WO2011137649A1 - 一种活塞式动力机 - Google Patents

一种活塞式动力机 Download PDF

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Publication number
WO2011137649A1
WO2011137649A1 PCT/CN2010/079839 CN2010079839W WO2011137649A1 WO 2011137649 A1 WO2011137649 A1 WO 2011137649A1 CN 2010079839 W CN2010079839 W CN 2010079839W WO 2011137649 A1 WO2011137649 A1 WO 2011137649A1
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WIPO (PCT)
Prior art keywords
piston
power machine
cylinder
gear
type power
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PCT/CN2010/079839
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English (en)
French (fr)
Inventor
吴伟健
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Wu Weijian
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Publication of WO2011137649A1 publication Critical patent/WO2011137649A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/03—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with movement in two directions being obtained by two single-acting piston liquid engines, each acting in one direction
    • F03C1/035—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with movement in two directions being obtained by two single-acting piston liquid engines, each acting in one direction one single-acting piston being always under the influence of the liquid under pressure
    • 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
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • 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
    • 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
    • F01B7/00—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F01B7/16—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with pistons synchronously moving in tandem arrangement

Definitions

  • the present invention relates to an improvement in a power machine.
  • the linear motion of the cylinder piston is converted into a circular rotary motion output, which is realized by a connecting rod-crankshaft transmission mechanism, that is, a piston-linkage-crankshaft structure in an internal combustion engine.
  • the connecting rod-crankshaft transmission the transmission arm is at most the tangent position of the connecting rod and the rotating circumference of the crankshaft, and the minimum is that the connecting rod extension line passes through the center position of the cranking rotation circumference, and the force arm is zero at this time, because the force arm is constantly changing, Therefore, the conversion efficiency is extremely low, which is also a bottleneck that hinders the power machine to further improve energy efficiency.
  • due to the use of the crankshaft form its volume is also large, and also limits the free design of the piston stroke and cylinder size, which is an important reason hindering the development of high efficiency piston power machine.
  • the technical problem to be solved by the present invention is to overcome the deficiencies of the prior art and provide a small and efficient piston type power machine.
  • a piston type power machine comprising a power machine cylinder and a piston assembly mounted in the cylinder body, the piston assembly comprising a piston symmetrically mounted at both ends, the piston being fixed at both ends of the connecting rod, and the connecting rod is arranged along the piston A rack arranged in the direction of movement and a gear meshing with the rack, the gear being fixed to the power take-off shaft of the power machine by a one-way bearing.
  • the rack and the gear include at least two pairs, the two racks are arranged in parallel up and down, and the two racks are dislocated in a vertical plane, and the two gears are located between the two racks and are coaxial. Installation, the two gears respectively mesh with the two racks, and the two one-way bearings that fix the two gears are locked in the same direction.
  • a combustion chamber capable of continuous combustion work is realized between the piston and the inner end surface of the cylinder, and an air inlet hole, an exhaust hole and an oil inlet hole are arranged in the inner wall of the combustion chamber, and the piston assembly is Positioning assemblies are provided between the cylinders to prevent movement of the piston assembly beyond the range.
  • the positioning assembly includes a positioning card disposed on the piston assembly and two positioning switches disposed on the cylinder. The distance between the two positioning switches is consistent with the stroke of the piston assembly.
  • a receiving chamber for accommodating a high-pressure gas or a high-pressure water flow between the piston and the end surface of the cylinder body is provided with an inlet and an outlet at the inner wall of the accommodating chamber, and are disposed at both ends of the connecting rod toward the gear direction.
  • the brake assembly includes a curved brake pad, and the brake pad corresponds to a circumferential surface of the step disposed on the gear.
  • the arc brake pad is mounted on the cylinder through the movable shaft and a spring that drives the brake pad to restore the initial state.
  • a push rod for pushing the brake pad toward the gear is mounted at both ends of the rod.
  • the present invention has the following advantages:
  • the energy utilization rate is greatly improved: when the existing connecting rod-crankshaft structure moves, when the connecting point of the connecting rod and the crankshaft moves to the tangent point of the circumference of the crankshaft motion, the conversion efficiency is the highest (can be regarded as 100%). When the connecting point between the rod and the crankshaft moves until the extension line of the connecting rod passes through the center of the circumference of the crankshaft movement, the conversion rate is zero (called dead point). During the one-turn rotation of the crankshaft, the connection point between the connecting rod and the crankshaft passes through two dead points.
  • the average conversion rate in this process does not exceed 50%, which shows that its energy utilization rate is less than 50%; and the structure of the present invention is equivalent to the link always acts on the crankshaft tangent point, conversion efficiency It has been in the highest state (can be regarded as 100%), which shows that it has more than doubled the energy utilization rate of the existing connecting rod-crankshaft structure of less than 50%.
  • the cylinder bulk density is greatly improved: the cylinder volume density of the power machine refers to the maximum cylinder volume per unit volume or weight of the power machine.
  • the existing connecting rod-crankshaft power machine cylinder length and diameter are limited by the crankshaft diameter and compression ratio, and the cylinder can only be monopolar.
  • Arrangement, connecting rod-crankshaft structure and its movement occupy a large amount of space, and other balance design necessary to overcome vibration during crankshaft motion, such a power machine can only have a small cylinder volume; and the present invention can adopt parallel Opposite multi-cylinder arrangement, the cylinder arrangement is more compact, the diameter and length of the cylinder can be freely designed, the movement of the connecting rod is completed in the cylinder, the required space of the connecting rod and the gear is small, and the balance design is not required.
  • the cylinder volume density can reach several times the bulk density of the existing power machine cylinder. And the size of the entire power machine can be made smaller.
  • the working efficiency of the cylinder is greatly improved: the power machine of the invention adopts a two-stroke working scheme and a working stroke to adopt a working mode of continuous fuel supply and gas continuous combustion to work, so that the working efficiency of the cylinder can be greatly improved.
  • the power density of the power machine is the maximum power per unit volume or weight of the power machine, and is proportional to the power conversion rate of the power machine, the cylinder volume density, the cylinder working efficiency, etc., from the above analysis, it can be seen that the power machine of the present invention
  • the energy conversion rate, cylinder volume density, and cylinder working efficiency have been greatly improved. Therefore, the power density is also greatly improved, which can reach ten times or even dozens of times of the existing power machine, and can be used with the power of the turbine power machine.
  • the density is equivalent.
  • the power machine structure designed by the invention eliminates the disadvantages of the existing power machine connecting rod-crankshaft structure, has high energy conversion rate, cylinder working efficiency, cylinder bulk density, power density and cylinder
  • the length and diameter selection can be freely designed according to the needs, and can be designed as a two-cylinder power machine or an even-numbered multi-cylinder power machine. Therefore, it is very convenient to design and manufacture various sizes, different powers, and various conditions.
  • Power machines including internal combustion engines, hydraulic and steam engines, such as large power plants, large vehicles, high-performance micro-aircraft and other power engines.
  • Figure 1 is a schematic view showing the connection structure of a piston, a connecting rod and a gear according to the present invention
  • Figure 2 is a schematic cross-sectional view showing the piston, the connecting rod and the gear of the present invention
  • Figure 3 is a schematic structural view of a first embodiment of the present invention.
  • FIG. 4 is a schematic structural view of a second embodiment of the present invention.
  • Figure 5 is a schematic enlarged view of a portion A of Figure 4.
  • Figure 6 is a schematic cross-sectional view of a gear and a one-way bearing with a brake assembly.
  • the invention discloses a higher The energy conversion rate, cylinder working efficiency, cylinder bulk density, power density, and the length and diameter of the cylinder can be selected according to the needs of the power machine.
  • the biggest improvement of the power machine is to abandon the linear motion of the existing connecting rod-crankshaft.
  • the structure of the movement proposes a completely new structural solution comprising a power machine cylinder 1 and a piston assembly 2 mounted in the cylinder 1, the piston assembly 2 comprising a piston 21 symmetrically mounted at both ends, the piston 21 being fixed to Both ends of the link 22 are provided with a rack 23 disposed in the direction of movement of the piston and a gear 24 meshing with the rack 23, and the gear 24 is fixed to the power take-off shaft 26 by a one-way bearing 25.
  • the The rack 23 and the gear 24 include at least two pairs.
  • the two racks 23 are arranged in parallel in the up and down direction, and the two racks 23 are dislocated in a vertical plane.
  • the two gears 24 are located between the two racks 23 and are coaxially mounted. 24 respectively meshes with the two racks 23 to fix the two gears 23
  • the two one-way bearings 25 are locked in the same direction. Details are shown in Figure 2. Under this configuration, regardless of which direction the piston 21 moves, one of the gears is driven to produce effective movement, so that the output shaft can continuously rotate the continuous output power.
  • FIG. 3 is a schematic structural view of an engine according to a first embodiment of the present invention.
  • the engine adopts the structure of the piston assembly 2 of the above-mentioned FIG. 2, in the piston assembly 2
  • the piston 21 and the inner end surface of the cylinder 1 are a combustion chamber, and the inner wall of the combustion chamber is provided with an air inlet hole, a gas exhaust hole and an oil inlet hole, and at the same time, a piston preventing assembly 2 is disposed between the piston assembly 2 and the cylinder block 1.
  • the positioning assembly 3 includes a positioning card 31 disposed on the piston assembly 2 and two positioning switches 32 disposed on the cylinder block 1. The two positioning switches 32 are aligned with the stroke of the piston assembly 2.
  • the embodiment is an internal combustion engine structure, and the continuous oil supply and gas supply modes can be used for continuous oil supply and gas supply in terms of oil supply and gas supply, which not only can greatly improve the working efficiency of the cylinder, but also overcome the design of the length and diameter of the cylinder.
  • the limitation of the air compression ratio of the existing internal combustion engine requires that the working efficiency of the internal combustion engine can be greatly improved if the oil supply and supply of the turbo engine is combined with the fuel supply.
  • the power machine is a hydraulic or steam engine.
  • the engine is a receiving chamber for accommodating a high-pressure gas or a high-pressure water flow between the piston 21 and the inner end surface of the cylinder block 1.
  • the inner wall of the accommodating chamber is provided with an inlet and an outlet, and the inlet is connected with a pressure water flow or high-pressure steam.
  • a brake assembly 4 is disposed at both ends of the connecting rod toward the gear direction to prevent the piston assembly 2 from being subjected to an excessive impact during the movement.
  • the brake assembly 4 includes an arc-shaped brake pad 41 corresponding to a step circumferential surface 42 disposed on the gear 24, and the arc-shaped brake pad 41 is mounted on the movable shaft 43 and the spring 44 that drives the brake pad 41 to return to the initial state.
  • a push rod 45 for pushing the brake pad 41 toward the gear direction is attached to both ends of the link 22, and the push rod 45 is buffered by the spring 46.
  • the push rod 45 pushes the movable shaft 43 and the brake pad 41 toward the step circumferential surface 42 to cause the brake pad 41 to rub against the step circumferential surface 42 to prevent the gear from continuing to rotate. Therefore, the rack 23 and the link 22 are no longer moved, and the link 22 and the rack 23 are restricted.
  • the above embodiment can be regarded as a basic functional unit, and can be superimposed as a multi-cylinder power machine on the same output shaft (the number of cylinders is an even number). Since the output shaft does not adversely affect the gear, the multi-cylinder type of power machine can conveniently control the corresponding number of cylinders according to the load demand, so that the power machine is always in the best working condition.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transmission Devices (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Description

一种活塞式动力机
技术领域
本发明涉及一种动力机的改进 。
背景技术
现有活塞式动力机如内燃机中，将气缸活塞的直线运动转换为圆周旋转运动输出采用的均是连杆－曲轴传动机构实现，即内燃机中的活塞－连杆－曲轴结构实现。在连杆－曲轴传动中，传动力臂最大为连杆与曲轴旋转圆周相切位置，最小为连杆延长线经过曲轴旋转圆周中心位置，并且此时力臂为零，由于力臂不断变化，因此转换的效率极低，这也是阻碍动力机进一步提高能源利用率的瓶颈。于此同时，由于采用的曲轴形式，其体积也较大，同时也限制了活塞行程和气缸大小的自由设计，这是阻碍高效率活塞动力机发展的重要原因。
发明内容
本发明所要解决的技术问题是克服现有技术不足，提供一种体积小、高效的活塞式动力机。
为解决上述技术问题，本发明采用以下技术方案实现：
一种活塞式动力机，包括动力机缸体以及安装于缸体内的活塞组件，所述的活塞组件包括位于两端对称安装的活塞，活塞固定于连杆两端，在连杆上设置有沿活塞运动方向布置的齿条以及与齿条啮合的齿轮，齿轮通过单向轴承固定于动力机动力输出轴上。
作为对上述方案的改进，所述的齿条以及齿轮至少包括两对，两齿条上下平行布置，且两齿条在竖直面上错位分布，两齿轮位于两齿条之间且同轴心安装，两齿轮分别与两齿条啮合，固定两齿轮的两单向轴承同方向锁死。
作为对上述方案的进一步改进，在活塞与缸体内端面之间为可实现连续燃烧做功方式的燃烧室，在燃烧室内壁设置有进气孔、排气孔以及进油孔，在活塞组件与缸体之间设置有防止活塞组件移动超出范围的定位组件。所述的定位组件包括设置于活塞组件上的定位卡以及两个设置于缸体上的定位开关，两定位开关距离与活塞组件行程一致。
作为对上述方案的另外一种改进，在活塞与缸体内端面之间为容纳高压气体或者高压水流的容纳腔，在容纳腔内壁设置有进口、出口，在连杆两端朝齿轮方向均设置有刹车组件。所述的刹车组件包括一弧形刹车片，刹车片与设置于齿轮上的台阶圆周面对应，弧形刹车片通过活动轴以及驱动刹车片恢复初始状态的弹簧安装于缸体上，在连杆内两端安装有用于将刹车片推向齿轮方向的推杆。
相对现有技术而言，本发明具有如下优点：
1. 能源利用率大幅度提高：现有的连杆－曲轴结构运动时，当连杆与曲轴连接点运动至曲轴运动圆周的切点位置时，其转换效率最高（可视为100％），当连杆与曲轴连接点运动至连杆延长线经过曲轴运动圆周圆心位置时，其转换率为零（称之为死点），在曲轴转动一周过程中，连杆与曲轴连接点经过两个死点以及两个切点，在此过程中平均的转换率不超过50％，由此可见其能源利用率低于50％；而本发明结构则相当于连杆始终作用于曲轴切点上，转换效率一直处于最高状态(可视为100％)，由此可见，与现有连杆－曲轴结构形式小于50％的能源利用率相比提高了一倍以上。
2. 气缸容积密度大幅度提高：动力机的气缸容积密度是指单位体积或重量动力机的最大气缸容积，现有的连杆－曲轴动力机气缸长度和直径受曲轴直径和压缩比的限制，气缸只能单极排列，连杆－曲轴结构及其运动占据大量的空间体积，以及为了克服曲轴运动时振动而必需的其他平衡设计等因素，这类动力机只能拥有很小的气缸容积；而本发明可采用平行对置的多气缸排列方式，各气缸排列更加紧凑，气缸的直径和长度可以自由设计，连杆的运动在气缸内完成，连杆、齿轮的所需的空间小，且无需过多的平衡设计，气缸容积密度可以达到现有动力机气缸容积密度的数倍以上。并且整个动力机的体积可以做得更小。
3. 大幅度提高了气缸的工作效率：本发明的动力机采取二冲程工作方案和工作冲程采取连续供油供气持续燃烧做功的工作模式，所以能大幅度提高气缸的工作效率。
4. 大幅度提高动力机的功率密度：动力机的功率密度为单位体积或重量动力机的最大功率，与动力机能源转换率、气缸容积密度、气缸工作效率等成正比，由上述几点分析可知，本发明动力机的能源转换率、气缸容积密度、气缸工作效率均有大幅度提高，所以，其功率密度也随之大幅度提高，可达到现有动力机的十倍甚至数十倍之多，可与涡轮动力机的功率密度相当。
5. 便于建造从微型到超大型的动力机：本发明设计的动力机结构消除了现有动力机连杆－曲轴结构存在的弊病，具有极高的能源转换率、气缸工作效率、气缸容积密度、功率密度以及气缸的长度和直径选择可以根据需要自由设计，并且可以设计为两缸动力机或者是偶数个的多缸动力机，因此，可以非常方便地设计、制造出各种尺寸、不同功率、满足各种情况要求的动力机，包括内燃式动力机，水力式动力机和蒸汽动力机等，比如大型发电厂、大型运输工具、高性能微型飞行器等的动力机。
附图说明
附图1为本发明活塞以及连杆、齿轮连接结构示意图；
附图2为本发明活塞以及连杆、齿轮横截面结构示意图；
附图3为本发明实施例一结构示意图；
附图4为本发明实施例二结构示意图;
附图5为附图4中A部放大结构示意图；
附图6为带有刹车组件的齿轮、单向轴承横截面结构示意图。
具体实施方式
为了便于本领域技术人员的理解，下面将结合具体实施例及附图对本发明结构原理作进一步详细描叙：
本发明揭示的是一种具有更高 能源转换率、气缸工作效率、气缸容积密度、功率密度以及气缸的长度和直径选择可以根据需要自由设计的动力机，该动力机最大改进之处为摒弃了现有连杆－曲轴形式的直线运动转圆周运动的结构，提出了一种全新的结构方案，该结构包括动力机缸体1以及安装于缸体1内的活塞组件2，该活塞组件2包括位于两端对称安装的活塞21，活塞21固定于连杆22两端，在连杆22上设置有沿活塞运动方向布置的齿条23以及与齿条23啮合的齿轮24，齿轮24通过单向轴承25固定于动力机动力输出轴26上。当活塞21连同连杆22、齿条23在缸体1内滑动时，如果齿条23移动方向与单向轴承25锁死方向一致时，齿条23驱动齿轮24转动形成输出动力；当齿条23移动方向与单向轴承25锁死方向相反时，齿轮24与输出轴之间则无动力输出。详细如附图1所示。
由于活塞21在缸体1内是往复直线运动，为了使活塞21在往复时都能形成动力输出，所述的 齿条23以及齿轮24至少包括两对，两齿条23上下平行布置，且两齿条23在竖直面上错位分布，两齿轮24位于两齿条23之间且同轴心安装，两齿轮24分别与两齿条23对应啮合，固定两齿轮23 的两单向轴承25同方向锁死。详细如附图2所示。在该结构下，无论活塞21向哪个方向移动，都会驱动其中一齿轮产生有效的移动，从而使输出轴能持续地转动连续的输出动力。
再如附图3所示为本发明具体实施方式一的发动机结构示意图。该发动机采用了上述附图2的活塞组件2结构，在活塞组件2的 活塞21与缸体1内端面之间为燃烧室，在燃烧室内壁设置有进气孔、排气孔以及进油孔，同时，在活塞组件2与缸体1之间设置有防止活塞组件2移动超出范围的定位组件3。该定位组件3包括设置于活塞组件2上的定位卡31以及两个设置于缸体1上的定位开关32，两定位开关32距离与活塞组件2行程一致。
该实施方案为内燃机结构，在供油供气方面可以采用连续供油、供气方式进行连续供油供气，不但能极大提高气缸的工作效率，更能使气缸的长度和直径的设计克服现有内燃机空气压缩比的限制要求，如果结合涡轮内燃机增压方式进行供油供气，则可以极大地提高内燃机的工作效率。
再如附图4～6所示为本发明具体实施方式二的动力机结构示意图。该动力机为水力或者蒸汽发动机，该发动机在活塞21与缸体1内端面之间为容纳高压气体或者高压水流的容纳腔，在容纳腔内壁设置有进口、出口，进口连通压力水流或高压蒸汽，在连杆两端朝齿轮方向均设置有刹车组件4，防止活塞组件2在运动过程中受到过大的冲击。该刹车组件4包括一弧形刹车片41，刹车片41与设置于齿轮24上的台阶圆周面42对应，弧形刹车片41通过活动轴43以及驱动刹车片41恢复初始状态的弹簧44安装于缸体1上，在连杆22内两端安装有用于将刹车片41推向齿轮方向的推杆45,推杆45通过弹簧46实现缓冲。当连杆22移动至齿轮24靠近连杆22端部时，推杆45推动活动轴43以及刹车片41向台阶圆周面42靠近进而使刹车片41与台阶圆周面42发生摩擦，阻止齿轮继续旋转，从而也使齿条23和连杆22不再移动，起到连杆22、齿条23限位的作用。
上述实施例可视为一个基本的功能单元，在同一根输出轴上可以叠加成多缸动力机（气缸数量为偶数个）。由于输出轴不会逆向影响齿轮，因此多缸形式的动力机时可以根据负载需要方便地控制相应数量的气缸工作，使动力机始终处于最佳工作状态。
上述实施例仅为本发明的较佳的实施方式，除此之外，本发明还可以有其他实现方式。也就是说，在没有脱离本发明构思的前提下，任何显而易见的替换均应落入本发明的保护范围之内。

Claims (6)

  1. 一种活塞式动力机，包括动力机缸体（1）以及安装于缸体内的活塞组件（2），其特征在于：所述的活塞组件包括位于两端对称安装的活塞（21），活塞固定于连杆（22）两端，在连杆上设置有沿活塞运动方向布置的齿条（23）以及与齿条啮合的齿轮（24），齿轮通过单向轴承（25）固定于动力机动力输出轴（26）上。
  2. 根据权利要求1所述的活塞式动力机，其特征在于：所述的齿条以及齿轮至少包括两对，两齿条上下平行布置，且两齿条在竖直面上错位分布，两齿轮位于两齿条之间且同轴心安装，两齿轮分别与两齿条啮合，固定两齿轮的两单向轴承同方向锁死。
  3. 根据权利要求1或2所述的活塞式动力机，其特征在于：在活塞与缸体内端面之间为可实现连续燃烧做功方式的燃烧室，在燃烧室内壁设置有进气孔、排气孔以及进油孔，在活塞组件与缸体之间设置有防止活塞组件移动超出范围的定位组件（3）。
  4. 根据权利要求3所述的活塞式动力机，其特征在于：所述的定位组件包括设置于活塞组件上的定位卡（31）以及两个设置于缸体上的定位开关（32），两定位开关距离与活塞组件行程一致。
  5. 根据权利要求1或2所述的活塞式动力机，其特征在于：在活塞与缸体内端面之间为容纳高压气体或者高压水流的容纳腔，在容纳腔内壁设置有进口、出口，在连杆两端朝齿轮方向均设置有刹车组件（4）。
  6. 根据权利要求5所述的活塞式动力机，其特征在于：所述的刹车组件包括一弧形刹车片（41），刹车片与设置于齿轮上的台阶圆周面（42）对应，弧形刹车片通过活动轴（43）以及驱动刹车片恢复初始状态的弹簧（44）安装于缸体上，在连杆内两端安装有用于将刹车片推向齿轮方向的推杆（45）
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150013635A1 (en) * 2013-07-11 2015-01-15 Mark Brooks Engine Combustion System
CN108798883A (zh) * 2018-06-13 2018-11-13 浙江大学 一种新型卧式齿轮齿条发动机

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101858251A (zh) * 2010-05-07 2010-10-13 吴伟健 一种活塞式动力机
CN102588103A (zh) * 2011-08-25 2012-07-18 龙全洪 平转发动机
CN102661199A (zh) * 2012-05-09 2012-09-12 曹德新 直轴驱动内燃机方法和装置
CN102705153B (zh) * 2012-07-09 2014-08-13 南宁舒曼特灯饰电器制造有限公司 自来水压力发动机
CN104632380A (zh) * 2015-02-09 2015-05-20 白云龙 一种水平对置连杆及对置缸体内燃机
CN108757172A (zh) * 2018-05-21 2018-11-06 浙江大学 一种四缸联动半齿轮发动机
CN109812333A (zh) * 2019-03-18 2019-05-28 张家港川梭车业有限公司 一种双缸齿轮齿条传动内燃机
CN113356995B (zh) * 2021-07-20 2022-09-09 唐显著 一种对称式内燃机

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3531862A1 (de) * 1985-09-06 1987-03-19 Zott Kg Hubkolben-verbrennungskraftmotor
CN2350537Y (zh) * 1998-03-09 1999-11-24 赵祝元 无曲轴活塞动力机
CN1699731A (zh) * 2004-05-19 2005-11-23 有限会社卡依·爱依知工业 汽缸型旋转式动力传动装置
CN201184240Y (zh) * 2008-04-17 2009-01-21 雷仲升 二缸二冲程直轴式发动机
CN101858251A (zh) * 2010-05-07 2010-10-13 吴伟健 一种活塞式动力机

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2109452U (zh) * 1992-01-10 1992-07-08 佘天白 双向作功往复式内燃机
CN1084248A (zh) * 1993-03-30 1994-03-23 袁炳夫 梭子发动机
CN2794950Y (zh) * 2005-04-20 2006-07-12 谢祖祺 一种带防抱死制动功能的汽车电动制动装置
CN201351536Y (zh) * 2008-04-25 2009-11-25 赵天佳 一种节能汽车

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3531862A1 (de) * 1985-09-06 1987-03-19 Zott Kg Hubkolben-verbrennungskraftmotor
CN2350537Y (zh) * 1998-03-09 1999-11-24 赵祝元 无曲轴活塞动力机
CN1699731A (zh) * 2004-05-19 2005-11-23 有限会社卡依·爱依知工业 汽缸型旋转式动力传动装置
CN201184240Y (zh) * 2008-04-17 2009-01-21 雷仲升 二缸二冲程直轴式发动机
CN101858251A (zh) * 2010-05-07 2010-10-13 吴伟健 一种活塞式动力机

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150013635A1 (en) * 2013-07-11 2015-01-15 Mark Brooks Engine Combustion System
CN108798883A (zh) * 2018-06-13 2018-11-13 浙江大学 一种新型卧式齿轮齿条发动机

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