WO2012048508A1 - 组合气缸活塞曲柄机构 - Google Patents

组合气缸活塞曲柄机构 Download PDF

Info

Publication number
WO2012048508A1
WO2012048508A1 PCT/CN2011/000470 CN2011000470W WO2012048508A1 WO 2012048508 A1 WO2012048508 A1 WO 2012048508A1 CN 2011000470 W CN2011000470 W CN 2011000470W WO 2012048508 A1 WO2012048508 A1 WO 2012048508A1
Authority
WO
WIPO (PCT)
Prior art keywords
sliding plug
crank mechanism
cylinder piston
vertical bearing
bearing structure
Prior art date
Application number
PCT/CN2011/000470
Other languages
English (en)
French (fr)
Inventor
靳北彪
Original Assignee
Jin Beibiao
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 Jin Beibiao filed Critical Jin Beibiao
Publication of WO2012048508A1 publication Critical patent/WO2012048508A1/zh

Links

Classifications

    • 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
    • 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
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • F02B75/228—Multi-cylinder engines with cylinders in V, fan, or star arrangement with cylinders arranged in parallel banks
    • 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
    • F02B2075/1804—Number of cylinders
    • F02B2075/182—Number of cylinders five

Definitions

  • the present invention relates to the field of thermal energy and power, and more particularly to a combined cylinder piston crank mechanism.
  • a combined cylinder piston crank mechanism includes a cylinder, a sliding plug structure and a crank pin journal, at least two of which are arranged in parallel in an axis, and one of the sliding plug structures is disposed in each of the cylinders, each The sliding plug structures are respectively connected to the vertical bearing structure;
  • the load-bearing structure is provided with a slide rail in a direction perpendicular to the axis of the cylinder, and a slider is arranged on the linkage slide, and the slider is slidably connected with the linkage slide.
  • a crank pin journal hole is disposed on the slider, and the crank pin journal hole is rotatably coupled to the crank pin journal.
  • a part of the sliding plug structure is fixedly connected to the vertical bearing structure, and another part of the sliding plug structure is slidably connected with the vertical bearing structure in a direction perpendicular to an axis of the cylinder; or a part of the sliding plug
  • the structural body is fixedly connected to the vertical bearing structure, and the other part of the sliding plug structure is universally connected to the vertical bearing structure.
  • the sliding plug structure is a piston link mechanism.
  • the sliding plug structure is a plunger; or the sliding plug structure is a piston structural rod.
  • a part of the cylinder and another part of the cylinder are disposed opposite to each other, and all the sliding plug structures are connected with the same vertical bearing structure to form an opposite arrangement. Cylinder piston crank mechanism.
  • the diameter of the sliding plug structure, the width of the combination of the sliding plug structure, and the width of the vertical bearing structure are both smaller than the same The distance between the two cranks corresponding to the crank pin journal.
  • a positioning guide is disposed, and the vertical bearing structure or the positioning structure fixed to the vertical bearing structure is in sliding contact with the positioning guide in a direction parallel to the cylinder.
  • At least two of the cylinders are arranged coaxially along the axis to form a structure in which the cylinders are disposed in a mutual arrangement, and in the structure in which the cylinders are disposed in a mutual arrangement, the sliding plug structure other than one of the sliding plug structures It is set as an annular sliding plug structure.
  • the operating phases of the sliding plug structures connected to the same vertical load-bearing structure are set to be different.
  • the so-called sliding plug structure of the present invention refers to a plug-like structure body which is slidingly sealed with a cylinder, and functions as a piston connecting rod mechanism, which may be a piston connecting rod mechanism, which may be a plunger or a piston structural rod.
  • the so-called piston structural rod refers to a structural member that fixes the piston and the connecting rod;
  • the so-called annular sliding plug structure refers to a sliding plug structure that is annular;
  • the so-called vertical bearing structure refers to two or more The structural members of the sliding plug structure are connected to each other, and the purpose thereof is to make the sliding plug structures reciprocate together under the direct action of the same crank pin journal or under the action of the main connecting rod, and in the sliding Carrying and transmitting a force between the plug structure and the crank pin journal;
  • the so-called main link refers to a connecting rod connecting the vertical bearing structure and the crank pin journal;
  • the slideway refers to a slide rail that is interlocked with the slider in other directions except for sliding contact with the slider in the set sliding direction, that is, the linked slide rail is in the cylinder In the direction of the axis Said interlocking slider into Reciprocating movement, sliding contact with the slider in the vertical direction of the axis of the cylinder;
  • the combination of the sliding plug structure
  • the slide rail replaces the connecting rod connected to the crank pin journal; the so-called "the working phase of the sliding plug structure connected to the same vertical load bearing structure is set to be different" means two or more When the sliding plug structure approaches the top dead center, one part is in the compression stroke and the other part is in the exhaust stroke, and the two or more sliding plug structures are similarly approached. Under When the point part is in the intake stroke, while the other part is in the power stroke, its purpose is to achieve a balancing mechanism.
  • the cylinder diameters in the present invention may be the same or different.
  • the combined cylinder piston crank mechanism disclosed by the invention can efficiently cool the compressed gas in the process of compressing the gas, greatly reducing the compression power consumption, and can realize low temperature compression, near constant temperature compression or Constant temperature compression, the so-called low temperature expansion compression means that the compressed gas is effectively cooled during the compression process so that the compressed gas pressure is high and the temperature is at a relatively low level. It means that the temperature of the compressed gas during the compression process is in a state of almost no increase.
  • the so-called oppositely disposed combination cylinder piston crank mechanism of the present invention means that the cylinders are disposed opposite to each other, and the sliding plug structure is disposed opposite to each other, and the sliding plug structure is located at an upper portion of the vertical bearing structure according to its position Connected or connected to the lower portion of the vertical load-bearing structure; the upper and lower portions herein refer to both sides bounded by the slide.
  • connection refers to direct connection and indirect connection.
  • the combined cylinder piston crank mechanism disclosed by the invention can be used as a compressor (such as an air compressor, etc.), or can be used as a piston engine, in particular, can be used for a pressure increase in the cylinder pressure.
  • a compressor such as an air compressor, etc.
  • a piston engine in particular, can be used for a pressure increase in the cylinder pressure.
  • Machine and engine can be used as a compressor (such as an air compressor, etc.), or can be used as a piston engine, in particular, can be used for a pressure increase in the cylinder pressure.
  • the combined cylinder piston crank mechanism disclosed by the present invention can be greatly reduced in the cylinder bore, and corresponds to an increase in the coolable interface of the compressed gas in the cylinder, so that efficient cooling of the compressed gas in the cylinder can be achieved.
  • the cylinder diameter of the combined cylinder piston crank mechanism disclosed by the present invention can also be equivalent to the conventional cylinder diameter.
  • the matrix arrangement of the cylinders can be realized, and the long and narrow conventional mode of the engine with a large number of cylinders can be changed. Achieving an engine's width close to length, equal to length, and even greater than the length of the cylinder arrangement provides a new option for optimizing crankshaft length, cylinder alignment and optimizing engine aspect ratio.
  • the invention can greatly improve the cooling efficiency of the compressed gas in the cylinder and reduce the compression power consumption.
  • Figure 1 is a schematic view of Embodiment 1 of the present invention.
  • Figure 2 is a schematic view of Embodiment 2 of the present invention.
  • Figure 3 is a cross-sectional view taken along line A - A of Figure 1 or Figure 2;
  • Figure 4 is a view taken along line M of Figure 2;
  • Figure 5 is a schematic view of Embodiment 3 of the present invention.
  • FIG. 6 is a schematic view of Embodiment 4 of the present invention.
  • Figure 7 is a schematic view of Embodiment 5 of the present invention.
  • Figure 8 is a cross-sectional view taken along the line Q-Q of Figure 7;
  • Figure 9 is a schematic view of Embodiment 6 of the present invention.
  • Figure 10 is a schematic view of Embodiment 7 of the present invention.
  • FIG. 1 is a schematic view of Embodiment 8 of the present invention.
  • Figure 12 is a cross-sectional view taken along line B - B of Figure 11; 13 and FIG. 14 are schematic views of Embodiment 9 of the present invention.
  • Figure 15 is a schematic view of Embodiment 10 of the present invention.
  • Figure 16 is a schematic view of Embodiment 1 of the present invention.
  • Figure 17 is a cross-sectional view taken along line W-W of Figure 16;
  • Figure 18 is a schematic view of Embodiment 12 of the present invention.
  • the combined cylinder piston crank mechanism shown in FIGS. 1 and 3 includes a cylinder 1, a sliding plug structure 2, and a crank pin journal 3, at least two cylinders 1 are arranged in parallel along the axis, and a sliding is provided in each cylinder 1
  • the plug structure 2 each sliding plug structure 2 is respectively connected with the vertical bearing structure 4, and the connecting rod pin 5 is arranged on the vertical bearing structure 4, and the connecting rod pin 5 is swing-connected with one end of the main connecting rod 6, The other end of the main link 6 is rotatably coupled to the crank pin journal 3.
  • the sliding plug structure 2 is set as the plunger 202, and the operating phase of the sliding plug structure 2 connected to the same vertical bearing structure 4 is set to be different.
  • the combined cylinder piston crank mechanism shown in FIG. 2, FIG. 3 and FIG. 4 includes a cylinder 1, a sliding plug structure 2 and a crank pin journal 3, at least two cylinders 1 being arranged in parallel in the axis, in each cylinder 1
  • a sliding plug structure 2 is provided, and each sliding plug structure 2 is respectively connected with a vertical bearing structure 4, and a linked slide is arranged on the vertical bearing structure in a direction perpendicular to the axis of the cylinder.
  • a slider 405 is disposed on the linked slide 401, the slider 405 is slidably coupled to the interlocking slide 401, and a crank pin journal hole 8 is provided on the slider 405, and the crank pin journal hole 8 and the crank pin journal are provided.
  • 3 rotational connection; the diameter A of the sliding plug structure 2, the width of the combination of the sliding plug structure 2 and the width B of the vertical bearing structure 4 are smaller than the two cranks 7 corresponding to the same crank pin journal 3 The distance between C.
  • the combined cylinder piston crank mechanism shown in FIG. 5 differs from the first embodiment in that: a part of the sliding plug structure 2 is fixedly connected to the vertical load-bearing structure 4, and another part of the sliding plug structure 2 is perpendicular to the vertical load-bearing structure 4.
  • the axis of the cylinder 1 is slidably connected in the vertical direction.
  • Example 4 The combined cylinder piston crank mechanism shown in FIG. 6 differs from the first embodiment in that: a part of the sliding plug structure 2 is fixedly connected to the vertical load-bearing structure 4, and another part of the sliding plug structure 2 and the vertical load-bearing structure is 40,000. To connect.
  • the combination cylinder piston crank mechanism shown in FIG. 7 and FIG. 8 differs from the first embodiment in that: a positioning slide 402 is provided, and the vertical load bearing structure 4 and the positioning slide 402 are in sliding contact with the cylinder 1 in a direction parallel to the cylinder 1.
  • the sliding plug structure 2 is set as the piston link mechanism 201.
  • the combined cylinder piston crank mechanism shown in Fig. 9 differs from the first embodiment in that the sliding plug structure 2 is provided as a piston structural rod 203.
  • the combination cylinder piston crank mechanism shown in Fig. 10 differs from the first embodiment in that the slide plug structure 2 is set as the piston link mechanism 201.
  • the combination cylinder piston crank mechanism shown in FIG. 11 and FIG. 12 differs from the first embodiment in that: at least two cylinders 1 are arranged in line along the axis to form a structure in which the cylinders 1 are arranged in a set, and the cylinders 1 are arranged in a set.
  • the sliding plug structure 2 other than one sliding plug structure 2 is provided as an annular sliding plug structure 206, and is provided with an outer sealing ring 9 and an inner sealing ring 10.
  • the combined cylinder piston crank mechanism shown in FIGS. 13 and 14 differs from the first embodiment in that: in the mechanism in which the combined cylinder piston crank mechanism is set as the engine combined cylinder piston crank mechanism 100, all or part of the cylinder 1 Share a combustion chamber. Among them, the two cylinders 1 in Fig. 13 share one combustion chamber, and the four cylinders 1 in Fig. 14 share one combustion chamber.
  • the combination cylinder piston crank mechanism shown in FIG. 15 differs from the second embodiment in that: a part of the cylinder 1 and another part of the cylinder 1 are disposed opposite to each other, and all the sliding plug structures 2 are connected to the same vertical bearing structure 4 to form a pair.
  • a combination cylinder piston crank mechanism 2244 is provided.
  • Example 1 1 The combination cylinder piston crank mechanism shown in FIG. 16 and FIG. 17 differs from the first embodiment in that: a positioning slide 402 is provided, and the vertical load bearing structure 4 and the positioning slide 402 are in sliding contact with the cylinder 1 in a direction parallel to the cylinder 1.
  • the cylinders 1 are arranged in a single row to shorten the distance between the two crankshafts.
  • the combination cylinder piston crank mechanism shown in FIG. 18 differs from the first embodiment in that: a positioning chute 402 is provided, and the positioning structure 440 and the positioning chute 402 fixed to the vertical bearing structure 4 are parallel to the cylinder 1. Sliding contact in the direction.

Landscapes

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

Description

说 明 书
组合气缸活塞曲柄机构
技术领域 本发明涉及热能与动力领域， 尤其是一种组合气缸活塞曲柄机构。
背景技术 无论是传统活塞式发动机或传统气体压縮机， 在压縮过程中由于缸径相对 比较大， 很难使被压縮的气体中的热量得以有效散出， 所以压縮过程中的压縮 功功耗较大。缸径较大的机构也很难适用于缸内压力大幅度增加的压縮过程或 缸内压力大幅度增加的发动机的爆炸作功冲程。 然而， 如果单纯将气缸缸径縮 小， 为保证一定的排气量， 必须增加曲轴的长度， 曲轴长度的增加会带来很多 问题。 为此， 需要发明一种小缸径、 大行程， 而且曲轴长度适当的活塞曲柄机 构。
发明内容
为了解决上述问题， 本发明提出的技术方案如下：
一种组合气缸活塞曲柄机构， 包括气缸、 滑动塞结构体和曲柄销轴颈， 至 少两个所述气缸按轴线平行设置，在每个所述气缸内设置一个所述滑动塞结构 体， 每个所述滑动塞结构体分别与垂直承载结构体连接；
在所述垂直承载结构体上设置连杆销轴，所述连杆销轴与主连杆的一端摆 动连接， 所述主连杆的另一端与曲柄销轴颈转动连接； 或在所述垂直承载结构 体上按与所述气缸的轴线相垂直的方向设连动式滑道，在所述连动式滑道上设 滑块， 所述滑块与所述连动式滑道滑动连接， 在所述滑块上设曲柄销轴颈孔， 所述曲柄销轴颈孔与曲柄销轴颈转动连接。
一部分所述滑动塞结构体与所述垂直承载结构体固连， 另一部分所述滑动 塞结构体与所述垂直承载结构体在所述气缸的轴线垂直方向上滑动连接；或一 部分所述滑动塞结构体与所述垂直承载结构体固连， 另一部分所述滑动塞结构 体与所述垂直承载结构体万向连接。 所述滑动塞结构体设为活塞连杆机构。
所述滑动塞结构体设为柱塞； 或所述滑动塞结构体设为活塞结构杆。 在设有所述连动式滑道的结构中，一部分所述气缸和另一部分所述气缸对 置设置， 所有所述滑动塞结构体与同一所述垂直承载结构体连接， 构成对置设 置组合气缸活塞曲柄机构。
在设有所述曲柄销轴颈孔的结构中， 所述滑动塞结构体的直径、所述滑动 塞结构体的组合体的宽度和所述垂直承载结构体的宽度均小于与同一个所述 曲柄销轴颈所对应的两个曲柄之间的距离。
设置定位滑道，所述垂直承载结构体或与所述垂直承载结构体固连的定位 结构体与所述定位滑道在与所述气缸平行的方向上滑动接触。
至少两个所述气缸按轴线共线设置构成所述气缸相互套装设置的结构，在 所述气缸相互套装设置的结构中，除一个所述滑动塞结构体之外的其他所述滑 动塞结构体设为环状滑动塞结构体。
与同一个所述垂直承载结构体连接的所述滑动塞结构体的工作相位设为 不同。
在将所述组合气缸活塞曲柄机构设为发动机用组合气缸活塞曲柄机构的 机构中， 全部或部分所述气缸共用一个燃烧室。
本发明所谓的滑动塞结构体是指与气缸滑动密封配合的塞状结构体，其功 能相当于活塞连杆机构， 它可以是活塞连杆机构， 可以是柱塞， 也可以是活塞 结构杆， 所谓活塞结构杆是指将活塞和连接杆固连的结构件； 所谓环状滑动塞 结构体是指设为环形的滑动塞结构体；所谓垂直承载结构体是指将两个或两个 以上的所述滑动塞结构体相互连接的结构件，其目的是使这些所述滑动塞结构 体在同一所述曲柄销轴颈直接作用下或经主连杆作用下共同往复运动，并在所 述滑动塞结构体和所述曲柄销轴颈之间承载和传递作用力；所谓主连杆是指将 所述垂直承载结构体和所述所述曲柄销轴颈相互连接的连杆；所谓连动式滑道 是指除在所设定的滑动方向上与所述滑块滑动接触外，在其他方向上与所述滑 块连动的滑道，即所述连动式滑道在所述气缸的轴线方向上与所述滑块连动进 行往复运动， 在所述气缸的轴线的垂直方向上与所述滑块滑动接触； 所谓滑动 塞结构体的组合体是指两个或多个所述滑动塞结构体所构成的整体； 所谓的 "所述滑动塞结构体的直径、所述滑动塞结构体的组合体的宽度和所述垂直承 载结构体的宽度均小于与同一个所述曲柄销轴颈所对应的两个所述曲柄之间 的距离"是为了实现使所述垂直承载结构体及与其相连的所述滑动塞结构体能 够进入与其相对应的两个曲柄之间， 从而降低整个机构的高度， 这实质上是用 滑块、滑道代替了与曲柄销轴颈连接的连杆； 所谓的 "与同一个所述垂直承载 结构体连接的所述滑动塞结构体的工作相位设为不同"是指两个或多个所述滑 动塞结构体共同趋近于上止点时， 其中一部分是处在压縮冲程， 而另一部分则 处在排气冲程， 同理两个或多个所述滑动塞结构体共同趋近于下止点时， 其中 一部分是处在吸气冲程， 而另一部分则处在作功冲程， 其目的是为了实现机构 的动平衡。
本发明中的气缸直径可以设为相同， 也可以设为不同。
本发明所公开的组合气缸活塞曲柄机构可以在对气体进行压縮的进程中 对被压縮气体进行高效冷却， 大幅度降低压縮功耗， 能够实现低增温压縮、 近 恒温压縮或恒温压縮，所谓的低增温压縮是指在压縮进程中有效地对被压縮气 体进行冷却使压縮后的气体压力高而温度处于相对较低的水平，所谓近恒温压 縮是指在压縮过程中被压縮气体的温度处于近乎不增加的状态。
本发明所谓的对置设置组合气缸活塞曲柄机构是指所述气缸对置设置、所 述滑动塞结构体对置设置，所述滑动塞结构体按其所在位置与所述垂直承载结 构体的上部连接或与所述垂直承载结构体的下部连接；此处的上部和下部是指 以滑道为界限的两侧。
所谓连接是指直接连接、 间接连接。
本发明所公开的组合气缸活塞曲柄机构可以用作压气机 （如空气压縮机 等）， 也可以用作活塞式发动机， 特别是可以用于缸内压力大幅度提高的压气 机和发动机。
本发明所公开的组合气缸活塞曲柄机构由于缸径可大幅度縮小，相当于缸 内被压縮气体的可以冷却的界面增大， 因此可以实现对缸内被压縮气体的高效 冷却。
本发明所公开的组合气缸活塞曲柄机构的气缸直径也可以与传统的气缸 直径相当， 在这种情况下可以实现气缸的矩阵式排列方式， 可以改变缸数较多 的发动机长而窄的传统模式， 实现发动机的宽度接近长度、 等于长度， 甚至大 于长度的气缸排列方式， 为优化曲轴长度， 气缸排列方式和优化发动机长宽比 提供一种新的选择。
本发明的有益效果如下：
1、本发明能够大幅度提高气缸内被压縮气体的冷却效率， 减少压縮功耗。
2、 由于缸径可以大幅度降低， 所以适合于缸内压力大幅度提高的机构。 附图说明
图 1为本发明的实施例 1的示意图；
图 2为本发明的实施例 2的示意图；
图 3为图 1或图 2的 A— A剖视图；
图 4为图 2的 M向视图；
图 5为本发明的实施例 3的示意图；
图 6为本发明的实施例 4的示意图；
图 7为本发明的实施例 5的示意图；
图 8为图 7的 Q— Q剖视图；
图 9为本发明的实施例 6的示意图；
图 10为本发明的实施例 7的示意图；
图 1 1为本发明的实施例 8的示意图；
图 12为图 11的 B _ B剖视图； 图 13和图 14为本发明的实施例 9的示意图；
图 15为本发明的实施例 10的示意图；
图 16为本发明的实施例 1 1的示意图；
图 1 7为图 16的 W— W剖视图；
图 18为本发明的实施例 12的示意图。
具体实施方式
实施例 1
如图 1和图 3所示的组合气缸活塞曲柄机构， 包括气缸 1、 滑动塞结构体 2和曲柄销轴颈 3， 至少两个气缸 1按轴线平行设置， 在每个气缸 1 内设置一 个滑动塞结构体 2， 每个滑动塞结构体 2分别与垂直承载结构体 4连接， 在垂 直承载结构体 4上设置连杆销轴 5， 连杆销轴 5与主连杆 6的一端摆动连接， 主连杆 6的另一端与曲柄销轴颈 3转动连接。 滑动塞结构体 2设为柱塞 202， 与同一个垂直承载结构体 4连接的滑动塞结构体 2的工作相位设为不同。
实施例 2
如图 2、 图 3和图 4所示的组合气缸活塞曲柄机构， 包括气缸 1、 滑动塞 结构体 2和曲柄销轴颈 3， 至少两个气缸 1按轴线平行设置， 在每个气缸 1内 设置一个滑动塞结构体 2，每个滑动塞结构体 2分别与垂直承载结构体 4连接， 在所述垂直承载结构体上按与所述气缸的轴线相垂直的方向设连动式滑道，在 连动式滑道 401上设滑块 405， 滑块 405与连动式滑道 401滑动连接， 在滑块 405上设曲柄销轴颈孔 8， 曲柄销轴颈孔 8与曲柄销轴颈 3转动连接； 滑动塞 结构体 2的直径 A、 滑动塞结构体 2的组合体的宽度和垂直承载结构体 4的宽 度 B均小于与同一个曲柄销轴颈 3所对应的两个曲柄 7之间的距离 C。
实施例 3
如图 5所示的组合气缸活塞曲柄机构， 其与实施例 1的区别在于： 一部分 滑动塞结构体 2与垂直承载结构体 4固连， 另一部分滑动塞结构体 2与垂直承 载结构体 4在气缸 1的轴线垂直方向上滑动连接。
实施例 4 如图 6所示的组合气缸活塞曲柄机构， 其与实施例 1的区别在于： 一部分 滑动塞结构体 2与垂直承载结构体 4固连， 另一部分滑动塞结构体 2与垂直承 载结构体 4万向连接。
实施例 5
如图 7和图 8所示的组合气缸活塞曲柄机构， 其与实施例 1的区别在于： 设置定位滑道 402， 垂直承载结构体 4与定位滑道 402在与气缸 1平行的方向 上滑动接触， 滑动塞结构体 2设为活塞连杆机构 201。
实施例 6
如图 9所示的组合气缸活塞曲柄机构， 其与实施例 1的区别在于： 滑动塞 结构体 2设为活塞结构杆 203。
实施例 7
如图 10所示的组合气缸活塞曲柄机构， 其与实施例 1的区别在于： 滑动 塞结构体 2设为活塞连杆机构 201。
实施例 8
如图 11和图 12所示的组合气缸活塞曲柄机构，其与实施例 1的区别在于： 至少两个气缸 1按轴线共线设置构成气缸 1相互套装设置的结构，在气缸 1相 互套装设置的结构中，除一个滑动塞结构体 2之外的其他滑动塞结构体 2设为 环状滑动塞结构体 206， 并设有外密封环 9和内密封环 10。
实施例 9
如图 13和图 14所示的组合气缸活塞曲柄机构，其与实施例 1的区别在于： 在将组合气缸活塞曲柄机构设为发动机用组合气缸活塞曲柄机构 100 的机构 中， 全部或部分气缸 1共用一个燃烧室。 其中， 图 13中两个气缸 1共用一个 燃烧室， 图 14中四个气缸 1共用一个燃烧室。
实施例 10
如图 15所示的组合气缸活塞曲柄机构， 其与实施例 2的区别在于： 一部 分气缸 1和另一部分气缸 1对置设置，所有滑动塞结构体 2与同一垂直承载结 构体 4连接， 构成对置设置组合气缸活塞曲柄机构 2244。
实施例 1 1 如图 16和图 17所示的组合气缸活塞曲柄机构，其与实施例 1的区别在于： 设置定位滑道 402， 垂直承载结构体 4与定位滑道 402在与气缸 1平行的方向 上滑动接触， 所述气缸 1单排设置， 可縮短两曲轴之间的距离。
实施例 12
如图 18所示的组合气缸活塞曲柄机构， 其与实施例 1的区别在于： 设置 定位滑道 402， 与垂直承载结构体 4固连的定位结构体 440与定位滑道 402在 与气缸 1平行的方向上滑动接触。
显然， 本发明不限于以上实施例， 还可以有许多变形。本领域的普通技术 人员， 能从本发明公开的内容直接导出或联想到的所有变形， 均应认为是本发 明的保护范围。

Claims

权 利 要 求
1、一种组合气缸活塞曲柄机构， 包括气缸（1 )、滑动塞结构体（2)和曲 柄销轴颈（3)， 其特征在于： 至少两个所述气缸 （1 )按轴线平行设置， 在每 个所述气缸 （1 ) 内设置一个所述滑动塞结构体 （2)， 每个所述滑动塞结构体 (2) 分别与垂直承载结构体（4)连接；
在所述垂直承载结构体（4)上设置连杆销轴（5)， 所述连杆销轴（5)与 主连杆（6) 的一端摆动连接， 所述主连杆（6) 的另一端与曲柄销轴颈（3) 转动连接； 或在所述垂直承载结构体（4)上按与所述气缸（1 ) 的轴线相垂直 的方向设连动式滑道（401 )， 在所述连动式滑道 （401 )上设滑块（405)， 所 述滑块（405) 与所述连动式滑道 （401 )滑动连接， 在所述滑块（405) 上设 曲柄销轴颈孔（8)， 所述曲柄销轴颈孔（8) 与曲柄销轴颈（3)转动连接。
2、 如权利要求 1 所述组合气缸活塞曲柄机构， 其特征在于： 一部分所述 滑动塞结构体（2)与所述垂直承载结构体（4) 固连， 另一部分所述滑动塞结 构体 （2) 与所述垂直承载结构体（4)在所述气缸 （1 ) 的轴线垂直方向上滑 动连接； 或一部分所述滑动塞结构体（2) 与所述垂直承载结构体（4) 固连， 另一部分所述滑动塞结构体（2) 与所述垂直承载结构体（4)万向连接。
3、 如权利要求 1 所述组合气缸活塞曲柄机构， 其特征在于： 所述滑动塞 结构体（2)设为活塞连杆机构（201 )。
4、 如权利要求 1 所述组合气缸活塞曲柄机构， 其特征在于： 所述滑动塞 结构体（2)设为柱塞（202);或所述滑动塞结构体（2)设为活塞结构杆（203)。
5、 如权利要求 1 所述组合气缸活塞曲柄机构， 其特征在于： 在设有所述 连动式滑道（401 ) 的结构中， 一部分所述气缸（1 )和另一部分所述气缸 （1 ) 对置设置，所有所述滑动塞结构体（2)与同一所述垂直承载结构体（4)连接， 构成对置设置组合气缸活塞曲柄机构（2244)。
6、 如权利要求 1 所述组合气缸活塞曲柄机构， 其特征在于： 在设有所述 曲柄销轴颈孔（8)的结构中， 所述滑动塞结构体（2) 的直径（A)、 所述滑动 塞结构体（2) 的组合体的宽度和所述垂直承载结构体（4) 的宽度 （B)均小 于与同一个所述曲柄销轴颈（3)所对应的两个曲柄（7)之间的距离（C)。
7、 如权利要求 1 所述组合气缸活塞曲柄机构， 其特征在于： 设置定位滑 道（402)， 所述垂直承载结构体（4)或与所述垂直承载结构体（4) 固连的定 位结构体（440) 与所述定位滑道（402) 在与所述气缸 （1 ) 平行的方向上滑 动接触。
8、 如权利要求 1 所述组合气缸活塞曲柄机构， 其特征在于： 至少两个所 述气缸（1 )按轴线共线设置构成所述气缸（1 )相互套装设置的结构， 在所述 气缸（υ相互套装设置的结构中， 除一个所述滑动塞结构体（2)之外的其他 所述滑动塞结构体（2)设为环状滑动塞结构体（206)。
9、 如权利要求 1 所述组合气缸活塞曲柄机构， 其特征在于： 与同一个所 述垂直承载结构体（4)连接的所述滑动塞结构体（2) 的工作相位设为不同。
10、 如权利要求 1所述组合气缸活塞曲柄机构， 其特征在于： 在将所述组 合气缸活塞曲柄机构设为发动机用组合气缸活塞曲柄机构 （100) 的机构中， 全部或部分所述气缸 （1 ) 共用一个燃烧室。
PCT/CN2011/000470 2010-10-15 2011-03-21 组合气缸活塞曲柄机构 WO2012048508A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201010508374.6 2010-10-15
CN2010105083746A CN101975111A (zh) 2010-10-15 2010-10-15 组合气缸活塞曲柄机构

Publications (1)

Publication Number Publication Date
WO2012048508A1 true WO2012048508A1 (zh) 2012-04-19

Family

ID=43575018

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2011/000470 WO2012048508A1 (zh) 2010-10-15 2011-03-21 组合气缸活塞曲柄机构

Country Status (2)

Country Link
CN (1) CN101975111A (zh)
WO (1) WO2012048508A1 (zh)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101975111A (zh) * 2010-10-15 2011-02-16 靳北彪 组合气缸活塞曲柄机构
CN104454165A (zh) * 2014-12-18 2015-03-25 江景通 一种采用十字头集结杆的多缸内燃机组
CN104929769B (zh) * 2015-07-14 2017-05-31 梁廷容 一种带气缸对置装置的无曲轴发动机

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN86108669A (zh) * 1986-12-17 1988-06-29 周健 无缸盖双活塞多缸共轭式柴油机
CN2380698Y (zh) * 1999-04-29 2000-05-31 张文 旋列式汽缸发动机
CN2716520Y (zh) * 2004-08-13 2005-08-10 张君航 多缸双体双曲轴柴油发动机
CN1680699A (zh) * 2004-09-07 2005-10-12 甘文洋 多缸组合发动机
DE102009050346A1 (de) * 2008-11-17 2010-05-20 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Kupplungsausrücksystem mit Verdrehsicherung für Nehmerzylinderkolben
CN101975111A (zh) * 2010-10-15 2011-02-16 靳北彪 组合气缸活塞曲柄机构
CN201810395U (zh) * 2010-10-15 2011-04-27 靳北彪 组合气缸活塞曲柄机构

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2629171B1 (fr) * 1988-03-25 1993-04-09 Moiroux Auguste Dispositif de transmission hydrostatique et application a un groupe motopropulseur ou un vehicule automobile
CN2260892Y (zh) * 1996-07-12 1997-08-27 周生元 套缸式发动机
CN1212322A (zh) * 1997-09-20 1999-03-31 郭崇 多列立式内燃机
KR20050035333A (ko) * 2003-10-10 2005-04-18 현대자동차주식회사 4행정 수평대향형 엔진
DE102006033960A1 (de) * 2006-07-22 2008-01-24 Brauers, Franz, Dr. Hubkolben-Verbrennungskraftmaschinen
DE102008047719B4 (de) * 2008-09-18 2011-03-10 Dieter Hartmann-Wirthwein Kurbeltrieb für Vierzylinderverbrennungsmotoren
CN201318216Y (zh) * 2008-12-22 2009-09-30 靳北彪 外置连杆发动机

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN86108669A (zh) * 1986-12-17 1988-06-29 周健 无缸盖双活塞多缸共轭式柴油机
CN2380698Y (zh) * 1999-04-29 2000-05-31 张文 旋列式汽缸发动机
CN2716520Y (zh) * 2004-08-13 2005-08-10 张君航 多缸双体双曲轴柴油发动机
CN1680699A (zh) * 2004-09-07 2005-10-12 甘文洋 多缸组合发动机
DE102009050346A1 (de) * 2008-11-17 2010-05-20 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Kupplungsausrücksystem mit Verdrehsicherung für Nehmerzylinderkolben
CN101975111A (zh) * 2010-10-15 2011-02-16 靳北彪 组合气缸活塞曲柄机构
CN201810395U (zh) * 2010-10-15 2011-04-27 靳北彪 组合气缸活塞曲柄机构

Also Published As

Publication number Publication date
CN101975111A (zh) 2011-02-16

Similar Documents

Publication Publication Date Title
US7383797B2 (en) Double piston cycle engine
US10502129B2 (en) Double-crankshaft engine
JP2007162694A (ja) ダブル六行程自体冷卻式エンジン
US20180306108A1 (en) Sliding linear internal combustion engine
WO2012048508A1 (zh) 组合气缸活塞曲柄机构
CN104806376A (zh) 三曲拐曲轴磁力传动的β型斯特林发动机
US9605708B2 (en) Single-shaft dual expansion internal combustion engine
US20160363045A1 (en) Single-shaft dual expansion internal combustion engine
US8720410B2 (en) Modified crankshaft piston interface for optimized cylinder pressure and torque output
CN109340078B (zh) 一种双对置活塞压缩机结构
JP6001993B2 (ja) 密閉型往復動圧縮機及びこれを用いた冷蔵庫
JP2000500545A (ja) 斜板エンジン
US20180216520A1 (en) An internal combustion engine
WO2016145734A1 (zh) 往复活塞内置链式连杆无死点发动机活塞连杆组
CN102966511B (zh) 一种动平衡式内燃空气压缩机
KR20160108361A (ko) 가변 공간 전달 셔틀 캡슐 및 밸브 기구
CN201810395U (zh) 组合气缸活塞曲柄机构
WO2014062068A1 (en) An internal combustion engine
NL2018451B1 (en) Engine with two annular cylinders and two crankshafts
CN203488654U (zh) 带压缩杆的内燃机增力器
KR102166541B1 (ko) 길이변환 커넥팅로드(성욱 싸이클)
CN205876489U (zh) 双曲轴发动机的连杆装置
CN104454153B (zh) 环缸发动机
CN104533614B (zh) 双曲柄机构二冲程发动机
RU2768343C1 (ru) ДВС с противоположными цилиндрами, снабженный механизмом, изменяющим направление передачи усилий

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11831905

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 11831905

Country of ref document: EP

Kind code of ref document: A1