WO2016155601A1 - 一种脉管制冷机 - Google Patents

一种脉管制冷机 Download PDF

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Publication number
WO2016155601A1
WO2016155601A1 PCT/CN2016/077610 CN2016077610W WO2016155601A1 WO 2016155601 A1 WO2016155601 A1 WO 2016155601A1 CN 2016077610 W CN2016077610 W CN 2016077610W WO 2016155601 A1 WO2016155601 A1 WO 2016155601A1
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WO
WIPO (PCT)
Prior art keywords
draft tube
regenerator
tube
vessel
cross
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/CN2016/077610
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English (en)
French (fr)
Inventor
姜晓
邱利民
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Zhejiang University ZJU
Sumitomo Heavy Industries Ltd
Original Assignee
Zhejiang University ZJU
Sumitomo Heavy Industries Ltd
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Publication date
Application filed by Zhejiang University ZJU, Sumitomo Heavy Industries Ltd filed Critical Zhejiang University ZJU
Priority to JP2017542437A priority Critical patent/JP6615900B2/ja
Publication of WO2016155601A1 publication Critical patent/WO2016155601A1/zh
Priority to US15/710,422 priority patent/US10551092B2/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • 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 
    • F25B2309/1413—Pulse-tube cycles characterised by performance, geometry or theory
    • 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 
    • F25B2309/1415—Pulse-tube cycles characterised by regenerator details
    • 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 
    • F25B2309/1418—Pulse-tube cycles with 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
    • 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 invention relates to the field of refrigerators, and in particular to a pulse tube refrigerator.
  • the present invention provides a refrigerator which suppresses the occurrence of a bias flow of a refrigerant in a pulse tube refrigerator.
  • a pulse tube refrigerator comprises a regenerator, a cold end heat exchanger, a pulse tube, a hot end heat exchanger and a phase modulation mechanism which are sequentially connected, and a draft tube is arranged along the axial direction in the regenerator.
  • a draft tube is arranged along the axial direction in the regenerator.
  • the airflow exchange path of the transverse section (the section perpendicular to the circumference) can be blocked and reduced, the flow field is more uniform, and the temperature unevenness in the regenerator is reduced, thereby realizing the efficiency of the refrigerator. jobs.
  • the draft tube is disposed coaxially with the regenerator.
  • the draft tube may also extend into the cold end heat exchanger.
  • the draft tube By extending the draft tube into the cold-end heat exchanger, the degree of reduction of the flow path in the cold-end heat exchanger can be reduced, the air flow structure can be optimized, the fin length of the cold-end heat exchanger can be shortened, and the cold end exchange can be enhanced. Heater Heat exchange capacity.
  • the draft tube can further extend into the vessel.
  • the circular vessel can be made into a circular vessel, and the reduction between the regenerator and the vessel can be reduced, optimizing the flow within the vessel.
  • the draft tube section located within the vessel is disposed coaxially with the vessel.
  • the outer wall of the draft tube section located within the vessel can be secured with a rectifying mesh.
  • a rectifying mesh In the case of large mass flow, because of the limitation of the shape of the cold-end heat exchanger and the hot-end heat exchanger, the gas entering the ends of the vessel is not necessarily uniform, so the use of the rectifying grid as the laminar fluidization component will be very It is necessary to fix the rectifying net, especially in the middle of the vascular tube. It is very difficult to fix the rectifying net in the middle of the vascular tube.
  • the present invention can provide a fixed point for the rectifying net to facilitate rectification in the vascular tube. Floor.
  • the draft tube may further extend into the hot end heat exchanger.
  • the inner wall and/or the outer wall of the draft tube may also be provided with at least one sensor, the at least one sensor being in communication with an external measuring device through a wire, the wire passing through the interior of the draft tube and located from the draft tube The end at the hot end heat exchanger extends outwardly to the external measuring device.
  • the sensor By arranging the sensor on the draft tube, it is possible to measure the temperature, pressure and other parameters inside the refrigerator without significantly affecting the internal flow field of the refrigerator. By measuring the temperature and pressure inside the refrigerator, it can also promote the deep understanding of the principle of the pulse tube refrigerator, and at the same time facilitate the in-depth analysis of the non-uniformity phenomenon in the regenerator with small aspect ratio, so as to find efficient and feasible. A method of suppressing losses.
  • the temperature distribution of more points of the regenerator can be obtained stereoscopically, and the internal non-uniformity of the regenerator and the optimal control of the refrigerating machine can be studied.
  • Significant significance for example, by measuring the temperature of the internal airflow in the cold-end heat exchanger (there is no heat flow), combined with the temperature measurement on the outer wall of the cold-end heat exchanger, the efficiency of the cold-end heat exchanger can be more realistically analyzed; Measuring the temperature inside the vessel, combined with the temperature measurement of the outer wall surface of the vessel, can obtain the stereoscopic temperature distribution of the vessel, which has a guiding effect on the optimization of the vessel.
  • the at least one sensor temperature sensor is disposed on an inner wall of the draft tube. Setting the temperature sensor on the inner wall of the draft tube does not affect the flow field in the refrigerator.
  • the portion of the draft tube in which the temperature sensor is provided may be made of a heat transfer material.
  • the senor may also be a pressure sensor embedded in the outer wall of the draft tube. This embedded arrangement minimizes the effect of the pressure sensor on the flow field in the refrigerator.
  • the cross-sectional area of the draft tube section located in the regenerator is the same, and the ratio of the cross-sectional area to the cross-sectional area of the regenerator is 1/20 or more and 1/2 or less, and the diversion tube area is located inside the vessel.
  • the cross-sectional area is the same throughout the section, and the ratio of the cross-sectional area to the cross-sectional area of the vessel is 1/20 or more and 1/2 or less.
  • the cross-sectional area of the draft tube section located within the regenerator is greater than the cross-sectional area of the draft tube section located within the vessel.
  • the cross section of the two ends of the draft tube section in the cold end heat exchanger and the draft tube section located in the regenerator respectively Matches the cross section of the draft tube section located within the vessel.
  • the draft tube has no shape and size limitation.
  • the outer contour of the cross section of the draft tube is a circular or regular polygon.
  • the outer contour of the cross section of the draft tube is preferably circular.
  • the draft tube can be integrally formed, or can be composed of a plurality of small parts according to actual conditions.
  • connection manner between them is not particularly limited, and may be various connection methods such as bonding, threading, welding, and snap-fit.
  • said phase modulation mechanism includes an inertia tube in communication with one end of the hot end heat exchanger remote from the regenerator and a gas reservoir coupled to the inertia tube.
  • the refrigerator is a pulse tube refrigerator, and the general category of the pulse tube refrigerator is not limited, and may be single-stage or multi-stage; it may be a thermally coupled pulse tube refrigerator, a gas-coupled pulse tube refrigerator, or Stirling.
  • Type pulse tube refrigerator or GM type pulse tube refrigerator can also be a small hole type pulse tube refrigerator, a two-way intake type pulse tube refrigerator, an inertial tube type pulse tube refrigerator or a two-way intake and inertia tube combined phase modulation Type pulse tube refrigerator.
  • the refrigerator When the refrigerator is a Stirling type pulse tube refrigerator, the refrigerator further includes a pressure connected in sequence A compressor, a transfer tube, and an aftercooler, the stage aftercooler being in communication with the regenerator.
  • the draft tube can also extend through the stage aftercooler into the transfer tube.
  • the extension of the draft tube is capable of rectifying air compressed by the compressor.
  • the refrigerator When the refrigerator is a GM type pulse tube refrigerator, the refrigerator further includes a stage aftercooler in communication with the regenerator, the stage cooler having a first air pipe connected to the high pressure gas source and connected to the low pressure gas source
  • the second air pipe, the first air pipe and the second air pipe are each provided with an electric valve.
  • the present invention it is possible to suppress the occurrence of a bias current in the regenerator or the intra-vessel refrigerant of the pulse tube refrigerator.
  • FIG. 1 is a schematic structural view of a pulse tube refrigerator according to an embodiment of the present invention.
  • Figure 2 is a schematic structural view of the draft tube of Figure 1;
  • Figure 3 is a cross-sectional view of a regenerator of a pulse tube refrigerator without a draft tube
  • Figure 4 is a cross-sectional view of a regenerator of a pulse tube refrigerator with a draft tube
  • Figure 5 is a micro-processing diagram of a cross section of the regenerator
  • Figure 6 is a schematic view showing the structure of the E micro-element of Figure 5 in the axial direction;
  • Figure 7 is a schematic enlarged view of the structure of the cold end heat exchanger of the pulse tube refrigerator without the draft tube;
  • Figure 8 is a partial enlarged view of the cold end heat exchanger of Figure 1;
  • FIG. 9 is a schematic structural view of a pulse tube refrigerator according to another embodiment of the present invention.
  • FIG. 10 is a schematic structural view of a refrigerator according to still another embodiment of the present invention.
  • a pulse tube refrigerator mainly has the following technical problems: First, the flow and temperature radial non-uniformity occurs inside the regenerator; Second, the cold end heat exchanger has a large heat exchange temperature difference under the large cooling capacity; The internal rectifier screen of the tube is difficult to fix; Fourth, the internal temperature and pressure of the refrigerator cannot be directly measured. These problems may have a significant limitation on the performance improvement of high-power Stirling-type pulse tube refrigerators.
  • the unevenness occurring in the regenerator has various causes.
  • the main reason is that the small length-diameter in the high-power pulse tube refrigerator will weaken the radial heat and hydraulic connection.
  • the circulation will appear in the regenerator.
  • the resulting temperature inhomogeneity further magnifies the resulting circulation.
  • the current main method is to enhance the heat transfer in the same section, fill the high thermal conductivity or the filler of different mesh at a specific position of the regenerator, or adopt the appropriate aspect ratio and reduce the sound. Input of power, etc., but all of the above can only reduce the regenerator loss to a certain extent, and the performance improvement of the whole machine is not significant enough. More effective methods are needed to be explored.
  • the vein is often filled in the vessel for rectification, but since the screen needs to be fixed, the rectifying device is usually arranged at both ends of the vessel. As the mass flow increases and the diameter of the vessel becomes larger, the possibility of uneven airflow in the middle of the vessel increases. It is practical to provide a screen for rectification in the middle of the vessel, although in the past there was a grid in the middle of the vessel. The experiment, but the arrangement method is more complicated.
  • the parameters of the currently studied pulse tube refrigerator are mainly temperature and pressure.
  • Temperature measurement generally involves placing a thermometer on the wall of the regenerator and the wall of the vessel, and the internal temperature distribution is not obtained. Later, an infrared camera was introduced to study the temperature field inside the vessel.
  • the temperature range minimum temperature 230K
  • the measurement principle the dense filling of the regenerator affects the internal temperature imaging
  • the refrigerator according to the present invention is a pulse tube refrigerator, and the type of the pulse tube refrigerator is not limited, and may be single-stage or multi-stage; it may be a thermally coupled pulse tube refrigerator, a gas-coupled pulse tube refrigerator, or Terrin type pulse tube refrigerator or GM type pulse tube refrigerator; can also be small hole type pulse tube refrigerator, two-way intake type pulse tube refrigerator, inertial tube type pulse tube refrigerator or two-way intake and inertia tube combination Phase-modulated pulse tube refrigerator.
  • the cross-section airflow exchange path can be blocked and reduced, the flow field is more uniform, the temperature unevenness in the regenerator is reduced, and the refrigerator is efficiently operated.
  • the degree of reduction of the flow channel in the cold-end heat exchanger can be reduced, the airflow structure can be optimized, the fin length of the cold-end heat exchanger can be shortened, and the cold can be strengthened.
  • the heat exchange capacity of the end heat exchanger is the heat exchange capacity of the end heat exchanger.
  • a circular vessel By extending the draft tube into the vessel, a circular vessel can be formed, which can reduce the diameter between the regenerator and the vessel, optimize the airflow in the vessel, and the C segment can provide a fixed point for the rectifier network, which is convenient.
  • a rectifying layer is disposed within the vessel.
  • the temperature, pressure and other parameters inside the refrigerator can be measured without affecting the internal flow field of the refrigerator.
  • a pulse tube refrigerator includes a compressor 1, a transfer pipe 2, a post-stage cooler 3, a regenerator 4, and a cold-end heat exchanger 5 which are sequentially connected.
  • the end portion of the regenerator 4 close to the vascular side is referred to as a low temperature end
  • the end portion near the compressor side is referred to as a high temperature end.
  • a draft tube is disposed in the regenerator 4 along its axial direction.
  • the draft tube is, for example, a hollow cylindrical member. Since the draft tube is hollow, it is possible to reduce heat entering the low temperature end from the high temperature end of the regenerator. Moreover, it is preferable to provide a plurality of openings in the side wall of the draft tube, and to communicate the internal space of the regenerator with the internal space of the draft tube.
  • the filler can be maintained at a high purity by providing a plurality of openings in the side walls of the draft tube.
  • the draft tube does not necessarily have to be hollow, and a solid member made of a material having a small thermal conductivity can also be used.
  • the internal space of the draft tube is preferably maintained in an airtight state with respect to the atmosphere.
  • the inner space of the draft tube and the inner space of the regenerator 4 may also be separated by the side walls of the draft tube without being in communication with each other.
  • the draft tube section located in the regenerator ie the regenerator section of the draft tube, is referred to as section A 15 .
  • the section A of the draft tube can be arranged coaxially with the regenerator 4.
  • the draft tube can extend to the cold end heat exchanger 5 to extend into the cold end heat exchanger.
  • the draft tube section located in the cold end heat exchanger, ie the cold end heat exchanger section of the draft tube, is referred to as section B 14.
  • the draft tube continues to extend through the cold end heat exchanger 5 to extend into the vessel 6.
  • the section of the draft tube located within the vessel, the vessel section of the draft tube, is referred to as the C section 13.
  • the section C of the draft tube can be arranged coaxially with the vessel 6.
  • the draft tube can continue to extend through the vessel 6 to extend into the hot end heat exchanger 7.
  • the draft tube section located in the hot end heat exchanger, ie the hot end heat exchanger section of the draft tube, is referred to as D section 12.
  • the inside of the regenerator 4 is filled with a filler.
  • the filler is, for example, a wire mesh of copper or the like.
  • Extending inside the regenerator 4 is a section A of the draft tube, the packing being an annular wire mesh corresponding to the shape of the draft tube. Since the packing is filled in such a manner as to protect the draft tube, the passage of the refrigerant gas exchange between the regenerator and any two points (two points which are spatially indistinguishable) equidistant from the midpoint of the section in the cross section is reduced. That is, the refrigerant cannot flow straight between two points, and thus the flow resistance between the two points increases.
  • Figure 3 is a cross-sectional view of a regenerator of a pulse tube refrigerator without a draft tube.
  • Figure 4 is a cross-sectional view of a regenerator of a pulse tube refrigerator with a draft tube.
  • the gas exchange passage between the two points where the space is indistinct is reduced to some extent as compared with the case of FIG. use
  • the draft tube can increase the flow resistance between the two points. Under the same pressure difference, the gas exchange between the two points with large flow resistance is smaller. Thereby, the unevenness of the flow field can be reduced.
  • FIG. 5 is a micro-processing diagram of the cross-section of the regenerator.
  • Fig. 6 is a schematic view showing the structure of the E microsphere of Fig. 5 in the axial direction.
  • the regenerator is divided into an infinite number of small regenerators, that is, an infinite number of small micro-elements, and the regenerator is divided into countless pieces along the cross section of the regenerator.
  • a small regenerator that is, a myriad of small micro-elements.
  • the small regenerators on the same section of the regenerator should have no gas exchange with each other. That is, there is no difference in position of any black-filled regenerator.
  • the pressure is equal on the same section.
  • the unit distance is randomly appearing in the axial direction.
  • Flow resistance the E micro-element is taken as an example, that is, the possible differential pressure gradients at I, II, and III are not the same, so that the flow resistance is not uniform in the axial direction or it is distributed as intended. For every small regenerator, this happens and there is a random distribution between them.
  • the total cumulative flow resistance in the axial direction does not show a large difference between the small regenerators.
  • a rectifying net (not shown) may be fixed to the outer wall of the C-section of the draft tube.
  • a plurality of temperature sensors may be disposed on the inner wall of the draft tube, and a plurality of pressure sensors (not shown) may be embedded in the outer wall of the draft tube.
  • Each sensor can be connected to the external measuring device 10 via a wire 11.
  • the wire 11 passes through the inside of the draft tube and extends outward from the end of the portion of the draft tube at the hot end heat exchanger 7 up to the external measuring device 10.
  • FIG 7 is a schematic enlarged view of the structure of the cold end heat exchanger of the pulse tube refrigerator without the draft tube.
  • Figure 8 is a partial enlarged view of the cold end heat exchanger of Figure 1.
  • the introduction of the B section of the draft tube can directly reduce the degree of diameter reduction from the regenerator to the vessel. Comparing Fig. 7 and Fig. 8, it is found that ⁇ >2 ⁇ , where ⁇ is the angle of change when the draft tube is not installed. 2 ⁇ is the variable diameter after the introduction of the draft tube, so the draft tube can effectively suppress the eddy current loss.
  • FIG. 9 is a schematic structural view of a pulse tube refrigerator according to another embodiment of the present invention.
  • the rest of the arrangement is the same as that of the embodiment illustrated in FIGS. 1 to 8 except that the introduction of the draft tube extension portion 16 is increased.
  • the same components are denoted by the same reference numerals, and the description thereof will be omitted.
  • the draft tube may also extend through the post-stage cooler 3 to the transfer tube 2, ie, a draft tube that passes through the stage after-cooler and is located in the transfer tube.
  • An extension 16 that can also penetrate deep into the compressor.
  • FIG 10 is a still further embodiment of the present invention.
  • the rest of the arrangement is the same as that of the embodiment described with reference to Figs. 1 to 8 except that the refrigerator is a U-type Stirling type pulse tube refrigerator.
  • the same components are denoted by the same reference numerals, and the description thereof will be omitted.
  • the cross-section airflow exchange path can be blocked and reduced, the flow field is more uniform, the temperature unevenness in the regenerator is reduced, and the refrigerator is highly efficient. Work; By providing a B-section of the draft tube in the cold-end heat exchanger, the degree of reduction of the flow path in the cold-end heat exchanger can be reduced, and the airflow structure can be optimized.
  • the fin length of the cold-end heat exchanger can be shortened, and the heat exchange capability of the cold-end heat exchanger can be enhanced; by providing the C-section of the draft tube in the vessel, a circular vessel can be formed, and the regenerator can be reduced
  • the diameter between the vessel and the vessel is optimized, and the airflow in the vessel is optimized, and the segment C of the draft tube can provide a fixed point for the rectifier net to facilitate the arrangement of the rectifying layer in the vessel; by arranging the sensor on the draft tube, the refrigeration can be not affected
  • the measurement of parameters such as temperature and pressure inside the refrigerator is realized.
  • the cross-sectional area is the same everywhere in section A, and the ratio of the cross-sectional area to the cross-sectional area of the regenerator is 1/20 or more and 1/2 or less, and the cross-sectional area is the same everywhere in the C section.
  • the ratio of the cross-sectional area to the cross-sectional area of the vessel is 1/20 or more and 1/2 or less.
  • the cross-sectional area of the A section is larger than the cross-sectional area of the C section.
  • the material used for manufacturing the draft tube is not particularly limited, and more is to reduce thermodynamic loss and fluid loss, but in order to make the data measured by the temperature sensor reliable and effective, in the present invention, the guide tube is
  • the part provided with the temperature sensor is a heat transfer material, such as a material having excellent thermal conductivity such as copper, and the other part may be a material having a low thermal conductivity such as stainless steel.
  • the draft tube has no shape and size limitation. In order to have the best effect of the draft tube, the outer contour of the cross section of the draft tube in this embodiment is circular.
  • the draft tube may be integrally formed, or may be composed of a plurality of small components according to actual conditions.
  • the connection manner between them is not particularly limited, and may be various connection methods such as bonding, threading, welding, and snap-fit.
  • the draft tube is generally a relatively atmospheric sealed structure, but the internal working fluid relative to the vessel may be a non-sealed structure.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

一种制冷机，其包括依次连接的回热器（4）、冷端换热器（5）、脉管（6）、热端换热器（7）以及调相机构（9），在回热器（4）内沿其轴向设置有导流管（17），该导流管（17）可延伸至冷端换热器（5）内，并且该导流管（17）可进一步延伸至脉管（6）内，该导流管（17）还可进一步延伸至热端换热器（7）内。该制冷机能够实现制冷机中流体流动的均匀化并防止偏流，尤其可以减少回热器（4）内温度不均匀现象，实现制冷机高效工作。

Description

一种脉管制冷机
本申请要求于2015年3月30日提交中国专利局、申请号为201510145151.0、发明名称为“一种脉管制冷机”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本发明涉及制冷机领域，具体涉及一种脉管制冷机。
背景技术
近年来，对大功率斯特林型脉管制冷机的研发得到关注。
为了提升脉管制冷机的制冷能力，需要使用大口径的回热器及脉管。但是，伴随回热器和脉管的大口径化，在回热器和脉管内制冷剂的流动容易发生偏流。制冷剂的偏流很可能会限制制冷性能的提升。
发明内容
针对上述问题，本发明提供了一种抑制了脉管制冷机内制冷剂出现偏流的制冷机。
为了实现上述发明目的，本发明采取的技术方案如下：
一种脉管制冷机，包括依次连接的回热器、冷端换热器、脉管，热端换热器以及调相机构，在回热器内沿其轴向设置有导流管。通过在回热器内设置导流管能够阻断和减少横向截面(与周向垂直的截面)气流交换路径，使流场更加均匀，减少回热器内温度不均匀现象，从而实现制冷机高效工作。优选地，所述导流管与所述回热器同轴设置。
作为本发明的优选实施方式，所述导流管还可延伸至冷端换热器内。通过将导流管延伸至冷端换热器内，能够降低流道在冷端换热器内的变径程度，能够优化气流组织，缩短冷端换热器的翅片长度，强化冷端换热器 的换热能力。
作为优选，所述导流管还可进一步延伸至脉管内。通过将导流管延伸至脉管内，能够使圆形脉管变为环形脉管，并且可以减小回热器与脉管间的变径，优化脉管内的气流。更为优选地，位于脉管内的导流管区段与所述脉管同轴设置。
作为优选，位于脉管内的导流管区段的外壁可固定有整流网。在大质量流的情况下，因为冷端换热器以及热端换热器的形状的限制，由此进入脉管两端的气体必然不是均匀的，因此用整流网作为层流化元件将是十分必要的，而固定整流网，尤其是在脉管中部固定整流网，是十分困难的，本发明通过将导流管延伸至脉管内，能够给整流网提供固定点，以方便在脉管内布置整流层。
作为优选，所述导流管还可进一步延伸至热端换热器内。
所述导流管的内壁和/或外壁还可布置有至少一个传感器，所述至少一个传感器通过导线与外部测量装置相连通，该导线穿过所述导流管的内部并从导流管位于热端换热器处的末端向外延伸至外部测量装置。
通过在导流管上布置传感器，能够在不显著影响制冷机内部流场的情况下，实现对制冷机内部的温度、压力等参数的测量。通过测得制冷机内部的温度与压力，还能够促进对脉管制冷机原理的深入了解，同时有利于对小长径比的回热器内不均匀性现象进行深入分析，从而寻找高效可行的抑制损失的方法。
如通过测量回热器内部的温度，结合回热器外壁面的温度测量，可以立体得到回热器的更多点的温度分布，对于研究回热器内部不均匀性以及对制冷机进行优化控制有重大的意义；如通过测量冷端换热器内部气流的温度(不存在热流)，结合冷端换热器外壁上的温度测量，可以更加真实地分析冷端换热器的效率；如通过测量脉管内的温度，结合脉管外壁面的温度测量，可以得到脉管立体温度分布，对于脉管优化有指导性作用。
作为优选，所述至少一个传感器温度传感器，设置在导流管的内壁。将温度传感器设置在导流管的内壁上就不会影响制冷机内的流场。
制造导流管所用的材料，没有特殊的限制，主要以能减少热力学与流 体损失为主。例如位于脉管内的导流管就可以使用热导率低的材料。但为了使温度传感器测得的数据具有可靠性和实效性，作为优选，导流管中设置有温度传感器的部分可由传热材质制成。
作为优选，所述传感器还可是压力传感器，嵌入导流管的外壁。这样嵌入式的布置能够最大程度的减小压力传感器对制冷机内流场的影响。
位于回热器内的导流管区段各处的横截面面积均相同，其横截面面积与回热器横截面面积的比为1/20以上且1/2以下，位于脉管内的导流管区段各处的横截面面积均相同，其横截面面积与脉管横截面面积的比为1/20以上且1/2以下。位于回热器内的导流管区段的横截面面积大于位于脉管内的导流管区段的横截面面积。为了使导流管从回热器到脉管能够平缓过渡，作为优选，所述位于冷端换热器内的导流管区段的两端的横截面分别与位于回热器内的导流管区段和位于脉管内的导流管区段的横截面相匹配。这样的设计，能够直接减少从回热器到脉管的变截面程度，能减少因变截面而产生的损失。
导流管没有形状和大小的限制，为了使导流管具有较好的效果，作为优选，所述导流管的横截面的外轮廓为圆形或正多边形。
为了使导流管的效果达到最好，所述导流管的横截面的外轮廓优选为圆形。
本发明中导流管可以一体成型，也可以根据实际情况由多个小部件共同组成。当为多个小部件组成时，相互之间的连接方式没有特殊限制，可以为粘合、螺纹配合，焊接、卡接配合等各种连接方式。
作为优选，所述调相机构包括与热端换热器的远离回热器的一端连通的惯性管以及与惯性管连接的气库。
所述制冷机为脉管制冷机，脉管制冷机的总类没有任何限制，可以为单级或多级；可以为热耦合型脉管制冷机、气耦合型脉管制冷机、斯特林型脉管制冷机或GM型脉管制冷机；也可以为小孔型脉管制冷机、双向进气型脉管制冷机、惯性管型脉管制冷机或双向进气与惯性管联合调相型脉管制冷机。
当制冷机为斯特林型脉管制冷机时，所述制冷机还包括依次连接的压 缩机、传输管和级后冷却器，所述级后冷却器与回热器连通。
作为优选，所述导流管还可延伸穿过级后冷却器至传输管内。该导流管的延伸区段能够对压缩机压缩的空气进行整流。
当制冷机为GM型脉管制冷机时，所述制冷机还包括与回热器连通的级后冷却器，所述级冷器具有与高压气源相连的第一气管以及与低压气源相连的第二气管，第一气管和第二气管均设有电动阀。
根据本发明，能够抑制脉管制冷机的回热器或脉管内制冷剂出现偏流。
附图说明：
图1是根据本实用新型的一种具体实施方式的脉管制冷机的结构示意图；
图2是图1中的导流管的结构示意图；
图3是没有导流管时脉管制冷机的回热器的横截面图；
图4是具有导流管时脉管制冷机的回热器的横截面图；
图5是回热器的横截面的微元化处理图；
图6是表示图5中E微元的轴向上的结构的示意图；
图7是没有导流管时脉管制冷机的冷端换热器处的结构示意放大图；
图8是图1中冷端换热器处的局部放大图；
图9是为根据本实用新型的另一种具体实施方式的脉管制冷机的结构示意图；
图10是为根据本实用新型的又一种具体实施方式的制冷机的结构示意图。
图中各附图标记为：
1.压缩机，2.传输管，3.级后冷却器，4.回热器，5.冷端换热器，6.脉管，7.热端换热器，8.惯性管，9.气库，10.测量装置，11.导线，12.导流管D段，13.导流管C段，14.导流管B段，15.导流管A段，16.导流 管延伸部，17.导流管。
具体实施方式：
一种脉管制冷机主要会存在如下技术问题：一、回热器内部出现流动与温度径向不均匀性；二、大冷量下冷端换热器存在过大换热温差；三、脉管内部整流丝网难以固定；四、制冷机内部温度与压力无法直接测量。这些问题可能对大功率斯特林型脉管制冷机的性能提升起到了不可忽略的限制。
关于问题一，回热器内出现的不均匀性具有多种原因。其中主要原因是，大功率脉管制冷机中的小长径比回热器会减弱径向热力和水力联系，当输入功率和温度梯度增大超过临界值时，回热器内便会出现环流，由此导致的温度不均匀性又会进一步放大产生的环流。针对回热器径向温度不均匀性现象，目前的主要方法为增强同截面传热，在回热器特定位置填充高热导率或不同目数的填料、或者采用适当的长径比、减少声功的输入等，但是以上都只能在一定程度减少回热器损失，对整机性能的提升不够显著。有待进一步发掘更加有效的方法。
关于问题二，针对于常见的狭缝式冷端换热器，绝大部分研究关注的都是其内部换热面积和对流场的影响。经分析表明，随着制冷量的急剧增加，冷端换热器的单位热流量也剧烈增加，同时冷端换热器性能损失占整机性能损失的比例也越来越来大。因此，冷端换热器的优化是高效率大冷量制冷机的必要条件。同时随着制冷机制冷量的增加，回热器直径相应的增加，导致回热器和脉管之间存在一个大变径段，这需要在较短的冷端换热器内进行过渡。如果不进行流道的优化，比如会造成巨大的涡流损失。
关于问题三，脉管内经常填充丝网进行整流，但是由于丝网需要固定，往往通常将此整流装置布置脉管的冷热两端。随着质量流的增加和脉管的直径变大，脉管中部出现气流不均匀的可能性增大，在脉管中部设置丝网进行整流具有实际意义，虽然过去也有在脉管中部布置丝网的实验，但是布置方法较为复杂。
关于问题四，目前研究的脉管制冷机的参数主要为温度与压力。其中 温度测量一般都是在回热器的壁面与脉管的壁面布置温度计，而无法得到内部真实的温度分布。后来引入红外摄像仪对脉管内部的温度场进行研究，但是由于测温范围的限制(最低温度230K)以及测量原理(回热器内填料密集填充影响内部温度成像)的问题，都无法准确和直观的反映机器内部的温度与压力。如果能将温度计或者压力计布置到内部，又不影响机器本身，将对制冷机的研究产生重大意义。
如果上述的四个问题能得到解决，斯特林型脉管制冷机将会得到飞跃性的发展。这将切合时代发展对具有高效可靠的低温制冷机巨大的需求，将会产生巨大的经济与社会效益。
本发明所说的制冷机为脉管制冷机，脉管制冷机的种类没有任何限制，可以为单级或多级；可以为热耦合型脉管制冷机、气耦合型脉管制冷机、斯特林型脉管制冷机或GM型脉管制冷机；也可以为小孔型脉管制冷机、双向进气型脉管制冷机、惯性管型脉管制冷机或双向进气与惯性管联合调相型脉管制冷机。
根据本发明的一种实施方式所涉及的脉管制冷剂，可以得到如下优点：
一、通过在回热器内设置导流管，能够阻断和减少横向截面气流交换路径，使流场更加均匀，减少回热器内温度不均匀现象，实现制冷机高效工作。
二、通过将导流管延伸至冷端换热器内，能够降低流道在冷端换热器内的变径程度，能够优化气流组织，缩短冷端换热器的翅片长度，强化冷端换热器的换热能力。
三、通过将导流管延伸至脉管内，能够形成环形脉管，可以减小回热器与脉管间的变径，优化脉管内的气流，且C段能够给整流网提供固定点，方便在脉管内布置整流层。
四、通过在导流管上布置传感器，能够在不影响制冷机内部流场的情况下，实现制冷机内部的温度、压力等参数的测量。
以下，以斯特林型脉管制冷机为例，结合各附图对本发明的实施方式作详细描述。
如图1、2所示，本发明的实施方式所涉及的脉管制冷机，包括依次连接的压缩机1、传输管2、级后冷却器3、回热器4、冷端换热器5、脉管6、热端换热器7、惯性管8以及气库9。制冷机工作时，回热器4的靠近脉管的一侧的温度下降，从靠近压缩机1的端部至靠近脉管的一侧出现温度梯度。因此，将回热器4的靠近脉管侧的端部称作低温端，将靠近压缩机侧的端部称作高温端。在回热器4内沿其轴向设置有导流管。导流管例如为中空的圆筒状部件。由于导流管是中空的，因此能够降低从回热器的高温端侵入低温端的热量。而且，优选在导流管的侧壁设置多个开口，并使回热器的内部空间和导流管的内部空间连通。通过在导流管的侧壁设置多个开口，能够将填料维持为高纯度。另外，导流管未必一定要中空，也可以使用由导热系数较小的材料制成的实心部件。导流管的内部空间优选相对于大气维持气密状态。而且，还可以对导流管的内部空间进行减压。导流管的内部空间和回热器4的内部空间也可以被导流管的侧壁隔开而彼此不相通。将位于回热器内的导流管区段，即导流管的回热器区段称作A段15。该导流管A段可以与回热器4同轴设置。该导流管可以向冷端换热器5延伸以延伸至冷端换热器内。将位于冷端换热器内的导流管区段，即导流管的冷端换热器区段称作B段14。该导流管继续延伸穿过冷端换热器5以延伸至脉管6内。将位于脉管内的导流管区段，即导流管的脉管区段称作C段13。该导流管C段可以与脉管6同轴设置。该导流管可以继续延伸穿过脉管6以延伸至热端换热器7内。将位于热端换热器内的导流管区段，即导流管的热端换热器区段称作D段12。
在回热器4的内部填充有填料。填料例如为铜等的金属丝网。在回热器4的内部延伸有导流管的A段，填料为与导流管的形状相对应的环形丝网。由于填料以保卫导流管的方式填充，因此回热器同截面中距截面中点等距的任意两点(空间上无差异的两点)之间的制冷剂气体交换的通道会减少。即，制冷剂无法在两点之间直线流动，因而两点之间的流阻增大。图3是没有导流管时脉管制冷机的回热器的横截面图。图4具有导流管时脉管制冷机的回热器的横截面图。如图4所示，通过设置A段，与图3的情况相比，在一定程度上减少空间无差异两点之间的气体交换通道。用 流体网络分析，导流管能增加两点之间的流阻，在具有相同的压差情况下，流阻大的两点之间气体交换量更小。由此，能够降低流场的不均匀性。
图5是回热器的横截面的微元化处理图。图6是表示图5中E微元的轴向上的结构的示意图。如图5和图6所示，将回热器延其轴线方向划分为无数个小的回热器，即无数个小的微元，并且沿回热器的截面将回热器划分为无数个小的回热器，即无数个小的微元。在理想情况(包括不存在径向不均匀现象)下，在回热器的同一截面上的小回热器应该彼此之间都不存在气体交换。即任一黑色填充的回热器都不存在位置上的差异性。因此在同一截面上压力相等。但实际过程中，尽管采用同一尽量均匀的填料填充，但是物质的不连续性和填充工艺等许多因素的存在，即使对于一根小的回热器而言，轴向上会随机出现单位距离不同的流阻。这里以E微元为例，即I、II、III处可能的压差梯度不相同，因此轴向方向上无法保证流阻均匀或者让其按设想进行分布。对于每个小的回热器而言，都会出现如此的情况，而且彼此之间的都会出现随机分布。但因为采用相同填充材料和相同的填充工艺，轴向上的随机累积的总流阻在各小的回热器之间不会出现大的差异性。但是在同一截面，因为轴向随机流阻分布导致了原本空间上无差异的两点出现压差，这个压差将会直接驱动小回热器彼此之间的气流交换，出现整体上径向不均匀，对外就体现在径向温度不均匀性。正如图5、6的分析所示，因为导流管的加入，将会减少空间上无差异的两点间气流交换，因此会减缓回热器内径向温度不均匀性现象，将会提升回热器的性能。
而且，在导流管C段的外壁，还可以固定未图示的整流网。
在导流管的内壁可以配置有未图示的若干个温度传感器，在导流管的外壁可以嵌入有未图示的若干个压力传感器。各传感器可以经由导线11与外部测量装置10连接。该导线11经过导流管的内部且从导流管的位于热端换热器7的部位的末端向外侧延伸直至外部测量装置10。
随着制冷量的需求的急剧增加，冷端换热器将面临更加大单位体积换热要求。图7是没有导流管时脉管制冷机的冷端换热器处的结构示意放大图。图8是图1中冷端换热器处的局部放大图。如图7、8所示，通过设 置导流管B段，迫使气流更加集中在冷端换热器的外端，减少换热热阻，提升换热器效率。同时，导流管B段的引入能直接减少由回热器到脉管变径的程度，对比图7和图8，发现α＞2β，其中α为未安装导流管时的变径角度，2β为安装了导流管后的变径角度，因此，导流管能有效的抑制涡流损失。
图9为根据本发明的另一种实施方式的脉管制冷机的结构示意图。在本实施方式中，除了增加设置导流管延伸部16外，其余设置与图1至图8说明的实施方式相同。在以下说明中，对相同的结构标注相同的符号，并省略对该结构以及作用效果的说明。
如图9所示，为了对压缩机压缩的空气进行整流，导流管还可以延伸穿过级后冷却器3至传输管2内，即形成穿过级后冷却器位于传输管内的导流管延伸部16，该延伸部还可以深入至压缩机中。
图10为本发明的又一种实施方式。在本实施方式中，除了制冷机为U型斯特林型脉管制冷机外，其余设置与图1至图8说明的实施方式相同。在以下说明中，对相同的结构标注相同的符号，并省略对该结构以及作用效果的说明。
如图10所示，通过在回热器内设置导流管A段，能够阻断和减少横向截面气流交换路径，使流场更加均匀，减少回热器内温度不均匀现象，实现制冷机高效工作；通过在冷端换热器内设置导流管B段，能够降低流道在冷端换热器内的变径程度，能够优化气流组织。由此，能够缩短冷端换热器的翅片长度，强化冷端换热器的换热能力；通过设置在脉管内设置导流管C段，能够形成环形脉管，可以减小回热器与脉管间的变径，优化脉管内的气流，且导流管C段能够给整流网提供固定点，方便在脉管内布置整流层；通过在导流管上布置传感器，能够在不影响制冷机内部流场的情况下，实现制冷机内部的温度、压力等参数的测量。
在本发明中，A段各处的横截面面积均相同，其横截面面积与回热器横截面面积的比为1/20以上且1/2以下，C段各处的横截面面积均相同， 其横截面面积与脉管横截面面积的比为1/20以上且1/2以下。A段的横截面面积大于C段的横截面面积，为了使A、C段能够平缓过渡，B段两端的横截面分别与A段和C段的横截面相匹配。
制造导流管的所用材料，没有特殊的限制，更多在于能减少热力学损失与流体损失为主，但为了使温度传感器测得的数据具有可靠性和实效性，本发明中，导流管中设置有温度传感器的部分为传热材质，例如铜等热导率优良的材料，其他部分可以为热导率低的材料，例如不锈钢等。导流管没有形状和大小的限制，为了使导流管具有最好的效果，本实施例中导流管的横截面的外轮廓为圆形。
在本发明中，导流管可以为一体成型，也可以根据实际情况由多个小部件共同组成。当为多个小部件组成时，相互之间的连接方式没有特殊限制，可以为粘合、螺纹配合，焊接、卡接配合等各种连接方式。
导流管整体为相对大气密封的结构，但相对脉管的内部工作流体可以是非密封的结构。
以上所述仅为本发明的优选实施方式，并非因此即限制本发明的专利保护范围，凡是运用本发明说明书及附图内容所作的等效结构变换，直接或间接运用在其他相关的技术领域，均同理包括在本发明的保护范围内。

Claims (14)

  1. 一种脉管制冷机，包括依次连接的回热器、冷端换热器、脉管、热端换热器以及调相机构，其特征在于，在所述回热器内沿其轴向设置有导流管。
  2. 如权利要求1所述的脉管制冷机，其特征在于，所述导流管与所述回热器同轴设置。
  3. 如权利要求1所述的脉管制冷机，其特征在于，所述导流管延伸至冷端换热器内。
  4. 如权利要求1所述的脉管制冷机，其特征在于，所述导流管进一步延伸至脉管内。
  5. 如权利要求4所述的脉管制冷机，其特征在于，位于所述脉管内的导流管区段与所述脉管同轴设置。
  6. 如权利要求1所述的脉管制冷机，其特征在于，所述导流管进一步延伸至热端换热器内。
  7. 如权利要求4所述的脉管制冷机，其特征在于，位于所述脉管内的导流管区段的外壁固定有整流网。
  8. 如权利要求6所述的脉管制冷机，其特征在于，所述导流管的内壁和/或外壁布置有至少一个传感器，所述至少一个传感器通过导线与外部测量装置相连通，所述导线穿过所述导流管的内部并从导流管位于热端换热器处的末端向外延伸至外部测量装置。
  9. 如权利要求1所述的脉管制冷机，其特征在于，位于所述回热器内的导流管区段各处的横截面面积均相同，其横截面面积与回热器横截面面积的比为1/20以上且1/2以下。
  10. 如权利要求9所述的脉管制冷机，其特征在于，位于所述脉管内的导流管区段各处的横截面面积均相同，其横截面面积与脉管横截面面积的比为1/20以上且1/2以下。
  11. 如权利要求10所述的脉管制冷机，其特征在于，位于所述脉管内的导流管区段的横截面面积小于位于所述回热器内的导流管区段的横截 面面积，位于所述冷端换热器的导流管区段的两端的横截面分别与位于所述回热器内的导流管区段和位于所述脉管内的导流管区段的横截面相匹配。
  12. 如权利要求1所述的脉管制冷机，其特征在于，所述导流管的横截面的外轮廓为圆形或正多边形。
  13. 如权利要求1所述的脉管制冷机，其特征在于，还包括依次连接的压缩机、传输管和级后冷却器，其中，级后冷却器与回热器相连接，所述导流管延伸至传输管内。
  14. 如权利要求1所述的脉管制冷机，其特征在于，所述导流管为相对大气密封的结构。
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