WO2010133125A1 - 气波制冷机及其转轮分配器 - Google Patents

气波制冷机及其转轮分配器 Download PDF

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Publication number
WO2010133125A1
WO2010133125A1 PCT/CN2010/072416 CN2010072416W WO2010133125A1 WO 2010133125 A1 WO2010133125 A1 WO 2010133125A1 CN 2010072416 W CN2010072416 W CN 2010072416W WO 2010133125 A1 WO2010133125 A1 WO 2010133125A1
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WO
WIPO (PCT)
Prior art keywords
impeller
nozzle
main shaft
wave refrigerator
distributor
Prior art date
Application number
PCT/CN2010/072416
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English (en)
French (fr)
Inventor
邢小月
单希壮
Original Assignee
深圳市力科气动科技有限公司
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Application filed by 深圳市力科气动科技有限公司 filed Critical 深圳市力科气动科技有限公司
Publication of WO2010133125A1 publication Critical patent/WO2010133125A1/zh

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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
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • F25B9/065—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders using pressurised gas jets

Definitions

  • the invention relates to a refrigeration machine, in particular to a gas wave refrigerator. Background technique
  • the existing cryogenic refrigeration technology uses a multi-stage compression refrigerant to achieve low temperature.
  • the first stage compresses a refrigerant
  • the second stage compresses the second refrigerant on the basis of absorbing the cold amount obtained by the first stage compression, and achieves the purpose of cooling by the vaporization endothermic of the refrigerant, usually the second stage compression.
  • the refrigerant liquefaction point temperature used is lower than the first stage refrigerant liquefaction point temperature.
  • Rotary heat separator is a kind of equipment that uses gas pressure to cool according to the principle of shock wave and expansion wave. Therefore, it is also called gas wave refrigerator. It has structural unit, energy saving, environmental protection, low cost, adaptability and operation and maintenance. Convenience and other characteristics, since the advent of the 1970s, has received people's attention, and has practical applications in the petrochemical industry.
  • the existing runner distributor usually comprises a main shaft and an impeller, and the impeller is arranged in the middle of the main shaft, and the inner portion of the main shaft is provided with an open end and an inner cavity closed at one end.
  • the transmission mechanism such as a motor is connected to the closed end of the main shaft, and the open end serves as an air inlet to input high-pressure gas, so that a high-pressure chamber is required at the other end of the main shaft.
  • the technical problem to be solved by the embodiments of the present invention is to provide a gas wave refrigerator which improves the structure of the runner distributor, thereby improving the structure of the entire air wave refrigerator, making the structure compact, and having a good transmission. Performance, and optimize the structural parameters of the runner distributor to improve the cooling efficiency of the air-wave refrigerator.
  • Another technical problem to be solved by the embodiments of the present invention is to provide a reel distributor which has improved structure, good transmission performance, and optimized structural parameters thereof, thereby improving the cooling efficiency of the air-wave refrigerator.
  • an embodiment of the present invention provides a gas wave refrigerator including a body, a bearing, a runner distributor, a sealing structure, and a receiving pipe, wherein the body is provided with an air inlet hole and an air outlet hole.
  • the sealing structure is disposed between the air inlet hole and the air outlet hole on the body,
  • the wheel distributor includes a main shaft and an impeller, and the main shaft is provided with an axially extending inner cavity, and both ends of the inner cavity are Closed, the main shaft is further provided with an air inlet connecting the inner cavity and the outer portion of the main shaft, the impeller is disposed outside the main shaft, and includes a nozzle, an inflating portion and a venting portion, and the inflating portion is
  • the deflation portions are alternately arranged around the impeller, the nozzle being a hole surrounded by the plenum, and the nozzle is in communication with the inner chamber.
  • an embodiment of the present invention further provides a rotor distributor for a gas wave refrigerator, comprising a main shaft and an impeller, wherein the main shaft is provided with an axially extending inner cavity, the inner cavity The two ends are closed, and the main shaft is further provided with an air inlet connecting the inner cavity and the outer portion of the main shaft, and the impeller is disposed outside the main shaft, and includes a nozzle, an inflating portion and a deflation portion, The inflator and the deflation portion are alternately arranged around the impeller, and the nozzle is a hole surrounded by the plenum, and the nozzle communicates with the inner chamber.
  • the embodiment of the present invention has the following beneficial effects:
  • the rotor distributor of the embodiment of the present invention and the air wave refrigerator using the same are improved, and the structure of the runner distributor is improved, thereby improving the entire air wave cooling.
  • the structure of the machine makes it compact and has good transmission efficiency fruit.
  • the structural parameters of the rotor distributor are also optimized, which significantly improves the cooling efficiency of the air-wave refrigerator.
  • FIG. 1 is a schematic cross-sectional structural view of a gas wave refrigerator according to the present invention.
  • Figure 2 is a perspective view showing the structure of a wheel distributor of the air-wave refrigerator of the present invention
  • Figure 3 is a front view of the wheel distributor of the air-wave refrigerator of the present invention
  • Figure 4 is a schematic cross-sectional view of the runner distributor of Figure 3 taken along line A-A;
  • Figure 5 is a schematic view showing the structure of the wheel distributor of Figure 3 in the X direction;
  • Figure 6 is a cross-sectional view of the runner distributor of Figure 3 taken along line C-C.
  • Figure 7 is a schematic cross-sectional structural view showing a sealing structure of the gas wave refrigerator of the present invention.
  • Figure 8 is a side view of the moving ring in the sealing structure of the gas wave refrigerator of the present invention.
  • Fig. 9 is a schematic cross-sectional view showing a receiving tube of a gas wave refrigerator and a part of the first casing. detailed description
  • a gas wave refrigerator includes a body 1, a runner distributor 2, a sealing structure 3, a receiving pipe 4, bearings 50, 52, and sealing ports 60, 62, 64.
  • the body 1 includes a first end cap 12, a first housing 14, a second housing 16, and a second end cap 18.
  • the first casing 14 and the second casing 16 are substantially hollow cylinders which are open at both ends, wherein the first casing 14 is provided with a through air outlet 142 and a plurality of hooks distributed around the first casing 14
  • the through receiving tube interface 144 receives the tube port 144 as a stepped through hole.
  • the second casing 16 is provided with a through air inlet 162.
  • the first end cover 12 covers one end of the first casing 14, the second casing 16 is fixedly connected to the other end of the first casing 14, and the second end cover 18 covers the second casing 16 and is not connected to the first casing.
  • One end of the 14 connection One end of the 14 connection.
  • Screws 192, 194 are respectively used between the first end cover 12 and the first casing 14, between the first casing 14 and the second casing 16, and between the second casing 16 and the second end cover 18, respectively.
  • 196 is fixedly coupled and between the first end cap 12 and the first housing 14 , between the first housing 14 and the second housing 16 , and the second housing 16 Sealing ports 60, 62, 64 are respectively provided at the joints with the second end caps 18 for sealing.
  • the wheel distributor 2 is disposed in the body 1, and includes a main shaft 22, an impeller 24, and a plug 26,
  • the main shaft 22 is a cylindrical shaft body, and as shown in Fig. 3, the first dam groove 220, the second dam groove 222 and the key groove 224 are disposed from the left to the right, and the key groove 224 is disposed at one end of the main shaft 22.
  • An inner cavity 226 extending axially along the main shaft 22 is formed at one end of the main shaft 22 where the key groove 224 is not provided.
  • the inner cavity 226 does not penetrate to the other end of the main shaft 22, but extends to the middle of the main shaft 22, that is, cut off, and is vertically in the middle of the main shaft 22.
  • a through air inlet 228 is axially open, and the air inlet 228 is in communication with the inner chamber 226.
  • a plug 26 is disposed in the open end of the inner chamber 226 in the main shaft 22, and is fixed to the open end by a threaded structure to close the open end of the inner chamber 226.
  • the impeller 24 is disposed between the first dam groove 220 and the air inlet 228 on the main shaft 22 and has a substantially disk shape, and includes a plurality of nozzles 240, an inflating portion 242 and a deflation portion 244, wherein the inflating portion 242 and the deflation portion 244 Alternatingly arranged around the impeller 24, the radius of the inflator 242 is the same as the inner radius of the first casing 14 of the body 1, and the radius of the deflation portion 244 is smaller than the inner radius of the first casing 14 of the body 1, that is, the deflation portion 244 The radius is smaller than the radius of the inflator 242.
  • the angle of the inflator 242 extending over the outer circumference of the impeller 24 is such that the angle of the deflation portion 244 extending over the outer circumference of the impeller 24 is ⁇ .
  • the nozzle 240 is a hole surrounded by the inflator 242 having a substantially trapezoidal cross section, the angle between the two waists of the trapezoid being ⁇ , and the nozzle 240 communicating with the inner cavity 226 of the main shaft 22.
  • the impeller 24 is provided with three sets of nozzles 240, an inflator 242, and a venting portion 244, and the angles of ⁇ , ⁇ , and ⁇ are as shown.
  • the wheel distributor 2 is disposed in the body 1, and one end of the setting plug 26 is fixed to the first end cover 12 of the body 1 through the bearing 50, and the other end passes through the second end cover 18 and is fixed by the bearing 52.
  • the axis of the nozzle 240 of the impeller 24 is on the same plane as the axis of the receiving tube interface 144 of the first housing 14.
  • the runner distributor 2 is connected to an external motor through one end of the second end cap 18.
  • the embodiment includes two sets of sealing structures 3 , which are disposed between the main shaft 22 of the runner distributor 2 and the second casing 16 and are located at the air inlet of the main shaft 22 . 228 sides.
  • the two sets of sealing structures 3 have the same structure and are symmetrically arranged, so that only one of the groups is Detailed description of the line.
  • the sealing structure 3 comprises a sleeve 30, a moving ring 31, a stationary ring 32, a push ring 33, a spring 34, a fixed body 35, a manifold block 36, a snap ring 37, a positioning ring 38, a pin 390, pins 392, 393 and 0. Type rings 394, 396, 397, 398, 399.
  • the sleeve 30 is sleeved on the main shaft 22 of the wheel distributor 2, and has a T-shaped cross section, and includes a sleeve portion 302 and a wall portion 304 extending from the sleeve portion 302 to the outer side of the axis thereof.
  • the wall portion 304 is The outer end thereof extends axially for a certain length, so as to form a receiving space (not labeled) with the sleeve portion 302 for accommodating the moving ring 31.
  • the bushing 30 is fixed to the main shaft 22 of the reel distributor 2 by means of a pin 390 and a snap ring 37, so that it can rotate with the main shaft 22, and a seal is formed between the sleeve 30 and the main shaft 22 via the 0-ring 394.
  • the moving ring 31 has an annular shape and is sleeved outside the sleeve portion 302 of the sleeve 30 and adjacent to the wall portion 304.
  • the pin 392 is engaged with the wall portion 304 of the sleeve 30 by the pin 392, so that the movable sleeve 30 can be used with the coaxial sleeve 30. It rotates together with the main shaft 22 of the wheel distributor 2, and is therefore referred to as a "moving ring".
  • a seal is formed between the movable ring 31 and the sleeve 30 by the 0-rings 396 and 398.
  • One side of the moving ring 31 is in contact with the stationary ring 32, and the surface of the contact surface has a high surface precision, and a spiral groove 312 (see Fig. 6) which is uniformly distributed in a spiral shape is provided on the contact surface.
  • the fixing body 35 is substantially annular, and the outside thereof is fixed to the second casing 16 of the body 1 by screws 197, and the inside thereof is sleeved outside the sleeve portion 302 of the sleeve 30, and extends along the outside of the sleeve portion 302.
  • the inner extending wall 352 has an outer extending wall 354 extending in the middle of the fixing body 35, and an accommodating space is formed between the inner extending wall 352 and the outer extending wall 354 for accommodating the static ring 32 and the push ring 33, and
  • the wall on the inner side of the accommodating space opens a hole parallel to the axis of the main shaft 22 of the wheel distributor 2, in which the spring 34 is housed, and one end abuts against the bottom wall of the hole.
  • a seal is formed between the fixed body 35 and the second housing 16 via the 0-ring 399.
  • the push ring 33 is sleeved on the outer side of the inner extending wall 352 of the fixing body 35, and is located in the accommodating space formed between the inner extending wall 352 and the outer extending wall 354, and one side abuts against one end of the spring 34 and the other side abuts Static ring 32.
  • a seal is formed between the push ring 33 and the fixed body 35 by the 0-ring 397.
  • the static ring 32 has an annular shape.
  • the inner and outer turns of the static ring 32 are both stepped, and the lower step of the inner ring is sleeved outside the sleeve portion 302 of the sleeve 30, and is sleeved.
  • the stationary ring 32 is interposed between the moving ring 31 and the push ring 33, and abuts against the moving ring 31, and the abutting side has a high precision, which is in abutment with the push ring 33 and forms with the push ring 33.
  • the slot 323 ownership has a certain gap between the stationary ring 32 and the sleeve portion 302, and does not rotate with the sleeve portion 302 and the main shaft 22 of the wheel distributor 2, so it is called a "static ring", but It can be slightly displaced between the positioning ring 38 and the inner extension wall 352 of the fixed body 35 with the thrust of the push ring 33 - 4 .
  • the pin 393 is fastened to the fixed body 35 through the stationary ring 32 so that the stationary ring 32 does not rotate relative to the fixed body 35.
  • the positioning ring 38 is fastened in the outer extension wall 354 of the fixed body 35, and its inner radius is smaller than the outer step radius of the static ring 32, so that the stationary ring 32 can be positioned.
  • the assembly block 36 is a four-piece metal piece, which is respectively fixed on the side of the fixing body 35 where the fixing body 35 is not provided with the screw, and is fastened to the sleeve 30, so that the sealing structure 3 is assembled into one body, so as to facilitate the assembly. It is assembled into a gas wave refrigerator, and after the sealing structure 3 is installed in the air wave refrigerator, the rotation of the wheel distributor 2 can be restricted to facilitate transportation and assembly of the air wave refrigerator. Before the air-wave refrigerator is installed in the required location, the manifold block 36 and the screws 362 must be removed before the air-wave refrigerator is ready for use, so that the air-wave refrigerator can work normally.
  • the two sets of sealing structures 3 and the second casing 16 and the main shaft 22 of the rotor distributor 2 together form a high pressure chamber 7, and a set of sealing structures 3 and a first casing 14 on the left side in FIG.
  • the end cap 12 and the runner distributor 2 together form a low greenhouse 8.
  • the high pressure chamber 7 is in communication with the inlet port 228 of the wheel distributor 2.
  • the moving ring 31 and the stationary ring 32 of the sealing structure 3 are in contact with each other; and when the air-wave refrigerator starts to operate, the high-pressure gas enters the high-pressure chamber 7 through the air inlet 162 of the second casing 16,
  • the runner distributor 2 rotates at a high speed under the driving of the external motor
  • the moving ring 31 of the sealing structure 3 and the sleeve 30 rotate with the main shaft 22 of the rotor distributor 2, and the high pressure gas enters the stationary ring 32 and the push ring.
  • the structure and sealing principle of the two sets of sealing structure 3 are the same.
  • the sealing structure 3 on the left side in FIG. 1 forms a gas seal between the low temperature chamber 8 and the high pressure chamber 7, and a set of sealing structures on the right side. 3
  • a gas seal is formed between the high pressure chamber 7 and the cavity on the right side of the sealing structure 3 to prevent the high pressure gas from leaking out.
  • the receiving tube 4 is a tubular body whose one end is closed at one end, and the open end of the receiving tube 4 is inserted into the receiving tube interface 144 of the first casing 14 of the body 1, and is fixed by the screw 41 and the flange 42. On a casing 14.
  • the receiving tube 4 includes a low temperature portion 43, a high temperature portion 44, and an amplifying chamber 45.
  • the low temperature portion 43 is a portion of the receiving tube 4 that is in contact with the first casing 14, and is externally covered with a heat insulating layer 432 to reduce the loss of cooling capacity.
  • An insulating joint 46 is provided between the low temperature portion 43 and the high temperature portion 44, which is made of a heat insulating material and has a hollow tubular shape whose inner diameter is equal to or larger than the inner diameter of the low temperature portion 43 (in this embodiment, greater than) and less than or equal to high temperature.
  • the inner diameter of portion 44 (less than in this embodiment).
  • One end of the high temperature portion 44 is connected to the heat insulating joint 46, and the other end is connected to the amplifying chamber 45.
  • the end of the high temperature portion 44 adjacent to the amplifying chamber 45 is provided with a damping plate 442, and the damping plate 442 is provided with one or more Holes.
  • a housing 47 is provided outside the high temperature portion 44 and the amplifying chamber 45. The housing 47 surrounds the high temperature portion 44 and the amplifying chamber 45, and a cooling chamber 472 is formed around it, and circulating water can be used for cooling in the cooling chamber 472.
  • the air wave refrigerator has two receiving tubes 4 which are disposed at positions symmetrical on both sides of the first casing 14.
  • the two sets of sealing structures 3 are first assembled on the second casing 16, and then the main shaft 22 of the runner distributor 2 is sequentially inserted into the two sets of sealing structures 3, and then the second The end cover 18 is covered at the right end of the second casing 16 in FIG. 1, and the first casing 14 assembled with the receiving pipe 4 is assembled at the left end of the second casing 16, and finally the first end cover 12 is covered in FIG.
  • the left end of the first casing 14 is in the middle.
  • the axis of the nozzle 240 of the runner distributor 2 is coplanar with the axis of the low temperature portion 43 of the receiving tube 4.
  • the air wave refrigerator is connected to the corresponding external device when it is needed, for example, the end of the main shaft 22 of the reel distributor 2 is connected to the external motor, and the air inlet 162 of the second casing 16 is connected to the air compression.
  • the air outlet 142 of the first casing 14 is connected to a cold air outlet pipe or the like.
  • an air compressor is first used to input high-pressure gas, usually high-pressure air, through the air inlet 162 of the second casing 16.
  • high-pressure gas usually high-pressure air
  • the external motor is started to drive the wheel distributor 2 to rotate at a high speed, and the sealing structure 3 forms a gas seal as described above.
  • High pressure gas enters its inner chamber 226 from the high pressure chamber 7 through the inlet 228 on the main shaft 22 of the wheel distributor 2 and enters the nozzle 240 in its impeller 24.
  • the high pressure gas is accelerated in the nozzle 240, and the accelerated high pressure gas flow rate can reach the supersonic speed and become a supersonic flow.
  • the supersonic flow passes through the receiving tube interface 144 into the receiving tube 4, which is the inflating phase.
  • the supersonic gas stream entering the receiving tube 4 generates a shock wave in the receiving tube 4.
  • the impeller 24 is then rotated such that the nozzle 240 is removed from the receiving tube interface 144 of the first housing 16 and the inflator 242 is moved to the receiving tube interface 144 to close it, which is a closed phase.
  • a closed phase an expansion wave is generated in the receiving pipe 4, and the expansion wave generates a cooling effect, so that the temperature of the airflow injected into the receiving pipe 4 is lowered to become cold air.
  • the shock wave is transmitted to the high temperature portion 44 of the receiving tube 4, and is attenuated or eliminated by the damper plate 442 and the amplifying chamber 45 to attenuate or eliminate the reflected shock wave reflected back into the low temperature portion 43, thereby improving the cooling efficiency.
  • the heat insulating joint 46 reduces heat transfer between the high temperature portion 44 and the low temperature portion 43, and most of the heat is cooled by the circulating water in the cooling chamber 472, thereby minimizing the loss of cooling in the low temperature portion 43.
  • the impeller 24 When the impeller 24 is further rotated such that its deflation portion 244 is rotated to the receiving tube interface 144, the cold air in the receiving tube 4 flows into the low temperature chamber 8 and is discharged from the air outlet 142 of the first casing 14 and is externally connected.
  • the cold air outlet tube is introduced into the space that needs to be cooled. This is the deflation phase.
  • the aeration stage, the closing stage and the deflation stage are one working cycle of the air wave refrigerator.
  • the impeller 24 of the wheel distributor 2 has three sets of nozzles 240, an inflator 242 and a deflation part 244, and thus The wheel distributor 2 is rotated one revolution and the gas wave refrigerator undergoes three working cycles.
  • the runner distributor 2 is continuously rotated, and the high-pressure gas is continuously charged into the high-pressure chamber 7, and the air-wave refrigerator continuously generates cold air, and the cold air is continuously discharged from the air outlet 142 of the first casing 14, thereby achieving the purpose of rapid cooling.
  • the impeller 24 of the runner distributor 2 may have from 1 to 6
  • the nozzle 240, the inflator 242, and the deflation portion 244 are grouped, and are axially symmetric.
  • the impeller 24 can also be split into two parts with the main shaft 22 to transmit torque through the keys.
  • the ratio of the angle ⁇ of the inflated portion 242 extending on the outer circumference of the impeller 24 to the angle ⁇ at which the deflation portion 244 extends on the outer circumference of the impeller 24 is in the range of 2:11 to 2:1.
  • the two waist angles ⁇ of the cross section of the nozzle 240 are in the range of 2 to 20 degrees.
  • the ratio is in the range of 1:15 to 1:3, and the arc length of the outer end of the nozzle 240 on the outer circumference of the impeller 24, that is, the arc IJ and the arc length of the plenum 242 extending on the outer circumference of the impeller 24 (in Fig. 6)
  • the ratio indicated as arc ⁇ is in the range of 1:11 to 1:2. It is also possible to adopt a structure in which the opening end of the inner cavity 226 of the wheel distributor 2 can be closed without the plug 26.
  • the first casing 14 and the second casing 16 of the body 1 can be made in one piece.
  • the sealing structure 3 can also take other forms, such as a conventional labyrinth seal.
  • the structure of the receiving tube 4 may take other forms, for example, the cooling chamber 42, the damper plate 442, the heat insulating layer 432, and the heat insulating joint 46 may be omitted, that is, the low temperature portion 43 and the high temperature portion 44 are directly connected.
  • the structure of the rotor distributor 2 is improved, thereby improving the structure of the entire air-wave refrigerator, making it compact, and having a good transmission effect.
  • the structural parameters of the rotor distributor 2 are also optimized, thereby significantly improving the cooling efficiency of the air-wave refrigerator.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Description

气波制冷机及其转轮分配器 本申请要求于 2009 年 5 月 22 日提交中国专利局、 申请号为 200910107476.4、 发明名称为 "用于气波制冷机的转轮分配器以及该气波 制冷机 "的中国专利申请，上述专利的全部内容通过引用结合在本申请中。
技术领域
本发明涉及一种制冷机械， 尤其涉及一种气波制冷机。 背景技术
现有的低温制冷技术， 多采用多级压缩制冷剂的方式达到低温的目 的。第一级压缩一种制冷剂，在吸收应用第一级压缩所得的冷量的基础上 第二级压缩第二种制冷剂，通过制冷剂的汽化吸热达到降温的目的，通常 第二级压缩所使用的制冷剂液化点温度要比第一级制冷剂液化点温度低。 采用这种制冷方式有许多缺点： 首先， 由于采用多级压缩， 制冷效率低； 其次， 由于须采用制冷剂， 不利于环境保护； 再次， 由于存在制冷剂泄漏 的风险， 采用这种制冷技术存在安全隐患。
旋转式热分离机是一种根据激波和膨胀波原理，利用气体压力进行制 冷的设备， 因此亦称气波制冷机， 具有结构筒单、 节能、 环保、 造价低、 适应性强和操作维护方便等特点， 自 20世纪 70年代问世以来，得到了人 们的重视， 并在石油化工领域有了实际应用。
但是现有的气波制冷机 ,尤其是其转轮分配器的设计存在一些技术难 点：
现有的转轮分配器通常包括主轴和叶轮，叶轮设置在主轴中部，主轴 内部设有一端开口，一端封闭的内腔。通常是在主轴的封闭端连接电机等 传动机构， 而开口端作为进气口，输入高压气体， 因而在主轴另一端需另 设高压腔。 这就使整个气波制冷机的结构臃肿， 不够紧凑。但是由于受力 问题， 主轴的开口端也不可能作为传动端。
另外，现有的转轮分配器的喷嘴形状等参数设计不够合理，导致气波 制冷机制冷效率不高。 发明内容
本发明实施例所要解决的技术问题在于，提供一种气波制冷机，使其 转轮分配器的结构改善，从而使整个气波制冷机的结构改善，使其结构紧 凑， 并且具有良好的传动性能， 并且使其转轮分配器的结构参数优化， 从 而提高气波制冷机的制冷效率。
本发明实施例所要解决的另一个技术问题在于， 提供一种转轮分配 器， 使其结构改善， 并且具有良好的传动性能， 并且使其结构参数优化， 从而提高气波制冷机的制冷效率。
为了解决上述技术问题，本发明实施例提供了一种气波制冷机，其包 括机体、 轴承、 转轮分配器、 密封结构以及接受管， 所述机体上设有进气 孔以及出气孔， 所述密封结构设置在所述机体上的进气孔与出气孔之间 , 所述转轮分配器包括主轴和叶轮，所述主轴内设有轴向延伸的内腔，所述 内腔两端均封闭，所述主轴上还设有连通所述内腔和所述主轴外部的进气 口， 所述叶轮设置在所述主轴外部， 其包括喷嘴、 充气部以及放气部， 所 述充气部与放气部交替排列在叶轮周围，所述喷嘴是由所述充气部围成的 孔， 所述喷嘴与所述内腔连通。
为了解决上述技术问题，本发明实施例还提供了一种用于气波制冷机 的转轮分配器， 其包括主轴和叶轮， 所述主轴内设有轴向延伸的内腔， 所 述内腔两端均封闭，所述主轴上还设有连通所述内腔和所述主轴外部的进 气口， 所述叶轮设置在所述主轴外部， 其包括喷嘴、 充气部以及放气部， 所述充气部与放气部交替排列在叶轮周围，所述喷嘴是由所述充气部围成 的孔， 所述喷嘴与所述内腔连通。
实施本发明实施例，具有如下有益效果： 采用本发明实施例的转轮分 配器以及应用该转轮分配器的气波制冷机，改善了转轮分配器的结构，从 而改善了整个气波制冷机的结构，使其结构紧凑，并且具有良好的传动效 果。对转轮分配器的结构参数也进行了优化，从而显著提高了气波制冷机 的制冷效率。 附图说明
图 1是本发明气波制冷机的截面结构示意图；
图 2是本发明气波制冷机的转轮分配器的立体结构示意图； 图 3是本发明气波制冷机的转轮分配器的主视图；
图 4是图 3中的转轮分配器沿 A-A线的截面结构示意图；
图 5是图 3中的转轮分配器 X向的结构示意图；
图 6是图 3中的转轮分配器沿 C-C线的截面结构示意图
图 7是本发明气波制冷机的密封结构的截面结构示意图；
图 8是本发明气波制冷机的密封结构中动环的侧视图；
图 9是气波制冷机的接受管以及部分第一机壳的截面结构示意图。 具体实施方式
为使本发明的目的、技术方案和优点更加清楚，下面将结合附图对本 发明作进一步地详细描述。
请参照图 1所示， 本发明实施例的气波制冷机包括机体 1 , 转轮分配 器 2, 密封结构 3, 接受管 4, 轴承 50、 52以及密封圏 60、 62、 64。
机体 1 包括第一端盖 12、 第一机壳 14、 第二机壳 16以及第二端盖 18。 第一机壳 14、 第二机壳 16均大致为两端开口的中空圓柱体， 其中第 一机壳 14上设有贯通的出气孔 142以及均勾分布在第一机壳 14周围的多 个贯通的接受管接口 144,在本实施例中接受管接口 144为阶梯状的通孔。 第二机壳 16上设有贯通的进气孔 162。 第一端盖 12覆盖在第一机壳 14 的一端， 第二机壳 16固定连接在第一机壳 14的另一端， 第二端盖 18覆 盖在第二机壳 16不与第一机壳 14连接的一端。 在第一端盖 12与第一机 壳 14之间、第一机壳 14与第二机壳 16之间以及第二机壳 16与第二端盖 18之间分别采用螺丝釘 192、 194、 196进行固定连接， 并且在第一端盖 12与第一机壳 14之间、第一机壳 14与第二机壳 16之间以及第二机壳 16 与第二端盖 18之间的连接处分别设置密封圏 60、 62、 64进行密封。 请一并参照图 2到图 6所示，转轮分配器 2设置在机体 1内，其包括 主轴 22、 叶轮 24以及堵头 26,
主轴 22为圓柱形轴体， 如图 3中所示其外部自左到右依次设置第一 挡圏槽 220,第二挡圏槽 222以及键槽 224,键槽 224设置在主轴 22的一 端。 在主轴 22未设键槽 224的一端开设沿主轴 22轴向延伸的内腔 226, 内腔 226并不贯通到主轴 22的另一端，而是延伸到主轴 22的中部即截止， 在主轴 22中部垂直轴向开设有贯通的进气口 228, 并且进气口 228与内 腔 226连通。
堵头 26设置在主轴 22内的内腔 226的开口端内，通过螺纹结构与该 开口端固定， 将内腔 226的开口端封闭。
叶轮 24设置在主轴 22上第一挡圏槽 220和进气口 228之间，大致呈 盘状， 包括多个喷嘴 240、 充气部 242以及放气部 244, 其中充气部 242 与放气部 244交替排列在叶轮 24周围， 充气部 242的半径与机体 1第一 机壳 14的内部半径相同， 而放气部 244的半径小于机体 1第一机壳 14 的内部半径， 亦即放气部 244的半径小于充气部 242的半径。 充气部 242 在叶轮 24的外周上延伸的角度为 ,而放气部 244在叶轮 24的外周上延 伸的角度为 β。 喷嘴 240是由充气部 242围成的孔， 其截面大致呈梯形， 该梯形的两腰的夹角为 γ , 喷嘴 240与主轴 22的内腔 226相通。 在本实 施例中， 叶轮 24上设有三组喷嘴 240、 充气部 242以及放气部 244, α、 β以及 γ的角度如图所示。
转轮分配器 2设置在机体 1 内， 其设置堵头 26的一端通过轴承 50 固定在机体 1的第一端盖 12上，而另一端穿过第二端盖 18并且通过轴承 52固定在第二端盖 18上，叶轮 24的喷嘴 240的轴线与第一机壳 14的接 受管接口 144的轴线位于同一平面上。 转轮分配器 2穿过第二端盖 18的 一端与外部电机相连。
请参照图 1、 图 7和图 8所示， 本实施例包括两组密封结构 3 , 设置 在转轮分配器 2的主轴 22与第二机壳 16之间， 位于主轴 22上的进气口 228两侧。 这两组密封结构 3结构相同， 对称设置， 因而仅对其中一组进 行详细描述。
密封结构 3包括轴套 30, 动环 31 , 静环 32, 推环 33 , 弹簧 34, 固 定体 35 , 集装块 36, 卡环 37, 定位环 38, 销釘 390, 销 392、 393以及 0型环 394、 396、 397、 398、 399。
轴套 30套设在转轮分配器 2的主轴 22上， 其截面呈 T形， 包括套 筒部 302以及自套筒部 302—端垂直其轴线向外侧延伸的壁部 304,壁部 304在其外端轴向延伸一定长度，从而与套筒部 302形成一个用以容纳动 环 31的容置空间（图未标）。轴套 30通过销釘 390以及卡环 37固定在转 轮分配器 2的主轴 22上， 因此可随主轴 22转动， 并且通过 0型环 394 在轴套 30与主轴 22之间形成密封。
动环 31呈环状， 套设在轴套 30的套筒部 302外侧， 并与壁部 304 相邻，其通过销 392与轴套 30的壁部 304卡固， 因此可随同轴套 30与转 轮分配器 2的主轴 22—同转动， 因而称之为 "动环"。 通过 0型环 396 和 398在动环 31与轴套 30之间形成密封。动环 31的一侧与静环 32接触， 该接触面的表面精度较高，并且在该接触面上设有均勾分布螺旋状的螺旋 槽 312 (见图 6 )。
固定体 35大致呈环状， 其外部通过螺丝釘 197固定在机体 1的第二 机壳 16上， 其内部套设在轴套 30的套筒部 302外侧， 并且沿套筒部 302 外侧延伸有内延伸壁 352, 在固定体 35中部沿轴向延伸有外延伸壁 354, 在内延伸壁 352和外延伸壁 354之间形成容置空间， 用以容纳静环 32和 推环 33 , 并且在位于该容置空间内侧的壁面开设与转轮分配器 2的主轴 22的轴线平行的孔， 弹簧 34容置在其中， 并且一端抵顶该孔的底壁。 通 过 0型环 399在固定体 35与第二机壳 16之间形成密封。
推环 33套设在固定体 35的内延伸壁 352外侧， 位于内延伸壁 352 和外延伸壁 354之间形成的容置空间内， 其一侧抵顶弹簧 34的一端， 另 一侧靠接静环 32。通过 0型环 397在推环 33与固定体 35之间形成密封。
静环 32呈环状，在本实施例中，静环 32的内圏和外圏均设置成台阶 状， 其内圏的下部台阶套设在轴套 30的套筒部 302外侧， 并且与套筒部 302之间具有一定间隙， 而上部台阶套设在固定体 35的内延伸壁 352外 侧。静环 32夹设在动环 31与推环 33之间， 其与动环 31靠接， 并且靠接 的侧面具有较高的精度，其与推环 33部分靠接，并且与推环 33形成狭槽 323„ 由于静环 32与套筒部 302之间具有一定间隙， 其不会与套筒部 302 以及转轮分配器 2的主轴 22—同转动， 因此称之为 "静环"，但是它可以 与推环 33—起 4氐抗弹簧 34预设的推力在定位环 38和固定体 35的内延伸 壁 352之间做微小位移。
销 393穿过静环 32卡固于固定体 35 , 以使静环 32不会相对固定体 35产生相对转动。
定位环 38卡固在固定体 35的外延伸壁 354内，其内圏半径小于静环 32的外圏台阶半径， 因而可对静环 32进行定位。
集装块 36是四片金属片，分别通过螺丝釘 362固定在固定体 35不设 容置空间的一侧， 并且卡扣于轴套 30, 其作用是使密封结构 3组装为一 体， 以便于将其组装到气波制冷机内，并且在密封结构 3装入气波制冷机 之后， 可限制转轮分配器 2的转动， 以便于气波制冷机的运输以及组装。 在气波制冷机安装到所需要的场所， 准备使用之前， 须将集装块 36以及 螺丝釘 362拆除， 以使气波制冷机能够正常工作。
上述两组密封结构 3与第二机壳 16和转轮分配器 2的主轴 22共同围 成高压腔 7, 而如图 1中左侧的一组密封结构 3与第一机壳 14、第一端盖 12和转轮分配器 2共同围成低温室 8。其中高压腔 7与转轮分配器 2的进 气口 228连通。 在气波制冷机运转之前， 密封结构 3的动环 31和静环 32 互相接触； 而当气波制冷机开始运转时， 高压气体通过第二机壳 16的进 气孔 162进入高压腔 7,而转轮分配器 2在外部电机的带动下高速转动时， 密封结构 3的动环 31与轴套 30与转轮分配器 2的主轴 22—同转动， 而 高压气体进入静环 32与推环 33之间的狭槽 323 , 从而推动推环 33抵抗 弹簧 34的推力产生微小位移，同时静环 32也在高压气体的推动下随同推 环 33产生微小位移， 高压气体进入动环 31的螺旋槽 312并且在动环 31 和静环 32之间形成气膜， 从而达到密封气体的作用。
两组密封结构 3的结构以及密封原理均相同，图 1中左侧的一组密封 结构 3在低温室 8和高压腔 7之间形成气体密封，而右侧的一组密封结构 3在高压腔 7和密封结构 3右侧的腔体之间形成气体密封， 以防止高压气 体外泄。
请参照图 9所示，接受管 4是一端开口一端封闭的管状体，其开口端 插接在机体 1第一机壳 14的接受管接口 144内， 通过螺丝釘 41和法兰 42固定在第一机壳 14上。
接受管 4包括低温部 43、 高温部 44以及放大腔 45 , 低温部 43即接 受管 4与第一机壳 14相接的一段， 其外部包覆有保温层 432以减少冷量 损失。 低温部 43与高温部 44之间设有隔热接头 46 , 其由隔热材料制成， 为中空管状， 其内径大于等于低温部 43的内径 （在本实施例中为大于） 而小于等于高温部 44的内径（在本实施例中为小于）。 高温部 44一端与 隔热接头 46相接， 另一端与放大腔 45相接， 高温部 44内靠近与放大腔 45相接的一端设有阻尼板 442,该阻尼板 442上设有一个或多个孔。在高 温部 44和放大腔 45的外部设有壳体 47 , 壳体 47包围高温部 44和放大 腔 45 ,并且在其周围形成冷却腔 472,在冷却腔 472内可采用循环水进行 冷却。
在本实施例中， 该气波制冷机具有两个接受管 4, 其装设在第一机壳 14两侧对称的位置。
在装配该气波制冷机时， 需先将两组密封结构 3装配在第二机壳 16 上， 然后将转轮分配器 2的主轴 22顺次插入上述两组密封结构 3 , 再将 第二端盖 18盖在图 1中第二机壳 16的右端，并且将装配好接受管 4的第 一机壳 14装配在第二机壳 16的左端， 最后将第一端盖 12盖在图 1中第 一机壳 14的左端。 装配好后， 转轮分配器 2的喷嘴 240的轴线与接受管 4的低温部 43的轴线共面。
当然， 在需要使用时还需将气波制冷机连接相应的外部设备， 例如， 将转轮分配器 2的主轴 22末端连接到外部电机，将第二机壳 16的进气孔 162连接空气压缩机的输出端， 将第一机壳 14的出气孔 142连接冷气导 出管等。
请参照图 1所示，在本发明实施例气波制冷机运行时，首先采用空气 压缩机将高压气体， 通常是高压空气， 通过第二机壳 16的进气孔 162输 入高压腔 7。 同时或者稍后启动外部电机带动转轮分配器 2高速转动， 密 封结构 3如上所述形成气体密封。 高压气体从高压腔 7经转轮分配器 2 主轴 22上的进气口 228进入其内腔 226 ,并且进入其叶轮 24内的喷嘴 240。 高压气体在喷嘴 240中加速， 加速后的高压气体气流流速可达到超声速， 成为超声速气流。
当叶轮 24旋转到喷嘴 240对准第一机壳 16的接受管接口 144时，超 声速气流经过接受管接口 144进入接受管 4, 此为充气阶段。 进入接受管 4的超声速气流在接受管 4中产生激波。
然后叶轮 24旋转， 使得喷嘴 240从第一机壳 16的接受管接口 144 移开， 而充气部 242移到接受管接口 144,从而将其封闭，此为封闭阶段。 在封闭阶段， 在接受管 4内产生膨胀波， 膨胀波会产生制冷效果，从而使 喷入接受管 4的气流温度降低成为冷气。上述激波会传到接受管 4的高温 部 44内，并且被阻尼板 442和放大腔 45减弱或者消除， 以减弱或者消除 反射回低温部 43内的反射激波， 提高制冷效率。 但是因为在高温部内入 射超声速气流通过激波对其内气体进行压缩，进行能量交换， 高温部内的 气体升温。 隔热接头 46则可减少高温部 44和低温部 43之间的热传导， 并且大部分热量由冷却腔 472内的循环水冷却，因而最大限度的减少低温 部 43内的冷量损失。
当叶轮 24 进一步旋转， 使得其放气部 244旋转到正对接受管接口 144,接受管 4内的冷气会流入低温室 8内，并且从第一机壳 14的出气孔 142排出， 并且通过外接的冷气导出管导入需要制冷的空间。 此为放气阶 段。
上述充气阶段、 封闭阶段以及放气阶段为气波制冷机的一个工作循 环，在本实施例中转轮分配器 2的叶轮 24具有三组喷嘴 240、充气部 242 以及放气部 244, 因而转轮分配器 2旋转一周， 气波制冷机经历三个工作 循环。 转轮分配器 2不断旋转， 高压气体不断充入高压腔 7, 则气波制冷 机不断生成冷气， 并且冷气不断从第一机壳 14的出气孔 142排出， 从而 达到快速制冷的目的。
在本发明的其它实施例中， 转轮分配器 2的叶轮 24上可具有 1到 6 组喷嘴 240、 充气部 242以及放气部 244, 并且其为轴对称结构。 叶轮 24 也可以和主轴 22分为两个部件， 通过键传递扭矩。 充气部 242在叶轮 24 的外周上延伸的角度 α与放气部 244在叶轮 24的外周上延伸的角度 β的 比值在 2:11到 2:1的范围内。 喷嘴 240截面的两腰夹角 γ在 2度到 20度 的范围内。 喷嘴 240外端在叶轮 24的外周上延伸的弧长（在图 6中标示 为弧 IJ )与放气部 244在叶轮 24的外周上延伸的弧长（在图 6中标示为 弧 ΚΡ ) 的比值在 1:15到 1:3的范围内， 而喷嘴 240外端在叶轮 24的外 周上延伸的弧长即弧 IJ与充气部 242在叶轮 24的外周上延伸的弧长（在 图 6中标示为弧 ΗΚ )的比值在 1:11到 1:2的范围内。也可以不设堵头 26, 而采取其它能够将转轮分配器 2的内腔 226开口端封闭的结构。
机体 1的第一机壳 14和第二机壳 16可以做成一体。密封结构 3也可 以采取其它的形式，例如传统的迷宫式密封。接受管 4的结构也可以采取 其它的形式， 例如可省略冷却腔 42、 阻尼板 442、保温层 432以及隔热接 头 46, 即将低温部 43与高温部 44直接连接在一起。
采用本发明实施例的气波制冷机，改善了转轮分配器 2的结构，从而 改善了整个气波制冷机的结构，使其结构紧凑，并且具有良好的传动效果。 对转轮分配器 2的结构参数也进行了优化，从而显著提高了气波制冷机的 制冷效率。
以上所揭露的仅为本发明一种较佳实施例而已，当然不能以此来限定 本发明之权利范围， 因此依本发明权利要求所作的等同变化，仍属本发明 所涵盖的范围。

Claims

权 利 要 求 书
1、 一种气波制冷机， 其包括机体、 轴承、 转轮分配器、 密封结构以 及接受管，所述机体上设有进气孔以及出气孔，所述密封结构设置在所述 机体上的进气孔与出气孔之间，所述转轮分配器包括主轴和叶轮，其特征 在于： 所述主轴内设有轴向延伸的内腔， 所述内腔两端均封闭， 所述主轴 上还设有连通所述内腔和所述主轴外部的进气口，所述叶轮设置在所述主 轴外部， 其包括喷嘴、 充气部以及放气部， 所述充气部与放气部交替排列 在叶轮周围，所述喷嘴是由所述充气部围成的孔，所述喷嘴与所述内腔连 通。
2、 如权利要求 1所述的气波制冷机， 其特征在于： 所述转轮分配器 的叶轮上具有 1到 6组喷嘴、充气部以及放气部，并且它们为轴对称结构。
3、 如权利要求 1所述的气波制冷机， 其特征在于： 所述喷嘴的截面 呈梯形， 所述梯形的两腰的夹角在 2度到 20度的范围内。
4、 如权利要求 1所述的气波制冷机， 其特征在于： 所述充气部在所 述叶轮的外周上延伸的角度与所述放气部在所述叶轮的外周上延伸的角 度的比值在 2:11到 2:1的范围内。
5、 如权利要求 1所述的气波制冷机， 其特征在于： 所述喷嘴外端在 所述叶轮的外周上延伸的弧长与所述放气部在所述叶轮的外周上延伸的 弧长的比值在 1:15到 1:3的范围内， 而所述喷嘴外端在所述叶轮的外周 上延伸的弧长与所述充气部在所述叶轮的外周上延伸的弧长的比值在 1:11到 1:2的范围内。
6、 一种用于气波制冷机的转轮分配器， 其包括主轴和叶轮， 其特征 在于： 所述主轴内设有轴向延伸的内腔， 所述内腔两端均封闭， 所述主轴 上还设有连通所述内腔和所述主轴外部的进气口，所述叶轮设置在所述主 轴外部， 其包括喷嘴、 充气部以及放气部， 所述充气部与放气部交替排列 在叶轮周围，所述喷嘴是由所述充气部围成的孔，所述喷嘴与所述内腔连 通。
7、如权利要求 6所述的用于气波制冷机的转轮分配器，其特征在于： 所述转轮分配器的叶轮上具有 1到 6组喷嘴、充气部以及放气部，并且它 们为轴对称结构。
8、如权利要求 6所述的用于气波制冷机的转轮分配器，其特征在于： 所述喷嘴的截面呈梯形，所述梯形的两腰的夹角在 2度到 20度的范围内。
9、如权利要求 6所述的用于气波制冷机的转轮分配器，其特征在于： 所述充气部在所述叶轮的外周上延伸的角度与所述放气部在所述叶轮的 外周上延伸的角度的比值在 2:11到 2:1的范围内。
10、如权利要求 6所述的用于气波制冷机的转轮分配器，其特征在于： 的外周上延伸的弧长的比值在 1:15到 1:3的范围内， 而所述喷嘴外端在 所述叶轮的外周上延伸的弧长与所述充气部在所述叶轮的外周上延伸的 弧长的比值在 1:11到 1:2的范围内。
PCT/CN2010/072416 2009-05-22 2010-05-04 气波制冷机及其转轮分配器 WO2010133125A1 (zh)

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CN115978856A (zh) * 2023-01-17 2023-04-18 大连理工大学 一种气波制冷过程鲸鱼优化扰动补偿Smith预估控制方法

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CN107843021B (zh) * 2017-11-13 2019-07-30 大连理工大学 一种内置驱动液压平衡的双层喷嘴双排管气波制冷机
CN114111081A (zh) * 2021-12-26 2022-03-01 大连理工大学 一种曲线通道热阻隔型气波制冷机
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