WO2011000228A1 - 用惯性管调相的脉冲管制冷机及其声功放大器 - Google Patents

用惯性管调相的脉冲管制冷机及其声功放大器 Download PDF

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Publication number
WO2011000228A1
WO2011000228A1 PCT/CN2010/071028 CN2010071028W WO2011000228A1 WO 2011000228 A1 WO2011000228 A1 WO 2011000228A1 CN 2010071028 W CN2010071028 W CN 2010071028W WO 2011000228 A1 WO2011000228 A1 WO 2011000228A1
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Prior art keywords
stage
tube
hot end
power amplifier
regenerator
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Ceased
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PCT/CN2010/071028
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English (en)
French (fr)
Inventor
甘智华
王博
邱利民
王龙一
范炳燕
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Zhejiang University ZJU
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Zhejiang University ZJU
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Priority to US13/381,500 priority Critical patent/US8695356B2/en
Publication of WO2011000228A1 publication Critical patent/WO2011000228A1/zh
Anticipated expiration legal-status Critical
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    • 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
    • F25B9/145—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 pulse-tube 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
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1402—Pulse-tube cycles with acoustic driver
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1407—Pulse-tube cycles with pulse tube having in-line geometrical arrangements
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1417—Pulse-tube cycles without any valves in gas supply and return lines
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1423—Pulse tubes with basic schematic including an inertance tube
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1424—Pulse tubes with basic schematic including an orifice and a reservoir
    • F25B2309/14241—Pulse tubes with basic schematic including an orifice reservoir multiple inlet pulse tube

Definitions

  • the invention relates to a sound power amplifier and a pulse tube refrigerator using inertia tube phase modulation, in particular to a sound power amplifier for inertial tube phase modulation and a pulse tube refrigerator thereof.
  • the pulse tube refrigerator has no moving parts at low temperature, and has the advantages of simple structure, low cost, small mechanical vibration, high reliability and long service life, and has become a research hotspot of the current low temperature refrigerator.
  • the Stirling type pulse tube refrigerator has received extensive attention due to its small size and compact structure.
  • the turbulence phase modulation theory the phase difference between the mass flow and the pressure wave has a great influence on the refrigeration performance of the pulse tube refrigerator. Therefore, it is important to select an appropriate phase modulation mechanism to improve the performance of the pulse tube refrigerator.
  • the pulse tube refrigerator can be mainly divided into the following three types according to the phase modulation method: a small hole type, a two-way intake type, and an inertial tube type.
  • the inertia tube utilizes the inertia action of the oscillating air flow in the elongated tube to adjust the phase difference, and has wider phase adjustment capability and better performance.
  • the inertia tube phase modulation method is more suitable for the Stirling type high. Frequency pulse tube refrigerator.
  • the ratio of the hot end sound work to the cold end sound work is proportional to the hot end temperature and the cold end temperature.
  • the regenerative material is filled in the appropriate position in the vessel and will have a cold end.
  • the effect of sound power amplification which is the core of the present invention, allows the vascular hot end inertia tube to achieve the desired phase adjustment.
  • the sound power amplifier for inertia tube phase modulation is: the metal tube is filled with a regenerative material inside, which is located at the hot end X of the vessel, or is filled with a length L of regenerative material at the hot end X of the vessel, satisfying XL >0.
  • a pulse tube refrigerator with a sound power amplifier includes a primary compressor, a primary regenerator, and a primary pulse Pipe, first-stage sound power amplifier, first-stage inertia tube, first-stage gas storage, first-stage compressor is connected with hot end of first-stage regenerator, and cold end of first-stage regenerator is connected with cold end of first-stage pulse tube.
  • the hot end of the vessel is connected to the first-stage gas reservoir via the first-stage inertia tube, and the first-stage acoustic power amplifier is located at the hot end X from the first-order vessel, wherein the distance between the first-stage acoustic amplifier and the hot end of the vessel is X, one level
  • the length of the sound amplifier is L, XL>0.
  • a pulse tube refrigerator with a sound power amplifier includes a first stage compressor, a primary regenerator, a first stage pulse, a first stage sound power amplifier, a first stage inertia tube, a first stage gas reservoir, a secondary compressor, and two Stage regenerator precooling section, secondary regenerator section, secondary vessel, secondary sound power amplifier, secondary inertial tube, secondary gas reservoir, thermal bridge, primary compressor and primary regenerator heat
  • the end is connected, the cold end of the first-stage regenerator is connected with the cold end of the first-stage pulse tube, and the hot end of the first-stage pulse tube is connected to the first-stage gas storage via the first-stage inertia tube, and the first-stage acoustic power amplifier is located in the distance from the first-stage pulse tube.
  • the distance between the primary acoustic amplifier and the hot end of the vessel is X, and the length of the primary acoustic amplifier is L, XL>0.
  • the secondary compressor is connected to the hot end of the pre-cooling section of the secondary regenerator, and the cold end of the pre-cooling section of the secondary regenerator is connected to the hot end of the secondary regenerator section, and the cold end and the secondary vein of the secondary regenerator section are connected.
  • the cold end of the tube is connected, the hot end of the second tube is connected to the second gas pool through the second inertia tube, and the second sound power amplifier is located at the hot end X from the second tube, wherein the second sound amplifier is hot from the tube.
  • the distance between the ends is X, and the length of the secondary sound amplifier is L, XL>0.
  • the cold end of the pre-cooling section of the secondary regenerator is connected to the first-stage cold end through a thermal bridge.
  • a pulse tube refrigerator with a sound power amplifier includes a first-stage pulse tube, a first-stage sound power amplifier, a first-stage inertia tube, a first-stage gas storage, a secondary compressor, a secondary regenerator pre-cooling section, and a secondary return Heater section, secondary vessel, secondary sound power amplifier, secondary inertial tube, secondary gas reservoir, thermal bridge, first stage cold end and secondary regenerator precooling section hot end, first stage pulse
  • the hot end of the tube is connected to the first-stage gas reservoir via the first-stage inertia tube, and the first-stage sound power amplifier is located at the hot end X from the first-stage pulse tube, wherein the distance between the first-stage sound power amplifier and the hot end of the pulse tube is X, the first-order sound
  • the length of the power amplifier is L, XL>0.
  • the secondary compressor is connected to the hot end of the secondary regenerator precooling section, the cold end of the secondary regenerator precooling section is connected to the hot end of the secondary regenerator section, and the secondary regenerator section is cold end and secondary vein
  • the cold end of the tube is connected, the hot end of the second tube is connected to the second gas pool through the second inertia tube, and the second sound power amplifier is located at the hot end X from the second tube, wherein the second sound amplifier is hot from the tube.
  • the distance between the ends is X, and the length of the secondary acoustic power amplifier A1 is L, XL>0.
  • the invention increases the acoustic power of the hot end of the vessel by adding a sound power amplifier in the vessel, thereby increasing the phase adjustment angle of the inertia tube and improving the performance of the refrigerator.
  • the ratio of the hot end to the cold end is proportional to the hot end temperature and the cold end temperature.
  • the sound power amplifier is added at the appropriate position in the vessel and will have a cold end sound.
  • the effect of power amplification which is the core of the present invention, allows the vascular hot end inertia tube to achieve the desired phase adjustment.
  • Figure 1 is a schematic diagram of a single-stage pulse tube refrigerator with a sound power amplifier, the sound power amplifier is located at a proper position of the vessel;
  • Figure 2 (a) is a schematic diagram of a two-stage thermal coupling type pulse tube refrigerator with a sound power amplifier, which uses a sound power amplifier for both the first and second stages;
  • Figure 2 (b) is a schematic diagram of a two-stage thermal coupling type pulse tube refrigerator with a sound power amplifier, and only a second stage uses a sound power amplifier;
  • Figure 3 (a) is a schematic diagram of a two-stage gas-coupled pulse tube refrigerator with a sound power amplifier, which uses a sound power amplifier for both the first and second stages;
  • Figure 3 (b) is a schematic diagram of a two-stage gas-coupled pulse tube refrigerator with a sound power amplifier, and only a second stage uses a sound power amplifier;
  • C1 First-stage linear compressor RG1: First-stage regenerator PT1: First-stage vascular
  • R1 First-stage gas storage
  • I1 First stage inertia tube (room temperature)
  • C2 Second stage linear compressor
  • RG21 Second stage regenerator precooling section
  • RG22 Second stage regenerator working section
  • PT2 Second stage pulse tube
  • R2 second Gas storage (room temperature)
  • I2 second stage inertial tube (room temperature)
  • TB thermal bridge
  • the sound power amplifier for inertia tube phase modulation is: the metal tube is filled with a regenerative material inside, which is located at the hot end X of the vessel, or is filled with a length L of regenerative material from the hot end X in the vessel, XL> 0.
  • the pulse tube refrigerator with the sound power amplifier includes a first stage compressor C1, a primary regenerator RG1, a primary pulse tube PT1, a primary acoustic power amplifier A1, a first inertia tube I1, a first stage.
  • the gas storage R1, the first-stage compressor C1 is connected with the hot end of the primary regenerator RG1, the cold end of the primary regenerator RG1 is connected with the cold end of the first-stage vascular PT1, and the hot end of the first-stage vascular PT1 is passed through the first-stage inertia tube.
  • I1 is connected to the first-stage gas storage R1, and the first-stage acoustic power amplifier A1 is located at a distance from the hot end X in the first-order pulse tube PT1, wherein the distance between the first-stage acoustic power amplifier A1 and the hot end of the pulse tube is X, and the first-stage sound power amplifier
  • the length of A1 is L, XL>0.
  • the pulse tube refrigerator with the sound power amplifier includes a first stage compressor C1, a primary regenerator RG1, a primary pulse tube PT1, a primary acoustic power amplifier A1, and a first inertia tube I1.
  • the library R2, the heat bridge TB, the first stage compressor C1 is connected with the hot end of the primary regenerator RG1, the cold end of the primary regenerator RG1 is connected with the cold end of the first stage vascular PT1, and the hot end of the first stage vascular PT1 is
  • the inertia tube I1 is connected to the first-stage gas reservoir R1, and the first-stage acoustic power amplifier A1 is located at a distance X from the first-stage vessel PT1, wherein the distance between the first-stage acoustic amplifier A1 and the hot
  • the secondary compressor C2 is connected to the hot end of the secondary regenerator precooling section RG21, the secondary regenerator precooling section RG21 cold end is connected to the secondary regenerator section RG22 hot end, and the secondary regenerator section RG22 is cold.
  • the end is connected to the cold end of the secondary vessel PT2, and the secondary vessel PT2
  • the hot end is connected to the secondary gas reservoir R2 via the secondary inertia tube I2, and the secondary acoustic power amplifier A2 is located at the hot end X from the secondary pulse tube PT2, wherein the distance between the secondary acoustic amplifier A2 and the hot end of the vessel is X, the length of the secondary sound power amplifier A1 is L, XL>0.
  • the cold end of the secondary regenerator precooling section RG21 is connected to the primary cold end through the thermal bridge TB.
  • the pulse tube refrigerator with the sound power amplifier includes a primary pulse tube PT1, a primary sound power amplifier A1, a first inertia tube I1, a first gas reservoir R1, a secondary compressor C2, and a secondary return.
  • the end is connected to the hot end of the preheating section RG21 of the secondary regenerator, and the hot end of the first stage pulsator PT1 is connected to the first stage air reservoir R1 via the first inertia tube I1, and the first stage acoustic power amplifier A1 is located within the first stage pulsator PT1.
  • the secondary compressor C2 is connected to the hot end of the secondary regenerator precooling section RG21, the secondary regenerator precooling section RG21 cold end is connected to the secondary regenerator section RG22 hot end, and the secondary regenerator section RG22 is cold.
  • the end is connected to the cold end of the secondary vessel PT2, the hot end of the secondary vessel PT2 is connected to the secondary gas reservoir R2 via the secondary inertial tube I2, and the secondary acoustic amplifier A2 is located within the secondary end of the secondary vessel PT2 from the hot end X
  • the distance between the secondary acoustic amplifier A2 and the hot end of the vessel is X
  • the length of the secondary acoustic amplifier A1 is L, XL>0.
  • the present invention comprises two major parts, the first part is a sound power amplifier, which is characterized by a metal tube filled with a regenerative material inside, which can be located in the vessel from the hot end X or within the vessel.
  • the regenerative material filled with length L at the end X constitutes a sound power amplifier, which satisfies XL>0.
  • the second part is that the sound power amplifier can be used simultaneously or separately for single-stage and multi-stage thermal coupling and gas-coupled pulse tube refrigerator systems.
  • the length L of the sound power amplifier can be freely selected according to specific requirements.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Amplifiers (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Description

[根据细则37.2由ISA制定的发明名称]　用惯性管调相的脉冲管制冷机及其声功放大器 技术领域
本发明涉及声功放大器和采用惯性管调相的脉管制冷机，尤其涉及一种用于惯性管调相的声功放大器及其脉管制冷机。
背景技术
脉管制冷机无低温下的运动部件，具有结构简单、成本低、机械振动小、可靠性高、寿命长等优点，成为当前低温制冷机的研究热点。相比GM型脉管制冷机，斯特林型脉管制冷机由于体积小、结构紧凑，受到广泛关注。由焓流调相理论可知，质量流和压力波之间的相位差对脉管制冷机的制冷性能影响很大，所以选择恰当的调相机构对提高脉管制冷机性能有着重要意义。目前脉管制冷机根据调相方式主要可分为以下三种：小孔型、双向进气型、惯性管型。与小孔型调相方式相比，惯性管利用细长管内振荡气流的惯性作用来调节相位差，具有更宽的相位调节能力和更好的性能。与双向进气型调相方式相比，惯性管型结构中没有环路，可消除由于直流现象引起的脉管冷端温度的波动，因此，惯性管调相方式更适用于斯特林型高频脉管制冷机。
Radebaugh 等人的研究表明：在交变流动中，当回热器中部质量流和压力波同相的时候，脉管制冷机的制冷效率最高，此时回热器热端的质量流约超前压力波 30°，冷端的质量流约落后压力波 30°，这就要求在惯性管入口处质量流落后压力波 约60°，这就意味着惯性管要有至少60°的调相能力。对于冷端PV功较小的脉管制冷机来说，惯性管入口质量流落后压力波60°是不现实的，迫切需要提高脉管热端的声功，增强惯性管调相能力，以满足调相角度！
对于理想的回热器，其热端声功与冷端声功之比正比于热端温度与冷端温度，利用这一原理，在脉管内适当位置填入回热材料，将具有将冷端声功放大的作用，也即本发明的核心内容，这使得脉管热端惯性管可获得所需要的相位调节。
 技术问题
本发明的目的是克服现有技术的不足，提供一种用于惯性管调相的声功放大器及其脉管制冷机。
技术解决方案
用于惯性管调相的声功放大器是：金属管内部填充回热材料，它位于距脉管热端X处，或在脉管内距热端X处填充长度为L的回热材料，满足X-L>0。
一种带有声功放大器的脉管制冷机包括一级压缩机、一级回热器、一级脉 管、一级声功放大器、一级惯性管、一级气库，一级压缩机与一级回热器热端相连，一级回热器冷端与一级脉管冷端相连，一级脉管热端经一级惯性管与一级气库相连，一级声功放大器位于距一级脉管内距热端X处，其中一级声功放大器距脉管热端的距离为X，一级声功放大器的长度为L，X-L>0。
一种带有声功放大器的脉管制冷机包括一级压缩机、一级回热器、一级脉管、一级声功放大器、一级惯性管、一级气库，二级压缩机、二级回热器预冷段、二级回热器段、二级脉管、二级声功放大器、二级惯性管、二级气库，热桥，一级压缩机与一级回热器热端相连，一级回热器冷端与一级脉管冷端相连，一级脉管热端经一级惯性管与一级气库相连，一级声功放大器位于距一级脉管内距热端X处，其中一级声功放大器距脉管热端的距离为X，一级声功放大器的长度为L，X-L>0。二级压缩机与二级回热器预冷段热端相连，二级回热器预冷段冷端与二级回热器段热端相连，二级回热器段冷端与二级脉管冷端相连，二级脉管热端经二级惯性管与二级气库相连，二级声功放大器位于距二级脉管内距热端X处，其中二级声功放大器距脉管热端的距离为X，二级声功放大器的长度为L，X-L>0。二级回热器预冷段冷端通过热桥与一级冷端相连。
一种带有声功放大器的脉管制冷机包括一级脉管、一级声功放大器、一级惯性管、一级气库，二级压缩机、二级回热器预冷段、二级回热器段、二级脉管、二级声功放大器、二级惯性管、二级气库，热桥，一级脉管冷端与二级回热器预冷段热端相通，一级脉管热端经一级惯性管与一级气库相连，一级声功放大器位于距一级脉管内距热端X处，其中一级声功放大器距脉管热端的距离为X，一级声功放大器的长度为L，X-L>0。二级压缩机与二级回热器预冷段热端相连，二级回热器预冷段冷端与二级回热器段热端相连，二级回热器段冷端与二级脉管冷端相连，二级脉管热端经二级惯性管与二级气库相连，二级声功放大器位于距二级脉管内距热端X处，其中二级声功放大器距脉管热端的距离为X，二级声功放大器A1的长度为L，X-L>0。
 有益效果
本发明通过在脉管内增加声功放大器，增大脉管热端的声功，从而增大惯性管的调相角度，提高制冷机的性能。对于理想的回热器，其热端声功与冷端声功之比正比于热端温度与冷端温度，利用这一原理，在脉管内适当位置增加声功放大器，将具有将冷端声功放大的作用，也即本发明的核心内容，这使得脉管热端惯性管可获得所需要的相位调节。
附图说明
图1是带有声功放大器的单级脉管制冷机示意图，声功放大器位于脉管适 当位置；
图2（a）是带有声功放大器的两级热耦合型脉管制冷机示意图，一级和二级均采用声功放大器；
图2（b）是带有声功放大器的两级热耦合型脉管制冷机示意图，仅二级采用声功放大器；
图3（a）是带有声功放大器的两级气耦合型脉管制冷机示意图，一级和二级均采用声功放大器；
图3（b）是带有声功放大器的两级气耦合型脉管制冷机示意图，仅二级采用声功放大器；
图中：C1：第一级线性压缩机 RG1：第一级回热器 PT1：第一级脉管 R1：第一级气库 I1：第一级惯性管（室温） C2：第二级线性压缩机 RG21：第二级回热器预冷段RG22：第二级回热器工作段 PT2：第二级脉管 R2：第二级气库（室温） I2：第二级惯性管（室温） TB：热桥
 本发明的最佳实施方式
用于惯性管调相的声功放大器是：金属管内部填充回热材料，它位于距脉管热端X处，或在脉管内距热端X处填充长度为L的回热材料，X-L>0。
如图1所示，带有声功放大器的脉管制冷机包括一级压缩机C1、一级回热器RG1、一级脉管PT1、一级声功放大器A1、一级惯性管I1、一级气库R1，一级压缩机C1与一级回热器RG1热端相连，一级回热器RG1冷端与一级脉管PT1冷端相连，一级脉管PT1热端经一级惯性管I1与一级气库R1相连，一级声功放大器A1位于距一级脉管PT1内距热端X处，其中一级声功放大器A1距脉管热端的距离为X，一级声功放大器A1的长度为L，X-L>0。
如图2所示，带有声功放大器的脉管制冷机包括一级压缩机C1、一级回热器RG1、一级脉管PT1、一级声功放大器A1、一级惯性管I1、一级气库R1，二级压缩机C2、二级回热器预冷段RG21、二级回热器段RG22、二级脉管PT1、二级声功放大器A2、二级惯性管I2、二级气库R2，热桥TB，一级压缩机C1与一级回热器RG1热端相连，一级回热器RG1冷端与一级脉管PT1冷端相连，一级脉管PT1热端经一级惯性管I1与一级气库R1相连，一级声功放大器A1位于距一级脉管PT1内距热端X处，其中一级声功放大器A1距脉管热端的距离为X，一级声功放大器A1的长度为L，X-L>0。二级压缩机C2与二级回热器预冷段RG21热端相连，二级回热器预冷段RG21冷端与二级回热器段RG22热端相连，二级回热器段RG22冷端与二级脉管PT2冷端相连，二级脉管PT2 热端经二级惯性管I2与二级气库R2相连，二级声功放大器A2位于距二级脉管PT2内距热端X处，其中二级声功放大器A2距脉管热端的距离为X，二级声功放大器A1的长度为L，X-L>0。二级回热器预冷段RG21冷端通过热桥TB与一级冷端相连。
如图3所示，带有声功放大器的脉管制冷机包括一级脉管PT1、一级声功放大器A1、一级惯性管I1、一级气库R1，二级压缩机C2、二级回热器预冷段RG21、二级回热器段RG22、二级脉管PT1、二级声功放大器A2、二级惯性管I2、二级气库R2，热桥TB，一级脉管PT1冷端与二级回热器预冷段RG21热端相通，一级脉管PT1热端经一级惯性管I1与一级气库R1相连，一级声功放大器A1位于距一级脉管PT1内距热端X处，其中一级声功放大器A1距脉管热端的距离为X，一级声功放大器A1的长度为L，X-L>0。二级压缩机C2与二级回热器预冷段RG21热端相连，二级回热器预冷段RG21冷端与二级回热器段RG22热端相连，二级回热器段RG22冷端与二级脉管PT2冷端相连，二级脉管PT2热端经二级惯性管I2与二级气库R2相连，二级声功放大器A2位于距二级脉管PT2内距热端X处，其中二级声功放大器A2距脉管热端的距离为X，二级声功放大器A1的长度为L，X-L>0。
综上所述，本发明包含两大部分，第一部分是声功放大器，其特征是内部填充回热材料的金属管，它可以位于脉管内距热端X处，或在脉管内部内距热端X处填充长度为L的回热材料构成声功放大器，满足X-L>0。第二部分是声功放大器可同时或分别用于单级和多级热耦合及气耦合脉管制冷机系统，声功放大器的长度L可根据具体要求自由选择。
下面通过计算比较来说明带声功放大器的惯性管调相方式的优势：取三台35K两级高频脉管脉管制冷机，其中一台用常温惯性管调相，一台用低温惯性管调相，另一台用带声功放大器的常温惯性管调相，其中声功放大器置于脉管中部1/3处。假设其频率均为40HZ，充气压力1.25MP，热端绝热温度300K,气库无限大，冷端压比1.15。
系统 脉管冷端声功 脉管热端声功 脉管热端压比 惯性管调相角度 备注
采用低温惯性管调相的35K两级高频脉管制冷机 2W 2W 约1.15 约70-80° 二级惯性管和气库置于80K处，调相角度较大，完全满足系统调相要求；但是低温惯性管结构复杂，难以控制。
采用常温惯性管调相的35K两级高频脉管制冷机 2W 2W 约1.15 约16° 调相角度很小，难以满足系统调相的要求。
采用一种用于惯性管调相的声功放大器的35K两级高频脉管制冷机 2W 10W 约1.10 约60° 安装声功放大器，压比减小，声功增大，均有利于调相，调相角度满足要求；整个调相装置置于室温下，避免了低温调相的复杂性。
由以上计算比较得知，增加声功放大器不仅可以大大增加脉管热端的声功，而且会降低压比，均有利于系统调相，同时避免了采用低温惯性管的复杂性。
 本发明的实施方式
工业实用性
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Claims (4)

  1. 一种用于惯性管调相的声功放大器，其特征在于，金属管内部填充回热材料，它位于距脉管热端X处，或在脉管内距热端X处填充长度为L的回热材料，满足X-L>0。
  2. 一种带有声功放大器的脉管制冷机，其特征在于包括一级压缩机（C1）、一级回热器（RG1）、一级脉管（PT1）、一级声功放大器（A1）、一级惯性管（I1）、一级气库（R1），一级压缩机（C1）与一级回热器（RG1）热端相连，一级回热器（RG1）冷端与一级脉管（PT1）冷端相连，一级脉管（PT1）热端经一级惯性管（I1）与一级气库（R1）相连，一级声功放大器（A1）位于距一级脉管（PT1）内距热端X处，其中一级声功放大器（A1）距脉管热端的距离为X，一级声功放大器A1的长度为L，X-L>0。
  3. 一种带有声功放大器的脉管制冷机，其特征在于包括一级压缩机（C1）、一级回热器（RG1）、一级脉管（PT1）、一级声功放大器（A1）、一级惯性管（I1）、一级气库（R1），二级压缩机（C2）、二级回热器预冷段（RG21）、二级回热器段（RG22）、二级脉管（PT1）、二级声功放大器（A2）、二级惯性管（I2）、二级气库（R2），热桥（TB），一级压缩机（C1）与一级回热器（RG1）热端相连，一级回热器（RG1）冷端与一级脉管（PT1）冷端相连，一级脉管（PT1）热端经一级惯性管（I1）与一级气库（R1）相连，一级声功放大器（A1）位于距一级脉管（PT1）内距热端X处，其中一级声功放大器（A1）距脉管热端的距离为X，一级声功放大器（A1）的长度为L，X-L>0。二级压缩机（C2）与二级回热器预冷段（RG21）热端相连，二级回热器预冷段（RG21）冷端与二级回热器段（RG22）热端相连，二级回热器段（RG22）冷端与二级脉管（PT2）冷端相连，二级脉管（PT2）热端经二级惯性管（I2）与二级气库（R2）相连，二级声功放大器（A2）位于距二级脉管（PT2）内距热端X处，其中二级声功放大器（A2）距脉管热端的距离为X，二级声功放大器（A1）的长度为L，X-L>0，二级回热器预冷段（RG21）冷端通过热桥TB与一级冷端相连。
  4. 一种带有声功放大器的脉管制冷机，其特征在于包括一级脉管（PT1）、一级声功放大器（A1）、一级惯性管（I1）、一级气库（R1），二级压缩机（C2）、二级回热器预冷段（RG21）、二级回热器段（RG22）、二级脉管（PT1）、二级声功放大器（A2）、二级惯性管（I2）、二级气库（R2），热桥（TB），一级脉管（PT1）冷端与二级回热器预冷段（RG21）热端相通，一级脉管（PT1）热端经一级惯性管（I1）与一级气库（R1）相连，一级声功放大器（A1）位于距一级 脉管（PT1）内距热端X处，其中一级声功放大器（A1）距脉管热端的距离为X，一级声功放大器（A1）的长度为L，X-L>0。二级压缩机（C2）与二级回热器预冷段（RG21）热端相连，二级回热器预冷段（RG21）冷端与二级回热器段（RG22）热端相连，二级回热器段（RG22）冷端与二级脉管（PT2）冷端相连，二级脉管（PT2）热端经二级惯性管（I2）与二级气库（R2）相连，二级声功放大器（A2）位于距二级脉管（PT2）内距热端X处，其中二级声功放大器（A2）距脉管热端的距离为X，二级声功放大器A1的长度为L，X-L>0
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