WO2012027918A1 - 带调相机构的g-m制冷机 - Google Patents

带调相机构的g-m制冷机 Download PDF

Info

Publication number
WO2012027918A1
WO2012027918A1 PCT/CN2010/077524 CN2010077524W WO2012027918A1 WO 2012027918 A1 WO2012027918 A1 WO 2012027918A1 CN 2010077524 W CN2010077524 W CN 2010077524W WO 2012027918 A1 WO2012027918 A1 WO 2012027918A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
cylinder
phase modulation
gas
refrigerator
Prior art date
Application number
PCT/CN2010/077524
Other languages
English (en)
French (fr)
Inventor
巢伟
陈杰
庄坤融
高金林
Original Assignee
南京柯德超低温技术有限公司
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 南京柯德超低温技术有限公司 filed Critical 南京柯德超低温技术有限公司
Priority to EP10856605.0A priority Critical patent/EP2482004B1/en
Priority to JP2012540263A priority patent/JP5589193B2/ja
Priority to US13/498,092 priority patent/US20120227417A1/en
Publication of WO2012027918A1 publication Critical patent/WO2012027918A1/zh

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/10—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point with several cooling stages

Definitions

  • the present invention relates to a cryogenic refrigerator, and more particularly to a regenerative cryogenic refrigerator, and more particularly to a G-M refrigerator with a phase modulation mechanism.
  • the G-M refrigeration cycle was invented by Gifford and Mcmahon, and the principle is to use adiabatic gas to vent gas.
  • G-M chillers have been widely used in cryogenic pumps and for cooling a variety of superconducting magnets. In applications, it is common to use a cold head of a chiller for direct contact or a material with a high thermal conductivity as a thermal bridge for cooling.
  • the sealing ring reciprocates with the piston in the cylinder, the sealing between the sealing ring and the cylinder and between the sealing ring and the piston is not strict, the high temperature gas in the hot chamber leaks through the sealing ring to the cold chamber, and the low temperature gas in the cold chamber passes. Leakage of the seal ring into the hot chamber will cause loss of cooling. This part of the loss is called leakage loss.
  • leakage loss As the running time of the chiller increases, the wear of the seal ring will gradually increase, the seal of the seal ring and the cylinder and the piston will become looser and looser, and the amount of air leakage through the seal ring will become larger and larger, and the amount of cold generated will be generated. The loss will also increase.
  • the frictional heat generated by the sliding seal of the seal ring in the cylinder can also cause a loss of cooling.
  • the object of the present invention is to provide a G-M refrigerator with a phase modulation mechanism by introducing a phase modulation mechanism.
  • the following technical problems are solved: changing the working process of the gas in the gap between the piston and the cylinder of the GM refrigerator, making full use of the partial gas expansion work, and preventing the gas leakage loss through the sealing ring, thereby making the GM refrigerator obtain better performance.
  • a GM refrigerator with a phase modulation mechanism comprising a compressor, an intake valve, an exhaust valve, a regenerator, a cylinder, a piston, a hot chamber, a cold chamber, a drive mechanism, an annular gap and a heat exchanger,
  • the outlet end of the compressor is connected to the intake valve
  • the intake end of the compressor is connected to the exhaust valve
  • the intake valve, the exhaust valve and the regenerator are connected
  • the regenerator is connected with the cylinder
  • the regenerator A heat exchanger is arranged between the cylinder;
  • a piston is arranged in the cylinder, a cold chamber is below the piston, a hot chamber is above the piston, an annular gap is formed between the piston and the inner wall of the cylinder, and a driving mechanism is connected to the piston; an annular gap and a phase modulation mechanism Connected.
  • the annular gap can be divided into a hot end gas, a gas piston, and a cold end gas.
  • the phase modulation mechanism includes a small orifice valve and a gas reservoir, and the annular gap communicates with the gas reservoir through the small orifice valve; a sealing ring is disposed between the piston and the cylinder at a position above the annular gap.
  • the phase modulation mechanism is a small hole gas reservoir structure or a two-way air intake mechanism or a four-valve mechanism or other more effective phase modulation mechanism that communicates with the hot end of the cylinder.
  • the phase modulation mechanism can be built in, including a built-in small hole valve and a gas reservoir, and the built-in small hole valve is placed in the annular gap of the hot end of the piston, and the heat chamber serves as a gas reservoir of the phase modulation mechanism.
  • Both the intake and exhaust valves are at room temperature.
  • the regenerator is provided with a regenerative filler.
  • the driving mechanism connected to the piston is a crank connecting rod driving mechanism, and the driving mechanism includes a piston rod, a connecting rod and a crank.
  • the invention changes the working process of the gas in the annular gap, can fully utilize the gas expansion work of the part, and prevents the gas leakage loss through the sealing ring, thereby obtaining better performance of the GM refrigerator.
  • FIG. 1 is a schematic view of a G-M refrigerator system with a phase modulation mechanism according to the present invention.
  • Figure 2 is one of the working processes of the gas in the annular gap after the phase modulation mechanism is introduced into the G-M refrigerator.
  • Figure 3 is the second working diagram of the gas in the annular gap after the phase modulation mechanism is introduced into the G-M refrigerator.
  • Figure 4 is the third working diagram of the gas in the annular gap after the phase modulation mechanism is introduced into the G-M refrigerator.
  • Figure 5 is a system diagram of the G-M refrigerator built in the phase modulation mechanism.
  • Figure 6 is a system diagram of introducing a phase modulation mechanism into the second stage of a two-stage G-M refrigerator.
  • GM refrigerator with phase modulation mechanism including compressor 1, intake valve 2, exhaust valve 3, regenerator 4, cylinder 5, piston 6, hot chamber 7, cold chamber 8, drive mechanism, annular clearance 13 and the heat exchanger 14, the outlet end of the compressor 1 is connected to the intake valve 2, the intake end of the compressor 1 is connected to the exhaust valve 3, the intake valve 2, the exhaust valve 3 and the regenerator 4
  • the regenerator 4 is connected to the cylinder 5, and the heat exchanger 14 is disposed between the regenerator 4 and the cylinder 5; the piston 6 is disposed in the cylinder 5, and the cold chamber 8 is below the piston 6, and the piston 6 is hot.
  • the cavity 7, the piston 6 and the inner wall of the cylinder 5 are an annular gap 13, and the piston 6 is connected to the driving mechanism; the annular gap 13 is in communication with the phase modulation mechanism.
  • the gas in the annular gap 13 can be divided into a hot end gas 20, a gas piston 21, and a cold end gas 22.
  • a hot end gas Above the gas piston 21 is a hot end gas, and below the gas piston 21 is a cold end gas.
  • the phase adjustment mechanism includes a small orifice valve 18 and a gas reservoir 19, and the annular gap 13 is communicated with the gas reservoir 19 through the small orifice valve 18; a sealing ring 9 is disposed between the piston 6 and the cylinder 5 at a position above the annular gap 13
  • the annular gap 13 is closed by the inner wall of the cylinder 5, the outer wall of the piston 6, the sealing ring 9, and the like. It is used to adjust the phase relationship of the working gas in the annular gap 13, thereby improving the performance of the G-M refrigerator.
  • phase modulation mechanism of the present invention may also be a two-way air intake mechanism or a four-valve mechanism or other more effective phase modulation mechanism in communication with the hot end of the cylinder 6.
  • FIG. 5 is another embodiment of the present invention, and is a system diagram of a GM refrigerator built in a phase modulation mechanism.
  • the phase modulation mechanism includes a built-in small orifice valve 23 and a gas reservoir, and a built-in small orifice valve 23 is placed in the annular gap 13 at the hot end of the piston 6, and the heat chamber 7 serves as a gas reservoir of the phase modulation mechanism.
  • Both intake valve 2 and exhaust valve 3 are at room temperature. It is mechanically controlled to open and close to control the flow and volume of the airflow and circulation through the regenerator 4 and cylinder 5.
  • the regenerator 4 is provided with a regenerative packing.
  • the hot and cold air flows alternately through it, functioning to store and recover the cold. Through this action, the purpose of heat exchange between the hot and cold air streams is achieved, and a large temperature difference between the room temperature and the cold end of the refrigerator is established.
  • the drive mechanism reciprocates the piston 6 up and down within the cylinder 5, as indicated by the double arrow in FIG.
  • the piston 6 is placed inside the cylinder 5; the piston 6 is driven by a crank-link mechanism to reciprocate up and down in the cylinder 5, as shown by the double-headed arrow in Fig. 6, causing two effective volume hot chambers at both ends of the cylinder 7 and cold chamber 8. Both are separated by a seal ring 9, a piston 6 and a cylinder 5.
  • the thermal chamber 7 is at room temperature and the cold chamber 8 is at a low temperature. Therefore, both the piston 6 and the cylinder 5 are subjected to a large longitudinal temperature gradient, and therefore are made of a material having poor thermal conductivity.
  • the material of the cylinder 5 is generally selected from stainless steel, which has sufficient strength and low thermal conductivity; and the material of the piston 6 is generally selected from bakelite, which can reduce heat conduction loss, because the specific gravity is smaller than that of stainless steel, and the piston 6 is light in weight, The reciprocating inertial force is reduced, and the bakelite has a small hardness and does not scratch the inner wall of the cylinder 5.
  • the working principle of the G-M chiller is as follows: At the beginning, the control mechanism causes the piston 6 to be at the bottom of the cylinder 5, at the same time opening the intake valve 2. The high pressure gas from the compressor 1 enters the regenerator 4, and the pressure of the regenerator 4 is increased. When the pressure is balanced, the piston moves upward from the bottom of the cylinder 5, and at the same time, the high-pressure gas cooled by the regenerator 4 enters the cold chamber 8. The piston 6 moves to the top of the cylinder 5 and the intake valve closes. The exhaust valve is opened to allow the gas of the cold chamber 8 to communicate with the low pressure end via the heat exchanger 14 and the regenerator 4.
  • the high-pressure gas in the cold chamber is deflated to the low-pressure side to obtain a cooling amount, which is transmitted from the heat exchanger 14.
  • the gas is heated back to the compressor via the regenerator 4.
  • the piston 6 is returned to the bottom of the cylinder 5, and the exhaust valve is closed. In this way, the system can work continuously and continuously to obtain cooling capacity.
  • the phase modulation structure such as the small hole gas reservoir can adjust the phase relationship between the mass flow of the working gas and the pressure wave, and can improve the performance of the pulse tube refrigerator.
  • the invention introduces the phase modulation mechanism into the GM refrigerator, as shown in Fig. 2, Fig. 3 and Fig. 4, to adjust the working process of the working gas in the annular gap 13.
  • the gas in the annular gap 13 can be divided into three sections, a hot end gas 20, a gas piston 21 and a cold end gas 22. When the gas in the annular gap 13 is compressed, the hot end gas 20 is pressed into the gas reservoir 19 through the gas piston 21, and the position of the gas piston 21 at the end of compression is as shown in Fig.
  • Fig. 4 is the equilibrium position of the gas piston 21 during compression or expansion.
  • the working process of the annular gap 13 is the same as that of the pulse tube cooling with the phase modulation mechanism, and the working gas in the annular gap 13 is converted from the original cooling loss to expand and work to generate a cold effect, so that the GM refrigerator obtains better performance.
  • the gas piston 21 also prevents leakage losses through the sealing ring 9.
  • Figure 6 is a system diagram of introducing a phase modulation mechanism into the second stage of a two-stage G-M refrigerator.
  • a two-stage GM refrigerator for introducing a phase modulation mechanism into a second stage, comprising a compressor 1, an intake valve 2, an exhaust valve 3, a primary cylinder 24, a primary piston 25, a primary sealing ring 26, a first stage
  • the cold chamber 27, the secondary cylinder 28, the secondary piston 29, and the secondary cold chamber 30 can be regarded as a secondary hot chamber and a secondary gas chamber.
  • the compressor 1 is used to supply a high pressure gas refrigerant such as high pressure helium.
  • the intake valve 2 and the exhaust valve 3 are both at room temperature, mechanically controlled to open and close, and are used to control the passage of the primary piston 25, the secondary piston 29, the primary cylinder 24, and the secondary cylinder 28. Airflow and circulation pressure and volume.
  • the primary cylinder 24 and the secondary cylinder 28 are made of stainless steel, and the primary cylinder 24 and the secondary cylinder 28 may be of unitary construction.
  • the secondary piston 29 includes a top cover 31, a bottom cover 32, a secondary piston cylinder 33, a secondary regenerative filler 34, a hard mesh 35-36, and a felt 37, etc.;
  • the gap between the walls of the cylinders 28 is a clearance fit with a gap of 0.01-0.03 mm. This gap can ensure the free reciprocating motion of the piston in the cylinder, and can prevent the gas from the secondary cold chamber 30 from directly entering the secondary heat chamber 27;
  • the secondary piston 29 is the same length as the secondary cylinder 28.
  • the bottom cover 32 has a flow passage 38 connecting the interior of the secondary piston 29 and the secondary cold chamber 30, the bottom
  • the outer diameter of the cover 32 is smaller than the outer diameter of the secondary piston 29 by about 0.05 mm, so that a gap is formed between the top cover 32 and the wall of the secondary cylinder 28, so that the working gas can enter and exit the secondary cold chamber 30 and the secondary piston. 29 internal.
  • the top cover 31 and the first stage piston 25 have a passage 39 communicating with the first cold chamber 27 and the second piston 29, and connected to the first stage piston 25, and reciprocating up and down with the first stage piston 25;
  • the piston barrel 33 is provided with a spiral groove 40.
  • the spiral groove 40 extends from the bottom end of the piston barrel 33 to about 30 mm from the top end of the top cover 31, and has a straight groove 41 through the end of the spiral groove 40 to the top end of the top cover 31. .
  • the secondary regenerative filler 34 such as a shot putter, is mounted inside the secondary piston 29, the bottom end is sealed with a hard mesh 35-36 and a felt 37, and the top end is sealed in the same manner;
  • the regenerative filler 34 can also be other regenerative fillers, such as magnetic regenerative fillers, or multiple layers of different regenerative fillers.
  • the straight groove 41 can be regarded as a small hole valve 18; the first stage cold chamber 27 can be regarded as a gas reservoir 19; the volume enclosed between the second cylinder 33 and the second cylinder 28 wall It can be regarded as the vessel 17; thus, the phase modulation mechanism is introduced into the second stage of the two-stage GM refrigerator, and the secondary seal ring is removed, and the working process of the annular gap 13 is changed to the pulse tube refrigeration with the phase modulation mechanism.
  • the working process of the machine makes full use of the expansion of the gas to generate a cold effect, and eliminates the leakage loss and friction loss through the sealing ring, thereby improving the performance of the GM refrigerator.
  • This embodiment simply introduces the phase modulation mode of the small-pore gas reservoir structure.
  • the size of the small hole and the gas reservoir can be accurately calculated, or other more effective phase modulation methods, such as two-way air intake, can be introduced. , four-valve structure and so on.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Description

说明书 带调相机构的 G-M制冷机 技术领域
本发明涉及一种低温制冷机， 尤其是一种回热式低温制冷机， 具体地说 是一种带调相机构的 G-M制冷机。
背景技术
G-M制冷循环是由吉福特 （Gifford)和麦克马洪 （Mcmahon)共同发明 的， 其原理是利用绝热气体放气制冷。 目前， G-M制冷机已广泛应用于低温 泵和冷却多种超导磁体。 在应用时， 一般使用制冷机冷头直接接触或者使用 高导热率的材料作为热桥来实现冷却作用。
目前， 普遍使用的 G-M制冷机的汽缸壁和活塞之间存在缝隙， 制冷机中 压力作周期性变化， 缝隙会造成泵气损失。 在活塞和气缸的热端有密封环封 死， 而冷端是开放的。 当冷腔处于低压时， 间隙中气量最少， 当压力升高时， 便有一些冷气进入间隙中，并从气缸壁和活塞吸收热量，直至达到最高压力， 然后在下一个周期压力下降时， 这些气体返回冷腔， 于是就把刚才吸收的热 量带到冷腔， 造成冷量损失。
另外， 密封环随活塞在气缸内做往复运动， 密封环与气缸之间以及密封 环与活塞之间密封不严， 热腔内高温气体通过密封环漏到冷腔， 冷腔中的低 温气体通过密封环漏到热腔，均会引起冷量损失，这部分损失称为漏气损失。 随着制冷机运行时间的增长， 密封环的磨损会逐渐增大， 密封环与气缸和活 塞的密封会越来越松， 通过密封环的漏气量就会越来越大， 产生的冷量损失 也会越来越大。 此外， 密封环在气缸内的滑动密封产生的摩擦热也会引起冷 量损失。
这些冷量损失严重影响制冷机的性能， 难以满足低温超导的试验与应用 要求。 发明内容
本发明的目的是通过引入调相机构， 提供一种带调相机构的 G-M 制冷 机。解决了以下技术问题： 改变 G-M制冷机的活塞与气缸之间间隙内气体的 工作过程， 充分利用该部分气体膨胀做功， 并阻止通过密封环的漏气损失， 从而使 G-M制冷机获得更好的性能。
本发明的技术方案是：
一种带调相机构的 G-M制冷机，其特征是包括压缩机、进气阀、排气阀、 回热器、 气缸、 活塞、 热腔、 冷腔、 驱动机构、 环形间隙和换热器， 所述压 缩机的出气端连接进气阀， 压缩机的进气端连接排气阀， 进气阀、 排气阀与 回热器三者连通连接， 回热器与气缸连通连接， 回热器与气缸之间设有换热 器； 气缸内设有活塞， 活塞下方为冷腔， 活塞上方为热腔， 活塞与气缸内壁 之间为环形间隙， 活塞上连接驱动机构； 环形间隙与调相机构连通。
所述环形间隙可分为热端气体、 气体活塞和冷端气体。
所述调相机构包括小孔阀和气库， 环形间隙通过小孔阀与气库连通； 所 述的活塞与气缸之间位于环形间隙上方位置设有密封环。
所述的调相机构为与气缸热端连通的小孔气库结构或双向进气机构或四 阀机构或其他更有效的调相机构。
所述的调相机构可内置， 包括内置小孔阀和气库， 内置小孔阀置于活塞 热端的环形间隙内， 热腔作为调相机构的气库。
所述的进气阀和排气阀都处在室温下。
所述的回热器内装有回热填料。
所述的活塞上连接的驱动机构为曲柄连杆驱动机构， 驱动机构包括活塞 杆、 连杆和曲柄。
本发明的有益效果：
本发明通过引入调相机构， 改变了环形间隙内气体的工作过程， 能够充 分利用该部分气体膨胀做功， 并阻止了通过密封环的漏气损失， 从而使 G-M 制冷机获得更好的性能。 附图说明
图 1是本发明的带调相机构的 G-M制冷机系统原理图。
图 2是将调相机构引入 G-M制冷机后环形间隙内气体工作过程图之一。 图 3是将调相机构引入 G-M制冷机后环形间隙内气体工作过程图之二。 图 4是将调相机构引入 G-M制冷机后环形间隙内气体工作过程图之三。 图 5是调相机构内置的 G-M制冷机系统图。
图 6是将调相机构引入两级 G-M制冷机第二级的系统图。
具体实施方式
下面结合附图和实施例对本发明作进一步的说明。
如图 1所示。一种带调相机构的 G-M制冷机， 包括压缩机 1、进气阀 2、 排气阀 3、 回热器 4、 气缸 5、 活塞 6、 热腔 7、 冷腔 8、 驱动机构、 环形间隙 13和换热器 14， 所述压缩机 1的出气端连接进气阀 2， 压缩机 1的进气端连 接排气阀 3， 进气阀 2、排气阀 3与回热器 4三者连通连接， 回热器 4与气缸 5连通连接， 回热器 4与气缸 5之间设有换热器 14; 气缸 5内设有活塞 6， 活塞 6下方为冷腔 8，活塞 6上方为热腔 7，活塞 6与气缸 5内壁之间为环形 间隙 13， 活塞 6上连接驱动机构； 环形间隙 13与调相机构连通。
环形间隙 13内的气体可分为热端气体 20、 气体活塞 21和冷端气体 22。 气体活塞 21上方为热端气体， 气体活塞 21下方为冷端气体。
调相机构包括小孔阀 18和气库 19， 通过小孔阀 18将环形间隙 13与气 库 19连通； 所述的活塞 6与气缸 5之间位于环形间隙 13上方位置设有密封 环 9， 即所述的环形间隙 13由气缸 5内壁、 活塞 6外壁， 密封环 9等封闭而 成。 用来调节环形间隙 13内工作气体的相位关系， 从而提高 G-M制冷机的 性能。
本发明的调相机构还可以为与气缸 6热端连通的双向进气机构或四阀机 构或其他更有效的调相机构。
活塞 6上连接的驱动机构为曲柄连杆驱动机构，驱动机构包括活塞杆 10、 连杆 11和曲柄 12。 如图 5， 为本发明的另一种实施方式， 为调相机构内置的 G-M制冷机系 统图。 调相机构包括内置小孔阀 23和气库， 内置小孔阀 23置于活塞 6热端 的环形间隙 13内， 热腔 7作为调相机构的气库。
进气阀 2和排气阀 3都处在室温下。 由机械控制其开启和关闭， 用来控 制通过回热器 4和气缸 5的气流和循环的压力及容积。
回热器 4内装有回热填料。 冷热气流交替的流过它， 起着储存和回收冷 量的作用。 通过该作用达到冷热气流间换热的目的， 并建立室温和制冷机冷 端之间的巨大温差。
驱动机构使活塞 6在气缸 5内上下往复运动， 如图 1中双向箭头所示。 所述的活塞 6置于气缸 5内部； 所述的活塞 6由曲柄连杆机构驱动， 在气缸 5内上下往复运动， 如图 6中双向箭头所示， 造成气缸两端的两个有效容积 热腔 7和冷腔 8。 二者由密封环 9、 活塞 6和气缸 5隔开。
所述的热腔 7处于室温下， 而冷腔 8处于低温下。 因而活塞 6和气缸 5 都承受着巨大的纵向温度梯度， 所以都是用导热性能差的材料制成。 所述的 气缸 5的材料一般选用不锈钢， 它具有足够的强度及低的热导率； 而活塞 6 的材料一般选用胶木， 它可减少导热损失， 因比重较不锈钢小， 活塞 6质量 轻， 可减小往复惯性力， 而且胶木硬度小， 不会划伤气缸 5内壁。
G-M制冷机的工作工程简述如下： 开始时， 控制机构使活塞 6处于气缸 5底部， 与此同时打开进气阀 2。 来自压缩机 1的高压气体进入回热器 4， 回 热器 4的压力增高。当压力平衡后， 活塞从气缸 5底部向上移动， 与此同时， 经回热器 4冷却的高压气体进入冷腔 8。 活塞 6移动到气缸 5顶部， 进气阀 关闭。 打开排气阀， 使冷腔 8的气体经换热器 14和回热器 4与低压端连通。 这时， 冷腔中的高压气体向低压侧放气， 获得冷量， 冷量由换热器 14传出。 气体经回热器 4加热后回到压缩机。 同时， 活塞 6重新回到气缸 5底部， 排 气阀关闭。这样， 周而复始， 整个系统就能连续工作， 连续不断地获取冷量。
在脉管制冷机中， 小孔气库等调相结构可以调节工作气体的质量流与压 力波之间的相位关系， 能够改善脉管制冷机的性能。 本发明将调相机构引入 G-M制冷机， 如图 2、 图 3、 图 4所示， 来调节 环形间隙 13内工作气体的工作过程。 可将环形间隙 13中的气体分成三个部 分， 热端气体 20， 气体活塞 21和冷端气体 22。 当环形间隙 13内的气体被压 缩时， 热端气体 20通过气体活塞 21被压入气库 19， 压缩结束时刻气体活塞 21的位置如图 2所示； 同理， 膨胀制冷阶段， 冷端气体 22在冷腔 8中膨胀， 膨胀结束时刻气体活塞 21的位置如图 4所示； 图 3为气体活塞 21在压缩或 膨胀过程中的平衡位置。上述环形间隙 13的工作过程与带调相机构的脉管制 冷相同，环形间隙 13内的工作气体便由原来造成冷量损失转而膨胀做功产生 冷效应， 从而使 G-M制冷机获得更好的性能。 此外， 气体活塞 21也阻止了 通过密封环 9的漏气损失。
图 6是将调相机构引入两级 G-M制冷机第二级的系统图。
一种将调相机构引入第二级的两级 G-M制冷机， 包括压缩机 1、 进气阀 2、 排气阀 3、 一级气缸 24、 一级活塞 25、 一级密封环 26、 一级冷腔 27、 二 级气缸 28、 二级活塞 29、 二级冷腔 30。 所述的一级冷腔 27可视为二级热腔 和二级气库。
所述的压缩机 1用来提供高压气体制冷剂， 如高压氦气。
所述的进气阀 2和排气阀 3都处在室温下， 由机械控制其开启和关闭， 用来控制通过一级活塞 25、二级活塞 29和一级气缸 24、二级气缸 28的气流 和循环的压力及容积。
所述的一级气缸 24和二级气缸 28材料为不锈钢，一级气缸 24和二级气 缸 28可为整体结构。
所述的二级活塞 29包括顶盖 31、 底盖 32、 二级活塞筒 33、 二级回热填 料 34、 硬质丝网 35-36以及毛毡 37等； 所述的二级活塞 29与二级气缸 28 壁之间为间隙配合， 间隙为 0.01-0.03 mm, 这个间隙即能保证活塞在气缸内 自由往复运动， 又能阻止二级冷腔 30气体直接进入二级热腔 27; 所述的二 级活塞 29与二级气缸 28的长度相同。
所述的底盖 32上有连通二级活塞 29内部和二级冷腔 30的流道 38， 底 盖 32的外径小于二级活塞 29的外径约 0.05 mm,这样在顶盖 32和二级气缸 28壁之间便形成了一个间隙， 使工作气体可以进出二级冷腔 30和二级活塞 29内部。
所述的顶盖 31和一级活塞 25上有通道 39连通一级冷腔 27和二级活塞 29内部， 并连接至一级活塞 25， 随一级活塞 25做上下往复运动；
所述的活塞筒 33开有螺旋槽 40， 螺旋槽 40从活塞筒 33底端开始， 延 伸至距离顶盖 31顶端约 30 mm处， 经螺旋槽 40末端至顶盖 31顶端开有直 槽 41。
所述的二级回热填料 34， 比如铅球， 装在二级活塞 29内部， 底端用硬 质丝网 35-36和毛毡 37封牢， 顶端采用同样的方式封牢； 所述的二级回热填 料 34也可为其他回热填料，比如磁性回热填料等，也可为多层不同回热填料。
具体工作时， 所述的直槽 41可视为小孔阀 18; 所述的一级冷腔 27可视 为气库 19; 二级活塞筒 33和二级气缸 28壁之间围成的体积可视为脉管 17; 这样便把调相机构引入了两级 G-M 制冷机的第二级， 同时去除了二级密封 环， 将环形间隙 13的工作过程改变为带调相机构的脉管制冷机的工作过程， 充分利用该部分气体膨胀产生冷效应， 并消除了通过密封环的漏气损失和摩 擦损失， 从而提高 G-M制冷机的性能。
本实施例只是简单引入小孔气库结构的调相方式， 为获得更好的性能， 可对小孔和气库的尺寸进行精确地计算， 或者引入其他更有效的调相方式， 比如双向进气、 四阀结构等等。
本发明未涉及部分均与现有技术相同或可采用现有技术加以实现。

Claims

权利要求书
1.一种带调相机构的 G-M制冷机， 其特征是包括压缩机 （1)、 进气阀 （2)、 排气阀 （3)、 回热器 （4)、 气缸 （5)、 活塞 （6)、 热腔 （7)、 冷腔 （8)、 驱 动机构、 环形间隙 （13) 和换热器 （14)， 所述压缩机 （1) 的出气端连接进 气阀 （2)， 压缩机 （1) 的进气端连接排气阀 （3)， 进气阀 （2)、 排气阀 （3) 与回热器（4)三者连通连接， 回热器（4)与气缸（5)连通连接， 回热器（4) 与气缸 （5) 之间设有换热器 （14); 气缸 （5) 内设有活塞 （6)， 活塞 （6) 下方为冷腔 （8)， 活塞 （6) 上方为热腔 （7)， 活塞 （6) 与气缸 （5) 内壁之 间为环形间隙 （13)， 活塞 （6) 上连接驱动机构； 环形间隙 （13) 与调相机 构连通。
2.根据权利要求 1所述的一种带调相机构的 G-M制冷机， 其特征是所述环形 间隙 （13) 可分为热端气体 （20)、 气体活塞 （21) 和冷端气体 （22)。
3.根据权利要求 1所述的一种带调相机构的 G-M制冷机， 其特征是所述调相 机构包括小孔阀 (18) 和气库 (19)， 环形间隙 (13)通过小孔阀 (18) 与气 库 （19) 连通； 所述的活塞 （6) 与气缸 （5) 之间位于环形间隙 （13) 上方 位置设有密封环 （9)。
4.根据权利要求 1所述的一种带调相机构的 G-M制冷机， 其特征是所述的调 相机构为与气缸（6)热端连通的小孔气库结构或双向进气机构或四阀机构或 其他更有效的调相机构。
5.根据权利要求 1所述的一种带调相机构的 G-M制冷机， 其特征是所述的调 相机构可内置， 包括内置小孔阀 （23) 和气库， 内置小孔阀 （23) 置于活塞
(6) 热端的环形间隙 （13) 内， 热腔 （7) 作为调相机构的气库。
6.根据权利要求 1所述的一种带调相机构的 G-M制冷机， 其特征是所述的进 气阀 （2) 和排气阀 （3) 都处在室温下。
PCT/CN2010/077524 2010-08-31 2010-09-30 带调相机构的g-m制冷机 WO2012027918A1 (zh)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP10856605.0A EP2482004B1 (en) 2010-08-31 2010-09-30 G-m refrigerator with phase adjusting mechanism
JP2012540263A JP5589193B2 (ja) 2010-08-31 2010-09-30 位相調節機構を有するｇ−ｍ冷凍機
US13/498,092 US20120227417A1 (en) 2010-08-31 2010-09-30 G-m refrigerator with phase modulation mechanism

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN2010102670758A CN101900447B (zh) 2010-08-31 2010-08-31 带调相机构的g-m制冷机
CN201010267075.8 2010-08-31

Publications (1)

Publication Number Publication Date
WO2012027918A1 true WO2012027918A1 (zh) 2012-03-08

Family

ID=43226208

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2010/077524 WO2012027918A1 (zh) 2010-08-31 2010-09-30 带调相机构的g-m制冷机

Country Status (5)

Country Link
US (1) US20120227417A1 (zh)
EP (1) EP2482004B1 (zh)
JP (1) JP5589193B2 (zh)
CN (1) CN101900447B (zh)
WO (1) WO2012027918A1 (zh)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014025652A (ja) * 2012-07-27 2014-02-06 Sumitomo Heavy Ind Ltd 極低温冷凍機
US9453662B2 (en) 2011-09-28 2016-09-27 Sumitomo Heavy Industries, Ltd. Cryogenic refrigerator
JP2016180590A (ja) * 2016-07-22 2016-10-13 住友重機械工業株式会社 極低温冷凍機
US9494346B2 (en) 2011-10-05 2016-11-15 Sumitomo Heavy Industries, Ltd. Cryogenic refrigerator

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102939506B (zh) * 2010-06-14 2015-05-20 住友重机械工业株式会社 超低温制冷机及冷却方法
JP5585987B2 (ja) 2011-02-25 2014-09-10 三菱重工コンプレッサ株式会社 圧縮機
CN103791147B (zh) * 2013-11-05 2016-08-03 北京卫星环境工程研究所 调节机械驱动g-m制冷机配气时序的调节工具及其应用
JP6109057B2 (ja) 2013-12-16 2017-04-05 住友重機械工業株式会社 蓄冷器式冷凍機
CN103808057B (zh) * 2014-01-23 2016-01-20 浙江大学 一种回收声功的级联型脉管制冷机
CN103821911B (zh) * 2014-03-11 2016-07-06 宁波巨匠自动化装备有限公司 消隙机构
JP6284794B2 (ja) * 2014-03-19 2018-02-28 住友重機械工業株式会社 蓄冷器
CN105222386B (zh) * 2014-05-27 2017-07-28 同济大学 一种气动gm制冷机及其控制过程
JP6578371B2 (ja) * 2015-06-03 2019-09-18 スミトモ （エスエイチアイ） クライオジェニックス オブ アメリカ インコーポレイテッドＳｕｍｉｔｏｍｏ（ＳＨＩ）Ｃｒｙｏｇｅｎｉｃｓ ｏｆ Ａｍｅｒｉｃａ，Ｉｎｃ． バッファを備えたガス圧均衡エンジン
CN106766322B (zh) * 2016-12-16 2019-05-07 浙江大学 一种冷端换热器运动的g-m制冷机和方法
CN106840728B (zh) * 2017-02-22 2023-07-04 中国科学院上海技术物理研究所 一种用于独立评价脉管冷指性能的装置及评价方法
CN108167163A (zh) * 2018-02-22 2018-06-15 方舟 一种用于声能制冷机的膨胀活塞装置
CN108954891B (zh) * 2018-08-27 2020-01-21 浙江大学 基于电涡流阻尼调相的斯特林/脉管复合型制冷机
CN112413919B (zh) * 2020-12-21 2022-06-07 深圳供电局有限公司 一种低温制冷机
CN114427982A (zh) * 2021-12-08 2022-05-03 兰州空间技术物理研究所 一种单级g-m制冷机回热器性能测试装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2367799Y (zh) * 1999-04-15 2000-03-08 中国科学院低温技术实验中心 用于活塞式低温制冷机的活塞式蓄冷密封结构
JP2001317827A (ja) * 2000-05-08 2001-11-16 Daikin Ind Ltd 極低温冷凍機
US6434947B2 (en) * 2000-03-31 2002-08-20 Aisin Seiki Kabushiki Kaisha Pulse tube refrigerator
JP2004144461A (ja) * 2002-08-29 2004-05-20 Mitsubishi Electric Corp 蓄冷型冷凍機及び蓄冷型冷凍機を搭載した超電導マグネット
CN101080600A (zh) * 2005-01-13 2007-11-28 住友重机械工业株式会社 输入功率减小的低温制冷机
JP2008002712A (ja) * 2006-06-20 2008-01-10 Sumitomo Heavy Ind Ltd 蓄冷式冷凍機の駆動制御装置
CN201764746U (zh) * 2010-08-31 2011-03-16 南京柯德超低温技术有限公司 带调相机构的g-m制冷机

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4471625A (en) * 1982-12-07 1984-09-18 Kabushiki Kaisha Suzuki Shokan Gas cycle refrigerator
SU1224514A1 (ru) * 1984-10-12 1986-04-15 Физико-технический институт низких температур АН УССР Криогенератор
JPS62116867A (ja) * 1985-11-16 1987-05-28 アイシン精機株式会社 冷凍装置
JP2550492B2 (ja) * 1988-10-31 1996-11-06 三菱電機株式会社 ガス圧縮機
US5099650A (en) * 1990-04-26 1992-03-31 Boreas Inc. Cryogenic refrigeration apparatus
US5335505A (en) * 1992-05-25 1994-08-09 Kabushiki Kaisha Toshiba Pulse tube refrigerator
JP2659684B2 (ja) * 1994-05-31 1997-09-30 住友重機械工業株式会社 蓄冷器式冷凍機
JP2780928B2 (ja) * 1994-06-16 1998-07-30 住友重機械工業株式会社 蓄冷器式冷凍機を使用した低温装置及び冷却方法
JP3625511B2 (ja) * 1995-02-23 2005-03-02 株式会社鈴木商館 ガスサイクル冷凍機
JP3679589B2 (ja) * 1997-12-12 2005-08-03 三洋電機株式会社 ２ピストン型ガス圧縮／膨張機
JP3751175B2 (ja) * 1999-12-21 2006-03-01 シャープ株式会社 スターリング冷凍機
US20060277925A1 (en) * 2003-03-28 2006-12-14 Yoichi Matsubara Pulse tube refrigerator

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2367799Y (zh) * 1999-04-15 2000-03-08 中国科学院低温技术实验中心 用于活塞式低温制冷机的活塞式蓄冷密封结构
US6434947B2 (en) * 2000-03-31 2002-08-20 Aisin Seiki Kabushiki Kaisha Pulse tube refrigerator
JP2001317827A (ja) * 2000-05-08 2001-11-16 Daikin Ind Ltd 極低温冷凍機
JP2004144461A (ja) * 2002-08-29 2004-05-20 Mitsubishi Electric Corp 蓄冷型冷凍機及び蓄冷型冷凍機を搭載した超電導マグネット
CN101080600A (zh) * 2005-01-13 2007-11-28 住友重机械工业株式会社 输入功率减小的低温制冷机
JP2008002712A (ja) * 2006-06-20 2008-01-10 Sumitomo Heavy Ind Ltd 蓄冷式冷凍機の駆動制御装置
CN201764746U (zh) * 2010-08-31 2011-03-16 南京柯德超低温技术有限公司 带调相机构的g-m制冷机

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9453662B2 (en) 2011-09-28 2016-09-27 Sumitomo Heavy Industries, Ltd. Cryogenic refrigerator
US9494346B2 (en) 2011-10-05 2016-11-15 Sumitomo Heavy Industries, Ltd. Cryogenic refrigerator
JP2014025652A (ja) * 2012-07-27 2014-02-06 Sumitomo Heavy Ind Ltd 極低温冷凍機
JP2016180590A (ja) * 2016-07-22 2016-10-13 住友重機械工業株式会社 極低温冷凍機

Also Published As

Publication number Publication date
EP2482004A4 (en) 2014-01-01
EP2482004B1 (en) 2017-06-07
EP2482004A1 (en) 2012-08-01
CN101900447B (zh) 2012-08-15
JP2013511696A (ja) 2013-04-04
CN101900447A (zh) 2010-12-01
US20120227417A1 (en) 2012-09-13
JP5589193B2 (ja) 2014-09-17

Similar Documents

Publication Publication Date Title
WO2012027918A1 (zh) 带调相机构的g-m制冷机
US8991196B2 (en) Regenerator, GM refrigerator, and pulse tube refrigerator
JP2013174411A (ja) 極低温冷凍機
JP2016075429A (ja) 極低温冷凍機
CN108800713B (zh) 采用斯特林制冷机的多温区风冷冰箱及控温方法
WO2018210089A1 (zh) 双作用α型斯特林制冷机
JP2017515085A (ja) 低温蓄冷器および低温冷凍機
CN201764746U (zh) 带调相机构的g-m制冷机
KR102046020B1 (ko) 하이브리드 브레이튼-기퍼드-맥마흔 팽창기
CN106766322B (zh) 一种冷端换热器运动的g-m制冷机和方法
US10677498B2 (en) Brayton cycle engine with high displacement rate and low vibration
JP5415503B2 (ja) 極低温冷凍機
JP2013217516A (ja) 蓄冷式冷凍機
JP2000121186A (ja) 蓄冷型冷凍機
JP6087168B2 (ja) 極低温冷凍機
WO2014040482A1 (zh) 制冷设备
JPH0452468A (ja) 極低温冷凍装置
US9453662B2 (en) Cryogenic refrigerator
JPH0336468A (ja) 冷却庫
JPH10132405A (ja) 蓄冷式冷凍機およびその運転方法
JP2005283026A (ja) 蓄冷式冷凍機
CN112413919B (zh) 一种低温制冷机
JPH0674584A (ja) 極低温冷凍機およびその運転方法
JPH11257769A (ja) 蓄冷式冷凍機
JP2000018742A (ja) 冷却装置

Legal Events

Date Code Title Description
REEP Request for entry into the european phase

Ref document number: 2010856605

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2012540263

Country of ref document: JP

Ref document number: 2010856605

Country of ref document: EP

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

Ref document number: 10856605

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 13498092

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE