WO2009133893A1 - Moteur à vapeur polycylindrique - Google Patents

Moteur à vapeur polycylindrique Download PDF

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Publication number
WO2009133893A1
WO2009133893A1 PCT/JP2009/058364 JP2009058364W WO2009133893A1 WO 2009133893 A1 WO2009133893 A1 WO 2009133893A1 JP 2009058364 W JP2009058364 W JP 2009058364W WO 2009133893 A1 WO2009133893 A1 WO 2009133893A1
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WO
WIPO (PCT)
Prior art keywords
control
rotation output
cylinder
reciprocating
steam
Prior art date
Application number
PCT/JP2009/058364
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English (en)
Japanese (ja)
Inventor
勝重 中村
Original Assignee
三鷹光器株式会社
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 三鷹光器株式会社 filed Critical 三鷹光器株式会社
Publication of WO2009133893A1 publication Critical patent/WO2009133893A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • 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
    • F01B25/00—Regulating, controlling, or safety means
    • F01B25/02—Regulating or controlling by varying working-fluid admission or exhaust, e.g. by varying pressure or quantity
    • F01B25/08—Final actuators
    • F01B25/10—Arrangements or adaptations of working-fluid admission or discharge valves
    • 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
    • F01B29/00—Machines or engines with pertinent characteristics other than those provided for in preceding main groups
    • F01B29/08—Reciprocating-piston machines or engines not otherwise provided for
    • F01B29/10—Engines
    • F01B29/12—Steam engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/04—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces

Definitions

  • the present invention relates to a multi-cylinder steam engine.
  • the present invention has been made paying attention to such conventional technology, and provides a multi-cylinder steam engine that can be used for power generation using steam and can be reduced in size.
  • a multi-cylinder steam engine is a rotary output portion having a cylindrical side surface, and is rotatable around a virtual axis along a longitudinal direction passing through the center of a cross section. And an endless cam groove formed so as to make one side of the side surface of the rotation output portion around the virtual axis, and the rotation output portion arranged in a predetermined radial direction of the cross section of the rotation output portion.
  • a plurality of reciprocating steam drive units interacting with the output unit, each having a piston rod that reciprocates in a direction parallel to the virtual axis, and an engagement unit fixed to the piston rod, the cam A control unit having information for controlling a reciprocating motion of each of the plurality of reciprocating steam driving units, and a control unit which engages with a groove and applies a driving force to the rotation output unit, and a side surface of the rotation output unit.
  • the information elements of the control information are distributed and fixed so as to make a round around the imaginary axis, and the plurality of reciprocating steam driving units are reciprocated in conjunction with each other based on the information of the information elements. Accordingly, the rotation output unit continuously rotates.
  • each of the reciprocating steam driving units further includes a cylinder in which a pair of supply ports and discharge ports are formed adjacent to each other at both ends, and a piston that reciprocates in the cylinder. And the piston rod integrally connected to the piston and projecting outward from the cylinder, and reciprocating at both ends of the cylinder, respectively, and alternately closing and closing the supply port and the discharge port at both ends of the cylinder by different combinations. And a pair of control valves.
  • the information element of the control unit is an endless control groove formed on a side surface of the rotation output unit so as not to intersect the cam groove, The reciprocating motion is controlled by engaging the control valve with the control groove.
  • FIG. 1 is a plan view of a multi-cylinder steam engine according to an embodiment of the present invention.
  • FIG. 2 is a partial cross-sectional view of a multi-cylinder steam engine viewed from the direction indicated by the arrow DA in FIG. 1.
  • FIG. 3 is a partial cross-sectional view corresponding to FIG. 2, illustrating a state in which the rotation output unit is rotated 90 ° from FIG. 2.
  • FIG. 4 is a partial cross-sectional view corresponding to FIG. 3, illustrating a state where the rotation output unit is rotated 90 ° from FIG. 3.
  • the side view which shows a rotation output part.
  • the developed view of the side surface of the rotation output part which shows the curve of a cam groove and a control groove.
  • the enlarged view which shows a cam follower and a cam groove.
  • the expanded sectional view which shows the cylinder part of a cylinder.
  • FIGS. 1 is a plan view of the whole (the center pulley and the like are not shown)
  • FIG. 2 is a partial sectional view as seen from the direction of the arrow DA in FIG. 1 (the central part is not shown)
  • FIG. FIG. 4 is a partial cross-sectional view showing a state where the rotation output portion is further rotated by 90 ° from FIG. 2 to 4 are all in the same viewing direction.
  • the multi-cylinder steam engine of this embodiment is composed of one rotation output unit 1 and four reciprocating steam drive units 2.
  • the rotation output portion 1 has a cylindrical shape that is long in the vertical direction, and is supported by a pair of upper and lower bearings 3 so as to be rotatable in a fixed direction R around an axis X passing through the center of the cross section.
  • the bearing 3 is provided with a bearing mechanism (not shown).
  • four reciprocating steam driving units 2 are arranged at the quarter positions of the cross section.
  • the reciprocating steam drive unit 2 has a known structure generally used as a steam engine except for the control structure of the control valve 4 by a control groove 22 as a control unit described later.
  • control of the control valve is more important for steam engines because the driving force changes continuously compared to engines that use explosive power. Therefore, the multi-cylinder steam engine of the present invention has a control structure in which a plurality of steam engines are stably linked as will be described later.
  • a piston 6 that can reciprocate up and down is accommodated in a cylinder 5 having a cylindrical section.
  • a piston ring 7 that slides with the inner surface of the cylinder 5 is provided on the side surface of the piston 6.
  • a piston rod 8 extending upward in a state parallel to the axis X of the rotation output unit 1 is integrally coupled to the piston 6.
  • the piston rod 8 passes through a cylindrical portion 9 provided at the upper part of the cylinder 5 and protrudes to the upper part of the cylinder 5.
  • a plurality of balls 10 for smoothly moving the piston rod 8 up and down are held on the inner surface of the cylindrical portion 9 (see FIG. 9).
  • the cylinder portion 9 has a certain length and holds the piston rod 8 vertically.
  • a control passage portion 11 is formed outside the cylinder 5 along the vertical direction. On the side surface of the cylinder 5 corresponding to the control passage portion 11, one set is formed in each of the upper and lower ends with the supply port 12 and the discharge port 13 being adjacent to each other. In each set, the supply port 12 is positioned on the outer side and the discharge port 13 is positioned on the inner side in the vertical direction (see FIG. 5).
  • control valves 4 are accommodated in a state where they are coupled by a control rod 14.
  • the control rod 14 is also parallel to the axis X of the rotation output unit 1.
  • the control rod 14 protrudes upward through the upper wall of the control passage portion 11.
  • the control valve 4 reciprocates up and down in a pair of upper and lower sides. When the control valve 4 moves upward, the control valve 4 closes the upper supply port 12 and the lower discharge port 13. When the control valve 4 moves downward, the upper discharge port 1. And the lower supply port 12 is closed.
  • a supply pipe 15 for supply-side steam A is connected to the upper and lower ends of the control passage section 11, and a discharge pipe 16 for discharge-side steam B is connected to the center. 2 to 5, the supply side water vapor A is shown in black, and the discharge side water vapor B is shown in a dotted grid.
  • the rotation output unit 1 has a cylindrical shape that is long in the vertical direction, and the vertical direction is rotatably supported by the bearing 3 as described above.
  • a center pulley 18 on which four V-groove belts 17 can be wound up and down is attached to the upper portion of the rotation output unit 1.
  • the center pulley 18 rotates in a fixed direction R integrally with the rotation output unit 1.
  • a generator 19 is supported on the four sides of the rotation output unit 1, and the V-groove belt 17 is wound around a pulley 20 at the end of the rotation shaft.
  • the generator 19 is large enough to be used as an engine accessory for an automobile, and even if the entire size of the multi-cylinder steam engine is horizontal, the generator 19 is compact enough to enter the engine room of an automobile.
  • a cam groove 21 for converting the reciprocating motions of the plurality of reciprocating steam driving units 2 into rotational motions is formed on the cylindrical side surface of the rotational output unit 1.
  • the cam groove 21 is formed by a modified sine curve (see FIG. 7) obtained by correcting the sine curve, and is associated with the radial position ⁇ of the rotation output unit 1 (a declination of cylindrical coordinates). Therefore, the deformed sine curve of the cam groove 21 is a non-stop and endless continuous curve, and when the rotation output portion 1 makes one rotation, the member engaged with the cam groove 21 reciprocates once in the vertical direction.
  • the cam groove 21 is formed in a state in which the ratio in the vertical direction is greatly enlarged.
  • the inclination angle ⁇ with respect to the axis X (piston rod 8) at the stroke center position of the cam groove 21 is set. It has become very small.
  • This angle ⁇ is preferably 45 ° or less (in this embodiment, about 20 °).
  • a control groove 22 is formed below the rotation output unit 1. That is, according to the present invention, the control groove 22 and the cam groove 21 are integrally formed so as to be fixed to the rotation output portion 1. This feature is important for multi-cylinder steam engines. By actively controlling the reciprocating steam drive units to be linked via a common rotation output unit 1, the engine starts smoothly and generates stable torque. Can be maintained.
  • control groove is a control unit having control information for controlling the reciprocating motion of each reciprocating steam drive unit 2 and is associated with the control information so as to go around the side surface of the rotation output unit 1.
  • Information elements are fixed in distribution.
  • control information associated with the radial position ⁇ of the rotation output unit 1 is one-dimensionally distributed and fixed on the side surface of the rotation output unit.
  • control information elements are the control groove 22 and its position (Z) in the rotation main axis direction.
  • the control information associated with the radial position ⁇ is transmitted to the control valve 4 of the reciprocating steam drive unit 2 via the driven unit 24 engaged with the control groove 22 to directly control the stroke position.
  • each reciprocating steam drive unit 2 and the position information of the piston 6 are transmitted to the rotation output unit 1 via each cam follower (engagement unit) 23 engaged with the cam groove 21 and fixed to the rotation output unit 1.
  • Control of the control valve 4 that is optimal for the position of the piston of the reciprocating steam drive unit 2 is performed via the control groove 22 and the driven portion 24 fixed to the piston rod 8.
  • the control groove 22 as the control unit is formed integrally with the rotation output unit 1 together with the cam groove 21 to control the reciprocating motion based on the control information corresponding to the position of the cam groove 21 in the radial direction.
  • the interlocking state with the other reciprocating steam drive unit is stable due to the degree of freedom such as a gap in the engagement state with the rotation output unit. In other words, stable control may become difficult during start-up or steady operation, and the control mechanism of each control valve 4 becomes complicated.
  • each reciprocating steam drive unit 2 is controlled to reciprocate based on control information corresponding to the radial position. Since the driving force is transmitted to the rotation output unit 1 via the cam follower 23, the plurality of reciprocating steam driving units 2 can be controlled uniformly with a simple configuration.
  • control information of the cam groove 21 and the control unit are both associated with the radial position ⁇ , the control unit is changed even if the number and arrangement of the reciprocating steam driving units 2 are changed. There is no need.
  • control groove 22 has a single continuous control curve that is formed at a position separated from the cam groove 21 so as not to intersect with the cam groove 21.
  • the control curve has a local maximum portion and a local minimum portion in the rotation main shaft direction (Z) when the radial position ⁇ is near 0 ° (360 °) and 180 °.
  • the shape of the control curve of the control groove corresponds to the position of the control valve 4, so it is not similar to the modified sine curve of the cam groove 21, and greatly deviates from the sine curve, and the maximum portion (near 0 °, 360 °) and The minimum part (near 180 °) stops and becomes flat.
  • the displacement difference between the top dead center and the bottom dead center of the control groove 22 corresponds to the reciprocating stroke of the control valve 4 in the vertical direction, and the cam groove 21 is in a curved state that is upside down. (See FIG. 7).
  • the control valve 4 controlled by the control groove 22 is controlled so that the rotation output unit 1 rotates in a constant direction R.
  • cam followers 23 extending in the horizontal direction are attached to the upper ends of the piston rods 8 projecting upward from the cylinders 5 of the four reciprocating steam driving units 2, and each cam follower 23 engages with a corresponding position of the cam groove 21. ing. The cam follower 23 is engaged with the side wall of the cam groove 21 while rotating, and the sliding resistance with the cam groove 21 is small.
  • a driven portion 24 extending in the horizontal direction is also attached to the upper end of the control rod 14 protruding upward from the control passage portion 11, and the tip of the driven portion 24 is engaged with the corresponding position of the control groove 22.
  • the driven portion 24 has a detoured shape so as not to interfere with the cylindrical portion 9.
  • the tip of the follower 24 is also engaged with the side wall of the control groove 22 while rotating, and the sliding resistance with the control groove 22 is small.
  • Supply-side steam A sent from a steam generator (not shown) is supplied to the four reciprocating steam driving units 2 via the supply pipe 15.
  • the control valves 4 of the four reciprocating steam driving units 2 have different stroke positions when the driven portion 24 of the control rod 14 is engaged with the control groove 22. For example, as shown in FIG. In the cylinder 5, when either the upper or lower discharge port 13 is closed by the control valve 4 and the supply port 12 is opened, the supply port 12 is closed by the control valve 4 on the opposite side and the discharge port 13 is reversed. Is released.
  • the supply-side water vapor A is supplied from the supply port 12 to the cylinder 5 to move the piston 6 from one end side to the other end side, and at the other end side of the piston 6 gas (discharge-side water vapor). B) is discharged from the supply port 12 through the discharge pipe 16 to the outside.
  • the pistons 6 of the four reciprocating steam driving units 2 are simultaneously moved in a preset direction by the pressure of the supply-side steam A.
  • the piston 6 repeats the above operation, and the piston rod 8 reciprocates to continuously rotate the rotation output unit 1 in a predetermined direction R with a predetermined rotational torque.
  • the control valve 4 is controlled by the engagement of the control groove 22 formed on the side surface of the rotation output portion 1 and the driven portion 24 provided on the control rod 14, the cam follower 23 of the piston rod 8 that pushes the cam groove 21. And the movement of the control valve 4 that controls the moving direction of the piston 6 can be completely synchronized, and there is no deviation in the movement of both.
  • the rotation output unit 1 can be reliably rotated even if the pressure of the supply-side water vapor A is small.
  • the stroke amount of the piston rod 8 must be increased accordingly.
  • the rotation output unit 1 continuously rotates in a certain direction R, the rotational torque is transmitted to the four generators 19 via the V-groove belt 17, and power can be generated by each generator 19.
  • the position (Z) of the control curve in the rotation main axis direction of the control groove 22 as the control unit is the control information, but for example, the depth of the groove may be the control information.
  • the distribution of the magnetic poles in the radial direction (N pole, S pole) may be used as the control information.
  • a cam groove that engages with an engaging portion of each reciprocating steam drive unit and a control unit for controlling the reciprocating motion of each reciprocating steam drive unit are integrated with the rotation output unit. Therefore, the reciprocating motion can be controlled based on the control information corresponding to the position of the cam groove in the rotational direction. Further, even if the number and arrangement of the reciprocating steam driving units are changed, it is not necessary to change the control unit and the control mechanism of the reciprocating steam driving unit. Furthermore, it is possible to change the characteristics of the steam engine simply by exchanging the cam groove and the rotation output section formed with the control section according to the torque characteristics.
  • the energy of the water vapor is first converted into a linear reciprocating motion by the reciprocating steam driving unit.
  • the energy of the water vapor can be efficiently converted into a linear reciprocating motion, and the size can be reduced.
  • the cam follower provided at the tip of the piston rod that reciprocates linearly is engaged with the cam groove formed on the side surface of the rotation output unit, and converted into the rotation motion of the rotation output unit. Since it is converted into a rotational motion by the engagement of the cam groove and the cam follower, the size can be reduced.
  • the reciprocating steam drive unit is arranged at three or more equal positions in the cross section of the rotation output unit, at least one cam follower always engages with a point other than the top dead center or bottom dead center of the cam groove. Since the cam follower always applies a rotational torque in a certain direction to the rotation output portion, the cam follower can pass through the top dead center or the bottom dead center smoothly, and a reliable rotational motion can be obtained.
  • the piston rod can be surely moved back and forth.
  • control valve is controlled by the engagement of the control groove formed on the side surface of the rotation output part and the driven part provided on the control rod integral with the control valve, the cam follower of the piston rod that pushes the cam groove;
  • the movement of the control valve that regulates the moving direction of the piston can be completely synchronized.
  • the pair of reciprocating steam driving units facing each other need only reverse their movements, and the adjacent reciprocating steam driving units. Since the drive units need only be displaced by a quarter, the design is easy.
  • the rotation output portion can be reliably rotated even if the water vapor pressure is small.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Transmission Devices (AREA)

Abstract

Une section d’entraînement à vapeur à mouvement alternatif (2) convertit l’énergie de la vapeur en un mouvement alternatif linéaire. Un poussoir de soupape (23) disposé sur l’extrémité distale d’une tige de piston (8) effectuant un mouvement alternatif linéaire est mis en prise avec un chemin de came (21) formé dans le côté d’une section de sortie de rotation (1) et un mouvement alternatif linéaire est converti en un mouvement rotatif de la section de sortie de rotation (1). Puisque le mouvement alternatif linéaire est converti en mouvement rotatif par la mise en prise du chemin de came (21) et du poussoir de soupape (23), un compactage peut être obtenu. Puisque les sections d’entraînement à vapeur à mouvement alternatif (2) sont disposées en des positions divisant la section transversale de la section de sortie de rotation (1) en trois parties égales ou plus, un ou plusieurs poussoirs de soupape (23) se mettent en prise en des points du chemin de came (21) autres que les points morts supérieur et inférieur, et puisqu'un couple rotatif est toujours communiqué à la section de sortie de rotation dans une direction fixe par le poussoir de soupape (23), le poussoir de soupape (23) traverse le point mort supérieur ou inférieur sans à-coups et un mouvement alternatif fiable est obtenu.
PCT/JP2009/058364 2008-05-02 2009-04-28 Moteur à vapeur polycylindrique WO2009133893A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008-120282 2008-05-02
JP2008120282A JP2009270459A (ja) 2008-05-02 2008-05-02 多気筒蒸気エンジン

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WO2009133893A1 true WO2009133893A1 (fr) 2009-11-05

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1352985A (en) * 1918-04-20 1920-09-14 Murphy Engineering Company Explosive-engine
US1918840A (en) * 1930-04-01 1933-07-18 Oliver H Eriksen Internal combustion engine
JPS5744701A (en) * 1980-06-13 1982-03-13 Haintsuuyoahimu Shiyumitsuto Pinston engine
WO1988005495A1 (fr) * 1987-01-16 1988-07-28 Geelong Engine Co., Pty. Ltd. Moteur axial
JP2004530068A (ja) * 2000-10-30 2004-09-30 チャールズ ラッセル トーマス 均質給気圧縮点火式バレルエンジン
US20060174613A1 (en) * 2005-02-09 2006-08-10 Edward Pritchard Valve and auxiliary exhaust system for high efficiency steam engines and compressed gas motors

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1352985A (en) * 1918-04-20 1920-09-14 Murphy Engineering Company Explosive-engine
US1918840A (en) * 1930-04-01 1933-07-18 Oliver H Eriksen Internal combustion engine
JPS5744701A (en) * 1980-06-13 1982-03-13 Haintsuuyoahimu Shiyumitsuto Pinston engine
WO1988005495A1 (fr) * 1987-01-16 1988-07-28 Geelong Engine Co., Pty. Ltd. Moteur axial
JP2004530068A (ja) * 2000-10-30 2004-09-30 チャールズ ラッセル トーマス 均質給気圧縮点火式バレルエンジン
US20060174613A1 (en) * 2005-02-09 2006-08-10 Edward Pritchard Valve and auxiliary exhaust system for high efficiency steam engines and compressed gas motors

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