WO2005111375A1 - Convertisseur de mouvement rotatif et reciproque de type sans manivelle et moteur dote d'un tel convertisseur et compresseur dote d'un tel convertisseur - Google Patents
Convertisseur de mouvement rotatif et reciproque de type sans manivelle et moteur dote d'un tel convertisseur et compresseur dote d'un tel convertisseur Download PDFInfo
- Publication number
- WO2005111375A1 WO2005111375A1 PCT/CN2005/000543 CN2005000543W WO2005111375A1 WO 2005111375 A1 WO2005111375 A1 WO 2005111375A1 CN 2005000543 W CN2005000543 W CN 2005000543W WO 2005111375 A1 WO2005111375 A1 WO 2005111375A1
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- WO
- WIPO (PCT)
- Prior art keywords
- gear
- power
- frame
- wheel
- ring gear
- Prior art date
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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
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/01—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being mechanical
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
- F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
- F01B9/042—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the connections comprising gear transmissions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
- F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
- F01B9/047—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft with rack and pinion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
-
- 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
Definitions
- the present invention relates to a power conversion mechanism that mutually converts reciprocating linear motion and rotary power; and also relates to a piston engine, a compressor, and the like using the power conversion mechanism.
- the present invention intends to provide a power conversion mechanism without a crankshaft.
- Chinese Patent Publication No. CN2291534Y, Authorization Announcement, September 16, 1998 and the name of the invention was "Three-tooth Double-Bar Reciprocating Rotary Interchange Mechanism", etc. .
- the disadvantages are: Because it uses the "incomplete gear and rack intermittent meshing" design, the gear teeth that mesh first must be subject to considerable impact, which affects its service life. In addition, when the engine speed is in a large range During the change, the synchronous operation between the gear and the rack is not easy to control, and misalignment may occur, which may have serious consequences.
- the present invention overcomes some of the shortcomings in the prior art, and aims to provide a crankless reciprocating and rotating power conversion mechanism with high efficiency, wide application range, and relatively small impact damage, and its engine and compressor.
- the power conversion mechanism includes a ring gear frame 1 fixedly connected to the reciprocating power component, a power wheel fixedly connected to the power shaft 20, and a planetary gear 3 directly or indirectly transmitted to the ring gear frame 1 and the power wheel 2. :
- the ring gear frame 1 is a toothed ring structure: two sides of the toothed ring frame 1 are symmetrical and parallel. And 12; the two ends of which are two symmetrical semi-circular gears (referred to as semi-circular gears) 13 and 14, the quiescent transition period (referred to as the transition period) of the gear axis at the two ends of the reciprocating stroke, respectively, with the power shaft 20 Coincident axis lines
- the planetary wheel 3 uses the shaft link 23 as a tie rod, which is both a planetary wheel of the power wheel 2 and a planetary wheel of the semicircular gear 13 or 14 respectively during the transition period:
- the planetary gear 3 is positioned by the co-action of the rack 11 or 12 and the shaft link 23 (or its limiting device 24>) to transmit power to each other between the ring gear frame 1 and the power wheel 2;
- the power wheel 2 continues to maintain the steering rotation in the linear stroke.
- the semi-circular gear 13 or 14 can be used as the positioning center wheel, and it can revolve from the end of the rack to the tooth at the end of the linear stroke At the starting point of the rack on the other side of the ring frame, it is ready to enter the next straight stroke;
- the present invention can also be implemented in the following ways:
- the ring gear frame 1 is an internal gear ring frame, that is, the semicircular gears 13 and 14 are internal gears, and the teeth of the racks 11 and 12 are symmetrically inward;
- the power wheel 2 It is an external gear;
- the restriction of the outer end position limiting device 24 of the shaft link 23 can only move along the edge of the ring gear frame 1, so that the planetary gear 3 always meshes with the ring gear frame 1.
- the present invention can also be implemented in the following ways:
- the ring gear frame 1 is an external ring gear frame;
- the power wheel 2 is an external gear, which is not on the same plane as the ring gear frame 1;
- the planetary gear 3 is coaxially fixed to the front and rear gears Gear trains; when directly meshing, the radius of the power wheel 2 is smaller than the radius of the semi-circular gears 13 and 14.
- the present invention can also be implemented in the following ways:
- the power wheel 2 is an internal gear
- the ring gear frame 1 is an external gear ring frame, and the two are not on the same plane.
- the present invention can also be implemented in the following ways: the power wheel 2 is an internal gear, the ring gear frame 1 is an internal gear ring frame, and the two are not in the same plane; when directly meshing, the radius of the power wheel 2 is larger than a semicircle The radii of the gears 13 and 14.
- the present invention also provides a compressor.
- the compressor includes at least one set of the aforementioned power conversion mechanism, and each set of mechanism drives at least one set of cylinder pistons.
- the invention also provides a crankshaft-less engine starting mechanism.
- the ring gear frame of the power conversion mechanism is fixedly connected to the piston, and the starting motor can drive the power shaft 20 of the engine to rotate.
- the invention also provides an engine.
- the engine includes at least one set of the above-mentioned power conversion mechanisms, and each set of mechanisms is driven by at least one set of cylinder pistons.
- the engine provided by the present invention can also be realized in the following ways: Four four-stroke cylinders or two two-stroke cylinders with an ignition phase interval of 180 degrees drive at least one group of mechanisms.
- the engine provided by the present invention can also be implemented in the following ways: Six four-stroke cylinders or three two-stroke cylinders drive six or three groups of mechanisms, respectively.
- the gears, racks and other transmission components in the mechanism are always in meshing state, and the instantaneous impact force between them is smaller than other incomplete gear or clutch conversion mechanisms.
- bearings can be used in each rotating part.
- the piston has a simple structure, is lightweight, and is easier to machine.
- Figures 1 and 2 are schematic diagrams of the ring gear frame type power conversion mechanism
- Figure 3 is a schematic diagram of the side (partial cross-section) of the ring gear frame mechanism
- Figure 4 is a schematic diagram of the external meshing planetary gear mechanism
- Figure 5 is a schematic side view of an external meshing planetary gear mechanism
- Figure 6 is a schematic diagram of a ring gear frame mechanism with a power wheel as an internal gear
- Figure 7 is a schematic diagram of an external ring gear frame mechanism with a power wheel as an internal gear
- FIG. 8 is a schematic side view (partial cross-section) of an external ring gear frame mechanism with a power wheel as an internal gear; and a partial cross-sectional schematic view of a sliding groove on the bottom plate of the back fastener of the ring gear frame.
- Figure 9 is a schematic diagram of the power shaft without passing through the ring gear frame
- Figure 10 is a schematic diagram when the ring gear frame is a solid ring gear
- Figure 11 is a schematic diagram of a planetary gear such as a bevel gear (including a spur gear), or the planetary gear shaft is not parallel to the power shaft, and a partial cross-sectional schematic diagram of the shaft end sliding groove
- Figure 12 is a schematic diagram of a sliding groove on the back of the ring fastener frame bottom plate
- Figure 13 is a schematic diagram of the indirect transmission between the power wheel and the planetary wheel through the intermediate (toothed) wheel.
- Figure 14 is a schematic diagram of the indirect transmission between the power wheel and the planetary wheel through a chain or belt and other components. Schematic of indirect transmission through intermediate gear
- Figure 16 shows the transmission between the ring gear frame and the planetary gear through an intermediate gear and a chain or belt.
- Figure 17 is a schematic diagram of a set of power conversion mechanisms connected to multiple sets of gas (gas) cylinder pistons
- Figure 18 is a schematic diagram of multiple groups of mechanisms arranged coaxially and longitudinally, as well as a flywheel and a starting mechanism.
- Figure 19 is a schematic diagram of power outputs of a non-output spindle of a power shaft, or multiple groups of different axis arrangements.
- the present invention will reciprocate at least one ring gear frame, at least one power wheel, and at least one planetary wheel with the same fixed member.
- the formed power conversion mechanism is called a "group of mechanisms"; the so-called “direct transmission” of the planetary gear 3, the ring gear frame 1 and the power wheel 2 refers to the direct meshing (or frictional transmission) between them, and the "indirect transmission” is Refers to indirect transmission between them through intermediate wheels or chains, belts and other components (see Note 5.1)
- the reciprocating ring gear frame 1 is a ring-shaped ring structure (see Figure 1, Figure 4, Figure 10, etc.): its two sides are two symmetrical parallel racks 11, 12; its two ends are two symmetrical semicircles Gears (semi-circular gears) 13, 14 whose gear axis coincides with the axis of the power shaft 20 during the transition period (see Figure 1, Figure 2 etc.); the planetary gear 3 is based on the shaft link 23
- the lever is not only the planetary gear of the power wheel 2, but also the planetary gears of the semicircular gears 13 or 14 in the later period.
- the ring gear frame 1 is an internal ring gear frame: that is, the semicircular gears 13 and 14 are semicircular internal gears, and the teeth of the racks 11 and 12 are symmetrically inward; the power wheel 2 is an external gear; the ring gear frame 1 The power wheel 2 and the planet wheel 3 can be located on the same plane;
- the limiting device 24 may be a rolling body such as a roller, a ball, a bearing, a gear, or a limiting pin, and it may slide along the outer edge of the ring gear frame 1 or its edge. 7
- the planetary gear 3 is positioned by the joint action of the rack 11 or 12 and the shaft link 23 (including the limit device 24): directly transmitting power to each other between the ring gear frame 1 and the power wheel 2; During the transition period, the power wheel 2 continues to maintain the steering rotation in the linear stroke.
- the semi-circular gear 13 or 14 can be used as the positioning center wheel, and it can revolve from the end of the rack to the tooth at the end of the linear stroke At the starting point of the rack on the other side of the ring frame, it is ready to enter the next straight stroke;
- the mechanism can convert rotary power into reciprocating linear motion:
- the ring gear frame 1 With the continuous rotation of the power shaft 20, the ring gear frame 1 performs a continuous, periodic reciprocating linear motion, and the piston 6 can be driven by the fixed member 6 to perform reciprocating work.
- This mechanism can be directly applied to devices and equipment that need to convert rotary power into reciprocating linear motion, such as piston compressors: the motor of the compressor drives at least one set of the power shaft 20 and power wheel 2 of the power conversion mechanism along arrow 21 Continuously rotate in the direction, and drive the continuous reciprocating movement of the ring gear frame 1, the fixed connection 6, the piston 4, etc., to periodically compress the gas in the cylinder 5 to perform work (see Figure 1); a group of mechanisms can also drive multiple sets of cylinder pistons (See Figure 17).
- This mechanism can also be used as the starting mechanism of a crankless engine (see Figure 18): the starter motor 16 drives the power shaft 20 through the flywheel 15 to rotate, driving at least one group of mechanisms to reciprocate until at least one cylinder is ignited or the engine is operating normally.
- the mechanism can convert reciprocating linear motion into continuous rotary motion with the assistance of flywheels and other mechanisms:
- the reciprocating components such as piston 4 can drive the ring gear frame 1 to perform continuous periodic reciprocating linear motion through the fixed member 6 (for example, the ring gear frame is fixedly connected to four four-stroke cylinders or two two-stroke cylinders, see FIG. 17);
- the power shaft 20 is connected to the flywheel inertia mechanism 15 (see FIG. 18):.
- the reciprocating component drives the ring gear frame 1 to perform work from bottom dead center to top dead center, and the rack 12 is pulled by the positioned planetary gear 3 Power wheel 2 and its shaft 20 continue to rotate in the direction of arrow 21 and output power (see the dotted line position on the right of Figure 1); at the same time, it can also drive the flywheel to accumulate energy to the top dead center;
- the reciprocating component can only intermittently drive the ring gear frame 1 to perform work in one direction (such as when there is only one set of cylinder pistons), then perform the work in a straight line after the stroke of 1. 2. 1 until the rest of the cycle before the work is performed again.
- Both the stroke and the process need to be driven by the power of the inertial flywheel energy storage mechanism or other groups of mechanisms, that is, the role of the mechanism temporarily becomes "converting rotary power to reciprocating linear motion" (see Note 1.1).
- the power shaft 20 continues to rotate in the direction of the arrow 21 and outputs power.
- the mechanism can be used as a power conversion mechanism of an engine to convert the reciprocating motion of a piston into a rotary power output: the engine includes at least one set of the power conversion mechanism, and each set of mechanisms is driven by at least one cylinder piston to drive the ring gear frame 1 to reciprocate When moving, the power shaft 20 can continuously rotate and output power.
- the ring gear frame 1 is an external gear ring frame, that is, the semicircular gears 13 and 14 are external gears, and the teeth of the racks 11 and 12 are symmetrical outward;
- the power wheel 2 is an external gear, and is not on the same plane as the ring gear frame 1, Assuming that it is located in front of the ring gear frame 1 (on the other side, the situation is similar, the same applies hereinafter), then the planetary gear 3 is a gear string formed by coaxially fixing two front and rear planetary gears 32 and 31, and the front planetary gear 32 Is the external meshing planetary gear of the power wheel 2, and the rear planetary gear 31 is the external meshing planetary gear of the semi-circular gear 13 or 14 during the transition period; Position, so in the case of an external ring gear frame, a stop device is no longer needed on the shaft link 23 (the same applies hereinafter).
- the planetary gear 3 is a gear string formed by coaxially fixing two front and rear planetary gears 32 and 31, and the front
- the radius of the power wheel 2 can be greater than or equal to the radius of the semicircular gears 13 and 14 (for example, FIG. 16 or FIG. 14 etc.), and the planetary gear 3 can also be a long cylindrical gear because of its form Complex and diverse, which can be specifically analyzed based on mechanical principles, and will not be discussed here (see Note 5.1 and Figure 13, Figure 15, etc.).
- the power wheel is an internal gear and the ring gear frame is an external gear ring frame:
- the power wheel 2 and the ring gear frame 1 are not on the same plane;
- the planet wheel 3 may be a long cylindrical gear, or the front and rear gears are the same.
- the front or front gear 32 is an internal meshing planetary gear of the power wheel 2
- the rear or rear gear 31 is an external meshing planetary gear of a semicircular gear 13 or 14 during a transition period.
- the power wheel is an internal gear and the ring gear frame is an internal gear ring frame:
- the power wheel 2 and the ring gear frame 1 are not on the same plane;
- the front gear 32 of the planet wheel 3 is the internal meshing planet gear of the power wheel 2, and the rear gear 31 is at The transition period is the internal meshing planetary gear of the semi-circular gear 13 or 14;
- the radius of the power wheel 2 can be less than or equal to the radius of the semi-circular gears 13 and 14 (for example, FIG. 15 and so on), and the planetary gear 3 can also be a long cylindrical gear because its form is also complicated and diverse. It can be specifically analyzed according to the mechanical principle, and it will not be discussed here (see Note 5.1 and Figure 13, Figure 14, Figure 16, etc.).
- the planetary wheel 3, the power wheel 2, and the ring gear frame 1 can be either directly meshed or frictionally driven, or indirectly transmitted through gears, friction wheels, chains, belts and other transmission parts (see Figure 13, Figure 14, ( Figure 15, Figure 16). That is, the semi-circular gears 13 and 14 can be gears or friction wheels; planetary gears 3, power wheels 2, intermediate gears 9 and the like can be both gears, friction wheels, sprocket wheels, or pulleys.
- the transmission surfaces of each component, including the planetary gear 3, the power wheel 2, the intermediate gear 9, the semi-circular gears 13 and 14, and the gear surfaces of the racks 11 and 12, etc. can be either gear teeth or Friction surface, sprocket, etc.
- the front (or front planetary wheel 32) of power wheel 2 and planetary wheel 3 can pass through the middle (tooth) Indirect transmission such as wheel 9 (see Figure 13; when there are more intermediate wheels or power wheels 2 as internal gears, the situation is similar, not shown in the figure); it can also be indirectly transmitted through chain 28 or belt 29 (see Figure 14) ;
- the rear part of the planetary gear 3 (or the rear planetary gear 31) and the ring gear frame 1 can be driven indirectly through the intermediate gear 9 (see Figure 15
- the shaft of the intermediate wheel 9 is also located on the shaft link 23.
- the power shaft 20 may not pass through the inside of the ring gear frame 1 (see FIG. 9).
- the ring gear frame 1 When the ring gear frame 1 is an external ring gear frame, it may be a solid ring gear bar (see FIG. 10).
- the radius of the semicircular gears 13 and 14 is made as small as possible to shorten the pause transition period between strokes.
- the moving range of the ring gear and the reciprocating member needs to be limited by the limit device (see Figure 9)-it can be on the ring gear 1 or the base plate 6 of the fastener.
- the hinge lever 27 is connected to the limiting protrusion 26 to limit the position.
- the planetary gear 3 can be a bevel gear (including a long cylindrical gear), and the axis 30 of the planetary gear 3 can be parallel or non-parallel to the power shaft 20 (see FIG. 11), then the power wheel 2, the semi-circular gear 13 And 14, can also be corresponding bevel gears (including cylindrical gears), racks 11, 12 should be corresponding bevel racks; the specific parameter settings of each wheel and tooth should ensure that they can always mesh with each other, operate reliably and Passing power.
- an annular sliding groove 7 (see Fig. 12, side part) can also be formed along the tooth edge on the ring gear frame or its fixing member base plate 6.
- the parameters such as the relative size of the radius of each wheel can affect the output torque of the mechanism, the transmission ratio and the transmission efficiency, and should be appropriately selected within the scope consistent with the principles of mechanics.
- a group of mechanisms can have more than one ring gear frame.
- two ring gear frames are coaxially and symmetrically distributed on both sides of the fixing member 6 (see the dotted line on the left in Figure 18).
- Each ring gear frame drives its own
- one reciprocating component can also be connected to more ring gear frames, output power in different directions, or output power uniformly through other transmission components such as bevel gears (not shown in the figure).
- the Rotary inertia drives the power shaft 20 and power wheel 2 to continue to rotate in the direction of arrow 21, and then drives the ring gear frame 1 and the piston 4 to reciprocate, and then completes the subsequent three strokes of exhaust, intake and compression (four-stroke engine) , Or complete the exhaust, sweep, intake and compression stroke (two-stroke engine).
- a set of power conversion mechanisms can be driven by more than one set of cylinder pistons. They can be arranged symmetrically with respect to the center point of the ring gear frame 1 (see Figure 17). The axis of the two sets of cylinder pistons in the solid line in the figure The lines are opposite to the racks on both sides. At this time, the side pressure of the piston on the cylinder wall is minimal, or even not; if it is symmetrically distributed to four four-stroke cylinders (or two two-stroke cylinders), each reciprocating linear stroke is One cylinder is doing work in bursts, outputting power to the main shaft, and driving other cylinders to perform power-consuming strokes such as compression.
- This design can not only drive the ring gear frame 1 to perform continuous reciprocating motions, but also reduce the impact of the reciprocating members on the power shaft 20 or the limit parts at the end of the burst stroke; however, it still needs to rely on the inertia of the flywheel mechanism during the transition period.
- each group of mechanisms can be arranged coaxially and longitudinally (see Figure 18); they can also be arranged in different axes (see Figure 19).
- each group of mechanisms may be unrelated; however, since each group of mechanisms ultimately transmits power directly or indirectly to the output spindle, it is always possible to With the mutual linkage, the following design has certain advantages: That is, the cylinders of each group of mechanisms ignite in sequence at a certain interval, and the cylinders of one group of mechanisms can drive the other groups of mechanisms while outputting power to the spindle during the burst stroke.
- the compression and other strokes of the cylinder can not only improve the efficiency of the engine, but also reduce the impact of the reciprocating components on the power shaft, and make the engine run more smoothly:
- the output spindle 19 may be the power shaft 20 of one of the groups (see Figure 19);
- Gear 17 is on the power shaft 20 of each group of mechanisms
- the power output gear, the gear 18 is the main shaft input gear on the engine output main shaft 19;
- the power shaft 20 When the power shaft 20 is not used as an output main shaft (see FIG. 19, solid line part), the power shaft 20 can be appropriately buffered and damped, and even if the reciprocating component has a large impact on the power shaft 20, it stabilizes the engine main shaft. The output also has little effect.
- the flywheel starting mechanism in the prior art can be directly applied to the engine:
- the starter motor 16 drives the flywheel 15 and the power shaft to rotate, thereby driving at least one group of mechanisms to reciprocate until at least one cylinder ignites or
- the engine is running normally (see Figure 18, the situation is similar when multiple groups of mechanisms are arranged non-coaxially).
- Gas distribution mechanism, fuel supply system, ignition system, etc. can use existing technology, but should be Correspondingly and reasonably adjust the control parameters such as fuel ratio, fuel supply amount, intake / exhaust valve opening and closing time, ignition time, etc. to adapt and improve the performance of this engine.
- the side pressure of the piston of the engine on the cylinder wall is very small, so there is no need for a long skirt; at the same time, because it can directly fix the ring gear frame without assembly of components such as connecting rod pins, it can be designed into a simple symmetrical cylinder. Making the radial thermal expansion amount the same makes processing easier.
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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CN200410045412.3 | 2004-05-18 | ||
CN200410045412 | 2004-05-18 |
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WO2005111375A1 true WO2005111375A1 (fr) | 2005-11-24 |
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PCT/CN2005/000543 WO2005111375A1 (fr) | 2004-05-18 | 2005-04-20 | Convertisseur de mouvement rotatif et reciproque de type sans manivelle et moteur dote d'un tel convertisseur et compresseur dote d'un tel convertisseur |
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN106842139A (zh) * | 2017-04-19 | 2017-06-13 | 青岛港湾职业技术学院 | 一种匀速扇形扫描装置及方法 |
CN110454348A (zh) * | 2019-09-13 | 2019-11-15 | 西南石油大学 | 一种超长冲程多缸往复泵 |
EP3627001A4 (en) * | 2017-05-18 | 2021-01-20 | Zheng, Anqing | TRANSFORMING DEVICE FOR RETURNING LINEAR MOTION AND ROTATING MOTION AND CYLINDER DEVICE |
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JPS5872601A (ja) * | 1981-10-24 | 1983-04-30 | Hiroyoshi Mori | エンジン |
US4608951A (en) * | 1984-12-26 | 1986-09-02 | Ambrose White | Reciprocating piston engine |
US5406859A (en) * | 1987-07-08 | 1995-04-18 | Belford; James R. | Device for transferring power between linear and rotary motion |
WO1990000676A1 (en) * | 1988-07-08 | 1990-01-25 | Wladyslaw Kurek | Internal combustion engine |
US5267002A (en) * | 1992-01-21 | 1993-11-30 | Sharp Kabushiki Kaisha | Document platen driving device |
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CN1084248A (zh) * | 1993-03-30 | 1994-03-23 | 袁炳夫 | 梭子发动机 |
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
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CN106842139A (zh) * | 2017-04-19 | 2017-06-13 | 青岛港湾职业技术学院 | 一种匀速扇形扫描装置及方法 |
CN106842139B (zh) * | 2017-04-19 | 2023-07-07 | 青岛港湾职业技术学院 | 一种匀速扇形扫描装置及方法 |
EP3627001A4 (en) * | 2017-05-18 | 2021-01-20 | Zheng, Anqing | TRANSFORMING DEVICE FOR RETURNING LINEAR MOTION AND ROTATING MOTION AND CYLINDER DEVICE |
CN110454348A (zh) * | 2019-09-13 | 2019-11-15 | 西南石油大学 | 一种超长冲程多缸往复泵 |
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