液氮温区同轴脉冲管制冷机的实验研究

脉冲管制冷机冷头朝上布置可以使制冷机与超导器件的耦合更方便 ,但对G -M型脉冲管制冷机 ,重力会对这种布置方式产生不利影响。对双向进气型脉冲管制冷机 ,直流和耦合传热会共同影响脉冲管制冷机的性能。介绍了液氮温区G -M型同轴脉冲管制冷机的实验结果 ,主要研究了蓄冷器温度分布和重力对脉冲管制冷机性能的影响     

脉冲管制冷机混合填充式蓄冷器的实验研究

基于脉冲管制冷机蓄冷器结构,提出了#400不锈钢丝网以及其与#300和#500组合而成的混合式蓄冷器填充方式.通过构建一单级分体式脉冲管制冷机测试平台,将#400及混合目数丝网分别填充至制冷机蓄冷器内进行整机实验,实验结果验证了低温制冷机蓄冷器冷热端分别填充高低目数丝网,可提高制冷机性能,是一种有效的蓄冷器优化方法.     

10W/80K高频同轴脉冲管制冷机的实验性能

介绍了一款大冷量高频单级同轴脉冲管制冷机的基本结构、数值模拟和实验性能。其线性压缩机采用Redlich动磁式直线电机驱动,压缩活塞对置布置,使用板弹簧支撑和间隙密封技术,80 K温区工作时的电机效率在83%以上。膨胀机的蓄冷器和脉冲管为同轴型布置,这种结构使冷头与器件之间的耦合非常方便。使用数值软件对制冷机整机和调相部件进行数值模拟,并对模拟结果进行实验验证。对制冷机的运行频率和制冷性能进行实验研究,制冷机在210.3 W输入电功时能获得10 W/80 K的制冷性能,比卡诺效率为12.66%,运行频率为62 Hz,整机重量小于5.5 kg。     

高频微型同轴非金属脉冲管制冷机几何尺寸优化的实验研究

寻找出能使制冷机达到最佳制冷性能的部件几何尺寸匹配规律,是脉冲管制冷机研制过程中的一个重要任务.以设计的高频微型同轴非金属脉冲管制冷机为例,在设定部分固定参数的条件下,通过实验得出了脉冲管和蓄冷器各自的最佳长径比,最佳的脉冲管与蓄冷器的空体积之比,所得实验结果可以作为该类型脉冲管制冷机的初设计依据.     

GM/PT混合式制冷机二级蓄冷器的实验研究

二级脉冲管蓄冷器对GM／PT混合式制同制冷性能有较大影响。蓄冷器与脉冲管结构的布置形式对GM／PT混合式制冷机性能有着较大影响,蓄冷器体积与脉冲管体积之间存在着最佳比较,介绍了GM／PT混合式制冷机的结构和实验装置,分析了整机性能的影响因素,给出了不同结构与体积比下的实验降温曲线,并对实验结果进行了分析讨论。     

脉冲管制冷机蓄冷器中交变流动过程理论分析

建立了交变流动蓄冷器热力学模型,分析了蓄冷器中气体微团的热力学变化过程,经计算得出了一周期内总热量和压力波与质量流之间相位的关系,对蓄冷器在制冷系统中的作用提出了新的认识,并通过对脉冲管蓄冷器中交变流动热力学特性的分析,对比一典型的双向进气型脉冲管制冷机的实验测量结果,分析了双向进气环流产生的直流分量对蓄冷器的影响,对脉冲管双向进气产生的直流分量对脉冲管制冷性能的影响提出了新的解释。     

高频微型非金属脉冲管制冷机轴向导热损失的计算分析

针对所开发的高频微型同轴非金属脉冲管制冷机进行了轴向导热损失的计算与分析,并与相同几何尺寸的金属脉冲管制冷机进行了比较。仅从降低轴向导热损失的角度讲,使用低导热率的非金属材料制作制冷机部件对制冷性能有较大的积极作用。对于2台实验样机而言,通过蓄冷器和脉冲管内的气体的轴向导热损失已经超出通过各自管壁的轴向导热而成为最大的导热损失项,但通过蓄冷填料的轴向导热损失却成为三项损失中一个可以忽略的小量,这是非金属脉冲管制冷机区别于相同几何尺寸的常规金属脉冲管制冷机的显著特点。     

脉冲管制冷机蓄冷器流动特性实验研究 第一部分：实验装置和数据处理系统

蓄冷器是脉冲管制冷机等回热式制冷机的关键部件，它性能的好坏直接影响到回热式制冷机的效率和性能。交变流动蓄冷器中的热量和动量传输及转换过程是一个十分复杂的传热学，流体力学及热力学问题。低温中心针对交变流动蓄冷器的特点建立了动态参数测试实验台。实验台可以模拟各种脉冲管制冷机的真实运行条件。针对50Hz的交变流动蓄冷器的阻力特性进行了系统的实验研究，第一部分介绍实验装置及数据处理系统。     

空间用3 W@80 K脉冲管制冷机实验研究

为冷却某空间用红外探测器,研制了一台斯特林型脉冲管制冷机。该制冷机为单级同轴型结构,整机重量4.5 kg,设计寿命5年。系统介绍了脉冲管制冷机系统结构及实验装置,测试了制冷机性能及其与杜瓦耦合后的降温特性曲线,实验结果表明,脉冲管制冷机在80 K可提供0—3 W制冷量,比卡诺效率11%,其制冷量可充分满足杜瓦组件的低温和长寿命的工程需求。     

大冷量同轴型脉冲管制冷机蓄冷器周向温度分布实验研究

针对一台液氮温区可产生100 W制冷量的脉冲管制冷机,通过控制变量的方法实验研究了工作频率、输入功率、冷头热负荷量对蓄冷器圆周方向温度分布和最大温差的影响。研究结果表明:工作频率的改变对蓄冷器的周向温度分布影响不大,增大输入功率导致蓄冷器的周向温度不均匀性明显变强,增大冷头热负荷量可以减小蓄冷器的周向温度不均匀性。     

Quarter-wave pulse tube

In high-power pulse-tube refrigerators, the pulse tube itself can be very long without too much dissipation of acoustic power on its walls. The pressure amplitude, the volume-flow-rate amplitude, and the time phase between them evolve significantly along a pulse tube that is about a quarter-wavelength long. Proper choice of length and area makes the oscillations at the ambient end of the long pulse tube optimal for driving a second, smaller pulse-tube refrigerator, thereby utilizing the acoustic power that would typically have been dissipated in the first pulse-tube refrigerator’s orifice. Experiments show that little heat is carried from the ambient heat exchanger to the cold heat exchanger in such a long pulse tube, even though the oscillations are turbulent and even when the tube is compactly coiled.     

Enthalpy flow rate of a pulse tube in pulse tube refrigerator

An integration formula of enthalpy flow rate along a pulse tube in pulse tube refrigerators is described on the assumption of sinusoidal mass flow rate and sinusoidal pressure fluctuation. For ideal double inlet and ideal orifice pulse tube with helium as working medium, it is simplified to a polynomial formula. Polynomial formulas for roughly evaluating the volume of the pulse tube in ideal double inlet and ideal orifice pulse tube refrigerators are also given.     

Numerical method of inertance tube pulse tube refrigerator

A nodal analysis method for simulating inertance tube pulse tube refrigerators is introduced. The energy equation, continuity equation, momentum equation of gas, energy equation of solid are included in this model. Boundary condition can be easily changed to enable the numerical program calculate thermal acoustic engines, inertance tube pulse tube refrigerators, double inlet pulse tube refrigerators, and others. Implicit control volume method is used to solve these equations. In order to increase the calculation speed, the continuity equation is changed to pressure equation with ideal gas assumption, and merged with momentum equation. Then the algebraic equation group from continuity and momentum equation becomes one group. With this numerical method, an example calculation of a large scale inertance tube pulse tube refrigerator is shown.     

Expansion efficiency of pulse tube in pulse tube refrigerator including shuttle heat transfer effect

This paper describes simple analysis of the pulse tube expansion efficiency. Four dimensionless operating parameters of pulse tube refrigerator are needed to express the enthalpy flow at the cold end of the pulse tube. In this analysis, the expansion efficiency is calculated from the ratio of the diathermic enthalpy flow (non-zero gas-to-wall heat transfer) to the adiabatic enthalpy flow (zero gas-to-wall heat transfer). The analytic procedure is carried out under several simplified assumptions, and the resultant expression is remarkably simple and useful. The optimal design of pulse tube refrigerator can be greatly assisted by the enthalpy flow calculation with four dimensionless parameters introduced in this paper.     

Acoustic streaming in pulse tube refrigerators: tapered pulse tubes

Acoustic streaming is investigated in tapered tubes with axially varying temperature, in the boundary layer limit. By appropriately shaping the tube, the streaming can be eliminated. Experimental data demonstrate that an orifice pulse tube refrigerator with a conical pulse tube whose cone angle eliminates streaming has more cooling power than one with either a cylindrical pulse tube or a conical pulse tube with twice the optimum cone angle.     

A review of pulse tube refrigeration

The pulse tube belongs to the class of miniature cryogenic refrigerators usually referred to as cryocoolers. In common with Stirling and Gifford-McMahon machines, operation depends on a regenerative gas expansion cycle but unlike these coolers the pulse tube has no moving parts at low temperature and hence offers the potential for high reliability. Although comparisons may be drawn between the operation of a pulse tube and that of a Stirling cooler, the exact nature of the working cycle is far from clear and the device continues to intrigue. We provide here an introduction to the device and attempt to explain it's operation as a conventional second law system.     

Intermediate cooling from pulse tube and regenerator in a 4 K pulse tube cryocooler

This paper introduces intermediate cooling by thermally attaching heat exchangers on the second stage pulse tube and regenerator in a commercial 4 K pulse tube cryocooler. Due to the large enthalpy flow in the 2nd stage pulse tube and regenerator, both intermediate heat exchangers on the pulse tube and regenerator can provide cooling capacities in the temperature range of 5–15 K without or with minor effect on the performance of the 4 K stage. Extracting cooling capacity from the pulse tube or regenerator reduces the 1st stage cooling performance in the present study. The joint intermediate heat exchanger on the pulse tube and regenerator has demonstrated promising results for applications.     

Performance characteristics of pulse tube refrigerators

In the present study experiments were carried out to investigate the performance characteristics of pulse tube refrigerators. It was found that the cool-down time t_c during the transient or start-up period is dominated by the time constant of the pulse tube wall τ_pt and that the dynamics of a basic pulse tube (BPT) refrigerator approaches that of a first-order system. For steady state operation, the cold-end temperature T_L was found to vary with τ_pt, and the cooling load Q_L increases monotonically with increasing τ_pt. This indicates that heat pumped by the gas from the cold to the hot end increases with decreasing h_pt (i.e. less energy exchange between the gas and wall). The process of heat storage or release of the pulse tube wall is thus shown to have a negative effect on the performance of a BPT refrigerator. It was thus found experimentally that the gas compression/expansion process inside the pulse tube, which is similar to a Brayton cycle but lies between isothermal and adiabatic, can explain the performance of BPT refrigerators. The present experiment also shows that the performance of a pulse tube refrigerator at transient and steady states is mainly dominated by the time constant of the pulse tube wall τ_pt.     

Performance of the inertance pulse tube

The rate of refrigeration of the inertance pulse tube (IPTR) is found as a function of the relevant parameters. In the simplified case of infinite volume of the reservoir and zero dead volume of the regenerator, these parameters are the dimensions of the inertance tube, the volume of the pulse tube, the conductance of the regenerator, the driving pressure, and the frequency. The effective conductance of the inertance tube is determined using a simple turbulent flow model. It is found that the performance of the IPTR is superior to that of the orifice pulse tube refrigerator (OPTR) over a limited range of frequencies. The improvement is explained in terms of the pressure amplitude in the pulse tube, the flow rate between the regenerator and the pulse tube, and the phase angle between these parameters. The analysis is extended to the case of finite reservoir and regenerator volumes. It is indicated how the results obtained can be useful in experimental work.     

A two-stage Stirling-type pulse tube cryocooler with a cold inertance tube

A thermally coupled two-stage Stirling-type pulse tube cryocooler (PTC) with inertance tubes as phase shifters has been designed, manufactured and tested. In order to obtain a larger phase shift at the low acoustic power of about 2.0 W, a cold inertance tube as well as a cold reservoir for the second stage, precooled by the cold end of the first stage, was introduced into the system. The transmission line model was used to calculate the phase shift produced by the cold inertance tube. Effect of regenerator material, geometry and charging pressure on the performance of the second stage of the two-stage PTC was investigated based on the well known regenerator model REGEN. Experimental results of the two-stage PTC were carried out with an emphasis on the performance of the second stage. A lowest cooling temperature of 23.7 K and 0.50 W at 33.9 K were obtained with an input electric power of 150.0 W and an operating frequency of 40 Hz.