CN101270931A - Damping opposite-thrust type gas wave refrigerating machine - Google Patents
Damping opposite-thrust type gas wave refrigerating machine Download PDFInfo
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- CN101270931A CN101270931A CNA2008100112552A CN200810011255A CN101270931A CN 101270931 A CN101270931 A CN 101270931A CN A2008100112552 A CNA2008100112552 A CN A2008100112552A CN 200810011255 A CN200810011255 A CN 200810011255A CN 101270931 A CN101270931 A CN 101270931A
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- 238000013016 damping Methods 0.000 title claims abstract description 61
- 238000007789 sealing Methods 0.000 claims description 12
- 210000004907 gland Anatomy 0.000 claims description 10
- 235000008733 Citrus aurantifolia Nutrition 0.000 claims description 6
- 235000011941 Tilia x europaea Nutrition 0.000 claims description 6
- 239000004571 lime Substances 0.000 claims description 6
- 238000005096 rolling process Methods 0.000 claims description 3
- 239000007789 gas Substances 0.000 abstract description 22
- 238000005057 refrigeration Methods 0.000 abstract description 9
- 230000010355 oscillation Effects 0.000 abstract description 5
- 230000006835 compression Effects 0.000 abstract description 2
- 238000007906 compression Methods 0.000 abstract description 2
- 230000005855 radiation Effects 0.000 abstract description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 abstract 2
- 239000004215 Carbon black (E152) Substances 0.000 abstract 1
- 238000004378 air conditioning Methods 0.000 abstract 1
- 230000005494 condensation Effects 0.000 abstract 1
- 238000009833 condensation Methods 0.000 abstract 1
- 229930195733 hydrocarbon Natural products 0.000 abstract 1
- 150000002430 hydrocarbons Chemical class 0.000 abstract 1
- 239000007788 liquid Substances 0.000 abstract 1
- 239000003345 natural gas Substances 0.000 abstract 1
- 239000003208 petroleum Substances 0.000 abstract 1
- 238000011084 recovery Methods 0.000 abstract 1
- 238000000926 separation method Methods 0.000 abstract 1
- 230000035939 shock Effects 0.000 abstract 1
- 230000008859 change Effects 0.000 description 3
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000005484 gravity Effects 0.000 description 2
- 230000014759 maintenance of location Effects 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- CWYNVVGOOAEACU-UHFFFAOYSA-N Fe2+ Chemical compound [Fe+2] CWYNVVGOOAEACU-UHFFFAOYSA-N 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 239000000112 cooling gas Substances 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000010358 mechanical oscillation Effects 0.000 description 1
- 239000000178 monomer Substances 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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Abstract
The invention provides a hedge damping gas wave refrigerator which belongs to the compressed air expansion refrigeration technical field. The device can realize refrigeration through the moving shock wave and the expansion wave produced in the oscillation tube by the air pressure. The hedge damping gas wave refrigerator is characterized in that the radiation tubes or the oscillation tubes arranged in a circular shape are arrayed in pairs with the same degree of angle between each other, and a damping dissipative structure is connected with the ends of each pair to put through the flow of the two pipes, thus reducing the rigidity of the air compression of the oscillation tubes; thereby the device can constantly run with high speed in working conditions that the short pipe is too long and the rotation rate is low. The device of the invention has the advantages that the structure is simple, the assembly and disassembly are convenient, the condensation and stagnancy of the liquid is avoided, the adaptability to variable working conditions is high, the isentropic efficiency of refrigeration is high, etc. The device of the invention can produce low temperature and can be widely used in the technical fields such as the liquefied separation of mixed gases, the recovery of light hydrocarbon in petroleum gases, the liquefaction of natural gas, and the supply of low-temperature air-conditioning source, etc.
Description
Technical field
The damping of the present invention formula air wave refrigerating device that liquidates belongs to the swell refrigeration technical field of pressed gas.
Background technology
Existing heat separator and air wave refrigerating device, all be to rely on pressed gas successively the retention gas in the oscillating tube of each root endcapped to be done the unsteadiness expansion work, in retention gas, produce compressional wave and dilatational wave, pressure can be converted into heat energy and shed by tube wall, incident pressure gas has consumed the energy of self because of the acting of expanding, and temperature reduces and realizes freezing.This class refrigeration machine can be worked under lower rotating speed efficiently, thereby has avoided as cryogenic turboexpander, must move under high rotating speed and a series of inconvenience of bringing.
But present heat separator and air wave refrigerating device are in actual applications, obtain high efficiency needs in order to satisfy under the slow-speed of revolution, and the length of its oscillating tube is long, easy vibration, the disconnected event of running affairs of normal appearance.And because the temperature of long oscillating tube end tube wall is lower, can not powerful ground dissipation energy, tubing function rate is lower.Also have pressure wave to get back to arrival end from the end reflection of sealing, heat gas fresh or that freezed, refrigerating efficiency is reduced, when the gas frequency of oscillation is inconsistent in jet frequency and the pipe, more very, make the scope that efficient fluctuates up and down with rotation speed change reach 10% or more.
Summary of the invention
Purpose of the present invention just provides a kind of short vibration pipe range and still can keep the monomer unsteadiness swell refrigeration machine of height and stable refrigerating efficiency when the slow-speed of revolution move--the damping formula air wave refrigerating device that liquidates.
Technical solution of the present invention is: the oscillating tube 8 of radiation or circumferential arrangement is matched in twos by the stagger principle of equal angular of circumference, connect a damping dissipative structure and realize that the runner of two pipes connects at per two end.For being implemented under the different operating modes, the jet frequency can both be synchronous with the ripple vibration in the pipe, organize right two-tube position in twos in a circumferential direction or tight adjacent or fork certain included angle, promptly connect interconnection to jump a mode of arranging, to the angle of pipe from being close to until expanding to 180 ° of relative one-tenth.Be made up of damping cavity 18, U type return bend 19, dissipation section connected chamber 20 and sealing gland draining pipe 21 managing terminal damping dissipative structure, the end of every pipe can connect a damping cavity 18 to several polyphones, and the two ends of dissipative structure are connected to the end of two pipes respectively.And each damping cavity 18 all is to be combined by one section cylinder chamber and one section cone cavity, and the compressional wave in the oscillating tube 8 is earlier through the post chamber, and major part enters the awl chamber again.Because the very difficult inlet that returns the post chamber again of compressional wave from the reflection of awl cavity wall dissipate and can only repeatedly reflect in damping cavity, so compressional wave just seldom can return the inlet heating and cooling gas of oscillating tube 8.And for escape from the compressional wave that comes from awl section, then adopt several damping cavity polyphones and the damping of carrying out tandem type are dissipated.For fully dissipation energy and buffering are to the time difference of pipe jet, the length of damping dissipative structure section is got more than 0.3 meter.Because the arragement direction of 8 pairs of pipes of every pair of oscillating tube all is an in-line arrangement in the same way, therefore with to managing the two terminal damping dissipative structures that link to each other, one section U type return bend 19 is arranged, so that two access ports of dissipative structure are equidirectional between damping cavity.
It is right that oscillating tube is organized in twos, and two is terminal by a kind of damping dissipation runner interconnected, and the pressure wave of two oscillating tubes can both enter this public dissipative structure, can produce following effect since like this:
1. because the connection of damping structure, greatly reduce the gas compression rigidity of oscillating tube, the gas frequency of oscillation significantly reduces, and the jet frequency of fresh pressure gas just can reduce thereupon, the rotating speed of gas distributor also just and then reduces, and promptly can move under lower rotating speed; Perhaps under identical rotating speed, the length of oscillating tube can shorten, and mechanical oscillation alleviate, and is not fragile.
Since the damping dissipative structure of oscillating tube far-end be two shared to managing, its energy charge is twice or more (when pipe range shortens) than the independent dissipative structure of single tube, the pipe range of single tube independence dissipative structure like this can not be lacked but the temperature of end and dissipative structure is low, the drawback of dissipation energy difference just can obtain basic improvement, the service efficiency of non-ferrous metal improves, and consumption can reduce.
3. the damping structure of two pipe perforations can be provided with the damping cavity of a plurality of polyphones, wave system in two pipes can interact, make compressional wave in a plurality of damping cavity, come back reflective and repeatedly dissipation, therefore the decay of energy waves dissipates more thorough, substantially can not turn back to the top opening of oscillating tube again, so the refrigerating efficiency of air wave refrigerating device will increase, and efficient in the past can be that the problem that the rotation speed change generation is fluctuateed also can be greatly improved with the jet frequency.
In order further to improve refrigerating efficiency, the liquidate technical solution of formula air wave refrigerating device of damping of the present invention also comprises following some architectural feature:
1. increased aperture discharge opeing structure.In the perforate of the appropriate location of damping dissipative structure, connect one section short tube and exhaust chamber, collect in the exhaust chamber the interior lime set that may accumulate of the section of dissipation and discharge regularly by means of the gravity effect.Guarantee oscillating tube 8 like this and the no lime set of section that dissipates, can make pressure wave smooth and easy motion, refrigeration machine is lowered efficiency with the continuity of running time in inside.Because two oscillating tube 8 shared discharge opeing structures, with single tube independently air wave refrigerating device compare, the complexity of machine reduces.
Rotating jet distributor 7 inner flow passages change into by original prolate type square, the pressure loss can reducing from the body air inlet pipe to the gas distributor process; Rotating jet distributor 7 inner flow passages the inclination angle axially arranged, loss is fallen further to reduce decompression.
Owing to adopted damping dissipative structure to pipe, the motion of wave system in the air wave refrigerating device is changed, and it is weak dilatational wave that pressure wave returns the oscillating tube arrival end, and refrigerating efficiency is risen, and pipe range also weakens the influence of efficient thereupon, guarantees machine stable operation under high efficiency.The damping section that dissipates is that two oscillating tubes 8 are shared, and the equivalent pipe range that can have under same single pipe range increases, oscillating tube 8 length thereby can reduce, thus can reduce the height and the volume of air wave refrigerating device.Because the application of damping cavity, pressure wave can be locked in wherein or the dissipation section between each damping cavity in dissipate repeatedly, tube wall temperature raises, material heat sinking function utilization rate rises.
The damping of the present invention beneficial effect that the formula air wave refrigerating device is reached that liquidates: can be in the slow-speed of revolution, short tube is long to obtain high and stable refrigerating efficiency down, and simple in structure, and volume is less, is difficult for the disconnected pipe of vibration.
The present invention will be further described with specific implementation method in conjunction with the accompanying drawings more below:
Description of drawings
Fig. 1 is the liquidate general structure sketch of formula air wave refrigerating device of damping of the present invention.
Fig. 2 is the liquidate profile schematic diagram of oscillating tube damping dissipative structure of formula air wave refrigerating device of damping of the present invention.
Among the figure, 1, air inlet pipe, 2, body, 3, following rolling bearing, 4, step, 5, rotating shaft, 6, escape pipe, 7, rotating jet distributor, 8, oscillating tube, 9, top chock 10, go up rolling bearing, 11, bearing inner race clamp nut, 12, airtight and watertight padding, 13, shaft coupling, 14, steady speed motor, 15, sealing gland, 16, upper end cover, 17, jet distributor clamp nut, 18, damping cavity, 19, U type return bend, 20, the section connected chamber that dissipates, 21, the sealing gland draining pipe, 22, lime set always collects endless tube.
The specific embodiment
The damping formula air wave refrigerating device that liquidates mainly is made of body 2, metal (upper seat 9,4, scroll-up/down bearing 10,3, rotating shaft 5, upper end cover 16, airtight and watertight padding 12, sealing gland 15, shaft coupling 13, steady speed motor 14, air inlet pipe 1, escape pipe 6, rotating jet distributor 7, oscillating tube 8, damping cavity 18, the U type return bend 19 along body 2 circumferential arrangement, dissipate section connected chamber 20 and sealing gland draining pipe 21.The end of oscillating tube 8 links to each other with the damping dissipative structure in twos, the damping dissipative structure is made up of damping cavity 18, U type return bend 19, dissipation section connected chamber 20 and sealing gland draining pipe 21, the simplest a kind of embodiment is that per two adjacent oscillating tube 8 ends interpenetrate by the damping dissipative structure, form to several damping cavity 18 polyphones by one, each damping cavity 18 is combined by one section cylinder chamber and one section cone cavity, is generally the combination of cylindrical cavity and conical cavity.Compressional wave in the oscillating tube 8 enters the awl chamber more earlier through the post chamber, and repeatedly reflection dissipates.There is a U type return bend 19 at the middle part of damping dissipative structure, with will the section of dissipation two connected entrances be bent to equidirectional, with being connected of convenient and 8 pairs of pipe ends of oscillating tube.Connected chamber 20 direction down connects a sealing gland draining pipe 21, adorns the restricting orifice of 2～5 polyphones in the conduit, and piecemeal by throttle orifice and cavity discharge opeing, gas then is difficult for unimpeded lime set under gravity and pressure fluctuation effect.Draining pipe 21 is always collected endless tube 22 with the lime set of machine and is linked to each other.Air inlet pipe 1 is inserted rotating shaft 5 endoporus, can reduce the leakage between air inlet and the exhaust.One end of rotating shaft 5 is hollow shaft part, and the circumferential wall perforate near sealing place makes the smooth and easy inflow rotating jet of gas distributor 7.Be processed with axial inclination in rotating jet distributor 7 porch, ensure and the smooth and easy transition of air inlet pipe 1 homalographic.Symmetric arrangement has 2～4 nozzle flow channels on the excircle of rotating jet distributor 7, its nozzle opening is on the periphery of the cylindrical segmental arc of rotating jet distributor 7, from perspective plane perpendicular to axial direction, the runner axis with radially have a certain degree, the torque of drive motors 14 is delivered to rotating shaft 5 by shaft coupling 13, and rotating jet distributor 7 changes with the speed rotation with per minute 1000～5000 with rotating shaft 5; The quantity of oscillating tube 8 is 20～100, and top radially is installed in the periphery of body 2, and the endoporus of oscillating tube 8 and body boring are aligned to smooth continuous runner.Each root oscillating tube 8 length is equal substantially, and length is 1.2～4.5 meters.
The operation principle of this specific embodiment and process are:
Pressed gas is imported in the hollow rotating shaft 5 by the dark air inlet pipe 1 of inserting axle, enter the rotating jet distributor 7 from the circumferential openings of rotating shaft 5, jet hole ejection high velocity air from its periphery, incide in turn successively in each oscillating tube 8 of circumferential arrangement with rotating, pool gas body in each oscillating tube 8 is done the unsteadiness expansion work, compressional wave that produces in the pool gas and dilatational wave successively enter into the damping dissipative structure by oscillating tube 8, the pressure wave major part enters the U type return bend 19 of the section that dissipates by damping cavity 18, returning weak dilatational wave and incident dilatational wave meets, weaken mutually and make that the dilatational wave energy that turns back to inlet is littler, the pressure wave that enters the section that dissipates interacts with the pressure wave that adjacent oscillating tube 8 is injected, and strengthens dissipation and is converted into heat and distributes to the external world by tube wall.During the reverse damping cavity 18 that enters another oscillating tube 8 of the remaining pressure wave of decaying, major part will reflect back in the section that dissipates and dissipate once more, and the energy of incidence wave almost dissipates totally like this, and seldom can turn back to the inlet of oscillating tube 8 again.Rotating jet distributor 7 nozzles leave 8 mouthfuls of each oscillating tubes successively, and the gas after the acting refrigeration that expands returns out from oscillating tube 8 porch successively, enters into exhaust cavity and compiles, and discharges from blast pipe 6 then, has finished swell refrigeration.
Claims (6)
1. the damping formula air wave refrigerating device that liquidates, comprise body (2), bearing block (9) (4), rolling bearing (3) (10), end cap (16), rotating shaft (5), rotating jet distributor (7), oscillating tube (8), damping cavity (18), U type return bend (19), section connected chamber (20) and sealing gland draining pipe (21) dissipate, it is characterized in that, the end of each root oscillating tube (8) all be organize in twos right, each is to all connecting by a damping dissipative structure, organize right two-tube position in twos in a circumferential direction or tight adjacent or fork certain included angle, promptly connect interconnection in a mode of jump arranging, to the angle of pipe from being close to until expanding to 180 ° of relative one-tenth.
2. the damping according to claim 1 formula air wave refrigerating device that liquidates, it is characterized in that, organize right oscillating tube (8) and form by damping cavity (18), U type return bend (19), dissipation section connected chamber (20) and sealing gland draining pipe (21) managing terminal damping dissipative structure.
3. the damping according to claim 1 and 2 formula air wave refrigerating device that liquidates is characterized in that, the polyphone number of the section damping cavity (18) that dissipates is 2～6, and each all is to be combined by one section cylinder chamber and one section cone cavity.
4. the damping according to claim 1 and 2 formula air wave refrigerating device that liquidates, it is characterized in that the through-flow basal area of damping cavity (18) shell of column is greater than vibrating to pipe, if cylindrical cavity, then diameter is 2～10 times of oscillating tube (8) diameter, and the cone angle of damping cavity (18) awl section is 20～70 °.
5. the damping according to claim 1 and 2 formula air wave refrigerating device that liquidates is characterized in that a U type return bend (19) is arranged between the damping cavity (18), and its flow area is 1～10 times of oscillating tube, and length is between 0.1～3m.
6. the damping according to claim 1 and 2 formula air wave refrigerating device that liquidates, it is characterized in that, U type return bend (19) links to each other with a discharge opeing structure, the section connected chamber (20) that dissipates connects a sealing gland draining pipe (21) down, adorn the restricting orifice of 2～5 polyphones in the conduit, draining pipe (21) is always collected endless tube (22) with the lime set of machine and is linked to each other.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200810011255A CN100575815C (en) | 2008-04-30 | 2008-04-30 | The damping formula air wave refrigerating device that liquidates |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200810011255A CN100575815C (en) | 2008-04-30 | 2008-04-30 | The damping formula air wave refrigerating device that liquidates |
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| Publication Number | Publication Date |
|---|---|
| CN101270931A true CN101270931A (en) | 2008-09-24 |
| CN100575815C CN100575815C (en) | 2009-12-30 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN200810011255A Active CN100575815C (en) | 2008-04-30 | 2008-04-30 | The damping formula air wave refrigerating device that liquidates |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107014583A (en) * | 2017-05-08 | 2017-08-04 | 大连理工大学 | A kind of multi-functional both ends open pressure oscillation pipe test platform |
| CN107166792A (en) * | 2017-05-08 | 2017-09-15 | 大连理工大学 | A kind of variable cross-section both ends open pressure oscillation control cold |
| CN114111081A (en) * | 2021-12-26 | 2022-03-01 | 大连理工大学 | Curved channel thermal-insulation type gas wave refrigerator |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2052509U (en) * | 1989-07-04 | 1990-02-07 | 大连理工大学 | Airwave refrigerating machine |
| CN1085824C (en) * | 1996-01-12 | 2002-05-29 | 大连理工大学 | Multi-stage gas wave refrigerator |
| CN1094189C (en) * | 1999-12-30 | 2002-11-13 | 上海交通大学 | Pulse tube type air wave refrigerator |
| JP2005351223A (en) * | 2004-06-11 | 2005-12-22 | Toyota Motor Corp | Thermal acoustic engine |
| CN201215413Y (en) * | 2008-04-30 | 2009-04-01 | 大连理工大学 | Damped opposite flushing type air wave refrigerator |
-
2008
- 2008-04-30 CN CN200810011255A patent/CN100575815C/en active Active
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107014583A (en) * | 2017-05-08 | 2017-08-04 | 大连理工大学 | A kind of multi-functional both ends open pressure oscillation pipe test platform |
| CN107166792A (en) * | 2017-05-08 | 2017-09-15 | 大连理工大学 | A kind of variable cross-section both ends open pressure oscillation control cold |
| CN107166792B (en) * | 2017-05-08 | 2022-11-29 | 大连理工大学 | Variable cross-section two-end opening pressure oscillation pipe refrigerator |
| CN107014583B (en) * | 2017-05-08 | 2023-07-04 | 大连理工大学 | Multifunctional pressure oscillation tube testing platform with two openings at two ends |
| CN114111081A (en) * | 2021-12-26 | 2022-03-01 | 大连理工大学 | Curved channel thermal-insulation type gas wave refrigerator |
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| Publication number | Publication date |
|---|---|
| CN100575815C (en) | 2009-12-30 |
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