WO2008019575A1 - Rotary expanding or compressing mechanism provided in fluid channel with blades for traversing shaft - Google Patents

Rotary expanding or compressing mechanism provided in fluid channel with blades for traversing shaft Download PDF

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Publication number
WO2008019575A1
WO2008019575A1 PCT/CN2007/002280 CN2007002280W WO2008019575A1 WO 2008019575 A1 WO2008019575 A1 WO 2008019575A1 CN 2007002280 W CN2007002280 W CN 2007002280W WO 2008019575 A1 WO2008019575 A1 WO 2008019575A1
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WO
WIPO (PCT)
Prior art keywords
expansion
wear
compression mechanism
shaft
stator
Prior art date
Application number
PCT/CN2007/002280
Other languages
French (fr)
Chinese (zh)
Inventor
Chuting Liu
Original Assignee
Chuting Liu
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 Chuting Liu filed Critical Chuting Liu
Priority to US12/376,777 priority Critical patent/US20100178189A1/en
Priority to EP07785195A priority patent/EP2058519A1/en
Publication of WO2008019575A1 publication Critical patent/WO2008019575A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C18/3445—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the vanes having the form of rollers, slippers or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F01C1/3441—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F01C1/3441—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F01C1/3445—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the vanes having the form of rollers, slippers or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/005—Structure and composition of sealing elements such as sealing strips, sealing rings and the like; Coating of these elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/02—Radially-movable sealings for working fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0881—Construction of vanes or vane holders the vanes consisting of two or more parts

Definitions

  • the present invention relates to the expansion or compression technique of a fluid on a fluid passage, in the form of a volume, particularly decisive for the reliability of the superior performance of the expansion or compression mechanism of the circularly rotating cylinder biasing cylinder.
  • the technology can be spread from basic theory to production practice. technical background
  • the invention of the steam engine marks the beginning of the human industrial revolution, and the core technology of steam expansion into mechanical kinetic energy originates from the blower bellows invented by Chinese blacksmiths.
  • the linear reciprocating force does not match the rotation of the normal machine, so that as long as there is a reciprocating piston expansion or compression mechanism, the energy efficiency will definitely be low.
  • the non-volume form of the turbine is used.
  • the leakage between the blades and the leakage between the impeller rotor and the vortex stator it is still impossible to obtain the ideal. Energy efficiency ratio. Why is it called the ideal energy efficiency ratio?
  • the through-axis blade After being restricted by the round end cap, the through-axis blade can pass through the concave
  • the rotor core can move back and forth at the same time, and at the same time, it is restricted by the cooperation of the cylindrical stator. It can be rotated continuously, which constitutes the forced and continuous expansion or compression of the rotation.
  • the experiment of a gasoline engine as an expansion function is a principle experiment in which the supply of oil and gas is stable, and the spark is generated by the blade strike.
  • the air-conditioning compressor as a compression function has a working pressure of 22 minus 4 kg and a refrigerant of 134 a.
  • the motor is self-made and operates at a speed of 1440 rpm.
  • the energy efficiency ratio at the end of the first test period is 6.1, which is nearly double the energy efficiency of the air conditioner compressor of the world's most advanced scroll mechanism, double the jitter and double the noise.
  • the energy efficiency ratio at the end of the two test periods is 5.8; the energy at the end of the third test period The efficiency ratio is 5.4; the energy efficiency ratio at the end of the fourth test period is 4.9; the energy efficiency ratio gradually decreases as the test period increases.
  • Wire that is, the curved surface of the cylindrical stator profile which was originally formed by a very uneconomical method must also be deformed. From this point of view, it is invented that the forced and continuous separation volume of the mechanism can be exerted.
  • the advantages of this can solve the contradiction between the wear and the closure between the shaft leaf and the cylindrical stator, and can also improve the new structure of wear and closure in other places, which becomes the mechanism from the basic theory to the production practice.
  • the key question is, at the same time is a fundamental solution to the human energy conservation, the key issues of the global meteorological disaster.
  • the present invention provides a special movable wear-resistant closed structure, the outer edges of which are composed of curved line segments, which can be designed into two sets according to the technical requirements of airflow or liquid flow: It is a wear-resistant sealing member with a "6" or " ⁇ " shape on the outer edge of the cross-section of the shaft and the cylindrical stator. The part of the shaft is extended to form a sway and is swayed and compensated for wear. The other set is a wear-resistant sealing member whose cross-section outer edge is rounded at the joint with the cylindrical stator, and can even be stabilized by additional bearings, and the worn position can be replaced uniformly by rolling. Good elastic stress constitutes a smooth rolling closure and wear compensation.
  • the shape of the curved surface, etc. tells us that when the concave rotor is biased, the circular stator distance is in accordance with the better configuration of the volume structure, the curved surface is only two places compared with the correct and precise curved surface required.
  • the gap is about 0.5% of the short axis of the caliber, and the gap can be fully compensated by the above-mentioned wear-resistant sealing member, and the mechanical deviation is always ubiquitous.
  • the wear-resistance tightness performance is enhanced, and the expansion function can be fully adapted to the technical requirements of the internal combustion type engine.
  • the invention can undoubtedly be more than twice the energy efficiency ratio of the world's most advanced expansion or compression mechanism, and the pressure is naturally large, and the noise is naturally soft and its jitter It is naturally light and its structure is naturally light. Not only can it replace the current volumetric expansion or compression mechanism, but it can also partially replace the current turboexpansion expansion or compression mechanism. In addition, because of its excellent performance, many new inventions can be formed.
  • any power station generates electricity by impeller rotors in the form of fluid impulse turbines.
  • the principle and structure of the impeller rotors are due to the spacing between the blades and the blades and the spacing between the stators.
  • the carrying machine can have a power device to work at a constant speed. It can also form thermal expansion by collecting heat energy. The power of the transmission is first and then small and can be steplessly changed. The driving force is extremely accurate, and when it can store excess energy. The volume can also be driven by all-wheel drive and all-wheel steering.
  • the carrier machine can have a large external airbag, etc., so that the two major problems can be solved. If you don't have the courage to use it in a car, we can at least use it on a bicycle to create a bicycle that can be folded into a baggage car by airflow or liquid flow.
  • FIG. 1 is a schematic diagram of an internal combustion engine expansion mechanism.
  • Figure 2 is a schematic illustration of a fluid flow expansion or compression mechanism.
  • Figure 3 is a schematic illustration of a gas flow expansion or compression mechanism.
  • Figure 4 is a schematic view of a smaller airflow compression mechanism
  • Figure 5 is a schematic illustration of a larger airflow expansion or compression mechanism.
  • an expansion or compression mechanism on the fluid passage includes a support frame 1, a fluid inlet and outlet port 2, 3, a non-circular cylindrical drum 4, a concave rotor 5, a through shaft
  • the cylindrical stator 4 which cooperates with it can be made less difficult to process and adapt to a large number of forming machines for processing, and on the other hand, the threaded blade block 6 can be reduced in friction when it is engaged with the cylindrical stator 4 and obtained. Wear compensation also forms a reliable seal (as shown in Figure 1, Figure 2, Figure 3, Figure 4, Figure 5).
  • the profile surface of the non-circular bobbin circular stator 4 can be a waist-curved surface, or a curved surface connected by several positive circular arc lines, or an elliptical surface. It can be a curved surface connected by an elliptical arc and a positive circular arc, or it can be a polar coordinate Shaped curved surface or equivalent mathematical model, etc., because when the concave rotor 5 biases the cylindrical stator 4 distance to match the optimal configuration of the volume structure, these curved surfaces are compared with the correct precision curved surface required. The surface with the largest deviation is only about 0.5% larger than the short axis of the aperture.
  • the diameter of the shortest axis is 100 mm, it is only about 50 filaments in two places, if the running-in process is adopted. It may be 20 filaments or even “zero to zero", but only after "zeroing", it will be biased by the dead and hard scraping.
  • the present invention will provide two basic forms of a movable wear-resistant member whose outer edges of the section are each composed of curved line lines:
  • the shaft bushing 6 is separately provided at the joint with the cylindrical stator 4, and is a rolling wear-resistant sealing member 11 having a circular outer circumference.
  • FIG. 2, FIG. 4, FIG. 5 Shown
  • sleek wear-resistant seal Why is it wear-resistant? This is because the smooth rolling can uniformly replace the worn position circumferentially to compensate for the size lost due to wear, and at the same time, the cylindrical stator 4 faces the rolling friction, which is a wear-resistant material or a wear-resistant coating having a small friction factor.
  • Plating process It is the best place to work. It is a coincidence that most of these materials also have extremely adaptable elastic stresses that can compensate for the size. Increase the awareness before use. The combination of the two can naturally resist long-term wear and compensation. The above deviation is closed.
  • the through-axis leaf block 6 is not only provided with a rolling wear-resistant sealing member 11 having a circular outer circumference but also a rolling bearing. 12 (as shown in Figure 2, Figure 5). If the rotational direction is determined, the center of the rolling wear-resistant sealing member 11 and the center of the rolling bearing 12 can also form a certain inclination with respect to the cylindrical stator 4. In this way, how can it resist the long-term wear and tear, and compensate for the closure of the above deviation?
  • the concave rotor 5 is additionally provided with a "P" or "L” shape on the outer edge of the cross section.
  • Stick-type wear-resistant sealing members 13, 14" (as shown in Figure 1, Figure 2, Figure 3, Figure 4, Figure 5)
  • the present invention puts the concave rotor 5 in and out.
  • the shaft block 6 is fitted with a groove 15 at the mating point, and a rolling cylinder 16 is arranged in the groove to constitute a rolling fit.
  • a rolling cylinder 16 is arranged in the groove to constitute a rolling fit.
  • the simplest way to use a rolling cylinder is that the diameter of the cylinder is slightly larger than the height of the surface, so that it can roll freely and reduce the pressure. According to the above technical solution, it is not difficult to find that the present invention basically wears and seals around the through-axis leaf block in the cylindrical stator and the concave rotor.
  • the expansion or compression mechanism that rotates the shaft leaf to bias the circular rotation of the shaft is called the expansion or compression mechanism of the circular rotation of the shaft-shaping block, and is simply referred to as a rotary expansion or compression mechanism of the shaft-through block, or simply called a live Block expansion compression mechanism.

Abstract

A rotary expanding or compressing mechanism provided in a fluid channel with blades for traversing a shaft comprises a supporting frame (1), an import (2) and export (3) of the fluid channel, a un-round type curve barrel stator (4), a rotor (5) with concave grooves, blades (6) for traversing a shaft, a round end cap (7) and a member (8) for transmitting force. Wherein, a movable wearable sealing member (9,10,11) is provided in the matching position between the blade (6) and the stator (4). The mechanism is of good wearlessness and energy efficiency.

Description

技术领域 Technical field
本发明将涉及到流体通道上流体的膨胀或压缩技术， 属于容积形式， 尤其对于穿轴叶块偏置筒圆旋转的膨胀或压缩机构之优异性能的可靠性 具有决定意义。 由此， 该技术才可从基础理论普及到生产实践之中。 技术背景  The present invention relates to the expansion or compression technique of a fluid on a fluid passage, in the form of a volume, particularly decisive for the reliability of the superior performance of the expansion or compression mechanism of the circularly rotating cylinder biasing cylinder. Thus, the technology can be spread from basic theory to production practice. technical background
大家知道， 蒸气机的发明标志着人类工业革命开始， 而蒸气膨胀变为 机械动能的核心技术却源于中国铁匠发明的吹火风箱。 该技术虽然经过不 断的改造， 但因直线往复的贯性力与通常机械的旋转并不相匹配， 所以就 造成了只要是有往复活塞式膨胀或压缩机构参与的机械， 其能效就肯定会 低下。 为了使得流体的膨胀或压缩可与机械旋转相匹配， 人们又采用 非 容积形式的透平形式， 但因叶片之间的泄漏及叶轮转子与涡圆定子之间的 泄漏， 仍然没法获得理想的能效比。 为何称之为有理想的能效比？这是因 为人们早就通过容积形式运用相关力学理论推算出了理想的能效比。 这 样， 人们也就围绕着容积形式匹配机械旋转方面作出了许许多多的努力， 并发明出了许多种膨胀或压缩机构。 目前的产品中虽然螺杆机构与涡旋机 构用于压缩的能效比相对略高， 但与理想的能效比相比还是相差甚远， 另 夕卜， 因结构上的先天不足已没法替代往复活塞或透平形 用于膨胀， 至使 人们不仅没有从根本上节约能源， 而且因此而转化的热能将弥漫在地球大 气层之内， 竭力造成了人们难以忍受的气象灾难。 所以， 发明出能效性高 可靠性好的流体膨胀或压缩机构便成了当代文明中的重中之重了， 否则， 人类将越是自动化越会加剧能源运用的恶性循环。 还是中国铁匠认识到了人类能源运用这一困境， 发明出了流体通道上 理论上最理想的穿轴叶块偏置筒圆旋转的膨胀或压缩机构。 这种机构它们 是由支承构架支撑着的， 其流体的进、 出通口的一向是与膨胀或压缩的工 作系统相联接， 而另一向则进入了椭圆型线的筒圆定子， 在筒圆定子内的 偏心处设置着可凹入叶块的转子， 在凹块转子上插入有贯穿了其自身轴心 的叶块， 当被筒圆端盖制约后， 穿轴叶块便通过可在凹块转子轴心处能往 返活动， 同时又受到筒圆定子相配合的制约， 可以不断地旋转着， 成而就 构成了旋转地强制性与连续性地膨胀或压缩。 As we all know, the invention of the steam engine marks the beginning of the human industrial revolution, and the core technology of steam expansion into mechanical kinetic energy originates from the blower bellows invented by Chinese blacksmiths. Although the technology has been continuously modified, the linear reciprocating force does not match the rotation of the normal machine, so that as long as there is a reciprocating piston expansion or compression mechanism, the energy efficiency will definitely be low. . In order to make the expansion or compression of the fluid match the mechanical rotation, the non-volume form of the turbine is used. However, due to the leakage between the blades and the leakage between the impeller rotor and the vortex stator, it is still impossible to obtain the ideal. Energy efficiency ratio. Why is it called the ideal energy efficiency ratio? This is because people have long used the relevant mechanical theory to calculate the ideal energy efficiency ratio. In this way, people have made many efforts to match the mechanical rotation of the volume form, and invented many kinds of expansion or compression mechanisms. In the current products, although the energy efficiency ratio of the screw mechanism and the scroll mechanism for compression is relatively high, it is still far from the ideal energy efficiency ratio. In addition, due to the structural congenital deficiency, there is no way to replace the reciprocating piston or The turbine shape is used for expansion, so that not only does it not fundamentally save energy, but the converted heat will pervade the Earth's atmosphere, trying to create an unbearable weather disaster. Therefore, inventing a fluid expansion or compression mechanism with high energy efficiency and high reliability has become a top priority in contemporary civilization. Otherwise, the more automation humans will intensify the vicious circle of energy use. It is also the Chinese blacksmith who recognizes the dilemma of human energy use and invented the theoretically optimal expansion or compression mechanism for the circular rotation of the shaft-leafing cylinder. Such mechanisms are supported by a support frame, the fluid inlet and outlet ports are always connected to the expanded or compressed working system, and the other direction enters the elliptical line of the cylindrical stator, in the cylinder The eccentricity in the stator is provided with a rotor that can be recessed into the leaf block, and the leaf block penetrating its own axis is inserted into the concave rotor. After being restricted by the round end cap, the through-axis blade can pass through the concave The rotor core can move back and forth at the same time, and at the same time, it is restricted by the cooperation of the cylindrical stator. It can be rotated continuously, which constitutes the forced and continuous expansion or compression of the rotation.
我们知道， 气流的技术要求远远高于液流。 本人为了通过实验证明这 种机构的优异性能， 在其膨胀的功能方面， 特将这种机构配制成能满足四 冲程技术本质要求的汽油发动机的基本形式； 在其压缩的功能方面， 特将 这种机构配制成全封闭定频空调压缩机， 并且还与目前世界上最先进的涡 旋机构的全封闭定频空调压缩机进行能效对比实验。 实验情况的通俗简介 是这样： 两种实验机器都是在有油润滑旋转平稳为前提下开始， 以不间歇 地工作两小时为一个测试时段。 作为膨胀功能的汽油发动机的实验是原理 性实验， 供油供气供水稳定， 火花是由叶块触击产生。 第一个测试时段响 声比较清脆， 速度极快； 第二个测试时段响声比较混浊， 速度稍慢； 第三 个测试时段响声更加混浊， 最后 "爆膨"停转。 作为压缩功能的空调压缩 机其工作压力为 22减 4公斤， 制冷剂为 134a， 电机是自制的， 运行速度 为每分钟 1440转。第一个测试时段末尾的能效比为 6. 1， 比目前世界上最 先进的涡旋机构的空调压缩机能效比 3. 3高出近一倍， 抖动小一倍， 噪声 小一倍； 第二个测试时段末尾的能效比为 5. 8; 第三个测试时段末尾的能 效比为 5. 4; 第四个测试时段末尾的能效比为 4. 9; 随着测试时段 的增加能效比在逐步地下降。 We know that the technical requirements for airflow are much higher than the flow. In order to prove the excellent performance of this mechanism through experiments, I have specially formulated this mechanism into the basic form of a gasoline engine that can meet the essential requirements of the four-stroke technology in terms of its expansion function. In terms of its compression function, The mechanism is equipped with a fully enclosed fixed-frequency air-conditioning compressor, and it is also compared with the fully enclosed fixed-frequency air-conditioning compressor of the world's most advanced scroll mechanism. A popular introduction to the experimental situation is this: Both experimental machines start on the premise of smooth rotation with oil lubrication, and work two hours without interruption as a test period. The experiment of a gasoline engine as an expansion function is a principle experiment in which the supply of oil and gas is stable, and the spark is generated by the blade strike. In the first test period, the sound was crisp and the speed was very fast. In the second test period, the sound was turbid and the speed was slightly slower. In the third test period, the sound was more turbid, and finally the "explosion" stopped. The air-conditioning compressor as a compression function has a working pressure of 22 minus 4 kg and a refrigerant of 134 a. The motor is self-made and operates at a speed of 1440 rpm. The energy efficiency ratio at the end of the first test period is 6.1, which is nearly double the energy efficiency of the air conditioner compressor of the world's most advanced scroll mechanism, double the jitter and double the noise. The energy efficiency ratio at the end of the two test periods is 5.8; the energy at the end of the third test period The efficiency ratio is 5.4; the energy efficiency ratio at the end of the fourth test period is 4.9; the energy efficiency ratio gradually decreases as the test period increases.
不久， 本人分别细心地拆开了这两种实验机器， 却很容易就发现了一 个共同存在的问题， 那就是这种机构所分隔的容积已经不闭合了， 已形成 了泄漏， 主要是穿轴叶块与筒圆定子的配合间隙太大。 其实这个问题在零 件的设计与制造时早就非常强烈地意识到了， 特别是穿轴叶块径向两端与 筒圆定子型线的配合其零件装配后最大间隙只有 4丝， 而筒圆定子的椭圆 型线之短轴却有 108毫米， 其穿轴叶块是由 HRC72的硬质合金制成， 其筒 圆定子是由热处理 HRC50的轴承钢制成， 按理说在有油润滑情况下， 两者 镜面对磨的磨损应该是极小的， 而实验后却证明每个测试时段穿轴叶块将 要磨损缩短 2丝， 筒圆定子在远离转子轴心处将要磨损扩大 0. 2〜0. 4丝， 即原来用很不经济的方法加工成形的筒圆定子型线曲面也要有所变形 ^由 此看来， 发明出既能发挥出这种机构旋转地强制性与连续性分隔容积的优 势， 又能解决穿轴叶块与筒圆定子之间磨损与闭合的矛盾， 还能改善其它 各处的磨损与闭合的新式结构， 就成了这种机构从基础理论普及到生产实 践之中的关键问题了， 同时也就是从根本上解决人类能源节约、 地球气象 灾难的关键问题了。  Soon, I carefully disassembled the two experimental machines, but it was easy to find a common problem, that is, the volume separated by this mechanism is not closed, and a leak has been formed, mainly through the shaft. The fit clearance between the leaf block and the cylindrical stator is too large. In fact, this problem has been very strongly recognized in the design and manufacture of parts. In particular, the radial ends of the shaft bushings are matched with the cylindrical stator profile. The maximum clearance after assembly of the parts is only 4 wires, and the cylindrical stator The short axis of the elliptical line is 108 mm, and the through-axis blade is made of HRC72 hard alloy. The cylindrical stator is made of heat-treated HRC50 bearing steel. It is reasonable to say that in the case of oil lubrication, 2〜0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 4. Wire, that is, the curved surface of the cylindrical stator profile which was originally formed by a very uneconomical method must also be deformed. From this point of view, it is invented that the forced and continuous separation volume of the mechanism can be exerted. The advantages of this, can solve the contradiction between the wear and the closure between the shaft leaf and the cylindrical stator, and can also improve the new structure of wear and closure in other places, which becomes the mechanism from the basic theory to the production practice. The key question is, at the same time is a fundamental solution to the human energy conservation, the key issues of the global meteorological disaster.
发明内容 Summary of the invention
我们知道， 磨损是自然规律， 我们肯定要使用摩擦因数小、 磨损率低 的材料， 甚至依靠润滑介质不摩擦而闭合， 但是在这种机构上特别是在穿 轴叶块与筒圆定子配合上的实验证明这还远远不够， 要保证其可靠性就必 须另有构件嵌入到穿轴叶块的径向两端， 能够降低其摩擦力和给予其磨损 补偿， 不至于使得穿轴叶块与筒圆定子的配合类似线接触的死磨硬刮。 本发明特此提供的是一种专门的活动的耐磨密闭的新式结构， 其断面 外沿均是由弧缘线段组成的， 它可以根据气流或液流的技术需要设计为两 套样式： 一套是穿轴叶块在与筒圆定子相配合处设置其断面外沿呈" 6 " 或 " Ω "字形的耐磨密闭构件，利用伸出正圆的部分而构成铲贴摆动闭合 并进行磨损补偿. 另一套是穿轴叶块在与筒圆定子相配合处设置其断面外 沿呈正圆形的耐磨密闭构件， 甚至还可附加轴承予以稳定， 利用滚动均匀 地替换被磨损的位置或用好弹性应力而构成圆滑滚动闭合并进行磨损补 偿。 We know that wear is a natural law, we must use materials with low friction factor and low wear rate, even relying on the lubrication medium to close without friction, but in this mechanism, especially on the shaft and the cylindrical stator The experiment proves that this is not enough. To ensure its reliability, other components must be embedded in the radial ends of the shaft bushing to reduce the friction and wear it. The compensation is such that the fit of the shaft leaf block and the cylindrical stator is similar to the dead-wire scraping of the line contact. The present invention provides a special movable wear-resistant closed structure, the outer edges of which are composed of curved line segments, which can be designed into two sets according to the technical requirements of airflow or liquid flow: It is a wear-resistant sealing member with a "6" or "Ω" shape on the outer edge of the cross-section of the shaft and the cylindrical stator. The part of the shaft is extended to form a sway and is swayed and compensated for wear. The other set is a wear-resistant sealing member whose cross-section outer edge is rounded at the joint with the cylindrical stator, and can even be stabilized by additional bearings, and the worn position can be replaced uniformly by rolling. Good elastic stress constitutes a smooth rolling closure and wear compensation.
为此， 要特别注意的是： 有了上述的耐磨密闭构件的存在， 原来需要 用很不经济的方法加工成形的筒圆定子型线曲面现在变得很经济了， 将:能 够适应很多种成形机械来加工， 而且在口径短轴等同情形下所构成的容积 还扩大了。 这是因为现在它们变得可以是腰圆曲面， 也可以是几条正圆弧 线连接而成的型线曲面， 又可以是椭圆曲面， 还可以是椭圆弧线与正圆弧 线连接而成的型线曲面等等， 计算告诉我们在凹块转子偏置筒圆定子距离 符合容积结构较佳配置时， 这些曲面与所需要的正确精密的曲面相比较， 其偏差最大的曲面也只是两处大了约口径短轴的 0. 5 %， 用上述的耐磨密 闭构件完全可以补偿得了这个间隙， 何况机械的偏差从来就是无处不在 的。 另外， 有了上述的耐磨密闭构件的存在， 其耐磨密1 性能增强了， 在 膨胀功能方面完全可以适应于内燃类发动机的技术要求。 这样一来， 这种 膨胀或压缩机构原来的主要发明特征就有了质的改变， 运用本发明其技术 可靠性与普及率便可大大提高， 并且， 其能效比在 6. 1的基础上自然还可 大大提高 (好在这种机构原来就是由本人发明， 谁都没有获得过如此高的 能效比， 免了争辩之苦）。 To this end, it is necessary to pay special attention to: With the above-mentioned existence of the wear-resistant sealing member, it is now economical to use a very uneconomical method to process the formed cylindrical stator-shaped line surface, which will be able to adapt to a variety of The forming machine is used for machining, and the volume formed by the short axis of the aperture is also enlarged. This is because now they can be a waist-curved surface, or a curved surface that is connected by several positive arc lines, or an elliptical surface, or an elliptical arc connected to a positive arc. The shape of the curved surface, etc., the calculation tells us that when the concave rotor is biased, the circular stator distance is in accordance with the better configuration of the volume structure, the curved surface is only two places compared with the correct and precise curved surface required. The gap is about 0.5% of the short axis of the caliber, and the gap can be fully compensated by the above-mentioned wear-resistant sealing member, and the mechanical deviation is always ubiquitous. In addition, with the presence of the above-mentioned wear-resistant sealing member, the wear-resistance tightness performance is enhanced, and the expansion function can be fully adapted to the technical requirements of the internal combustion type engine. In this way, the original invention features of the expansion or compression mechanism have a qualitative change, the reliability and the penetration rate of the technology can be greatly improved by the use of the present invention, and the energy efficiency ratio is naturally based on 6.1. Can also Greatly improved (fortunately, this institution was originally invented by myself, and no one has ever achieved such a high energy efficiency ratio, free of arguments).
有了上述的发明我们还可以对于凹块转子与穿轴叶块的配合也进行改 造， 这对获得较高的能效比也是至关重要的。  With the above invention, we can also modify the fit of the concave rotor and the shaft bushing, which is also crucial for achieving a higher energy efficiency ratio.
技术效果： 能量是守恒的， 根据实验与计算本发明无疑可以比目前世 界最先进的膨胀或压缩机构高出一倍以上的能效比， 其压力就自然较大， 其噪声就自然轻柔， 其抖动就自然轻微， 其结构就自然轻巧。 不仅可以全 部取代目前的容积形式膨胀或压缩机构， 而且可以部份取代目前的透平形 式膨胀或压縮机构， 另外， 因为它的性能卓越还可形成许许多多的新型发 明。  Technical effect: The energy is conserved. According to the experiment and calculation, the invention can undoubtedly be more than twice the energy efficiency ratio of the world's most advanced expansion or compression mechanism, and the pressure is naturally large, and the noise is naturally soft and its jitter It is naturally light and its structure is naturally light. Not only can it replace the current volumetric expansion or compression mechanism, but it can also partially replace the current turboexpansion expansion or compression mechanism. In addition, because of its excellent performance, many new inventions can be formed.
我们知道， 任何发电站都是通过流体冲动透平形式的叶轮转子而发电 的， 其叶轮转子在原理与结构上因为有着叶片与叶片之间的间隔再加上与 祸圆定子之间的间隔， 便就有着压力泄漏的缺陷， 作为从动其亊实证明都 有至少一半的能量损失，如果运用本发明就没有这种泄漏的缺陷并且其流量与 流速也可相当， 将提高能效近一倍。  We know that any power station generates electricity by impeller rotors in the form of fluid impulse turbines. The principle and structure of the impeller rotors are due to the spacing between the blades and the blades and the spacing between the stators. There is a defect of pressure leakage. As a follow-up, it proves that there is at least half of the energy loss. If the invention is used, there is no such defect and the flow rate and flow rate are comparable, which will nearly double the energy efficiency.
我们都知道， 内燃类发动机也分容积形式与透平形式的膨胀， 两者能 效比都很低， 如果运用本发明肯定可以在同等燃料情况下使.目前的容积形 式提高超倍的输出力， 成而完全取代透平形式的膨胀。  As we all know, internal combustion engines are also expanded in volume and turbine form, both of which have low energy efficiency. If the invention is used, it is sure to increase the output capacity of the current volume by the same fuel. Completely replaces the expansion of the turbine form.
我们还知道， 运载机械的节能与安全一直以来都是困扰人类的两个重 大难题， 如果运用本发明并将其扩展为有贮气容器的气流传动系统， 就能 使得运载机械具有动力装置匀速工作又可通过收集热能形成热胀， 传动的 力量是先大后小又可无级变速， 驱驶的力量极为恰,当又可存贮多余的能 量， 还能全轮驱动又可全轮转向； 另外， 还能使得运载机械具有很大的外 置气囊等等， 这样两大难题就算解决了。 如果在汽车上运用还没有胆识， 我们至少可以在脚踏车上运用， 制造出靠气流或液流传动的可折叠为行李 车的自行车来。 We also know that the energy saving and safety of the carrying machinery has always been two major problems that plague humans. If the invention is applied and extended to an air flow transmission system with a gas storage container, the carrying machine can have a power device to work at a constant speed. It can also form thermal expansion by collecting heat energy. The power of the transmission is first and then small and can be steplessly changed. The driving force is extremely accurate, and when it can store excess energy. The volume can also be driven by all-wheel drive and all-wheel steering. In addition, the carrier machine can have a large external airbag, etc., so that the two major problems can be solved. If you don't have the courage to use it in a car, we can at least use it on a bicycle to create a bicycle that can be folded into a baggage car by airflow or liquid flow.
我们已经知道， 空调或制冷的压缩机一直以来都在耗费人类的大量能 源， 如果运用本发明将节约能源一倍， 这是无需置疑的。  We already know that air-conditioning or refrigeration compressors have been consuming a lot of human energy, and there is no doubt that using this invention will save energy twice.
我们应该知道， 实验表明： 利用超音速的高压气流冲动触电溶化的不 锈金属轰击钢铁表面是最好的钢铁不锈方法， 但是因空气压缩设备庞大， 既不经济也不方便， 一直停滞于实验室内无法面对实际。 如果运用本发明 就可将该设备縮小到比操作背包式火焰喷射器还要方便的形状， 成而就最 便捷地解决了钢铁的锈蚀问题。  We should know that the experiment shows that: the use of supersonic high-pressure air current impulse electro-oxidized stainless metal to bombard the steel surface is the best method of steel stainless, but because the air compression equipment is huge, it is neither economic nor convenient, and has been stagnant in the experiment. The interior cannot face the reality. If the present invention is used, the apparatus can be reduced to a shape more convenient than the operation of the backpack type flame ejector, and the rust problem of steel can be solved most conveniently.
本发明适用范围极其广泛， 以上仅是启发性的提示， 如果运用于气流 马达、 液流马达、 气流压泵、 液流压泵、 真空泵、 混流泵就将涵盖几乎 ¾ 个工业领域与生活领域，这明显是一次机械大革命，是解决人类能源节约， 地球气象灾难的核心技术， 也是每个有机械常识的人都能理解的通用技 术。  The scope of application of the present invention is extremely wide. The above is only an instructive suggestion. If applied to an air flow motor, a flow motor, a gas pressure pump, a liquid pressure pump, a vacuum pump, a mixed flow pump, it will cover almost 3⁄4 industrial fields and living areas. This is obviously a mechanical revolution, a core technology for solving human energy conservation, earth meteorological disasters, and a universal technology that can be understood by everyone with mechanical common sense.
以上所述仅仅用以解释为本发明的基本实施方案， 并非企图据此对本 发明做任何形式的运用限制； 于是， 凡是有在与本发明相关的任何改进或 变更， 均仍应该包括在本发明之权利要求的保护范围之内。  The above description is merely illustrative of the basic embodiments of the present invention and is not intended to limit the scope of the application to the present invention; therefore, any improvements or modifications related to the present invention should still be included in the present invention. Within the scope of the claims.
附图说明 DRAWINGS
为了更为具体地阐述本发明， 我们应该对照附图进行详细的了解： 图 1为一种内燃发动机膨胀机构的示意图。 图 2为一种液流膨胀或压缩机构的示意图。 In order to explain the present invention more specifically, it should be understood in detail with reference to the accompanying drawings: FIG. 1 is a schematic diagram of an internal combustion engine expansion mechanism. Figure 2 is a schematic illustration of a fluid flow expansion or compression mechanism.
图 3为一种气流膨胀或压縮机构的示意图。  Figure 3 is a schematic illustration of a gas flow expansion or compression mechanism.
图 4为一种较小的气流压缩机构的示意图  Figure 4 is a schematic view of a smaller airflow compression mechanism
图 5为一种较大的气流膨胀或压缩机构的示意图。  Figure 5 is a schematic illustration of a larger airflow expansion or compression mechanism.
(注意： 附图中的所示结构只是为了说明本发明特征的示意， 并非是 要依据附图所示结构， 对于等同功能的彼结构或此结件、 液流或气流、 膨 胀或压缩作任何相应运用上的限制； 如图 1的 10与图 3的 9， 图 2的 14 与图 4的 13其配合结构就可以互换运用； 如图 5同样可以作为较小的气 流膨胀或压缩机构， 同理， 若将进出通口开得一般大也就可以作为液流的 膨胀或压縮机构了。）  (Note: The structures shown in the drawings are merely illustrative of the features of the present invention, and are not intended to be in accordance with the structure shown in the drawings, for any structure or equivalent of this function, flow or air flow, expansion or compression Corresponding application restrictions; 10 in Fig. 1 and 9 in Fig. 3, 14 in Fig. 2 and 13 in Fig. 4 can be used interchangeably; as shown in Fig. 5, it can also be used as a small airflow expansion or compression mechanism. In the same way, if the inlet and outlet ports are generally open, they can be used as expansion or compression mechanisms for the liquid flow.)
具体实施方式 detailed description
显而易见， 本人所提供的是一种流体通道上的膨胀或压缩机构； 它包 括有支承构架 1、 流体进出通口 2、 3、 非正圆型线筒圆定子 4、 凹块转子 5、 穿轴叶块 6、 筒圆端盖 7、 输力构件 8; 其特征是: 轴叶块 6在与筒 圆定子 4相配合处另行设置有其断面外沿均由弧缘线条组成的活动的耐磨 密闭构件 9、 10、 11。 这样， 一方面可以使得与之配合的筒圆定子 4其加 工难度降低并适应众多的成形机械来加工， 另一方面可以使得穿轴叶块 6 在与筒圆定子 4配合时降低摩擦力并获得磨损补偿还形成可靠的密闭 (如 图 1、 图 2、 图 3、 图 4、 图 5所示）。  Obviously, what I have provided is an expansion or compression mechanism on the fluid passage; it includes a support frame 1, a fluid inlet and outlet port 2, 3, a non-circular cylindrical drum 4, a concave rotor 5, a through shaft The leaf block 6, the round end cover 7, the power transmission member 8; the feature is: the shaft leaf block 6 is separately provided with the movable wear resistance of the outer edge of the section which is composed of the curved edge line at the cooperation with the cylindrical stator 4 The sealing members 9, 10, 11. In this way, on the one hand, the cylindrical stator 4 which cooperates with it can be made less difficult to process and adapt to a large number of forming machines for processing, and on the other hand, the threaded blade block 6 can be reduced in friction when it is engaged with the cylindrical stator 4 and obtained. Wear compensation also forms a reliable seal (as shown in Figure 1, Figure 2, Figure 3, Figure 4, Figure 5).
在此之前我们应该清楚： 非正圆型线筒圆定子 4的型线曲面可以是腰 圆曲面，也可以是几条正圆弧线连接而成的型线曲面，又可以是椭圆曲面， 还可以是椭圆弧线与正圆弧线连接而成的型线曲面， 更可以是极轴坐标方 式连接而成的型线曲面或者等同的数学模型等等， 因为在凹块转子 5偏置 筒圆定子 4距离符合容积结构最佳配置时， 这些曲面与所需要的正确精密 的曲面相比较， 其偏差最大的曲面也只是两处大了约口径短轴的 0. 5 %， 也就是说偏差最大的曲面若口径短轴为 100毫米也只是两处大了约 50丝， 如若采用运转磨合工艺也就可能是 20丝 10丝甚至 "对零"， 只是 "对零" 后还会因被死磨硬刮再又产生偏差。 Before this, we should be clear: The profile surface of the non-circular bobbin circular stator 4 can be a waist-curved surface, or a curved surface connected by several positive circular arc lines, or an elliptical surface. It can be a curved surface connected by an elliptical arc and a positive circular arc, or it can be a polar coordinate Shaped curved surface or equivalent mathematical model, etc., because when the concave rotor 5 biases the cylindrical stator 4 distance to match the optimal configuration of the volume structure, these curved surfaces are compared with the correct precision curved surface required. The surface with the largest deviation is only about 0.5% larger than the short axis of the aperture. That is to say, if the diameter of the shortest axis is 100 mm, it is only about 50 filaments in two places, if the running-in process is adopted. It may be 20 filaments or even "zero to zero", but only after "zeroing", it will be biased by the dead and hard scraping.
所以， 本发明将提供两种其断面外沿均是由弧缘线条组成的活动的耐 磨密闭构件之基本形式： 一  Therefore, the present invention will provide two basic forms of a movable wear-resistant member whose outer edges of the section are each composed of curved line lines:
之一种其特征是穿轴叶块 6在与筒圆定子 4相配合处另行设置的是其 断面外沿呈 "6"或 " Ω "字形的摆动的耐磨密闭构件 9、 10， （如图 1、'. 图 3所示） 构成铲贴式耐磨密闭。 何以说其耐磨密闭？这是因为如果穿轴 叶块 6的径向两端是半圆曲面， 在偏置于非正圆型线筒圆定子 4旋转配合 时， 其两侧始终可以挤出多余的空间， 该空间可使半圆形变更为呈" 6 "' 或 " Ω "字形嵌入其中构成摆动， 而且可将呈" 6 "或 " Ω "字形中正圆 部分的至少 20 %与至少 60 %之尺寸作为其正圆伸出一向的厚度与宽度以 构成铲贴块片， 有如此宽厚的摆动的铲块再加上使用耐磨材料， 自然就可 以抵挡长期的磨损， 补偿上述偏差的闭合了。  One of the features is that the shaft bushing 6 is separately provided at the joint with the cylindrical stator 4 with a oscillating wear-resistant sealing member 9, 10 whose outer edge of the section is "6" or "Ω". Figure 1, '. Figure 3 shows a shovel-type wear-resistant seal. Why is it wear-resistant? This is because if the radial ends of the through-axis leaf block 6 are semi-circular curved surfaces, when the circular stator 4 is rotated and biased to the non-circular-shaped bobbin, the both sides can always squeeze excess space, and the space can be The semicircle is changed to a "6"' or "Ω" shape embedded in it to form a wobble, and at least 20% and at least 60% of the size of the perfect circle in the "6" or "Ω" shape can be used as its perfect circle. The thickness and width are always formed to form the shovel patch. With such a wide swinging shovel and the use of wear-resistant materials, it is naturally able to withstand long-term wear and compensate for the closure of the above deviation.
另一种其特征是穿轴叶块 6在与筒圆定子 4相配合处另行设置的是其 断面外沿呈正圆形的滚动的耐磨密闭构件 11， （如图 2、 图 4、 图 5所示） 构成圆滑式耐磨密闭。 何以说其耐磨密闭？这是因为圆滑滚动可以圆周性 均匀地替换被磨损的位置以弥补因磨损而失去的尺寸， 同时使得筒圆定子 4面对的是滚动摩擦， 这对于摩擦因素小的耐磨材料或耐磨涂镀工艺来说 是最好的用务之地， 奏巧的是， 大凡这样的材料同时还具有极为适应的能 补偿尺寸的弹性应力， 使用前增加认识， 两者合一， 自然就可以抵挡长期 的磨损， 补偿上述偏差的闭合了。 Another feature is that the shaft bushing 6 is separately provided at the joint with the cylindrical stator 4, and is a rolling wear-resistant sealing member 11 having a circular outer circumference. (FIG. 2, FIG. 4, FIG. 5 Shown) sleek wear-resistant seal. Why is it wear-resistant? This is because the smooth rolling can uniformly replace the worn position circumferentially to compensate for the size lost due to wear, and at the same time, the cylindrical stator 4 faces the rolling friction, which is a wear-resistant material or a wear-resistant coating having a small friction factor. Plating process It is the best place to work. It is a coincidence that most of these materials also have extremely adaptable elastic stresses that can compensate for the size. Increase the awareness before use. The combination of the two can naturally resist long-term wear and compensation. The above deviation is closed.
为了加强圆滑式耐磨密闭， 其特征是穿轴叶块 6在与筒圆定子 4相配 合处不仅另行设置有其断面外沿呈正圆形的滚动的耐磨密闭构件 11，而且 还附着有滚动轴承 12 (如图 2、 图 5所示）。 如果确定了旋转旋向的话， 其滚动的耐磨密闭构件 11的圆心与滚动轴承 12的圆心还可以相对于筒圆 定子 4形成一定的斜度。 如此这般， 哪有不能抵挡长期的磨损， 补偿上述 偏差的闭合之理？  In order to enhance the rounded wear-resistant sealing, the through-axis leaf block 6 is not only provided with a rolling wear-resistant sealing member 11 having a circular outer circumference but also a rolling bearing. 12 (as shown in Figure 2, Figure 5). If the rotational direction is determined, the center of the rolling wear-resistant sealing member 11 and the center of the rolling bearing 12 can also form a certain inclination with respect to the cylindrical stator 4. In this way, how can it resist the long-term wear and tear, and compensate for the closure of the above deviation?
对于凹块转子 5与穿轴叶块 6的闭合与磨损， 其特征是凹块转子 5在 与穿轴叶块 6相配合处另行设置有其断面外沿呈 " P "或 "L"字形的 贴式耐磨密闭构件 13、 14, " (如图 1、 图 2、 图 3、 图 4、 图 5所示） 我们 应该知道， 凹块转子 5中间如有穿轴叶块 6长期滑动并又受到流体压力作 用必然会有磨损， 有磨损就有泄漏， 而且这种磨损会形成过凹块转子 5轴 心的摆动角， 长此一往这种泄漏会使得高压流体直接冲往低压区间， 造成 这种机构形不成正常的膨胀或压缩， 所以， 在此处设置铲贴式耐磨密闭构 件 13、 14是必不可少的。  For the closing and wear of the concave block rotor 5 and the threading shaft block 6, the concave rotor 5 is additionally provided with a "P" or "L" shape on the outer edge of the cross section. Stick-type wear-resistant sealing members 13, 14" (as shown in Figure 1, Figure 2, Figure 3, Figure 4, Figure 5) We should know that if there is a long-term sliding of the shaft block 6 in the middle of the concave rotor 5 There will be wear due to the pressure of the fluid, there will be leakage when there is wear, and this kind of wear will form the swing angle of the axis of the concave rotor 5, and this leakage will cause the high pressure fluid to directly rush to the low pressure range, resulting in Such a mechanism does not form a normal expansion or compression, so it is indispensable to provide the blade-type wear-resistant sealing members 13, 14 here.
为了整体的给这种机构缩小磨损、减少摩擦，成而达到完好的闭合，（如 图 1、 图 2、 图 3、 图 4、 图 5所示） 本发明就将凹块转子 5在与穿轴叶块 6相配合处开有沟槽 15， 在沟槽之中装有滚动圆柱 16， 以构成滚动配合。 大家知道， 使用的滚动圆柱最简单的是圆柱直径稍大于曲面高度， 这样既 可滚动自如， 又可减小压强。 根据上述技术方案， 我们不难发现， 本发明基本上都是围绕着穿轴叶 块能够在筒圆定子内及凹块转子中灵活自如地耐磨与密闭， 为此， 本人通 过本发明特将穿轴叶块偏置筒圆旋转的膨胀或压缩机构改称为穿轴活块 偏置筒圆旋转的膨胀或压缩机构， 并简称为穿轴活块旋转式膨胀或压缩机 构， 或者干脆称为活块式膨胀压缩机构。 In order to reduce the wear and reduce the friction of the mechanism as a whole, the perfect closure is achieved (as shown in Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5). The present invention puts the concave rotor 5 in and out. The shaft block 6 is fitted with a groove 15 at the mating point, and a rolling cylinder 16 is arranged in the groove to constitute a rolling fit. As you know, the simplest way to use a rolling cylinder is that the diameter of the cylinder is slightly larger than the height of the surface, so that it can roll freely and reduce the pressure. According to the above technical solution, it is not difficult to find that the present invention basically wears and seals around the through-axis leaf block in the cylindrical stator and the concave rotor. For this reason, I have passed the special invention of the present invention. The expansion or compression mechanism that rotates the shaft leaf to bias the circular rotation of the shaft is called the expansion or compression mechanism of the circular rotation of the shaft-shaping block, and is simply referred to as a rotary expansion or compression mechanism of the shaft-through block, or simply called a live Block expansion compression mechanism.

Claims

权 利 要 求 Rights request
1、 一种流体通道上的膨胀或压縮机构； 它包括有支承构架（1)、 流体 进出通口 （2) (3)、 非正圆型线筒圆定子 （4 )、 凹块转子 （5 )、 穿轴叶 块 （6)、 筒圆端盖 （7)、 输力构件 （8); 其特征是： 穿轴叶块 (6)在与筒 圆定子 (4)相配合处另行设置有活动的耐磨密闭构件 (9) (10) (11)。  1. An expansion or compression mechanism on a fluid passage; comprising a support frame (1), a fluid inlet and outlet port (2) (3), a non-circular cylindrical drum stator (4), a concave rotor ( 5), the shaft leaf block (6), the round end cover (7), the power transmission member (8); the feature is: the shaft leaf block (6) is separately arranged in cooperation with the cylindrical stator (4) There are movable wear-resistant sealing members (9) (10) (11).
2、 根据权利要求 1所述的膨胀或压缩机构， 其特征是穿轴叶块（6) 在与筒圆定子 (4)相配合处另行设置的是摆动的耐磨密闭构件 (9) (10)。  2. An expansion or compression mechanism according to claim 1, characterized in that the shafting leaf block (6) is provided separately with a cylindrical wear-resisting member (9) (10). ).
3、 根据权利要求 1所述的膨胀或压缩机构， 其特征是穿轴叶块（6) 在与筒圆定子 (4)相配合处另行设置的是滚动的耐磨密闭构件 (11)。  3. Expansion or compression mechanism according to claim 1, characterized in that the threaded leaf block (6) is additionally provided with a rolling wear-resistant sealing member (11) in cooperation with the cylindrical stator (4).
4、 根据权利要求 1所述的膨胀或压縮机构， 其特征是穿轴叶块（6) 在与筒圆定子 （4)相配合处不仅另行设置有滚动的耐磨密闭构件（11)， 而且还附着有滚动轴承（12)。  4. The expansion or compression mechanism according to claim 1, characterized in that the through-axis leaf block (6) is not only provided with a rolling wear-resistant sealing member (11) in cooperation with the cylindrical stator (4), Also attached is a rolling bearing (12).
5、 根据权利要求 1所述的膨胀或压縮机构， 其特征是凹块转子 （5) 在与穿轴叶块 （6)相配合处另行设置有铲贴式耐磨密闭构件（13) (14)。  5. The expansion or compression mechanism according to claim 1, characterized in that the concave rotor (5) is additionally provided with a shovel-type wear-resistant sealing member (13) in cooperation with the thread-piercing blade (6) ( 14).
6、 根据权利要求 1所述的膨胀或压缩机构， 其特征是凹块转子（5) 在与穿轴叶块（6)相配合处开有沟槽（15)，在沟槽之中装有滚动圆柱（16)。  6. The expansion or compression mechanism according to claim 1, wherein the concave rotor (5) is provided with a groove (15) at a position where it fits with the shaft bushing (6), and is fitted in the groove Roll the cylinder (16).
PCT/CN2007/002280 2006-08-08 2007-07-30 Rotary expanding or compressing mechanism provided in fluid channel with blades for traversing shaft WO2008019575A1 (en)

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Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMI20091513A1 (en) * 2009-08-31 2011-03-01 Enea Mattei Spa Ing COMPRESSOR / EXPANDER WITH PALETTE HEADS WITH ROTATING ELEMENTS
WO2012118456A1 (en) * 2011-03-03 2012-09-07 Macsik Juraj Rotary vane machine provided with a non- cylindrical shaped working chamber
EP2639125A1 (en) * 2012-03-14 2013-09-18 Pierburg Pump Technology GmbH Automotive vacuum pump
CN107542657A (en) * 2016-06-24 2018-01-05 王辉明 Rotor sliding plate type air compressor
CN107387403A (en) * 2017-09-07 2017-11-24 浙江森汉图机电有限公司 A kind of extreme pressure pump

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2458681A1 (en) * 1979-06-11 1981-01-02 Jaffre Claude Rotary two stroke IC engine - has rotor with sliding radial vanes turning eccentrically with cylindrical stator
CN86103779A (en) * 1986-05-20 1988-03-09 潘景贤 Wearless sealing type power machine with sliding blade
WO1989002533A2 (en) * 1987-09-18 1989-03-23 Macleod Mitchell & Associates Ltd Rotary hydraulic machines
DE29720052U1 (en) * 1997-11-12 1998-02-19 Zaar Bernhard Rotary piston internal combustion engine
CN2308736Y (en) * 1997-07-24 1999-02-24 何崇恒 Rotary vane air conditioning compressor
DE20113784U1 (en) * 2001-08-17 2002-04-04 Iav Gmbh Variable-speed vane pump
CN2522647Y (en) * 2001-03-13 2002-11-27 王允江 Blade pump
CN1431396A (en) * 2003-01-27 2003-07-23 刘矗汀 Eccentric die insert type fluid drive mechanism without centrifugal force
CN2697351Y (en) * 2003-11-19 2005-05-04 何卫平 Vane pump

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1649256A (en) * 1923-02-10 1927-11-15 Rotary Machine & Engineering C Rotary pump
US2071799A (en) * 1934-09-08 1937-02-23 Mabille Raoul Rotary engine
US2048825A (en) * 1935-05-08 1936-07-28 Smelser Henry Daniel Rotary internal combustion engine
US2174664A (en) * 1937-06-17 1939-10-03 Julius S Korany Rotary internal combustion engine
US2260888A (en) * 1939-06-23 1941-10-28 Walwin L Davis Pump
US2410596A (en) * 1943-11-09 1946-11-05 Aaron C Bradford Sliding vane engine or pump
US3373929A (en) * 1965-11-15 1968-03-19 Trw Inc Vane assembly for rotary vane compressors
US3464395A (en) * 1967-11-27 1969-09-02 Donald A Kelly Multiple piston vane rotary internal combustion engine
US4938671A (en) * 1989-01-26 1990-07-03 Thompson George A Rotary roller pump with complementary ribs and grooves between housing, rotor and rollers
CN2208625Y (en) * 1994-08-31 1995-09-27 江南机器厂 Eccentric rotator type compressor
CN2306204Y (en) * 1997-07-22 1999-02-03 北京燕山粉研精机有限公司 Flexible sealed air-locking rotary valve for feeding
EP1424495A3 (en) * 2000-03-15 2004-06-23 Joma-Hydromechanic GmbH Vane pump

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2458681A1 (en) * 1979-06-11 1981-01-02 Jaffre Claude Rotary two stroke IC engine - has rotor with sliding radial vanes turning eccentrically with cylindrical stator
CN86103779A (en) * 1986-05-20 1988-03-09 潘景贤 Wearless sealing type power machine with sliding blade
WO1989002533A2 (en) * 1987-09-18 1989-03-23 Macleod Mitchell & Associates Ltd Rotary hydraulic machines
CN2308736Y (en) * 1997-07-24 1999-02-24 何崇恒 Rotary vane air conditioning compressor
DE29720052U1 (en) * 1997-11-12 1998-02-19 Zaar Bernhard Rotary piston internal combustion engine
CN2522647Y (en) * 2001-03-13 2002-11-27 王允江 Blade pump
DE20113784U1 (en) * 2001-08-17 2002-04-04 Iav Gmbh Variable-speed vane pump
CN1431396A (en) * 2003-01-27 2003-07-23 刘矗汀 Eccentric die insert type fluid drive mechanism without centrifugal force
CN2697351Y (en) * 2003-11-19 2005-05-04 何卫平 Vane pump

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CN101122365A (en) 2008-02-13
CN101122365B (en) 2012-07-04
US20100178189A1 (en) 2010-07-15
EP2058519A1 (en) 2009-05-13

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