CN108870792A - A kind of sound energy refrigerator device - Google Patents
A kind of sound energy refrigerator device Download PDFInfo
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- CN108870792A CN108870792A CN201810869333.6A CN201810869333A CN108870792A CN 108870792 A CN108870792 A CN 108870792A CN 201810869333 A CN201810869333 A CN 201810869333A CN 108870792 A CN108870792 A CN 108870792A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
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Abstract
The invention discloses a kind of sound energy refrigerator devices, including shell and supporting mechanism, sonic compressor structure and sound wave expansion mechanism, the sonic compressor structure includes compression piston, compression piston spring, linear motor, and the compression piston connect with compression piston spring, is drivingly connected with linear motor；The sound wave expansion mechanism includes displacer, piston rod and displacer spring, and the piston rod passes through and clearance seal is connect with displacer, displacer spring in the compression piston axial center hole and respectively；The displacer is connect with the displacer spring；The shell and supporting mechanism include being adapted respectively with the compression piston and the displacer and forming the cylinder part of clearance seal；The present invention can reduce influence of the lateral force for deviateing cylinder axial direction to piston, to reduce the abrasion in refrigerator operation, reduce axial heat conduction loss, improve refrigerating efficiency, prolong the service life.
Description
Technical field
The present invention is to be related to a kind of sound energy refrigerator device, belongs to technical field of refrigeration equipment.
Background technique
The theoretical refrigerating efficiency of sound energy refrigeration machine is equal with the inverse efficiency of Carnot cycle.Free-piston type sound energy refrigeration machine is adopted
There is structure so that comparing with other refrigeration systems with technologies such as linear compressor driving, flexure spring support, clearance seals
Compact, the advantages that noise is small, the service life is long, high reliablity, any angle can work normally, refrigeration working medium is environmentally friendly.More than relying on
Advantage, free-piston type sound energy refrigeration machine have obtained extensively in Aeronautics and Astronautics, superconduction, low temperature refrigerator or even domestic refrigeration field
Using.
Since flexure spring support is located at one end of compression piston and displacer, especially displacer, away from flexure spring
Supporting point is farther, and displacer is be easy to cause to contact with cylinder wall, and being influenced by other factors such as lateral forces can be bigger.Therefore, disappear
The influence for the unstable factors such as radially wobbling that the gravity of piston and vibration generate when except motor magnetic lateral force, refrigeration machine inclination,
Guarantee that refrigeration machine is run without abrasion for a long time, is the key that refrigeration machine improves refrigerating efficiency, prolongs the service life.
Summary of the invention
In view of the above-mentioned problems existing in the prior art and demand, the object of the present invention is to provide a kind of free-piston type sound energy
Refrigerating plant reduces influence of the lateral force for deviateing cylinder axial direction to piston and is mentioned with reducing the abrasion in refrigerator operation
High refrigerating efficiency prolongs the service life.
To achieve the above object, the technical solution adopted by the present invention is as follows：
A kind of sound energy refrigerator device, it is characterised in that：Including shell and supporting mechanism and be set to the shell and
Sonic compressor structure and sound wave expansion mechanism in supporting mechanism, the sonic compressor structure include compression piston, compression piston
Spring and linear motor, the compression piston connect with the compression piston spring, the linear motor respectively and pass through described
Linear motor driving；The sound wave expansion mechanism includes displacer, piston rod and displacer spring, and the piston rod passes through described
The axial center hole of compression piston and with the axial center hole inner wall formed clearance seal, the both ends of the piston rod respectively with
The displacer is connected with the displacer spring；The shell and supporting mechanism include respectively with the compression piston and described
Displacer is adapted and forms the cylinder part of clearance seal.
Preferably, the gap of the clearance seal is 8 μm~20 μm, and the leakage loss of clearance seal is less than refrigeration
Machine runs the 5% of institute's air demand.
Preferably, the resonant frequency phase of the running frequency of the sound energy refrigeration machine and the sonic compressor structure
Together, and the single order natural frequency not far from the compression piston spring, to avoid resonance occurs for the compression piston spring arm and
Fracture, and sonic compressor structure is made to resonate, compression piston goes to electric current minimum required when range；The sound wave compression
The resonant frequency of mechanism is less than its intrinsic frequency, considers the presence of damping, and resonant frequency is 1Hz~3Hz smaller than intrinsic frequency.
As further preferred scheme, the calculation formula of the intrinsic frequency of the sonic compressor structure is：
Wherein, fn is the intrinsic frequency of sonic compressor structure；K is the global stiffness of sonic compressor structure；M is sonic compressor
The mover quality of structure；
The global stiffness of sonic compressor structure includes the axial rigidity and the stiffness of air spring of compression piston spring 71；
The mover quality m of sonic compressor structure is quality, the quality of 1/3 times of compression piston spring and the company of compression piston
Connect the sum of the quality of the connection component of compression piston and compression piston spring.
As further preferred scheme, the operation frequency of the resonant frequency of the sonic compressor structure and the sound energy refrigeration machine
Identical rate is all 60Hz~80Hz, and the single order natural frequency of the compression piston spring and the displacer spring is greater than
120Hz。
Preferably, the resonant frequency phase of the running frequency of the sound energy refrigeration machine and the sound wave expansion mechanism
Together, so that the stroke of displacer can achieve maximum, so that refrigerating capacity is maximum；The resonant frequency of the sound wave expansion mechanism is less than
Its intrinsic frequency, considers the presence of damping, and resonant frequency is generally 1Hz~3Hz smaller than intrinsic frequency.
As further preferred scheme, the mover quality of the sound wave expansion mechanism is the quality of displacer, piston rod
Quality, the quality of 1/3 times of displacer spring and the displacer connection component that connect displacer, piston rod and displacer spring
The sum of quality.
Preferably, the sound wave expansion mechanism further includes accumulator, and the accumulator is sheathed on positioned at the row
The outside of the cylinder part at device out, the accumulator both ends abut respectively the sound wave expansion mechanism cool end heat exchanger and
Hot end heat exchanger, the accumulator use porosity for 50%~80% plastic film rolls contour roll forming accumulator.
Preferably, the ratio of the compression piston length and the compression piston stroke is 17%~27%, institute
The ratio for stating displacer length and the displacer stroke is 11%~21%；The compression piston outer diameter and the compression piston
The ratio of length is 39%~49%；The displacer outer diameter and the ratio of the displacer length are 39%~49%；It is described
The ratio of displacer stroke and the compression piston stroke is 60%~70%；So that the displacer and compression piston tool
There is the smallest damping, and clearance seal length is enough to ensure that sealing effect.
As further preferred scheme, it is 80mm, the pressure that the compression piston is identical with the length of the displacer
The stroke of contracting piston is 20mm, and the displacer stroke is 14mm, and the compression piston is identical as the outer diameter of displacer to be
35mm。
Preferably, the piston rod external diametrical extent accounts for institute for the sectional area of 7mm~10.5mm or the piston rod
Stating displacer bottom area proportional region is 10%~30%, and the outer diameter or sectional area of the piston rod are bigger, then the discharge
Area occupied by device bottom is smaller, and the pressure difference at the displacer both ends is bigger, then the aerodynamic force of the displacer is bigger, stroke more
Greatly, refrigerating capacity is bigger, is suitble to the lower occasion of cryogenic temperature.Conversely, when cryogenic temperature is lower, to prevent displacer 21 from hitting
Cylinder selects the lesser piston rod outer diameter of outer diameter.
Preferably, the shell and supporting mechanism further include lower bracket and displacer cylinder, the lower bracket and
The expansion cylinder, which is coaxially disposed and is connected through a screw thread to be formed, forms gap with the compression piston and the displacer respectively
The cylinder part of sealing, the displacer cylinder and the displacer upper section are all made of the lower material of axial thermal conductivity coefficient and prepare,
To reduce axial heat conduction loss.
As further preferred scheme, the shell and supporting mechanism further include thin-wall stainless steel shell, finned heat exchanger
Pedestal, motor base and lower case, the thin-wall stainless steel shell, the finned heat exchanger pedestal, the motor base and institute
It states lower case and is successively welded to connect the shell structure for forming sealing, the thin-wall stainless steel shell is the cool end heat exchanger, storage
Can device and the corresponding outside shell of hot end heat exchanger, the thin-wall stainless steel shell with a thickness of 0.4mm~0.8mm, will be described
Thin-wall stainless steel shell is arranged to thin-wall construction, because having lesser cross-sectional area, efficiently reduces axial thermal conductivity damage herein
It loses.
As further preferred scheme, the shell and supporting mechanism further include electric machine support, and the lower bracket passes through spiral shell
Nail one is fixed on the motor base, and described electric machine support one end passes through the outer yoke of the sonic compressor structure by long spiro nail
Iron is pressed abd fixed on the motor base, by being equipped with cylindrical body between the compression piston spring and the displacer spring
Interval setting, by screw three sequentially pass through the compression piston spring, the cylindrical body and the displacer spring with it is described
The other end of electric machine support is fixedly connected, and twice O-ring is equipped between motor base and the lower bracket, by the gas of back pressure cavity
It is opened with the channel interval of compression chamber.
As further preferred scheme, the shell and supporting mechanism further include cold ring, and the outer diameter of the cylinder is slightly larger than
The internal diameter of the cool end heat exchanger of the sound wave expansion mechanism, can make the cool end heat exchanger preferably be adjacent to the shell mechanism
Thin-wall stainless steel shell.
Preferably, the compression piston and the displacer are gas bearing structure, the gas bearing knot
Structure includes porous flow-restrictive material, support ring, radial hole, check valve and gas storage chamber, and the gas storage chamber is set to the gas axis
The inside of bearing structure, check valve and the compressor on end face of the gas storage chamber by being set to the gas bearing structure
The compression chamber connection of structure, by the radial hole and gas bearing structure on the side wall that is set to the gas bearing structure and
Gap connection between cylinder part, the porous flow-restrictive material are closely pressed in the gas storage chamber inner wall by the support ring
And the radial hole is covered, current stabilization, the outer end of the radial hole are carried out by porous flow-restrictive material in the gas process of circulation
The circular groove for expanding stream is additionally provided at mouthful.
As further preferred scheme, the displacer includes displacer upper section and displacer lower section, on the displacer
The low engineering plastics production of Duan Caiyong thermal coefficient, the engineering plastics include PPO, MPPO or nylon, the displacer upper section
Gap with the expansion cylinder is 100 μm~200 μm, and the length of the displacer upper section is 50mm~60mm；Close to compression
The displacer lower section of chamber is gas bearing structure, and the displacer lower section high, light weight aluminium alloy production using intensity is described
Displacer lower section outer surface is equipped with one layer of wear-resistant material, forms clearance seal, the displacer lower section and institute with the cylinder part
The seal clearance for stating expansion cylinder is 8 μm~16 μm, and the length of the displacer lower section is 20mm~30mm.
As further preferred scheme, the lesser fluff material of thermal coefficient is filled with inside the displacer, it is described fluffy
Pine material includes steeping wool, polyester fiber, for weakening the axial heat conduction loss of displacer.
A kind of embodiment, the operating voltage of the linear motor is in 0VAC~20VAC, maximum operating currenbt 15A, surely
Determining operating current is 13A, and maximum wasted work is 300W.
Preferably, the outer yoke and interior yoke are soft magnetic materials, and the soft magnetic materials includes electrical pure iron, pressure
Powder soft magnetic materials and silicon steel sheet processed.
Preferably, the permanent magnet is permanent-magnet material, and the permanent-magnet material includes Ru-Fe-Mn and Al-Ni-Co permanent magnet.
Compared with prior art, the present invention has the advantages that：
Sound energy refrigerator device of the present invention, by between compression piston and cylinder part, displacer and cylinder part it
Between, between piston rod and axial center hole form clearance seal at three, reduce the lateral force for deviateing cylinder axial direction to pressure
The abrasion that the influence of contracting piston and displacer, compression piston and displacer run smoothly, are effectively reduced in refrigerator operation；
By the setting of the intrinsic frequency to sonic compressor structure and sound wave expansion mechanism, motor magnetic lateral force, system further reduced
The unstable lateral force factor radially wobbled that the gravity of piston and vibration generate when cold tilts is to compression piston and displacer
The influence of operation reduces gas leakage loss, improves refrigerating efficiency, prolongs the service life；In addition, the present invention also has principle can
It leans on, fabricate simple and convenient for safeguarding feature, there is significant progress and good application value.
Detailed description of the invention
Fig. 1 is a kind of sound energy refrigerator device structural schematic diagram provided in an embodiment of the present invention；
Fig. 2 is linear motor operation principle schematic diagram provided in an embodiment of the present invention；
Fig. 3 is sound wave expansion mechanism operation principle schematic diagram provided in an embodiment of the present invention；
Fig. 4 is compression piston structural schematic diagram provided in an embodiment of the present invention；
Fig. 5 is displacer structural schematic diagram provided in an embodiment of the present invention.
Figure label is schematically as follows：1, sonic compressor structure；11, outer yoke；12, coil；13, permanent magnet；14, interior yoke
Iron；15, permanent magnetism body support frame；16, compression piston；17, compression piston spring；18, connection component；181, screw five；182, it connects
Part one；183, connector two；184, gasket；19, cylindrical body；2, sound wave expansion mechanism；21, displacer；211, fluff material；
212, sheet rubber；22, displacer spring；23, piston rod；24, cool end heat exchanger；25, accumulator；26, hot end heat exchanger；27,
Finned heat exchanger；28, expansion chamber；29, compression chamber；3, gas bearing structure；31, cylinder part；32, porous flow-restrictive material；33, it props up
Pushing out ring；34, radial hole；35, circular groove；36, check valve；37, gas storage chamber；4, shell and supporting mechanism；41, lower bracket；42, thin
Wall stainless steel casing；43, finned heat exchanger pedestal；44, motor base；45, lower case；46, electric machine support；47, displacer gas
Cylinder；48, cold ring；49, O-ring；51, screw one；52, screw two；53, long spiro nail；54, screw three；55, screw four.
Specific embodiment
Technical solution of the present invention is described in further detail below in conjunction with drawings and examples.
Embodiment
In conjunction with shown in Fig. 1 to Fig. 4, a kind of sound energy refrigerator device provided in this embodiment, including shell and supporting mechanism 4
And it is set to sonic compressor structure 1 and sound wave expansion mechanism 2 in the shell and supporting mechanism 4, the sonic compressor
Structure 1 include compression piston 16, compression piston spring 17 and linear motor, the compression piston 16 respectively with the compression piston bullet
Spring 17, the linear motor connect and pass through the linear motor and drive；The sound wave expansion mechanism 2 includes displacer 21, lives
Stopper rod 23 and displacer spring 22, the piston rod 23 pass through the compression piston 16 axial center hole and in the axial direction
Heart hole inner wall forms clearance seal, and the both ends of the piston rod 23 connect with the displacer 21 and the displacer spring 22 respectively
It connects；The shell and supporting mechanism 4 include being adapted respectively with the compression piston 16 and the displacer 21 and forming gap
The cylinder part 31 of sealing.
The present invention drives the variation of the formation of the sonic compressor structure 1 21 both ends air pressure of displacer by linear motor
It realizes the pneumatic actuation of the sound wave expansion mechanism 2, while to reach by the heat exchanger that the sound wave expansion mechanism 2 is equipped with
The gas of 21 upper end of displacer is low temperature low pressure gas, and then realizes refrigeration, by compression piston 16 and cylinder part 31
Between, between displacer 21 and cylinder part 31, between piston rod 23 and axial center hole form clearance seal at three, reduce partially
Influence of the lateral force to compression piston 16 and displacer 21 from cylinder axial direction, for example, refrigeration machine tilt when piston weight
Influence of the unstable lateral force factor radially wobbled that power and vibration generate to piston, is effectively reduced in refrigerator operation
Abrasion；Also, in the present embodiment, the gap of the clearance seal is 8~20 μm, and the leakage loss of clearance seal is less than system
Cold runs the 5% of institute's air demand, fully ensured that between two components for forming clearance seal contactless friction operation with it is enough
Refrigerating capacity.
The compression piston spring 17 and the displacer spring 22 are flat spring.The performance of flat spring is mainly reflected in tired
This four aspects of labor intensity, axial rigidity, radial rigidity and natural frequency.1) fatigue limit：Due to need of work, spring is reciprocal
It moves past 2,000,000,000 times, it requires that the maximum stress of flat spring is much smaller than the fatigue limit of material, usual maximum stress is only
The 60%~70% of the fatigue limit of materials；2) axial rigidity：Elastomeric element of the flat spring as oscillator system, axial rigidity pair
The energy consumption of the sonic compressor structure 1 of entire sound energy refrigeration machine and it is stable have very important effect, to make flat spring with most
Small quality provides the design object that suitable axial rigidity is flat spring, usually can by change molded line, groove width, arm number,
The parameters such as thickness adjust the axial rigidity of flat spring.3) radial rigidity：In order to guarantee between compression piston 16 and cylinder part 31
Clearance seal, the radial rigidity inevitable requirement of flat spring is larger, the thickness of the radial rigidity of usual flat spring and flat spring at
Direct ratio.4) natural frequency：Flat spring makees high speed reciprocating motion with main shaft, and motion frequency is limited by the natural frequency of spring leaf.
In the present embodiment, the running frequency of the sound energy refrigeration machine is identical as the resonant frequency of the sonic compressor structure 1, and different
In the natural frequency of the compression piston spring, to avoid resonance occurs for the compression piston spring arm and is broken, and make sound wave
Compression mechanism 1 resonates, and compression piston 16 goes to electric current minimum required when range；The sonic compressor structure 1 and institute
The resonant frequency for stating sound wave expansion mechanism 2 is smaller than its intrinsic frequency, considers the presence of damping, resonant frequency is generally than intrinsic frequency
Small 1Hz~the 3Hz of rate.
For the mover quality of accurate sonic compressor structure 1, the calculation formula of the intrinsic frequency of the sonic compressor structure 1
For：
Wherein, fn is the intrinsic frequency of sonic compressor structure；K is the global stiffness of sonic compressor structure；M is sonic compressor
The mover quality of structure；
The global stiffness of sonic compressor structure 1 includes the axial rigidity and the stiffness of air spring of compression piston spring 17；
The mover quality m of sonic compressor structure is quality, the quality of 1/3 times of compression piston spring 17 of compression piston 16
With the quality for the connection component 18 for connecting compression piston 16 and compression piston spring 17 and.
In the present embodiment, the connection component 18 includes screw 5 181, connector 1, connector 2 183 and pad
Piece 184, the linear motor include outer yoke 11, coil 12, permanent magnet 13, interior yoke 14 and permanent magnetism body support frame 15, the sound
The mover quality m of wave compression mechanism be the quality of compression piston 16, the quality of connector 1, the quality of connector 2 183,
Quality, the quality of permanent magnetism body support frame 15, the gross mass of several screws 5 181 and 1/3 times of the compression piston spring 17 of gasket 184
Quality sum.
Preferably, the resonant frequency of the sonic compressor structure 1 and the running frequency of the sound energy refrigeration machine are all
The single order natural frequency of 70Hz, the compression piston spring and the displacer spring is 121Hz.
For the mover quality of accurate sound wave expansion mechanism 2, the running frequency of the sound energy refrigeration machine and the sound wave are swollen
The resonant frequency of swollen mechanism 2 is identical, so that the stroke of displacer 21 can achieve maximum, so that refrigerating capacity is maximum；The sound wave
The mover quality of expansion mechanism 2 is quality, the quality of piston rod 23, the quality of 1/3 times of displacer spring 22 of displacer 21
With the quality for the displacer connection component for connecting displacer 21, piston rod 23 and displacer spring 22 and；In the present embodiment,
The displacer connection component includes screw 2 52 and screw 4 55, and the mover quality of the sound wave expansion mechanism is displacer 21
Quality, the quality of piston rod 23, the quality of screw 2 52, the matter of the quality of screw 4 55 and 1/3 times of displacer spring 22
The sum of amount.
In order to further increase heat exchange property, the sound wave expansion mechanism 2 further includes accumulator 25,25 sets of the accumulator
Set on the outside for the cylinder part 31 being located at the displacer 21, it is swollen that 25 both ends of accumulator abut the sound wave respectively
The cool end heat exchanger 24 and hot end heat exchanger 26 of swollen mechanism 2, the accumulator 25 use porosity for 50%~80% plastics
Film roll contour roll forming accumulator, one end of accumulator 25 close to expansion chamber 28, the other end close to compression chamber 29, accumulator 25 there is
The porosity of biggish axial-temperature gradient, accumulator 25 is bigger, then flow resistance loss of the sound wave in accumulator 25 is smaller, but fills out
Material entity is less to also result in sound wave and the heat exchange of regenerator is insufficient, influences sound energy refrigeration machine performance, on the contrary then flow resistance loss
It is larger, but backheat effect promoting, the present embodiment use plastic film rolls contour roll forming accumulator, have biggish specific heat capacity, specific surface
Long-pending and lesser axial thermal conductivity coefficient, while porosity is 50%~80%, flow resistance loss and backheat effective balance, energy storage effect
It is good.Accumulator 25 is that the heat storage and cold accumulation element of sound energy refrigeration machine is the critical component of sound energy refrigeration machine, undertakes week between cold and hot fluid
The task of phase property heat exchange；Different from traditional heat exchanger, the characteristics of accumulator 25, is that cold and hot fluid alternately flows through together
One flow channel space, by realizing heat exchange with directly contacting for regeneration filler；In the present embodiment, the filler of the accumulator 25
Including the random silk screen of metal, random non-metallic fibers, stainless steel cloth, winding up resin film etc..
For the size of accurate compression piston 16 and displacer 21, the compression piston length and the compression piston stroke
Ratio be 17%~27%, the ratio of the displacer length and the displacer stroke is 11%~21%；The compression
Piston external diameter and the ratio of the compression piston length are 39%~49%；The displacer outer diameter and the displacer length
Ratio is 39%~49%；The ratio of the displacer stroke and the compression piston stroke is 60%~70%；So that described
Displacer 21 and the compression piston 16 have the smallest damping, and clearance seal length is enough to ensure that sealing effect；It is preferred that square
Case, it is 80mm that the compression piston 16 is identical with the length of the displacer 21, and the stroke of the compression piston 16 is 20mm,
The 21 stroke 14mm of displacer, the compression piston 16 identical as the outer diameter of displacer 21 is 35mm.
For the size of accurate piston rod 23,23 external diametrical extent of piston rod is 7mm~10.5mm or the piston rod
It is 10%~30% that 23 sectional area, which accounts for the 21 bottom area proportional region of displacer, the outer diameter of the piston rod 23 or section
Product is bigger, then area occupied by 21 bottom of displacer is bigger, and the pressure difference at 21 both ends of displacer is bigger, then the discharge
The aerodynamic force of device 21 is bigger, stroke is bigger, and refrigerating capacity is bigger, be suitble to the lower occasion of cryogenic temperature, conversely, when cryogenic temperature compared with
Gao Shi selects the lesser piston rod 23 of outer diameter to prevent displacer 21 from hitting cylinder.
In order to precisely guarantee to seal, support and be further reduced axial heat conduction loss, as shown in Figure 1, the shell and branch
Support mechanism 4 further includes thin-wall stainless steel shell 42, finned heat exchanger pedestal 43, motor base 44 and lower case 45, the thin-walled
Stainless steel casing 42, the finned heat exchanger pedestal 43, the motor base 44 and the lower case 45 are successively welded to connect shape
At the shell structure of sealing, the thin-wall stainless steel shell 42 is the cool end heat exchanger 24, accumulator 25 and hot end heat exchanger
26 corresponding outside shells, the thin-wall stainless steel shell 42 with a thickness of 0.4mm~0.8mm, will be outside the thin-wall stainless steel
Shell 42 is arranged to thin-wall construction, because having lesser cross-sectional area, efficiently reduces axial heat conduction loss herein；In this implementation
In example, the shell and supporting mechanism 4 further include lower bracket 41 and displacer cylinder 47, the lower bracket 41 and the expansion gas
Cylinder, which is coaxially disposed and is connected through a screw thread to be formed, forms clearance seal with the compression piston 16 and the displacer 21 respectively
Cylinder part 31, the displacer cylinder 47 are all made of the lower material of axial thermal conductivity coefficient with the displacer upper section and prepare, with
Reduce displacer 21 axial heat conduction loss；In the present embodiment, the shell and supporting mechanism 4 further include electric machine support
46, the lower bracket 41 is fixed on the motor base 44 by screw 1, and described 46 one end of electric machine support passes through long spiral shell
The outer yoke 11 that nail 53 passes through the sonic compressor structure 1 is pressed abd fixed on the motor base 44, the compression piston bullet
By being equipped with the setting of the interval of cylindrical body 19 between spring 17 and the displacer spring 22, to guarantee that two springs do not occur during exercise
Collision, by screw 3 54 sequentially pass through the compression piston spring 17, the cylindrical body 19 and the displacer spring 22 with
The other end of the electric machine support 46 is fixedly connected, and twice O-ring 49 is equipped between motor base 44 and the lower bracket 41, will
The gas of back pressure cavity and the channel interval of compression chamber 29 are opened；In the present embodiment, the shell and supporting mechanism 4 further include cold ring
48, the outer diameter of the cold ring 48 is slightly larger than the internal diameter of the cool end heat exchanger 24 of the sound wave expansion mechanism 2, and the cold end can be made to change
Hot device 24 is preferably adjacent to the thin-wall stainless steel shell 42, to reduce thermal contact resistance, cooling capacity is more fully conducted extremely with cold
Environment.
In view of running smoothly for compression piston and displacer, as shown in Figure 4, Figure 5, the compression piston and the discharge
Device is gas bearing structure 3, the gas bearing structure 3 include porous flow-restrictive material 32, support ring 33, radial hole 34,
Check valve 36 and gas storage chamber 37, the gas storage chamber 37 are set to the inside of the gas bearing structure 3, and the gas storage chamber is by setting
The check valve 36 being placed on the end face of the gas bearing structure 3 is connected to the compression chamber 29 of the compression mechanism, passes through setting
Gap between radial hole 34 described on the side wall of the gas bearing structure 3 and gas bearing structure 3 and cylinder part 31
Connection, the porous flow-restrictive material are closely pressed in 37 inner wall of gas storage chamber by the support ring and cover the radial direction
Aperture 34 carries out current stabilization by porous flow-restrictive material in the gas process of circulation, is additionally provided at the external port of the radial hole 34
For expanding the circular groove 35 of stream.
As shown in figure 5, the left and right ends of the displacer 21 are compression chamber 29 and expansion chamber 28, the compression chamber 29 respectively
It is temperature up to 35 DEG C~50 DEG C, 28 temperature of expansion chamber can be down to -100 DEG C hereinafter, so generating at 21 both ends of displacer
Biggish axial-temperature gradient, in order to weaken by 21 axial heat conduction loss of axial-temperature gradient bring displacer, the row
Device 21 includes displacer upper section and displacer lower section, the engineering low using thermal coefficient close to the displacer upper section of expansion chamber 28 out
Plastic production, the engineering plastics include PPO, MPPO or nylon, and the gap of the displacer upper section and the expansion cylinder is
100 μm~200 μm, the length of the displacer upper section is 50mm~60mm；Displacer lower section close to compression chamber 28 is gas
Bearing arrangement 3, the displacer lower section high, light weight aluminium alloy production using intensity, displacer lower section outer surface is set
There is one layer of wear-resistant material, clearance seal is formed with the cylinder part, between the displacer lower section and the sealing of the expansion cylinder
Gap is 8 μm~16 μm, and the length of the displacer lower section is 20mm~30mm；The 21 lower section internal cavities of displacer are gas
The inflatable chamber of bearing arrangement 3；The 21 upper section cavity inside of displacer is filled with the lesser fluff material 211 of thermal coefficient, institute
Stating fluff material 211 includes steeping wool, polyester fiber, for weakening the axial heat conduction loss of displacer 21, in the discharge
It is equipped with sheet rubber 212 between device upper section and the displacer lower section to avoid steeping wool axial movement, steeping wool is constrained
In 21 upper section cavity of displacer.
In the present embodiment, the operating voltage of the linear motor is in 0VAC~20VAC, maximum operating currenbt 15A, surely
Determining operating current is 13A；Maximum wasted work is 300W.
In the present embodiment, as shown in Figure 1,43 outer ring surface of finned heat exchanger pedestal is equipped with finned heat exchanger 27；Pressure
The heat elder generation heat convection that contracting chamber 29 generates passes to hot end heat exchanger 26, then passes to finned heat exchanger in thermally conductive form
Pedestal 43 is being transferred to finned heat exchanger 27 in thermally conductive form, and last finned heat exchanger 27 will be warm in a manner of heat convection
Amount is released to high temperature heat source；The finned heat exchanger pedestal 43 is using the higher red copper production of thermal coefficient.
Work below with reference to linear motor working principle, gas bearing structure working principle harmony energy refrigerator device is former
Reason is described in detail.
Linear motor working principle described in the present embodiment is as follows：
As shown in Figure 1, Figure 2, the linear motor includes outer yoke 11, coil 12, permanent magnet 13, interior yoke 14 and forever
Magnet carrier 15, the outer yoke 11, coil 12, permanent magnet 13, interior yoke 14 and permanent magnetism body support frame 15 in a ring and use
Coaxially arranged, the permanent magnet 13 is placed in the groove that permanent magnetism body support frame 15 is equipped with and is carried out by spreading glue on the contact surface
Fixed, the outer yoke 11 and interior yoke 14 are soft magnetic materials, including electrical pure iron, pressed powder soft magnetic materials and silicon steel sheet,
The permanent magnet 13 is permanent-magnet material, including Ru-Fe-Mn, Al-Ni-Co permanent magnet；The compression piston 16 passes through the connection component being equipped with
18 connect with the compression piston spring 17, the linear motor respectively, and the connection component 18 includes screw 5 181, connection
Part 1, connector 2 183, gasket 184, the permanent magnetism body support frame 15 pass through gasket 184 and screw five with compression piston 16
181 are connected and fixed, and the compression piston spring 17 is fixed by connector 1, connector 2 183 and compression piston 16.
When coil 12 is passed through direct current, outer yoke 11 and interior yoke 14 will form the magnetic as shown in Fig. 2 (lower half portion)
Power loop line, to generate magnetic pole as shown in Figure 1 on outer yoke 11 and interior yoke 14, permanent magnet 13 is radial magnetizing, such as Fig. 2
Shown in (top half), the left part of outer yoke 11 and interior yoke 14 generates attraction to permanent magnet 13, and right part is to forever
Magnet 13 generates repulsive force, and under the action of resultant force, the component of electromagnetic force radially is balanced, and is permanent magnetism along axial component
Driving force suffered by body 13.After being passed through one-way communication electricity in coil 12, permanent magnet 13 receives axial alternating electromagnetic force,
Axial linear reciprocating motion is done, drives permanent magnetism body support frame 15 and compression piston 16 also to do axial linear reciprocating motion, at this time
The volume of compression chamber 29 will change.In order to stablize the needs of starting sound energy refrigeration machine, also it is not acted upon in gas bearing structure 3
When, the compression piston spring 17 needs to provide biggish radial support to compression piston 16, and compression piston spring 17 is avoided to send out
Raw radial deflection is in contact friction with cylinder part 31, while compression piston spring 17 has suitable axial rigidity, guarantees pressure
Contracting piston 16 reaches ideal amplitude, and in 3 steady operation of gas bearing structure, the nothing between compression piston 16 and cylinder part 31 is connect
Touching movement relies primarily on the gas film stiffness support of gas bearing structure 3.
The working principle of gas bearing structure described in the present embodiment is as follows：
In conjunction with shown in Fig. 4, Fig. 5,21 lower section of displacer and the compression piston 16 are all gas bearing structure 3；When
In compression chamber 29 when pressure rise check valve 36 open, Working medium gas by after porous current limliting medium flow-limiting voltage-stabilizing by radial hole
34 project and act on cylinder inner wall face, and sufficient radial support power is provided to displacer 21 and compression piston 16, guarantee piston with
Clearance seal between cylinder；When the pressure difference at 36 both ends of check valve is higher than the cracking pressure of valve, check valve 36 is opened, and gas is from pressure
Contracting chamber 29 enters gas storage chamber 37 and inflates；Otherwise check valve 36 is closed, and avoids gas backstreaming in gas storage chamber 37 to compression chamber 29.Branch
Pushing out ring 33 closely compresses porous flow-restrictive material 32 flows into porous limit with piston inner wall face, gas along the direction of arrow in the figure
It flows material 32 and carries out current stabilization, then radially uniformly sprayed from radial hole 34 and circular groove 35, act on the inner wall of cylinder part 31
Face forms uniform air film in the annular space between piston and cylinder part 31, prevents displacer 21, compression piston 16 and cylinder part 31
Directly contact friction.In general, check valve 36 can just be beaten when gas pressure is more than the 90% of pressure peak only in compression chamber 29
It opens, that is to say, that only it is in this bit of section of pressure peak 90%~100% in the gas pressure in compression chamber 29,
Gas storage chamber 37 can just be inflated, therefore the gas pressure average value in gas storage chamber 37 is higher, about 29 pressure peak of compression chamber
92%~95%.Therefore the gas film stiffness of gas bearing structure 3 is larger, can provide very well to displacer 21 and compression piston 16
Radial support power；The air consumption of gas bearing structure 3 accounts for about 2% of institute's air demand in refrigerator operation, and gas consumption loss accounts for about
The 4% of refrigeration machine expansion work.
Sound energy refrigerator device working principle described in the present embodiment is as follows：
As shown in connection with fig. 3, displacer 21 is pure pneumatic actuation, utilizes the displacement phase between displacer 21 and compression piston 16
Potential difference generates refrigeration effect, and the leading 16 displacement phase difference of compression piston of the displacement of usual displacer 21 is 70 °~100 °, in low temperature
When area's (cold head temperature is at -160 DEG C or less), institute's displacing phase difference can be decreased to 50 °~70 °.Since linear motor is sine
Electric excitation is exchanged, so it is in sinusoidal continuous movement that the movement of displacer 21 and compression piston 16, which is also, but in order to illustrate
Its working principle, it is assumed that displacer 21 and compression piston 16 do intermittent touchdown formula according to circulation law and move.
Sound wave compression process (a → b)：Displacer 21 rests on that top dead centre is motionless, and compression piston 16 is transported upwards by lower dead center
Dynamic, the sound wave in compression chamber 29 is compressed at this time, and flows into the annular hot end heat exchanger 26 on the outside of cylinder, and compression process is generated
Heat be released to hot end heat exchanger 26, heat is passed to the finned heat exchanger in outside by hot end heat exchanger 26 by outer housing again
27, finally it is released to environment.Ideally think cylinder part 31 and outer housing is completely thermally conductive, while hot end heat exchanger 26
It is infinitely great with the heat exchange area of finned heat exchanger 27, therefore the temperature of working medium remains unchanged.But in the actual process, isotherm compression
Be it is impossible, and displacer 21 can not intermittent movement, when compression piston 16 moves upwards, displacer 21 has been
Start to move downward.
Exothermic process (b → c)：Compression piston 16 continues up, and displacer 21 is moved downward since top dead centre, this
Shi Shengbo comes into full contact with heat exchange by the filler in accumulator 25, with accumulator 25, heat is discharged to accumulator 25, at this time
The temperature of accumulator 25 increases, acoustic wave temperature and pressure reduction.But in practical heat transfer process, 25 heat transfer process of accumulator is not
It is constant volume, it is also not possible to the complete heat exchange of 25 filler of real sound wave and accumulator.
Sound wave expansion process (c → d)：Displacer 21, which continues to move downward, reaches lower dead center, and compression piston 16 rests on
Stop is motionless, and the volume of expansion chamber 28 becomes larger at this time, and sound wave swell refrigeration in expansion chamber 28, the cooling capacity of generation passes to cold end
Heat exchanger 24, and then passed to by shell with cold environment.The process acoustic attenuation, the temperature and pressure of sound wave reach minimum
Point.In practical work process, compression piston 16 can't rest on always top dead centre, but can be with displacer 21 downwardly together
Movement.
Endothermic process (d → a)：Displacer 21 moves up to top dead centre since lower dead center, and compression piston 16 moves to
Lower dead center, displacer 21 push back to the sound wave in expansion chamber 28 in annular accumulator 25, in sound wave working medium and accumulator 25
Filler comes into full contact with heat exchange, after absorbing the heat in accumulator 25, returns to compression chamber 29 and waits next second compression.The process
The temperature and pressure of sound wave rises, the decline of 25 temperature of accumulator.In the actual process, discharge when compression piston 16 reaches lower dead center
Device 21 and not up to top dead centre, but during returning to top dead centre, but its still advanced compression piston on displacement wave phase
16。
It is visible in summary：Sound energy refrigerator device of the present invention, by between compression piston 16 and cylinder part, row
Clearance seal at three is formed between device 21 and cylinder part, between piston rod 23 and axial center hole out, reduces deviation cylinder axis
Influence of the lateral force to compression piston 16 and displacer 21 to direction, compression piston 16 and displacer 21 run smoothly, effectively
The abrasion reduced in refrigerator operation；Pass through setting for the intrinsic frequency to sonic compressor structure 1 and sound wave expansion mechanism 2
It sets, by sonic compressor structure mover and sound wave expansion mechanism mover quality, compression piston 16, displacer 21, piston rod 23
The improvement of size, the radial pendulum that the gravity of piston and vibration generate when further reduced motor magnetic lateral force, refrigeration machine inclination
The influence that dynamic unstable lateral force factor runs compression piston 16 and displacer 21 reduces gas leakage loss, improves system
Cold efficiency prolongs the service life；The lower material of axial thermal conductivity coefficient is used by displacer cylinder 47 and 21 upper section of displacer
The design of preparation, is further reduced axial heat conduction loss, reduces thermal contact resistance by the setting of cold ring 48, keeps cooling capacity more abundant.
In addition, the present invention also has the characteristics that principle is reliable, processing and manufacturing is simple and convenient for safeguarding, with significant progress and well
Application value.
It is last it is necessarily pointed out that：The foregoing is merely the preferable specific embodiment of the present invention, but the present invention
Protection scope be not limited thereto, anyone skilled in the art in the technical scope disclosed by the present invention,
Any changes or substitutions that can be easily thought of, should be covered by the protection scope of the present invention.
Claims (14)
1. a kind of sound energy refrigerator device, it is characterised in that：Including shell and supporting mechanism and it is set to the shell and branch
Sonic compressor structure and sound wave expansion mechanism in support mechanism, the sonic compressor structure include compression piston, compression piston bullet
Spring and linear motor, the compression piston connect with the compression piston spring, the linear motor respectively and pass through described straight
Line motor driven；The sound wave expansion mechanism includes displacer, piston rod and displacer spring, and the piston rod passes through the pressure
The axial center hole of contracting piston and with the axial center hole inner wall formed clearance seal, the both ends of the piston rod respectively with institute
Displacer is stated to connect with the displacer spring；The shell and supporting mechanism include respectively with the compression piston and the row
Device is adapted and forms the cylinder part of clearance seal out.
2. sound energy refrigerator device according to claim 1, it is characterised in that：The running frequency of the sound energy refrigeration machine with
The resonant frequency of the sonic compressor structure is identical, and the single order natural frequency not far from the compression piston spring；The sound
The resonant frequency of wave compression mechanism is less than its intrinsic frequency.
3. sound energy refrigerator device according to claim 2, it is characterised in that：The intrinsic frequency of the sonic compressor structure
Calculation formula be：
Wherein, fn is the intrinsic frequency of sonic compressor structure；K is the global stiffness of sonic compressor structure；M is sonic compressor structure
Mover quality；
The global stiffness of sonic compressor structure includes the axial rigidity and the stiffness of air spring of compression piston spring 71；
The mover quality m of sonic compressor structure is the quality of compression piston, the quality of 1/3 times of compression piston spring and connect pressure
The sum of the quality of the connection component of contracting piston and compression piston spring.
4. sound energy refrigerator device according to claim 3, it is characterised in that：The resonant frequency of the sonic compressor structure
Identical as the running frequency of the sound energy refrigeration machine is all 60Hz~80Hz, the compression piston spring and the displacer bullet
The single order natural frequency of spring is greater than 120Hz.
5. sound energy refrigerator device according to claim 1, it is characterised in that：The running frequency of the sound energy refrigeration machine with
The resonant frequency of the sound wave expansion mechanism is identical, and the resonant frequency of the sound wave expansion mechanism is less than its intrinsic frequency.
6. sound energy refrigerator device according to claim 1, it is characterised in that：The sound wave expansion mechanism further includes accumulation of energy
Device, the accumulator are sheathed on outside the cylinder part at the displacer, and the accumulator both ends abut the sound respectively
The cool end heat exchanger and hot end heat exchanger of wave expansion mechanism, the accumulator use porosity for 50%~80% plastic film
Scroll type accumulator.
7. sound energy refrigerator device according to claim 1, it is characterised in that：The compression piston length and the compression
The ratio of piston stroke is 17%~27%, and the ratio of the displacer length and the displacer stroke is 11%~21%；
The compression piston outer diameter and the ratio of the compression piston length are 39%~49%；The displacer outer diameter and the discharge
The ratio of device length is 39%~49%；The ratio of the displacer stroke and the compression piston stroke is 60%~70%.
8. sound energy refrigerator device according to claim 7, it is characterised in that：The compression piston and the displacer
Identical length is 80mm, and the stroke of the compression piston is 20mm, the displacer stroke 14mm, the compression piston and row
It is 35mm that the outer diameter of device is identical out.
9. sound energy refrigerator device according to claim 1, it is characterised in that：Under the shell and supporting mechanism further include
Bracket and displacer cylinder, the lower bracket and the expansion cylinder be coaxially disposed and be connected through a screw thread to be formed respectively with it is described
Compression piston and the displacer form the cylinder part of clearance seal, and the displacer cylinder is lower using axial thermal conductivity coefficient
Material preparation.
10. sound energy refrigerator device according to claim 9, it is characterised in that：The shell and supporting mechanism further include
Thin-wall stainless steel shell, finned heat exchanger pedestal, motor base and lower case, the thin-wall stainless steel shell, the fin change
Hot device pedestal, the motor base and the lower case are successively welded to connect the shell structure for forming sealing, and the thin-walled is stainless
Outer steel shell be the cool end heat exchanger, accumulator and the corresponding outside shell of hot end heat exchanger, the thin-wall stainless steel shell
With a thickness of 0.4mm~0.8mm.
11. sound energy refrigerator device according to claim 10, it is characterised in that：The shell and supporting mechanism further include
Cold ring, the outer diameter of the cylinder are slightly larger than the internal diameter of the cool end heat exchanger of the sound wave expansion mechanism.
12. sound energy refrigerator device according to claim 1, it is characterised in that：The compression piston and the displacer
It is gas bearing structure, the gas bearing structure includes porous flow-restrictive material, support ring, radial hole, check valve and storage
Air cavity, the gas storage chamber are set to the inside of the gas bearing structure, and the gas storage chamber is by being set to the gas bearing
Check valve on the end face of structure is connected to the compression chamber of the compression mechanism, the side by being set to the gas bearing structure
The radial hole is connected to the gap between gas bearing structure and cylinder part on wall, and the porous flow-restrictive material passes through described
Support ring is closely pressed in the gas storage chamber inner wall and covers the radial hole.
13. sound energy refrigerator device according to claim 12, it is characterised in that：The displacer includes displacer upper section
With displacer lower section, the displacer upper section using thermal coefficient it is low engineering plastics production, the engineering plastics include PPO,
The gap of MPPO or nylon, the displacer upper section and the cylinder part is 100 μm~200 μm, the length of the displacer upper section
Degree is 50mm~60mm；Displacer lower section close to compression chamber is gas bearing structure, the displacer lower section is high using intensity,
The aluminium alloy of light weight makes, and displacer lower section outer surface is equipped with one layer of wear-resistant material, the displacer lower section with it is described
The seal clearance of cylinder part is 8 μm~16 μm, and the length of the displacer lower section is 200mm~30mm.
14. sound energy refrigerator device according to claim 13, it is characterised in that：Intersegmental part is filled on the displacer
The lesser fluff material of thermal coefficient, the fluff material include steeping wool, polyester fiber.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810869333.6A CN108870792A (en) | 2018-08-02 | 2018-08-02 | A kind of sound energy refrigerator device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810869333.6A CN108870792A (en) | 2018-08-02 | 2018-08-02 | A kind of sound energy refrigerator device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN108870792A true CN108870792A (en) | 2018-11-23 |
Family
ID=64307195
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
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| CN201810869333.6A Withdrawn CN108870792A (en) | 2018-08-02 | 2018-08-02 | A kind of sound energy refrigerator device |
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| CN (1) | CN108870792A (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110081632A (en) * | 2019-04-19 | 2019-08-02 | 东南大学 | A kind of sterlin refrigerator driven using linear motor |
| CN110118165A (en) * | 2019-05-23 | 2019-08-13 | 江苏热声机电科技有限公司 | A kind of thermoacoustic motor piston air floating structure |
| CN110118166A (en) * | 2019-05-23 | 2019-08-13 | 江苏热声机电科技有限公司 | A kind of expansion piston air floating structure |
| CN111058965A (en) * | 2019-11-18 | 2020-04-24 | 上海厚酷科技有限公司 | Clearance sealing structure of refrigerating machine |
| CN111076442A (en) * | 2019-11-18 | 2020-04-28 | 上海厚酷科技有限公司 | Pressure shell of refrigerating machine |
| CN111089435A (en) * | 2019-11-18 | 2020-05-01 | 上海厚酷科技有限公司 | Refrigerating machine |
| CN111121334A (en) * | 2019-11-18 | 2020-05-08 | 上海厚酷科技有限公司 | Refrigerating machine power piston component |
| CN111140653A (en) * | 2019-11-18 | 2020-05-12 | 上海厚酷科技有限公司 | Refrigerating machine power piston assembly |
| CN111140654A (en) * | 2019-11-18 | 2020-05-12 | 上海厚酷科技有限公司 | Gas distribution piston of refrigerator |
| CN114440488A (en) * | 2022-03-11 | 2022-05-06 | 中国电子科技集团公司第十六研究所 | Stirling cycle heat engine |
| CN115218602A (en) * | 2022-06-27 | 2022-10-21 | 青岛海尔生物医疗股份有限公司 | Method and device for controlling temperature of refrigerator, refrigerator and storage medium |
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| CN115218602A (en) * | 2022-06-27 | 2022-10-21 | 青岛海尔生物医疗股份有限公司 | Method and device for controlling temperature of refrigerator, refrigerator and storage medium |
| CN115218602B (en) * | 2022-06-27 | 2023-08-11 | 青岛海尔生物医疗股份有限公司 | Method and device for controlling temperature of refrigerator, refrigerator and storage medium |
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