocating input along which the y-axis component slides relative to the base.   The engine of claim 10, wherein the linear bearing surface restricts the y component from moving relative to the base except in the direction of the reciprocating input.   The engine of claim 1, comprising a linear bearing surface that slides along the x-axis component substantially perpendicular to the direction of the reciprocating input. In a drive mechanism for generating a rotational motion output from a reciprocating motion input of a reciprocating engine piston assembly,
an axially moving y-axis component configured to reciprocate along the y-axis of the reciprocating input of the piston assembly relative to a base to which the y-axis component is attached;
an x-axis component that is slidably coupled and moved along the y-axis direction to the y-axis component, and i) reciprocates substantially perpendicular to the y-axis with respect to the y-axis component An x-axis component comprising: ii) an inner ring gear; and iii) a track engagement component disposed substantially concentrically with the inner ring gear;
An output shaft assembly having an output pinion gear rotatably coupled to the base and connected to the inner ring gear in a tangential direction;
A fixed engagement component coupled to or integrally formed with the base, substantially concentric with the output shaft assembly, the track engagement configuration of the x-axis component The connection between the fixed engagement component and the track engagement component of the x-axis component is such that the inner ring gear circulates around the output pinion gear Fixed to apply force to the x-axis component to maintain a tangential engagement between the inner ring gear and the output pinion gear so as to drive the drive shaft of the engine A drive mechanism comprising an engagement component.   The drive mechanism according to claim 13, wherein the reciprocating engine includes an opposed-piston multi-cylinder engine, and a y-axis component that moves in the axial direction is connected to two opposed pistons.   The drive mechanism according to claim 14, wherein the reciprocating engine includes an internal combustion engine.   The drive mechanism according to claim 13, wherein the reciprocating engine includes an in-line multi-cylinder combustion engine.   The drive mechanism of claim 13, wherein the fixed engagement component comprises a rotatable element.   The drive mechanism according to claim 17, wherein the rotating element includes a gear.   The drive mechanism of claim 13, wherein the fixed engagement component comprises a recess to which the track engagement component is joined.   The drive mechanism of claim 13, wherein the track engagement component comprises a gear or a roller.   The drive mechanism of claim 13, wherein the track engaging component comprises a shaft device.   The drive mechanism of claim 21, wherein the shaft device is fixedly coupled or integrally formed in the x-axis component.   A pitch diameter of the output pinion gear is substantially equal to a stroke length of the reciprocating engine, and a pitch diameter of the inner ring gear is substantially equal to twice the stroke length of the reciprocating engine; The drive mechanism of claim 13, wherein the sum of the respective pitch diameters of the fixed engagement component is substantially equal to a stroke length of the reciprocating engine.   The drive mechanism according to claim 13, wherein the output shaft assembly includes a torque transmission gear that transmits torque from the output shaft assembly to the drive shaft.   25. The drive mechanism of claim 24, wherein the torque transmission gear includes a sprocket and chain assembly.   The drive mechanism according to claim 13, wherein the base includes a part of an engine block.   The drive mechanism of claim 13, wherein the base includes components attached to the engine block.   The drive mechanism according to claim 13, wherein the y-axis component includes a linear bearing surface, and the y-axis component slides relative to the base in the reciprocating motion along the linear bearing surface.   29. A drive mechanism according to claim 28, wherein the linear bearing surface limits movement of the y-axis component relative to the base except in the direction of the reciprocating motion input.   14. The x-axis component includes a linear bearing surface, and the x-axis component slides substantially perpendicular to the direction of the reciprocating input along the linear bearing surface. Drive mechanism. An axial force from a reciprocating input of the reciprocating element is converted into a torque applied to the output shaft assembly and / or a torque applied from the output shaft assembly is axially applied to the reciprocating movement of the reciprocating element. In the method of converting to force,
Applying an axial force to move an axially moving y-axis component using the reciprocating input of the piston assembly relative to a base to which the y-axis component is slidably mounted a step configured to reciprocate along the y-axis;
Transmitting the axial force through an x-axis component that is slidably coupled with the y-axis component along the y-axis, wherein the x-axis component is i) the a track engagement component configured to reciprocate substantially perpendicular to the y axis relative to the y axis component, ii) comprising an inner ring gear, and iii) disposed substantially concentrically with the inner ring gear With
Transmitting the axial force to an output shaft assembly having an output pinion gear rotatably coupled to the base and tangentially engaged to the inner ring gear, wherein the axial force is coupled to the base; or A fixed engagement component formed integrally along the base and substantially concentric with the output shaft assembly is joined to the fixed engagement component and the track engagement component of the x-axis component. Tangentially engaged and the joint between the fixed and orbital engagement component of the x-axis component is steadily applied torque and vice versa, the axial force is When transmitted from a ring gear to the output pinion gear, a force is applied to the x-axis component to maintain a tangential engagement between the inner ring gear and the output pinion gear. Comprising the steps of obtaining, the method.   32. The method of claim 31, wherein the fixed engagement component comprises a rotatable element.   32. The method of claim 31, wherein the track engagement component comprises a gear or a roller.   32. The method of claim 31, wherein the y-axis component comprises a linear bearing surface, and the y-axis component slides relative to the base in the reciprocating motion along the linear bearing surface.   The x-axis component comprises a linear bearing surface, and the x-axis component slides substantially perpendicular to the direction of the reciprocating motion along the linear bearing surface. Method. In a method for converting a reciprocating axial force from a reciprocating motion of a reciprocating motion element into a torque applied to an output shaft,
Applying the axial force to the output shaft to slide the axially moving component with the reciprocating motion of the reciprocating element with the reciprocating motion of the reciprocating element, the axially moving component Is axially coupled to an inner ring gear engaged with the output shaft, the inner ring gear being relative to the axially moving component in a direction substantially perpendicular to the reciprocating movement of the reciprocating element. A step configured to slide
Maintaining contact between the inner ring gear and the output shaft using an idler assembly secured substantially concentrically to the inner ring gear;
The inner ring gear is applied by the idler assembly when the inner ring gear coupled to the axial movement component and the inner ring gear coupled to the axial movement component is axially slid relative to the output shaft. Allowing the inner ring gear to circulate around the output shaft, allowing the torque to be steadily applied during the reciprocating movement of the reciprocating element. Applying to the output shaft.   Allowing the inner ring gear to slide in a direction substantially perpendicular to the reciprocating motion of the reciprocating element means that the inner ring gear is one or more relative to the axially moving component. 37. The method of claim 36, comprising allowing movement along the bearing surface of the.   The maintenance of contact between the inner ring gear and the output shaft using the idler assembly uses a fixed engagement component that is substantially concentric with the output shaft, coupled to a base or integrally formed. 37. The method of claim 36, comprising applying a force to a track engagement component disposed substantially concentric with the inner ring gear. In a drive mechanism for generating a rotational motion output from a reciprocating motion input and / or for generating a reciprocating motion output from a rotational motion input,
An axially moving y component configured to reciprocate along the y axis with the reciprocating input relative to the base to which the y axis component is attached;
an x-axis component that is slidably coupled and moved along the y-axis direction to the y-axis component, and i) reciprocates substantially perpendicular to the y-axis with respect to the y-axis component An x-axis component comprising: ii) an inner ring gear; and iii) a track engagement component disposed substantially concentrically with the inner ring gear;
An output shaft assembly having an output pinion gear rotatably coupled to the base and connected to the inner ring gear in a tangential direction;
A fixed engagement component coupled to or integrally formed with the base, substantially concentric with the output shaft assembly, the track engagement configuration of the x-axis component The connection between the fixed engagement component and the track engagement component of the x-axis component is such that the inner ring gear circulates around the output pinion gear A fixed engagement component that is actuated to apply force to the x-axis component to maintain tangential engagement between the inner ring gear and the output pinion gear.   The pitch diameter of the output pinion gear is substantially equal to one unit of length, the pitch diameter of the inner ring gear is substantially equal to twice the pitch diameter of the output pinion gear, and the track engaging component and 40. The drive mechanism of claim 39, wherein the sum of the pitch diameters of each of the fixed engagement components is substantially equal to the pitch diameter of the output pinion gear. In reciprocating compressors or pumps,
A cylinder block defining at least one cylinder;
At least one piston assembly reciprocating within the at least one cylinder;
A drive mechanism for generating a reciprocating motion of the piston assembly from a rotational motion input;
The drive mechanism is
An axially moving y component configured to reciprocate along the y axis with the reciprocating input of the piston assembly relative to a base to which the y axis component is slidably mounted;
an x-axis component that is slidably coupled to the y-axis component and moves along the y-axis direction, i) reciprocating substantially perpendicular to the y-axis with respect to the y-axis component An x-axis component configured to include: ii) an inner ring gear; and iii) a track engagement component disposed substantially concentrically with the inner ring gear;
An output shaft assembly having an input pinion gear rotatably coupled to the base and connected tangentially in connection with the inner ring gear;
A fixed engagement component coupled to or integrally formed with the base and substantially concentric with the input shaft assembly, the track engagement configuration of the x-axis component The connection between the fixed engagement component and the track engagement component of the x-axis component is such that the inner ring gear is the input of the input shaft assembly. A fixed engagement component that circulates and drives around a pinion gear to apply force to the x-axis component to maintain tangential engagement between the inner ring gear and the output pinion gear; A reciprocating compressor or pump. The pitch diameter of the output pinion gear is substantially equal to the stroke length of the reciprocating compressor or pump, and the pitch diameter of the inner ring gear is substantially twice the stroke length of the compressor or pump. 42. The compressor or pump of claim 41, wherein the sum of the respective pitch diameters of the track engagement component and the fixed engagement component is substantially equal to the stroke length of the compressor or the pump.

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