WO2012079269A1 - 放出式高效气体压縮机 - Google Patents

放出式高效气体压縮机 Download PDF

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Publication number
WO2012079269A1
WO2012079269A1 PCT/CN2011/000221 CN2011000221W WO2012079269A1 WO 2012079269 A1 WO2012079269 A1 WO 2012079269A1 CN 2011000221 W CN2011000221 W CN 2011000221W WO 2012079269 A1 WO2012079269 A1 WO 2012079269A1
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WIPO (PCT)
Prior art keywords
gas
gas discharge
cooler
piston
compressor
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PCT/CN2011/000221
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English (en)
French (fr)
Inventor
靳北彪
Original Assignee
Jin Beibiao
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Publication date
Application filed by Jin Beibiao filed Critical Jin Beibiao
Publication of WO2012079269A1 publication Critical patent/WO2012079269A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/16—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by adjusting the capacity of dead spaces of working chambers
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/08—Actuation of distribution members
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves

Definitions

  • This invention relates to the field of thermal energy and power and gas compression, and more particularly to a discharge efficient gas compressor.
  • the compressed gas (high temperature and high pressure gas) in the clearance volume has a high temperature and high pressure, and will fill the volume above the piston when the piston descends, so that fresh air cannot enter the cylinder, thereby seriously affecting the efficiency of the gas compressor.
  • the clearance volume can hardly be eliminated in a piston gas compressor. For this reason, it is necessary to invent a new type of high efficiency gas compressor in which the clearance volume exists but reduces its effect on the efficiency reduction of the gas compressor. Summary of the invention
  • a discharge type high efficiency gas compressor comprising a piston type gas compressor, wherein a gas discharge seat is provided on a wall of a clearance volume envelope of the piston type gas compressor, at the gas discharge seat a gas discharge valve is provided, wherein the gas discharge valve is controlled by a gas discharge valve control mechanism; when the exhaust valve of the piston type gas compressor discharges high pressure gas and returns to a closed state, the gas discharge valve control mechanism The gas discharge valve is opened; when the piston of the piston type gas compressor has not left the top dead center or a small distance from the top dead center, the high temperature and high pressure gas in the clearance volume is pressurized from the piston gas The cylinder of the reducer is discharged through the gas discharge seat.
  • gas discharge passage communicating with the gas discharge seat at the gas discharge seat, the gas discharge passage being in communication with a gas inlet of the power turbine to recover high temperature and high pressure gas in the clearance volume of the power turbine
  • the energy turbine outputs power externally.
  • a compressor gas turbine is provided on an intake passage of the piston type gas compressor, and the power turbine outputs power to the compressor turbine.
  • the cooled gas outlet of the cooler is in communication with a gas inlet of the restrictor, the gas outlet of the restrictor being in communication with the inlet of the piston gas compressor.
  • the cooled gas outlet of the cooler is in communication with the sealed gas storage tank, so that high temperature and high pressure gas from the clearance volume is cooled and cooled in the cooler and stored in the sealed gas storage tank; the gas is released
  • the valve is opened by the gas discharge valve control mechanism during all or a certain time interval in the intake stroke of the piston type gas compressor, and is realized in an intake stroke of the piston type gas compressor.
  • High-temperature and high-pressure gas from the clearance volume that has been cooled in the sealed gas storage tank, all or a certain time interval flows through the cooler, the gas discharge passage, and then through the gas discharge seat Entering into the cylinder of the piston gas compressor.
  • the cooled gas outlet of the cooler is in communication with the sealed gas storage tank, and the high temperature and high pressure gas from the clearance volume is cooled and cooled in the cooler and stored in the sealed gas storage tank;
  • the discharge valve is opened by the gas discharge valve control mechanism at a certain time interval before the compression stroke of the piston type gas compressor, to realize a certain period before the compression stroke of the piston type gas compressor
  • the high temperature and high pressure gas from the clearance volume that has been cooled in the sealed gas storage tank is stored in the sealed gas tank through the cooler, the gas discharge passage, and then returned to the gas through the gas discharge seat.
  • the cylinder of the piston type gas compressor In the cylinder of the piston type gas compressor.
  • the gas discharge valve is a direct acting valve
  • the gas discharge valve control mechanism is a piston
  • the direct acting valve is controlled by the piston
  • a rotational inertia body is disposed on the power turbine and/or on a power output shaft of the power turbine, the rotary inertia body functions to maintain a rotational speed of the power turbine to achieve insufficient gas to push the power turbine ⁇ , it can form a suction effect on the gas, and more effectively discharge the gas in the clearance gap. If the intake valve is in the open state at this time, a scavenging and cooling effect on the clearance gap can be formed.
  • the so-called clearance volume envelope in the present invention refers to a surface in contact with the space constituting the clearance volume when the piston is at the top dead center, such as a piston crown, a cylinder head, and a part of the upper end of the cylinder.
  • the so-called gas discharge seat of the present invention is to be in communication with the clearance volume.
  • the so-called gas discharge seat is to communicate with the space forming the clearance volume.
  • the "the piston is separated from the top dead center by a small distance” means that the distance between the piston and the top dead center is small, and the volume above the piston is not much different from the clearance volume. Theoretically, the piston leaves the top dead center. The smaller the distance, the better, but according to the specific structure and the response speed of the control mechanism, the time when most of the high-temperature and high-pressure gas in the clearance volume is released is required to lag the top dead center of the piston. For this reason, the so-called “piston leaves the top dead center.
  • the "small distance” can be interpreted as the distance from the top dead center when the piston can effectively release the high temperature and high pressure gas in the clearance volume.
  • the so-called piston type gas compressor in the present invention includes a crank-and-rod type piston type gas compressor and a free piston type gas compressor.
  • the so-called direct acting valve in the present invention refers to a valve controlled by a piston;
  • the so-called rotational inertia body refers to a structure having a mass for rotational motion.
  • the so-called sealed gas storage tank in the present invention refers to a space for storing the cooled high-temperature high-pressure gas from the clearance volume (the temperature has been lowered after being cooled), and the so-called sealed gas storage tank can be integrated with the cooler. That is, a space in which the cooled high-temperature and high-pressure gas from the clearance volume can be stored is provided on the cooler to constitute a structure in which the cooler and the sealed gas storage tank are integrated.
  • compression stroke in the present invention means a part of the compression stroke from the start of the compression stroke to the end of the compression stroke.
  • the length of the pre-compression stroke is determined according to the pressure of the sealed gas storage tank. The purpose is to store the cooled high temperature and high pressure body from the clearance volume in the sealed gas storage tank under the condition of appropriate pressure difference. Reflux into the cylinder to reduce pressure loss and increase efficiency.
  • the cooler in the present invention may be a radiator or a heat exchanger, and the purpose thereof is to cool and cool the gas discharged from the clearance volume.
  • the present invention can reduce the influence of the clearance volume on the intake of the gas compressor, thereby improving the efficiency of the gas compressor.
  • Embodiment 1 is a schematic structural view of Embodiment 1 of the present invention.
  • Embodiment 2 is a schematic structural view of Embodiment 2 of the present invention.
  • Embodiment 3 is a schematic structural view of Embodiment 3 of the present invention.
  • Figure 4 is a schematic structural view of Embodiment 4 of the present invention.
  • Figure 5 is a schematic view showing the structure of Embodiment 5 of the present invention.
  • Figure 6 is a schematic view showing the structure of Embodiment 6 and Embodiment 7 of the present invention.
  • FIG. 7 is a schematic view showing the structure of Embodiment 8 of the present invention.
  • Figure 8 is a schematic view showing the structure of Embodiment 9 of the present invention.
  • the discharge type high-efficiency gas compressor shown in FIG. 1 includes a piston type gas compressor 1, and a gas discharge seat 2 is provided on a wall of the clearance volume envelope of the piston type gas compressor 1,
  • the gas discharge port 2 is provided with a gas discharge valve 3, and the gas discharge valve 3 is controlled by the gas discharge valve control mechanism 4; after the exhaust valve 5 of the piston type gas compressor 1 discharges high pressure gas, it is restored to In the closed state, the gas discharge valve control mechanism 4 opens the gas discharge valve 3; when the piston of the piston type gas compressor 1 has not left the top dead center or left the top dead center, The high temperature and high pressure gas in the clearance volume is discharged from the cylinder 100 of the piston type gas compressor 1 through the gas discharge seat 2 .
  • the discharge type high efficiency gas compressor shown in FIG. 2 is different from the first embodiment in that: the gas discharge seat 2 is provided with a gas discharge passage 6 communicating with the gas discharge seat 2, The gas discharge passage 6 communicates with the gas inlet of the power turbine 7, and the energy of the high-temperature and high-pressure gas in the clearance volume is recovered by the power turbine 7, and the power turbine 7 outputs power to the outside.
  • Example 3 The discharge type high efficiency gas compressor shown in FIG. 3 differs from the second embodiment in that: a gas turbine 8 is provided on the intake passage 101 of the piston type gas compressor 1, and the power turbine 7 is paired. The compressor turbine 8 outputs power.
  • the discharge type high-efficiency gas compressor shown in FIG. 4 is different from the first embodiment in that: a gas discharge passage 6 communicating with the gas discharge seat 2 is provided at the gas discharge seat 2; The gas discharge passage 6 is provided with a cooler 9 communicating with the cooled gas inlet of the cooler 9, the cooled gas outlet of the cooler 9 and the piston type gas compressor 1
  • the intake port 101 is in communication.
  • the discharge type high efficiency gas compressor shown in FIG. 5 is different from the first embodiment in that: a gas discharge passage 6 communicating with the gas discharge seat 2 is provided at the gas discharge seat 2; The gas discharge passage 6 is provided with a cooler 9 that communicates with the cooled gas inlet of the cooler 9, and the cooled gas outlet of the cooler 9 communicates with the gas inlet of the restrictor 10, The gas outlet of the restrictor 10 communicates with the intake port 101 of the piston type gas compressor 1.
  • the discharge type high efficiency gas compressor shown in FIG. 6 is different from the first embodiment in that: a gas discharge passage 6 communicating with the gas discharge seat 2 is provided at the gas discharge seat 2;
  • the gas discharge passage 6 is provided with a cooler 9 that communicates with the cooled gas inlet of the cooler 9, and the cooled gas outlet of the cooler 9 communicates with the sealed gas storage tank 12 to realize The high temperature and high pressure gas in the clearance volume is cooled and cooled in the cooler 9 and stored in the sealed gas storage tank 12;
  • the gas discharge valve 3 is controlled by the gas discharge valve control mechanism 4 at the piston All or a certain time interval of the intake stroke of the gas compressor 1 is opened, and is realized in all or a certain time interval in the intake stroke of the piston type gas compressor 1
  • the high temperature and high pressure gas from the clearance volume that has been cooled in the sealed gas storage tank 12 is returned to the piston gas pressure through the cooler 9, the gas discharge passage 6 and the gas discharge seat 2 Inside the cylinder 100 of the compressor 1.
  • the discharge type high efficiency gas compressor shown in FIG. 6 is different from the first embodiment in that: a gas discharge passage 6 communicating with the gas discharge seat 2 is provided at the gas discharge seat 2;
  • the gas discharge passage 6 is provided with a cooler 9 that communicates with the cooled gas inlet of the cooler 9, and the cooled gas outlet of the cooler 9 communicates with the sealed gas storage tank 12 to realize The high temperature and high pressure gas in the clearance volume is cooled and cooled in the cooler 9 and stored in the sealed gas storage tank 12; the gas discharge valve 3 is controlled by the gas discharge valve control mechanism 4 at the piston
  • the gas compressor 1 is opened at a certain time interval before the compression stroke, and is stored in the sealed gas tank at a certain time interval before the compression stroke of the piston gas compressor 1
  • the high temperature and high pressure gas from the clearance volume that has been cooled in 12 is returned to the piston type gas compressor 1 through the cooler 9, the gas discharge passage 6 and through the gas discharge seat 2 Inside the cylinder 100.
  • the discharge type high efficiency gas compressor shown in FIG. 7 is different from the first embodiment in that: the gas discharge valve 3 is a direct acting valve 3000, and the gas discharge valve control mechanism 4 is set as a piston 4000.
  • the direct acting valve 3000 is controlled by the piston 4000.
  • the discharge type high efficiency gas compressor shown in Fig. 8 differs from the second embodiment in that a rotational inertia body 7000 is provided on the power turbine 7 and/or on the power output shaft of the power turbine 7.
  • the function of the rotary inertia body 7000 is to maintain the rotational speed of the power turbine to achieve a function of aspirating the gas when the gas that pushes the power turbine is insufficient, and more effectively discharge the gas in the clearance gap.
  • the intake valve 1000 is in an open state, and a scavenging and cooling effect on the clearance gap can be formed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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Description

说 明 书
放出式高效气体压縮机
技术领域
本发明涉及热能与动力及气体压縮领域， 尤其是一种放出式高效气体压縮 机。
背景技术
余隙容积内的被压縮气体 （高温高压气体）， 温度高压力大， 在活塞下行 时会充满活塞上方容积， 使新鲜空气无法进入气缸内， 从而严重影响气体压縮 机的效率。 然而， 由于机械加工误差、 机械磨损、 热变形以及部件结构特征等 因素， 使余隙容积在活塞式气体压縮机中几乎无法消除。 为此， 需要发明一种 余隙容积存在但减少其对气体压縮机效率降低作用的新型高效气体压縮机。 发明内容
为了解决上述问题， 本发明提出的技术方案如下：
一种放出式高效气体压縮机， 包括活塞式气体压縮机， 在所述活塞式气体 压縮机的余隙容积包络的壁上设气体放出座口，在所述气体放出座口处设气体 放出阀， 所述气体放出阀受气体放出阀控制机构控制; 在所述活塞式气体压縮 机的排气门排出高压气体后恢复到关闭状态时，所述气体放出阀控制机构将所 述气体放出阀打开； 实现在所述活塞式气体压縮机的活塞还没有离开上止点或 离开上止点很小距离时，将余隙容积内的高温高压气体从所述活塞式气体压縮 机的气缸内经所述气体放出座口放出。
在所述气体放出座口处设与所述气体放出座口连通的气体放出通道，所述 气体放出通道与动力涡轮的气体入口连通， 实现以所述动力涡轮回收余隙容积 内的高温高压气体的能量， 所述动力涡轮对外输出动力。
在所述活塞式气体压縮机的进气道上设压气涡轮，所述动力涡轮对所述压 气涡轮输出动力。
在所述气体放出座口处设与所述气体放出座口连通的气体放出通道， 在所 述气体放出通道上设冷却器， 所述气体放出通道与所述冷却器的被冷却气体入 口连通， 所述冷却器的被冷却气体出口与所述活塞式气体压縮机的进气道连 通。
在所述气体放出座口处设与所述气体放出座口连通的气体放出通道，在所 述气体放出通道上设冷却器，所述气体放出通道与所述冷却器的被冷却气体入 口连通， 所述冷却器的被冷却气体出口与节流器的气体入口连通， 所述节流器 的气体出口与所述活塞式气体压縮机的进气道连通。
在所述气体放出座口处设与所述气体放出座口连通的气体放出通道，在所 述气体放出通道上设冷却器，所述气体放出通道与所述冷却器的被冷却气体入 口连通， 所述冷却器的被冷却气体出口与密封储气罐连通， 实现来自余隙容积 内的高温高压气体在所述冷却器中被冷却降温并储存在所述密封储气罐内； 所 述气体放出阀受所述气体放出阀控制机构控制在所述活塞式气体压縮机的吸 气冲程中的全部或某一时间间隔内打开， 实现在所述活塞式气体压縮机的吸气 冲程中的全部或某一时间间隔内将储存在所述密封储气罐中已被冷却的来自 余隙容积内的高温高压气体经所述冷却器、所述气体放出通道再经所述气体放 出座口回流进入到所述活塞式气体压縮机的所述气缸内。
在所述气体放出座口处设与^ f述气体放出座口连通的气体放出通道，在所 述气体放出通道上设冷却器，所述气体放出通道与所述冷却器的被冷却气体入 口连通， 所述冷却器的被冷却气体出口与密封储气罐连通， 实现来自余隙容积 内的高温高压气体在所述冷却器中被冷却降温并储存在所述密封储气罐内； 所 述气体放出阀受所述气体放出阀控制机构控制在所述活塞式气体压縮机的压 縮冲程前期的某一时间间隔内打开， 实现在所述活塞式气体压縮机的压縮冲程 前期的某一时间间隔内将储存在所述密封储气罐中已被冷却的来自余隙容积 内的高温高压气体经所述冷却器、所述气体放出通道再经所述气体放出座口回 流进入到所述活塞式气体压縮机的所述气缸内。
所述气体放出阀设为直动阀， 所述气体放出阀控制机构设为活塞， 所述直 动阀受所述活塞控制。
在所述动力涡轮上和 /或在所述动力涡轮的动力输出轴上设旋转惯量体， 所述旋转惯量体的作用是维持所述动力涡轮的转速以实现当推动所述动力涡 轮的气体不足吋，能够对气体形成吸出的作用，更有效排出余隙间隙内的气体， 如果这时进气门处于开启状态， 可形成对余隙间隙的扫气降温作用。
本发明中所谓的余隙容积包络是指活塞位于上止点时，构成余隙容积的空 间所接触的面， 如活塞顶， 缸盖以及气缸上端的一部分。
本发明中所谓的气体放出座口要与余隙容积连通， 换句话说， 所谓的气体 放出座口要与形成余隙容积的空间连通。
本发明中所谓 "活塞离开上止点很小距离"是指活塞离开上止点的距离很 小， 活塞上方容积与余隙容积相差不大的状态， 从理论上讲, 活塞离开上止点 的距离越小越好， 但是根据具体结构和控制机构的响应速度， 余隙容积内的高 温高压气体被大部分放出时的时间需要滞后活塞上止点， 为此， 所谓的 "活塞 离开上止点很小距离"可以解释为能够将余隙容积内的高温高压气体有效放出 时的活塞离开上止点的距离。
本发明中所谓的活塞式气体压縮机包括曲柄连杆机构活塞式气体压縮机 和自由活塞式气体压縮机。
本发明中所谓的直动阀是指受活塞控制的阀； 所谓旋转惯量体是指具有质 量的作旋转运动的结构体。
本发明中所谓的密封储气罐是指储存被冷却的来自余隙容积的高温高压 气体（被冷却后温度已降低） 的空间， 所谓的密封储气罐可以与所述冷却器设 为一体式，也就是说可以在所述冷却器上设置可以储存被冷却的来自余隙容积 的高温高压气体的空间， 以构成将所述冷却器和所述密封储气罐设为一体式的 结构。
本发明中所谓压縮冲程前期是指自压縮冲程开始起至压縮冲程未结束止 的压縮冲程的部分过程。压縮冲程前期的长短要根据所述密封储气罐的压力决 定， 其目的是要在压差适当的条件下， 将储存在密封储气罐内的被冷却的来自 余隙容积的高温高压 体回流到气缸内， 以减少压力损失， 提高效率。
本发明中的冷却器， 可以是散热器， 也可以是热交换器， 其目的是将从余 隙容积内排出的气体进行冷却降温。
本发明中， 根据热能与动力领域及气体压縮领域的公知技术， 在必要处设 置必要的机构、 单元及系统， 如阀、 泵、 控制机构等。 本发明的有益效果如下：
本发明能减小余隙容积对气体压縮机的进气影响，从而提高气体压縮机的 效率。
附图说明
图 1所示的是本发明实施例 1的结构示意图；
图 2所示的是本发明实施例 2的结构示意图；
图 3所示的是本发明实施例 3的结构示意图；
图 4所示的是本发明实施例 4的结构示意图；
图 5所示的是本发明实施例 5的结构示意图；
图 6所示的是本发明实施例 6和实施例 7的结构示意图；
图 7所示的是本发明实施例 8的结构示意图；
图 8所示的是本发明实施例 9的结构示意图。
具体实施方式
实施例 1
如图 1所示的放出式高效气体压縮机， 包括活塞式气体压縮机 1， 在所述 活塞式气体压縮机 1的余隙容积包络的壁上设气体放出座口 2， 在所述气体放 出座口 2处设气体放出阀 3,所述气体放出阀 3受气体放出阀控制机构 4控制； 在所述活塞式气体压縮机 1的排气门 5排出高压气体后恢复到关闭状态时，所 述气体放出阀控制机构 4将所述气体放出阀 3打开； 实现在所述活塞式气体压 縮机 1的活塞还没有离开上止点或离开上止点很小距离时，将余隙容积内的高 温高压气体从所述活塞式气体压縮机 1的气缸 100内经所述气体放出座口 2放 出。
实施例 2
如图 2所示的放出式高效气体压縮机， 其与实施例 1的区别是： 在所述气 体放出座口 2处设与所述气体放出座口 2连通的气体放出通道 6， 所述气体放 出通道 6与动力涡轮 7的气体入口连通， 实现以所述动力涡轮 7回收余隙容积 内的高温高压气体的能量， 所述动力涡轮 7对外输出动力。
实施例 3 如图 3所示的放出式高效气体压縮机， 其与实施例 2的区别是： 在所述活 塞式气体压縮机 1的进气道 101上设压气涡轮 8， 所述动力涡轮 7对所述压气 涡轮 8输出动力。
实施例 4
如图 4所示的放出式高效气体压縮机， 其与实施例 1的区别是： 在所述气 体放出座口 2处设与所述气体放出座口 2连通的气体放出通道 6， 在所述气体 放出通道 6上设冷却器 9， 所述气体放出通道 6与所述冷却器 9的被冷却气体 入口连通，所述冷却器 9的被冷却气体出口与所述活塞式气体压縮机 1的进气 道 101连通。
实施例 5
如图 5所示的放出式高效气体压縮机， 其与实施例 1的区别是： 在所述气 体放出座口 2处设与所述气体放出座口 2连通的气体放出通道 6， 在所述气体 放出通道 6上设冷却器 9， 所述气体放出通道 6与所述冷却器 9的被冷却气体 入口连通， 所述冷却器 9的被冷却气体出口与节流器 10的气体入口连通， 所 述节流器 10的气体出口与所述活塞式气体压縮机 1的进气道 101连通。
实施例 6
如图 6所示的放出式高效气体压縮机， 其与实施例 1的区别是： 在所述气 体放出座口 2处设与所述气体放出座口 2连通的气体放出通道 6， 在所述气体 放出通道 6上设冷却器 9， 所述气体放出通道 6与所述冷却器 9的被冷却气体 入口连通， 所述冷却器 9的被冷却气体出口与密封储气罐 12连通， 实现来自 余隙容积内的高温高压气体在所述冷却器 9中被冷却降温并储存在所述密封储 气罐 12内； 所述气体放出阀 3受所述气体放出阀控制机构 4控制在所述活塞 式气体压縮机 1的吸气冲程中的全部或某一时间间隔内打开， 实现在所述活塞 式气体压縮机 1的吸气冲程中的全部或某一时间间隔内将储存在所述密封储气 罐 12中已被冷却的来自余隙容积内的高温高压气体经所述冷却器 9、所述气体 放出通道 6再经所述气体放出座口 2回流进入到所述活塞式气体压縮机 1的所 述气缸 100内。 如图 6所示的放出式高效气体压縮机， 其与实施例 1的区别是： 在所述气 体放出座口 2处设与所述气体放出座口 2连通的气体放出通道 6， 在所述气体 放出通道 6上设冷却器 9， 所述气体放出通道 6与所述冷却器 9的被冷却气体 入口连通， 所述冷却器 9的被冷却气体出口与密封储气罐 12连通， 实现来自 余隙容积内的高温高压气体在所述冷却器 9中被冷却降温并储存在所述密封储 气罐 12内； 所述气体放出阀 3受所述气体放出阀控制机构 4控制在所述活塞 式气体压縮机 1的压縮冲程前期的某一时间间隔内打开， 实现在所述活塞式气 体压縮机 1 的压縮冲程前期的某一时间间隔内将储存在所述密封储气罐 12中 已被冷却的来自余隙容积内的高温高压气体经所述冷却器 9、 所述气体放出通 道 6再经所述气体放出座口 2回流进入到所述活塞式气体压縮机 1的所述气缸 100内。
实施例 8
如图 7所示的放出式高效气体压縮机， 其与实施例 1的区别是： 所述气体 放出阀 3设为直动阀 3000， 所述气体放出阀控制机构 4设为活塞 4000， 所述 直动阀 3000受所述活塞 4000控制。
实施例 9
如图 8所示的放出式高效气体压縮机， 其与实施例 2的区别是： 在所述动 力涡轮 7上和 /或在所述动力涡轮 7的动力输出轴上设旋转惯量体 7000。 所述 旋转惯量体 7000的作用是维持所述动力涡轮的转速以实现当推动所述动力涡 轮的气体不足吋，能够对气体形成吸出的作用，更有效排出余隙间隙内的气体， 如果这时进气门 1000处于开启状态， 可形成对余隙间隙的扫气降温作用。

Claims

权 利 要 求
1、 一种放出式高效气体压縮机， 包括活塞式气体压縮机 （1 )， 其特征在 于：在所述活塞式气体压縮机（1 )的余隙容积包络的壁上设气体放出座口（2)， 在所述气体放出座口 （2)处设气体放出阀 （3)， 所述气体放出阀 （3) 受气体 放出阀控制机构 （4) 控制； 在所述活塞式气体压縮机 （1 ) 的排气门 （5) 排 出高压气体后恢复到关闭状态时， 所述气体放出阀控制机构 （4) 将所述气体 放出阀 （3)打开； 实现在所述活塞式气体压縮机 （1 ) 的活塞还没有离开上止 点或离开上止点很小距离时，将余隙容积内的高温高压气体从所述活塞式气体 压縮机 （1 ) 的气缸 （100) 内经所述气体放出座口 （2) 放出。
2、 根据权利要求 1 所述放出式高效气体压縮机， 其特征在于： 在所述气 体放出座口 （2)处设与所述气体放出座口 （2)连通的气体放出通道（6); 所 述气体放出通道（6) 与动力涡轮（7) 的气体入口连通， 实现以所述动力涡轮
(7) 回收余隙容积内的高温高压气体的能量， 所述动力涡轮（7)对外输出动 力。
3、 根据权利要求 2所述放出式高效气体压縮机， 其特征在于： 在所述活 塞式气体压縮机（1 ) 的进气道 （101 ) 上设压气涡轮 （8)， 所述动力涡轮（7) 对所述压气涡轮 （8) 输出动力。
4、 根据权利要求 1 所述放出式高效气体压縮机， 其特征在于： 在所述气 ^放出座口 （2)处设与所述气体放出座口 （2)连通的气体放出通道（6)， 在 所述气体放出通道（6) 上设冷却器 （9)， 所述气体放出通道（6) 与所述冷却 器 （9) 的被冷却气体入口连通， 所述冷却器 （9) 的被冷却气体出口与所述活 塞式气体压縮机 （1 ) 的进气道 （101 ) 连通。
5、 根据权利要求 1 所述放出式高效气体压縮机， 其特征在于： 在所述气 体放出座口 （2) 处设与所述气体放出座口 （2)连通的气体放出通 ϋ (6)， 在 所述气体放出通道（6)上设冷却器 （9)， 所述气体放出通道（6) 与所述冷却 器 （9) 的被冷却气体入口连通， 所述冷却器 （9) 的被冷却气体出口与节流器
( 10) 的气体入口连通， 所述节流器（10) 的气体出口与所述活塞式气体压縮 机 （1 ) 的进气道 （101 ) 连通。
6、 根据权利要求 1 所述放出式高效气体压縮机， 其特征在于： 在所述气 体放出座口 （2)处设与所述气体放出座口 （2) 连通的气体放出通道（6)， 在 所述气体放出通道（6) 上设冷却器 （9)， 所述气体放出通道 （6) 与所述冷却 器 （9) 的被冷却气体入口连通， 所述冷却器（9) 的被冷却气体出口与密封储 气罐 （12) 连通， 实现来自余隙容积内的高温高压气体在所述冷却器 （9) 中 被冷却降温并储存在所述密封储气罐 （12) 内； 所述气体放出阀 （3) 受所述 气体放出阀控制机构（4)控制在所述活塞式气体压縮机（1 ) 的吸气冲程中的 全部或某一时间间隔内打开， 实现在所述活塞式气体压縮机 （1 ) 的吸气冲程 中的全部或某一时间间隔内将储存在所述密封储气罐（12) 中已被冷却的来自 余隙容积内的高温高压气体经所述冷却器 （9)、 所述气体放出通道 （6) 再经 所述气体放出座口（ 2 )回流进入到所述活塞式气体压縮机（ 1 )的所述气缸（ 100 ) 内。
7、 根据权利要求 1 所述放出式高效气体压縮机， 其特征在于： 在所述气 体放出座口 （2)处设与所述气体放出座口 （2)连通的气体放出通道（6)， 在 所述气体放出通道（6)上设冷却器 （9)， 所述气体放出通道（6) 与所述冷却 器 （9) 的被冷却气体入口连通， 所述冷却器 （9) 的被冷却气体出口与密封储 气罐 （12) 连通， 实现来自余隙容积内的高温高压气体在所述冷却器 （9) 中 被冷却降温并储存在所述密封储气罐 （12) 内； 所述气体放出阀 （3) 受所述 气体放出阀控制机构（4)控制在所述活塞式气体压縮机（1 ) 的压縮冲程前期 的某一时间间隔内打开， 实现在所述活塞式气体压縮机 （1 ) 的压縮冲程前期 的某一时间间隔内将储存在所述密封储气罐（12) 中已被冷却的来自余隙容积 内的高温高压气体经所述冷却器 （9)、 所述气体放出通道 （6) 再经所述气体 放出座口 （2) 回流进入到所述活塞式气体压縮机 （1 ) 的所述气缸 （100) 内。
8、 根据权利要求 1 所述放出式高效气体压縮机， 其特征在于： 所述气体 放出阀（ 3 )设为直动阀（ 3000 )，所述气体放出阀控制机构（ 4 )设为活塞（ 4000 )， 所述直动阀 （3000) 受所述活塞 （4000) 控制。
9、 根据权利要求 2所述放出式高效气体压縮机， 其特征在于： 在所述动 力涡轮（7)上和 /或在所述动力涡轮（7)的动力输出轴上设旋转惯量体（7000)。
PCT/CN2011/000221 2010-12-17 2011-02-12 放出式高效气体压縮机 WO2012079269A1 (zh)

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