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WO2008010490A1 - MOTEUR ALTERNATIF cycloïdAL ET POMPE EMPLOYANT CE MÉCANISME DE VILEBREQUIN - Google Patents

MOTEUR ALTERNATIF cycloïdAL ET POMPE EMPLOYANT CE MÉCANISME DE VILEBREQUIN Download PDF

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Publication number
WO2008010490A1
WO2008010490A1 PCT/JP2007/064095 JP2007064095W WO2008010490A1 WO 2008010490 A1 WO2008010490 A1 WO 2008010490A1 JP 2007064095 W JP2007064095 W JP 2007064095W WO 2008010490 A1 WO2008010490 A1 WO 2008010490A1
Authority
WO
WIPO (PCT)
Prior art keywords
engine
piston
unit
cycloid
reciprocating
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2007/064095
Other languages
English (en)
Japanese (ja)
Inventor
Takashi Matsuda
Motohiro Sato
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shizuoka University NUC
Suzuki Motor Corp
Original Assignee
Shizuoka University NUC
Suzuki Motor Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Shizuoka University NUC, Suzuki Motor Corp filed Critical Shizuoka University NUC
Priority to JP2008525862A priority Critical patent/JPWO2008010490A1/ja
Publication of WO2008010490A1 publication Critical patent/WO2008010490A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts, not specific to groups F01B1/00 - F01B7/00
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts, not specific to groups F01B1/00 - F01B7/00 with crankshaft
    • F01B9/023—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts, not specific to groups F01B1/00 - F01B7/00 with crankshaft of Bourke-type or Scotch yoke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts, not specific to groups F01B1/00 - F01B7/00
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts, not specific to groups F01B1/00 - F01B7/00 with crankshaft
    • F01B9/026—Rigid connections between piston and rod; Oscillating pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/24—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type
    • F02B75/246—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type with only one crankshaft of the "pancake" type, e.g. pairs of connecting rods attached to common crankshaft bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/02—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders arranged oppositely relative to main shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H21/00—Gearings comprising primarily only links or levers, with or without slides
    • F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
    • F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
    • F16H21/18—Crank gearings; Eccentric gearings
    • F16H21/36—Crank gearings; Eccentric gearings without swinging connecting-rod, e.g. with epicyclic parallel motion, slot-and-crank motion
    • F16H21/365—Crank gearings; Eccentric gearings without swinging connecting-rod, e.g. with epicyclic parallel motion, slot-and-crank motion with orbital gearing having a ratio of 2:1 between central gear and orbital gear

Definitions

  • the present invention relates to a so-called linear crank type reciprocating engine, and in particular, in addition to reduction of vibration, reduction of friction loss and reduction of required rigidity of a crankcase, the compactness of the engine.
  • the present invention relates to a cycloid reciprocating engine which has been improved to achieve smooth movement and the like and has been put to practical use, and a pump apparatus using this crank mechanism.
  • crankshaft In order to change the reciprocating motion of the piston into a rotational motion by the crank mechanism, the crankshaft is supported by the left and right eccentric crank members, and the planetary gear mechanism is interposed between the crankshaft and the crankcase. The planetary rod is moved in a planetary motion, and the bottom end of the piston rod moves on a straight locus.
  • Patent Document 1 JP-A-9 125981
  • the present invention has been made in view of such a background, and is reduced in size and weight, and has multiple cylinders.
  • the name of the present invention is “cycloidal reciprocating engine” because the movement of the linear crank mechanism is a cycloid motion.
  • a cycloid reciprocating engine includes a piston unit including an opposing piston that reciprocates in a cylinder, a piston rod that is integrated with the piston and extends to a crankcase, and rotational movement of the piston. And a stationary planetary gear mechanism having a pitch circle diameter of 4e in the regulating planetary gear mechanism is fixed to the crankcase, while a cranking gear mechanism is interposed between the crankshaft and the piston unit.
  • the rotation eccentric disk with an eccentricity e including a planetary gear with a pitch circle diameter of 2 e is coaxially arranged with the crank pin on the crankshaft so that the center of the planetary gear can rotate, and the rotation eccentric disk is placed at the lower end of the piston rod.
  • the engine is a unit engine with a combination of two cylinders arranged horizontally facing each other, and a unit component engine consisting of two unit unit engines connected in series to form four cylinders opposed horizontally. One or a plurality of components are connected to each other, and the pistons facing each unit engine are configured to share a mouth end.
  • unit angle of the unit engine in the unit component engine is characterized by 180.degree.
  • the cycloid reciprocating engine according to claim 2 is configured such that the unit component engine is connected to other members at an integral structure portion of a crankshaft positioned between the unit unit engines. It is characterized by being configured to transmit power.
  • the cycloid reciprocating engine according to claim 3 is such that the piston has a flat head shape with a short crankshaft direction. It is characterized by this.
  • the cycloid reciprocating engine according to claim 4 includes, in addition to the requirements according to claim 1, 2 or 3, any two elements of the piston unit, the crankshaft, and the cylinder, or all of them. Between elements, it is characterized by having a linear motion error tolerance structure that corresponds to and allows the linear motion error of the piston unit.
  • the cycloid reciprocating engine according to claim 5 has sufficient clearance between the piston unit and the cylinder with respect to the linear motion error allowable structure. It consists of
  • the cycloid reciprocating engine according to claim 6 is configured such that the rotational eccentricity disk of the restriction planetary gear mechanism is It is characterized by being mounted via a movable block provided with a slight operating clearance in a direction perpendicular to the cylinder sliding direction.
  • the cycloid reciprocating engine according to claim 7 is configured so that the rod end of the piston unit is divided into two parts, and the piston unit as a whole has a rod end. It is characterized by being configured to be slightly refractable at the border.
  • the cycloid reciprocating engine according to claim 8 is integrated with each opposing piston in the unit unit engine as an opposing piston. It is characterized by being formed.
  • the cycloid reciprocating engine according to claim 9 is the claim 1, 2, 3, 4, 5, 6, 7 or
  • crank web of the cycloidal reciprocating engine is characterized in that it is supported by a crankcase on its peripheral surface.
  • the base combination is configured as a horizontally opposed 4-cylinder cylinder
  • the connecting parts of the crankshaft between the unit component engines are connected to each other in the unit component engine connection part.
  • the crankshaft has a predetermined phase difference (180 ° ⁇ ).
  • the cycloid reciprocating engine according to claim 11 is characterized in that the claim 1, 2, 3, 4, 5, 6, 7, 8,
  • the transmission shaft of the cycloidal reciprocating engine is characterized in that those taken out from each unit component engine are connected together.
  • the reciprocating mass inertial force and the inertia torque are unbalanced, leaving only the crank torque due to the reciprocating mass inertia as an unbalancer, and divided by each piston and cylinder. It is characterized in that it is configured so as to be balanced dynamically by smoothing the crank torque generated by the expansion force generated in the working chamber.
  • the cycloid reciprocating engine according to claim 13 is characterized in that the claim 1, 2, 3, 4, 5, 6, 7, 8, 9,
  • end balancers are provided at both ends of the crankshaft, and cranks located at the center of each unit engine It is characterized in that it is configured so as to be dynamically balanced by a transmission shaft counter balancer that transmits power to the outside at the center of the shaft.
  • the cycloid reciprocating engine according to claim 14 is characterized in that the claim 1, 2, 3, 4, 5, 6, 7, 8,
  • the inertia force of the reciprocating mass and the unbalance of the inertia torque are as follows:
  • the cycloid reciprocating engine according to claim 15 is characterized in that the claim 1, 2, 3, 4, 5, 6, 7, 8,
  • the pump device according to claim 17 is used in the cycloid reciprocating engine according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13 or 14. It is characterized by the use of a crank mechanism.
  • the power transmission part is an integral part of the crankshaft, there is almost no so-called twist of the crankshaft, and a well-balanced engine can be obtained.
  • the cylinder interval can be designed to be narrow, and the length of the piston unit can be shortened when the stroke is the same as compared with the circular piston type.
  • the size in the cylinder direction (engine height) can also be reduced, and the overall engine can be compact.
  • the flat piston head is suitable for absorbing the slight shaking of the center of the rotating eccentric disk in the direction perpendicular to the crankshaft.
  • the piston unit having a flat piston head can be formed into a flat plate shape as a whole, and even if manufactured by a method such as light alloy forging, it is easy to manufacture and can be easily downsized. Can be achieved.
  • each balancer acts in a complex manner and vibrates during operation. Noise and the like can be reduced.
  • the difference in phase angle between unit units is set to a predetermined value to eliminate unbalanced reciprocating mass and reduce vibration. can do.
  • the force received by the piston can be efficiently converted into a rotational motion, and the piston unit reciprocates while taking a linear locus, whereby the piston
  • the loss due to friction between the cylinder and the cylinder surface can be reduced and the thermal efficiency can be increased.
  • FIG. 1 is a perspective view and a cross-sectional view showing a horizontally opposed four-cylinder cycloid reciprocating engine according to the present invention.
  • FIG. 2 is a transverse sectional view showing a horizontally opposed four-cylinder cycloid reciprocating engine according to the present invention.
  • FIG. 3 is a longitudinal sectional view showing a horizontally opposed four-cylinder cycloid reciprocating engine according to the present invention.
  • FIG. 4 is a perspective view showing a part of a piston unit and a crankshaft used in a horizontally opposed cycloidal reciprocating engine according to the present invention, and an embodiment including an example of a linear motion tolerance structure It is.
  • Fig. 7 is a transverse sectional view and an explanatory diagram of the return mass of the horizontally opposed 8-cylinder cycloid reciprocating engine according to the present invention.
  • FIG. 8 is a longitudinal sectional view showing a horizontally opposed 8-cylinder cycloid reciprocating engine according to the present invention.
  • FIG. 9 A longitudinal sectional view showing the positional relationship among a piston unit, a crankshaft, and a transmission shaft used in a horizontally opposed 8-cylinder cycloid reciprocating engine according to the present invention.
  • FIG. 10 An explanatory diagram of the balance of inertia force and torque of the reciprocating mass of the horizontally opposed 8-cylinder cycloid reciprocating engine according to the present invention.
  • FIG. 11 is a cross-sectional view showing a horizontally opposed 12-cylinder cycloid reciprocating engine according to the present invention and an explanatory diagram of reciprocating mass.
  • FIG. 13 is a longitudinal sectional view showing the positional relationship among a piston unit, a crankshaft and a transmission shaft used in a horizontally opposed 12-cylinder cycloid reciprocating engine according to the present invention.
  • a conceptual diagram showing a cycloid reciprocating engine of the present invention where (1) shows a 4-cycle engine and (2) shows a 2-cycle engine.
  • FIG. 16 It is a conceptual diagram showing a crank mechanism of a cycloid reciprocating engine of the present invention applied to a pump or a compressor.
  • FIG. 17 is a longitudinal sectional view skeletally showing an engine in which a plurality of cycloidal reciprocating engines of the present invention having different crank shafts with respect to a common transmission shaft are arranged.
  • FIG. 20 is an exploded perspective view with a focus on a movable member including the crank assembly.
  • FIG. 21 is an exploded perspective view showing an embodiment in which another crank web mechanism (independent type for each unit engine) is further adopted based on the technical idea of the crank assembly section.
  • FIG. 22 A longitudinal section showing another method for allowing a linear motion error, and embodying the basic technical idea of the structure for allowing a linear motion error.
  • FIG. 23 is an explanatory diagram showing still another method of the linear motion error allowable structure.
  • E4 unit component engine (horizontally opposed 4-cylinder cycle 1-roid reciprocating engine)
  • a valve corresponding to the specification mode is not written in the cylinder head part.
  • at least one set of an intake valve and an exhaust valve is provided.
  • a multi-valve type in which a plurality of these intake valves and exhaust valves are provided. Further, since these techniques are already well known, detailed explanations thereof are omitted.
  • the number attached to the symbol E is based on the number of cylinders. For example, the symbol E8 described later indicates that eight cylinders are provided in total.
  • the basic unit engine unit E2 is roughly divided into a crankcase 1, a crankshaft 2 supported by the crankcase 1, a piston unit 3 reciprocating in a cylinder 11 attached to the crankcase 1, and the piston.
  • the control planetary gear mechanism 4 interposed between the unit 3 and the crankshaft 2 is a main member.
  • the cycloid reciprocating engine E of the first embodiment shown in FIG. 1 and the like has a single unit component engine E4 according to claim 1, and therefore the cylinder 11 is arranged horizontally. Cylinder.
  • crankcase 1 is constituted by die casting having an appropriate strength, and the crankcase 1 is a separate cylinder so as to protrude further to the side.
  • 4 units are installed, and a cylinder head 12 is attached to each.
  • crankcase 1 is provided with a center journal bearing 13 as a bearing member in the center thereof, and a side journal bearing 14 near the front and rear outside thereof.
  • a center journal bearing 13 as a bearing member in the center thereof
  • a side journal bearing 14 near the front and rear outside thereof.
  • the explanation of the arrangement position of the side journal bearing 14 is For example, when the cycloid reciprocating engine E is used in an automobile, a motorcycle, etc., the longitudinal direction of the crankshaft 2 to be described later depends on the longitudinal direction of the automobile. Needless to say, it may be more appropriate to express it as side.
  • crankshaft 2 that is rotatably supported by such a crankcase 1.
  • the crankshaft 2 is supported by the center journal bearing 13 in a crank web 21 that also functions as a crank boss in a conventional engine as shown in the figure, and the crank web 21 is transmitted to the center thereof.
  • the gear 22 is arranged.
  • crank pin 23 is formed so as to extend from the crank web 21 force to the base side of the cylinder 11 aligned in the axial direction, and the crank pin 23 is formed at each end of the crank web 24.
  • the side journal bearing 14 provided in the crankcase 1 is rotatably supported.
  • the crank angle of the pair of crank pins 23 is 180 °.
  • crankshaft balancer 25 corresponding to the end balancer described in claim 2 is assembled at both ends of the crankshaft 2, and the balancer state is as shown in FIGS. The positions are set so as to face each other at both ends.
  • the piston unit 3 reciprocates in the cylinder 11, and the piston 31, which is a part of the piston unit 3, is provided with a piston ring 31a on its periphery in order to maintain airtightness.
  • a piston rod 32 is formed to extend from the back side of the piston 31, and the rod end 33 at the end thereof is assembled so as to be connected to the regulating planetary gear mechanism 4.
  • the rod end 33 and the regulating planetary gear mechanism 4 are assembled to each other through a rod end bearing 34 so as to be rotatable.
  • the rod end 33 is commonly attached to the piston rod 32 extending from each of the horizontally opposed pistons 31, and the pistons for the horizontally opposed two cylinders.
  • Unit 3 takes the form of an integrated so-called monoblock. Therefore, the rod end 33 is located in the center of the piston unit 3 as a part shape regardless of its name.
  • a pin-shaped connecting member is interposed between the lower end of the piston 31 and the rod end 33, so that it does not matter.
  • a circular hole portion is provided in the portion of the rod end 33, and the rod end bearing 34 is combined with the circular hole portion so as to be fitted thereinto.
  • the rod end bearing 34 is combined so that a rotation eccentric disc 41 described later is fitted therein.
  • the rod end 33 the force described in claim 1 that the pair of pistons 31 in a horizontally opposed state share the rod end 33 of the piston rod 32. This means that the center of the action position of the rod end 33 is shared. Therefore, the rod end 33 may have a structure that divides this part into two parts, and the rod end 33 is in a shared state. is there.
  • the piston unit 3 applied to FIG. 13 has a configuration in which weight reduction can be attempted while maintaining sufficient strength. That is, as shown in the end view in the figure, the upper end portion of the piston 31 and the rod end 33 are formed in a thin plate shape as a whole, and the central portion is thinned in a side view, and the peripheral portion is relatively thin. It has a thick rib shape.
  • Reference numeral 321 in the end view of FIG. 13 indicates a thin portion, and reference numeral 322 indicates a thick portion.
  • piston 31 When pursuing such a compact piston 31 and piston rod 32 and rod end 33 or a reduction in thickness, the piston 31 itself is also as shown in FIGS.
  • the surface shape of the piston head may be flat rather than circular.
  • an oval piston head shape is taken as an example.
  • the long side portion of the oval shape or the oval shape may be bulged somewhat outward.
  • Such a configuration is appropriately selected in consideration of the manufacturing accuracy and ease of manufacturing of the piston ring fitted therein.
  • the length dimension in the direction of the crankshaft 2 can be significantly reduced even in the assembled state of the engine, that is, in the unit component, as shown in FIG.
  • Fig. 19 also shows the length dimension (actual cylinder width W) in the two directions of the crankshaft when a skeleton-shaped piston head with a circular shape is applied.
  • crankshaft 2 can be reduced to about 1Z2 compared to the one using a stone.
  • the axial unbalance element of the crankshaft 2 can be more concentrated in the center and contribute to the reduction of vibration generating elements.
  • the length of the piston unit 3 can be shortened when the stroke is the same, so the dimension in the cylinder direction (engine length) can be reduced and the entire engine can be designed in a compact manner. Become.
  • the flat piston head is also suitable for absorbing slight fluctuations at the center of the rotating eccentric disk in the direction perpendicular to the crankshaft.
  • the piston unit 3 when viewed as the piston unit 3, it can be formed into a flat plate as a whole, and even if it is manufactured by a method such as light alloy forging, it is easy to achieve downsizing.
  • the rod end bearing 34 described above is directly attached to the rod end 33 portion of the piston unit 3 or may be attached via a movable block 35 as shown in FIG. Yo!
  • the movable block 35 is a rectangular plate member with four corners, and a bearing receiving hole 35a for fitting the rod end bearing 34 is provided at the center thereof. Is.
  • the movable block 35 is fitted so that the minute sliding surface 35f faces the minute sliding surface 36f of the movable block receiving hole 36 provided in the center of the piston unit 3 with a very small clearance. In the direction perpendicular to the reciprocating direction of the piston unit 3, It is configured to provide a movable block clearance 35c.
  • the rod end bearing 34 is held with respect to the piston unit 3 so as to be finely movable in a direction perpendicular to the reciprocating direction of the piston 31, so that the piston unit 3 is finely moved in the direction perpendicular to the cylinder. Even when such a force is applied, it is allowed to slide in the cylinder 11 with the allowance.
  • a movement in a case where reverse torque is generated such that an engine brake is applied can be mentioned.
  • the configuration provided with the above-described movable block 35 is an example of a linear motion error allowable structure for causing the piston 31 to smoothly reciprocate. , 23 can be adopted. As shown skeletally and exaggeratedly in FIG. 22, if the piston clearance Pc is sufficient for the cylinder and the piston 31 is exaggeratedly speaking, the sliding locus is selected up and down as shown in FIG.22 (c). It may be in the form of obtaining. If configured in this way, the smooth operation allowing the operation error, the change of the torque direction, etc. at the time of power transmission as described above becomes possible.
  • the rod end 33 part is divided into two by the center line as an example, and two piston unit elements 3F are obtained.
  • a slight dividing surface clearance Dc is provided between the dividing surfaces 33D, and the piston unit 3 as a whole is configured so that it can be somewhat refracted around this intermediate portion.
  • the piston unit 3 operates as a unit and must be assembled as a unit.
  • a retainer ring 33R that is fitted on both the left and right sides, and a circlip 33C for retaining the retainer ring 33R are fitted. Realizes an integrated assembly configuration.
  • the dividing surface 33D may be on a center line that is inclined perpendicular to the central diameter line that is orthogonal to the longitudinal direction of the piston unit 3, or may be on a center line that is inclined, not on the diameter line, and bends at the center and is divided.
  • Unit element 3F may be asymmetrical.
  • the rotating eccentric disc 41 in the regulating planetary gear mechanism 4 is rotatably fitted to the crank pin 23 via a bearing such as a crank pin bearing 23a, and the crank pin 23 is in an eccentric state.
  • the rod end 33 is fitted into the rod end 33 so as to be rotatable through the rod end bearing 34.
  • a planetary gear 42 is integrally provided on the side surface of the rotating eccentric disc 41 with the crankpin 23 and the shaft center in common, and the planetary gear 42 is fixed on the inside of the crankcase 1. The planetary movement is carried out by holding inside the ring gear 43.
  • the ratio of the pitch circle diameters of the planetary gear 42 and the stationary ring gear 43 must be 1: 2.
  • the pitch circle diameter of the stationary ring gear 43 is equal to the piston stroke (4e).
  • This transmission mechanism 5 is a member that bears a smooth power transmission between the crankshaft 2 and the outside, and balances an inertia torque T about the y-axis generated by the inertia of the reciprocating mass described later.
  • this is composed of a transmission shaft 51 for transmitting power to both sides, and a transmission gear 52 fixed thereto.
  • the transmission gear 52 of the transmission mechanism 5 serves as an output gear to transmit power to the outside.
  • a pump or compressor using the crank mechanism of the moving engine E it is used as an input gear when external motor power is transmitted to the crankshaft 2. Move.
  • the transmission mechanism 5 including a combination of the transmission gear 22 and the transmission gear 52 includes a crankshaft.
  • crankshaft 2 When viewed in the axial direction of 2, when the unit component engine E4 is used as a reference, it is preferable that the crankshaft 2 is disposed between the body structural parts, that is, between the cylinders 11. As a result, power transmission is achieved at the most rigid part of the crankshaft 2 and an assembly structure is required.In the case of the crankshaft 2, the crankshaft 2 is effectively prevented from being twisted. , In
  • the transmission mechanism 5 may be arranged at both ends of the crankshaft 2 as disclosed in a unit component engine E4 to which the flat piston type shown in FIGS.
  • the central connecting portion (between cylinders) of the unit component engine E4 is an assembly crank, and a crank pin 23 and a crank web 24 at both ends are integrally provided with a transmission gear 22.
  • the transmission shaft 51 is connected by a mating transmission gear 52.
  • this assembly structure is provided with a crank pin receiving hole 21P disposed at 180 ° on the center crank web 21 as a connecting medium, and on the other hand, A crankpin insertion portion 23P is formed at the end of the crankpin 23 that is divided into two, and the crankpin insertion portion 23P is press-fitted into the crankpin receiving hole 21P.
  • the unit unit engine E2 can be configured to be completely independent as shown in FIG. It is. That is, in this case, the central crank web 21 is divided into the applied force and the axial direction, and is composed of two members, the crank web 21A and the crank web 21B.
  • Each crank web 21A, 21B has one crank pin receiving hole 21P for receiving the crank pin 23, and when both the crank webs 21A, 21B are in the assembled state, they are shown in FIG. 21 (b).
  • each crank pin receiving hole 21P is provided at a position opposed to 180 °.
  • crankshaft 2 can be improved. Also the torsional load on the assembly portion of the crankshaft 2, that is, the crank web 21, is removed, and the crankshaft 2 is prevented from being twisted. In addition, the crankshaft 2 can be easily manufactured and the mechanism can be easily assembled. In addition, it can contribute to the smooth engagement of the planetary gears provided on the left and right
  • the transmission gear 52 meshes with the transmission gear 22 fixed to the crankshaft 2 described above, and the ratio of the number of gear teeth between the transmission gear 52 and the transmission gear 22 is such that the transmission mechanism 5 has a balancer. It depends on whether or not it has a function as a mechanism.
  • the transmission mechanism 5 is used as a balancer mechanism, which will be described later, and a unit component engine E4, a horizontally opposed 4-cylinder cycloid reciprocating engine E4, and two unit component engines E4 are connected. This is the case of a horizontally opposed 8-cylinder cycloidal reciprocating engine E8.
  • the ratio of the number of gear teeth between the transmission gear 52 and the transmission gear 22 is set to the ratio of the number of teeth of 1: 1.
  • a unit component engine E4 with N ⁇ 3 is connected (cycloid reciprocation of horizontally opposed 12 cylinders and 16 or more cylinders).
  • the ratio of the number of gear teeth between the transmission gear 52 and the transmission gear 22 can be arbitrarily set.
  • the transmission shaft 51 that supports the transmission gear 52 has two transmission shaft balancers 55 on both sides (front and rear) of the transmission gear 52 for reducing vibration and noise, which will be described later. It is attached.
  • the transmission shaft balancer 55 plays the role of the counter balancer as defined in claim 13.
  • the planetary gear 42 having a pitch circle diameter 2e is rotatably supported by the crankpin 23 via the crankpin bearing 23a, so that it is engaged with the stationary ring gear 43 and centered on the crankpin axis O.
  • the rotational eccentric shaft center O of the eccentric amount e integrally formed with the planetary gear 42 is the cylinder
  • each unit unit E2 is shown as C force C in the figure.
  • Stroke 4e linear reciprocating motion that is, cycloid motion.
  • the present invention is a horizontally opposed type cylinder arrangement sharing the mouth end 33, the opposed pistons 31 repeat the compression state and the expansion state.
  • the inner space on the rod end 33 side of the piston 31 is used as the crank chamber 10a, and the space on the head side of the piston 31 is used as the working chamber 10b.
  • the linear reciprocating motion of the piston unit 3 of the cycloidal reciprocating engine E of the present invention is as follows: the angular velocity ⁇ around the crankshaft axis of the crankshaft 2 ⁇ , the crankpin axis of the crankpin 23
  • the inertia torque T of Y, the inertia torque T around the y axis, and the inertia torque T around the X axis are based on the right-handed orthogonal coordinate system O-xyz as shown in Fig. 6 with the origin at the center of the crankshaft. Described for the coordinate system.
  • the balancer may not be symmetrically arranged with respect to the origin 0, but here, from a practical viewpoint, the apparatus structure including the balancer is symmetric with respect to the origin o.
  • the mass M is concentrated at the axial center points E and E of the rotating eccentric disc axis,
  • the crank torque caused by the force applied to the piston 31 such as the combustion chamber explosive force is smoothed. Leave inertia torque T without balancing.
  • M E edE (MARA JA + MBRBCIBJ ( 1 )
  • crankshaft balancer 25 of each unit component engine E4 is eliminated, and a common crank web-like connecting plate 26 is provided on the end side of the unit, as shown in Figs.
  • each transmission gear 52 is connected to a common transmission shaft 51 so as to mesh with the transmission gear 22 provided at the center of each unit component engine E4. Attach to. Furthermore, a transmission shaft balancer 55 for suppressing vibration is attached to the transmission shaft 51.
  • the inertia torque T, the inertia torque T about the y axis, and the inertia torque T about the X axis are based on the right-handed orthogonal coordinate system O-xyz as shown in Fig. For the quasi-coordinate system.
  • the balancer may not be symmetrically arranged with respect to the origin 0, but here, from a practical point of view, the structure of the apparatus including the balancer is symmetric with respect to the origin 0.
  • mass M is the axial center point E, E, E, E
  • d, d, and d be the distances in the direction of the rotational axis of the center of gravity of M, respectively.
  • crankshaft balancer of both unit component engines E4 is abolished, and a common crank web-like connecting board 26 is provided at the end side.
  • a common crank web-like connecting board 26 is provided at the end side.
  • three unit component institutions E4 are connected.
  • each transmission gear 52 is connected to a common transmission shaft so as to mesh with transmission gear 22 provided at the center of each unit component engine E4. Attach to 51. Since the transmission mechanism 5 does not have a function as a balancer mechanism, a transmission shaft balancer for suppressing vibrations at both ends of the transmission shaft 51 is not attached.
  • the imbalance between the back and forth mass inertia force and the inertia torque in the horizontally opposed 16-cylinder cycloid reciprocating engine E (4-cycle engine) is strictly the same as that of the horizontally opposed 4- and 8-cylinder cycloid reciprocating engines E4 and E8.
  • a plurality of horizontally opposed n-cylinder cycloid reciprocating engines E with different crankshafts 2 may be configured such that their transmission gears 22 are held together on a common transmission shaft 51.
  • the transmission shaft 51 itself does not have a balancer function, the number of teeth of the transmission gear 52 can be made arbitrary, and different crankshafts 2
  • each horizontally opposed 12-cylinder reciprocating piston engine E12 equipped with so as not to buffer each other Specifically, as shown in FIG. 17, the transmission gear 22 is engaged with the common transmission shaft 51 from both the upper and lower sides. The arrangement is such that the transmission shaft 51 is sandwiched.
  • the cycloid reciprocating engine E has a crank according to the configuration of each engine from the viewpoint of dynamics in order to eliminate the imbalance that is the cause of vibration-noise in the operating state.
  • a crankshaft balancer 25 at both ends of the shaft 2 and a transmission shaft balancer 55 at both ends of the transmission shaft 51 are appropriately provided.
  • the present invention is basically of the horizontally opposed piston type, a part of the configuration can be used to realize a non-horizontal opposed type as shown in FIG.
  • the one shown in FIG. 24 is of a flat piston type and has sufficient novelty itself.
  • symbol, etc. since it can use in common with the already described Example, detailed description is abbreviate
  • a cycloid reciprocating engine E employing such a mechanism can also be expected to be put into practical use.
  • the cycloid reciprocating engine E described above can be used as a power source of a transport machine, a power source of a generator, and the like that generate output using fossil fuel or the like. Furthermore, it is also possible to use as a pump device by obtaining power from the outside using the crank mechanism of the cycloid reciprocating engine E. Each operation mode will be described below.
  • the pump device used in this specification means a device that continuously lifts, presses, compresses or discharges fluid by mechanical or other means. Both the pump and the compressor are used. Is included.
  • the cylinder head 12 is provided with an intake hole 15a and an intake valve 15b for opening and closing the intake hole 15a. Further, an exhaust hole 16a and an exhaust valve 16b for opening and closing the exhaust hole 16a are provided, and a spark plug P is further provided.
  • a fuel injection nozzle is provided instead of the spark plug P.
  • valve operating mechanism As for the number of supply / exhaust valves, etc., at least two of the exhaust valve 16b and the intake valve 15b are necessary, but it may be a multi-valve type, but the description thereof will be omitted.
  • the rotation output obtained by this is taken out from the transmission gear 22 via the transmission gear 52.
  • the intake hole 15a opens to the side of the cylinder 11 closer to the crankcase 1, and the crank chamber 10a and the working chamber 10b closer to the crank are connected to the scavenging hole.
  • the exhaust hole 16 a having a timing earlier than the scavenging hole 17 is opened on the side surface of the cylinder 11.
  • the piston 31 includes a piston skirt 31b that extends downward from the head of the piston 31 so as to open and close the exhaust hole 16a and the scavenging hole 17.
  • crank mechanism of the cycloid reciprocating engine of the present invention When the crank mechanism of the cycloid reciprocating engine of the present invention is applied to a compressor and a pump, first, power from the outside is obtained through the transmission gear 52 and the crankshaft 2 is rotated as shown in FIG. As a result, the piston 31 reciprocates and sucks or sucks in a desired medium such as gas or liquid from the intake hole 15a in the cylinder 11, and the piston 31 moves up in the next process to compress the desired medium. And is discharged from the exhaust hole 16a. In such a case, a one-way valve is sufficient for the intake valve 15b and the exhaust valve 16b.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Reciprocating Pumps (AREA)
  • Transmission Devices (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

L'invention concerne un moteur alternatif cycloïdal fournissant un moteur de travail utilisant un mécanisme de vilebrequin linéaire suffisamment pratique grâce à des améliorations d'ordre général en incluant l'utilisation d'un système poly-cylindrique et l'application de son agencement de cylindre, l'application de son élément équilibreur, et l'application de la structure de l'arbre de vilebrequin. Le moteur alternatif cycloïdal (E) est caractérisé en ce que le moteur de travail - utilisant une unité de piston (3) intégrant un piston (31), et une tige de piston (32), et un prétendu vilebrequin linéaire pour le mouvement en va-et-vient linéaire de la tige de piston (31), en réglant un mécanisme d'engrenage planétaire (4) afin de convertir le mouvement du piston en mouvement de rotation - inclut une combinaison d'une disposition à deux cylindres horizontalement opposés, en tant qu'unité moteur (E2), et quatre cylindres horizontalement opposés concaténant deux unités, en tant qu'unité de composant moteur (E4), et le moteur est constitué d'un composant ou par concaténation d'une pluralité de composants.
PCT/JP2007/064095 2006-07-18 2007-07-17 MOTEUR ALTERNATIF cycloïdAL ET POMPE EMPLOYANT CE MÉCANISME DE VILEBREQUIN Ceased WO2008010490A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2008525862A JPWO2008010490A1 (ja) 2006-07-18 2007-07-17 サイクロイド往復動機関並びにこのクランク機構を用いたポンプ装置

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JP2006-195884 2006-07-18
JP2006195884 2006-07-18

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WO2008010490A1 true WO2008010490A1 (fr) 2008-01-24

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EP2177758A1 (fr) * 2008-10-15 2010-04-21 GNC Galileo S.A. Mécanisme de transformation de mouvement circulaire en mouvement translationnel pour commander les pistons d'un compresseur pour gaz naturel comprimé
CN102052279A (zh) * 2011-01-21 2011-05-11 中国石油化工集团公司 高转速活塞式气体压缩机
WO2011030237A3 (fr) * 2009-09-10 2011-05-26 Gea Niro Soavi S.P.A. Homogénéisateur haute-pression à unité d'engrenage de réduction épicycloïdal
CN103343713A (zh) * 2013-07-26 2013-10-09 白云龙 一种新型内燃机的水平对置活塞、圆缺口曲柄、曲轴及水平对置缸体
CN104153964A (zh) * 2014-08-29 2014-11-19 上海上隆压缩机制造有限公司 一种往复式氮氢气压缩机
JP2015532963A (ja) * 2012-09-25 2015-11-16 − グスタフ ライサー、ハインツ 軌道周回プラネタリギアリングシステム及びそれを採用した内燃機関
JP5843184B1 (ja) * 2014-12-25 2016-01-13 Ｚメカニズム技研株式会社 Ｘｙ分離クランク機構を備えた駆動装置
WO2016016617A1 (fr) * 2014-07-28 2016-02-04 Oxford Two Stroke Limited Moteur à combustion interne
WO2016140323A1 (fr) * 2015-03-03 2016-09-09 Ｚメカニズム技研株式会社 Dispositif d'entrainement ayant un mécanisme manivelle de séparation xy
WO2016139751A1 (fr) * 2015-03-03 2016-09-09 Ｚメカニズム技研株式会社 Dispositif d'entraînement équipé d'un mécanisme de manivelle à séparation xy
JP2016166598A (ja) * 2015-03-03 2016-09-15 Ｚメカニズム技研株式会社 Ｘｙ分離クランク機構を備えた駆動装置
JP2017501341A (ja) * 2013-12-12 2017-01-12 北京中清能発動機技術有限公司 往復式プランジャポンプとその筐体、クランク円形スライダ機構と円形スライダ、軸受ハウジング、クランクシャフトケースの上カバー及びプランジャシート
WO2017132492A3 (fr) * 2016-01-27 2017-08-31 Ge Oil Gas Compression Systems Llc Prévention de la déformation de cadre sur un compresseur alternatif
AT518769B1 (de) * 2016-08-18 2018-01-15 Ecool Advanced Urban Eng Gmbh Brennkraftmaschine
EP2604889A4 (fr) * 2010-07-02 2018-03-14 Beijing Sinocep Engine Technology Co., Ltd Mécanisme de manivelle à bloc circulaire coulissant, parties de ce mécanisme et équipement résultant
WO2018123029A1 (fr) * 2016-12-28 2018-07-05 Ｚメカニズム技研株式会社 Appareil d'entraînement doté d'un mécanisme de mouvement linéaire oscillant
JP2021105393A (ja) * 2019-12-26 2021-07-26 竹本　護 無振動レシプロエンジン
DE102011009546B4 (de) 2011-01-27 2022-02-10 Adalbert Kieper Viertakt-Brennkraftmaschine mit Vorverdichtung in Zylindern
US20220136493A1 (en) * 2007-08-09 2022-05-05 Optimum Power Technology, L.P. Apparatuses, Systems, and Methods for Improved Performance of a Pressurized System
WO2023068219A1 (fr) * 2021-10-18 2023-04-27 株式会社日本ビデオセンター Structure de manivelle et moteur alternatif pourvu de ladite structure de manivelle
JP2023060794A (ja) * 2021-10-18 2023-04-28 株式会社日本ビデオセンター クランク構造及び当該クランク構造を備えたレシプロエンジン

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US11692533B2 (en) * 2007-08-09 2023-07-04 Optimum Power Technology, L.P. Apparatuses, systems, and methods for improved performance of a pressurized system
US20220136493A1 (en) * 2007-08-09 2022-05-05 Optimum Power Technology, L.P. Apparatuses, Systems, and Methods for Improved Performance of a Pressurized System
EP2177758A1 (fr) * 2008-10-15 2010-04-21 GNC Galileo S.A. Mécanisme de transformation de mouvement circulaire en mouvement translationnel pour commander les pistons d'un compresseur pour gaz naturel comprimé
US8979696B2 (en) 2009-09-10 2015-03-17 Gea Mechnical Equipment Italia S.p.A. High-pressure homogenizer with an epicyclic reduction gear unit
WO2011030237A3 (fr) * 2009-09-10 2011-05-26 Gea Niro Soavi S.P.A. Homogénéisateur haute-pression à unité d'engrenage de réduction épicycloïdal
EP2604889A4 (fr) * 2010-07-02 2018-03-14 Beijing Sinocep Engine Technology Co., Ltd Mécanisme de manivelle à bloc circulaire coulissant, parties de ce mécanisme et équipement résultant
US10012224B2 (en) 2010-07-02 2018-07-03 Beijing Sinocep Engine Technology Co., Ltd. Crank circular sliding block mechanism, parts thereof, and equipment therefrom
CN102052279B (zh) * 2011-01-21 2014-04-02 中国石油化工集团公司 高转速活塞式气体压缩机
CN102052279A (zh) * 2011-01-21 2011-05-11 中国石油化工集团公司 高转速活塞式气体压缩机
DE102011009546B4 (de) 2011-01-27 2022-02-10 Adalbert Kieper Viertakt-Brennkraftmaschine mit Vorverdichtung in Zylindern
JP2015532963A (ja) * 2012-09-25 2015-11-16 − グスタフ ライサー、ハインツ 軌道周回プラネタリギアリングシステム及びそれを採用した内燃機関
CN103343713A (zh) * 2013-07-26 2013-10-09 白云龙 一种新型内燃机的水平对置活塞、圆缺口曲柄、曲轴及水平对置缸体
CN103343713B (zh) * 2013-07-26 2016-06-22 白云龙 一种内燃机
JP2017501341A (ja) * 2013-12-12 2017-01-12 北京中清能発動機技術有限公司 往復式プランジャポンプとその筐体、クランク円形スライダ機構と円形スライダ、軸受ハウジング、クランクシャフトケースの上カバー及びプランジャシート
US10473098B2 (en) 2013-12-12 2019-11-12 Beijing Sinocep Engine Technology Co., Ltd. Reciprocating plunger pump and its engine body, the slider crank mechanism and the slide block, the bearing seat, the crankcase upper cover and the plunger seat
WO2016016617A1 (fr) * 2014-07-28 2016-02-04 Oxford Two Stroke Limited Moteur à combustion interne
CN106715867A (zh) * 2014-07-28 2017-05-24 牛津两冲程有限公司 内燃机
US10112693B2 (en) 2014-07-28 2018-10-30 Joost Engines Ltd Internal combustion engine
CN104153964A (zh) * 2014-08-29 2014-11-19 上海上隆压缩机制造有限公司 一种往复式氮氢气压缩机
WO2016103414A1 (fr) * 2014-12-25 2016-06-30 Ｚメカニズム技研株式会社 Dispositif d'entraînement équipé d'un mécanisme de manivelle à séparation xy
JP5843184B1 (ja) * 2014-12-25 2016-01-13 Ｚメカニズム技研株式会社 Ｘｙ分離クランク機構を備えた駆動装置
US10138807B2 (en) 2015-03-03 2018-11-27 Z Mechanism Technology Institute Co., Ltd. Drive device provided with XY-separating crank mechanism
JPWO2016139751A1 (ja) * 2015-03-03 2017-04-27 Ｚメカニズム技研株式会社 Ｘｙ分離クランク機構を備えた駆動装置
WO2016140323A1 (fr) * 2015-03-03 2016-09-09 Ｚメカニズム技研株式会社 Dispositif d'entrainement ayant un mécanisme manivelle de séparation xy
WO2016139751A1 (fr) * 2015-03-03 2016-09-09 Ｚメカニズム技研株式会社 Dispositif d'entraînement équipé d'un mécanisme de manivelle à séparation xy
JP2016166598A (ja) * 2015-03-03 2016-09-15 Ｚメカニズム技研株式会社 Ｘｙ分離クランク機構を備えた駆動装置
GB2562936A (en) * 2016-01-27 2018-11-28 Ge Oil & Gas Compression Systems Llc Preventing deformation of frame on a reciprocating compressor
WO2017132492A3 (fr) * 2016-01-27 2017-08-31 Ge Oil Gas Compression Systems Llc Prévention de la déformation de cadre sur un compresseur alternatif
US10087921B2 (en) 2016-01-27 2018-10-02 Ge Oil & Gas Compression Systems, Llc Preventing deformation of frame on a reciprocating compressor
AT518769A4 (de) * 2016-08-18 2018-01-15 Ecool Advanced Urban Eng Gmbh Brennkraftmaschine
AT518769B1 (de) * 2016-08-18 2018-01-15 Ecool Advanced Urban Eng Gmbh Brennkraftmaschine
US10519853B2 (en) 2016-12-28 2019-12-31 Z Mechanism Technology Institute Co., Ltd. Driving apparatus with swinging linear motion mechanism
JP6376634B1 (ja) * 2016-12-28 2018-08-22 Ｚメカニズム技研株式会社 揺動直線運動機構を備えた駆動装置
WO2018123029A1 (fr) * 2016-12-28 2018-07-05 Ｚメカニズム技研株式会社 Appareil d'entraînement doté d'un mécanisme de mouvement linéaire oscillant
JP2021105393A (ja) * 2019-12-26 2021-07-26 竹本　護 無振動レシプロエンジン
WO2023068219A1 (fr) * 2021-10-18 2023-04-27 株式会社日本ビデオセンター Structure de manivelle et moteur alternatif pourvu de ladite structure de manivelle
JP2023060794A (ja) * 2021-10-18 2023-04-28 株式会社日本ビデオセンター クランク構造及び当該クランク構造を備えたレシプロエンジン

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