CN218644421U - Linear compressor and stirling cryocooler - Google Patents

Abstract

The application relates to the technical field of refrigeration equipment, and discloses a linear compressor and a Stirling refrigerator. The linear compressor includes: a housing defining a compressor cavity; the compressor piston is movably positioned in the compressor cavity and encloses a back pressure cavity with the shell, and the compressor cavity comprises the back pressure cavity; the plate spring is connected with the compressor piston and is positioned in the back pressure cavity; and the silencing device is positioned in the back pressure cavity and on one side of the plate spring, which deviates from the compressor piston, and is used for absorbing noise. The silencing device is located the backpressure intracavity, because the backpressure intracavity does not participate in the refrigerated effect of compressor piston front to the system work, consequently, plate spring and silencing device all locate the backpressure intracavity, are convenient for place, can not influence stirling refrigerator's normal work moreover. The Stirling refrigerator can absorb the working noise of the Stirling refrigerator, and thus a better silencing effect can be achieved.

Description

Linear compressor and stirling cryocooler

Technical Field

The present application relates to the technical field of refrigeration equipment, and for example, relates to a linear compressor and a stirling refrigerator.

Background

At present, the Stirling type refrigerating machine has the advantages of simple structure, reliable operation, long service life, no fault operation time which can even be as long as ten years, wide attention in the field of refrigeration and low temperature since the past, and high preference of researchers. However, during stirling operation, vibrations are inevitably generated due to the imbalance of forces, and the vibrations of the refrigerator are mainly generated by the linear motor motion.

In the related art, a large metal block is generally placed in a Stirling refrigerator, so that the resonant frequency of the whole refrigerator is greatly improved, the actual operating frequency deviates from the resonant frequency, and the vibration of the whole refrigerator is reduced. The sound generated in the partial area is still not absorbed.

It is to be noted that the information disclosed in the above background section is only for enhancement of understanding of the background of the present application and therefore may include information that does not constitute prior art known to a person of ordinary skill in the art.

SUMMERY OF THE UTILITY MODEL

The following presents a simplified summary in order to provide a basic understanding of some aspects of the disclosed embodiments. This summary is not an extensive overview nor is intended to identify key/critical elements or to delineate the scope of such embodiments but rather as a prelude to the more detailed description that is presented later.

The embodiment of the disclosure provides a linear compressor and a Stirling refrigerator, so that the Stirling refrigerator can absorb noise and achieve the purpose of noise elimination.

The disclosed embodiment provides a linear compressor, which includes: a housing defining a compressor cavity; the compressor piston is movably positioned in the compressor cavity and encloses a back pressure cavity with the shell, and the compressor cavity comprises the back pressure cavity; the plate spring is connected with the compressor piston and is positioned in the back pressure cavity; and the silencing device is positioned in the back pressure cavity and on one side of the plate spring, which deviates from the compressor piston, and is used for absorbing noise.

Optionally, the silencing device comprises: a cavity; and the porous body is communicated with the cavity and is used for absorbing noise.

Optionally, the porous body comprises: the pipeline is arranged at one end, facing the plate spring, of the cavity and communicated with the cavity; and the porous medium is filled in the pipeline.

Optionally, the cross-sectional area of the cavity is greater than the cross-sectional area of the conduit such that the cavity and the conduit form a helmholtz resonator.

Optionally, the linear compressor further comprises: and the support reed is connected between the silencing device and the inner wall surface of the back pressure cavity.

Optionally, the number of the supporting reeds is multiple, and the supporting reeds are sequentially arranged on the outer side wall of the silencer at intervals along the circumferential direction of the silencer.

Optionally, one end of the support reed is connected with the outer side wall of the silencer, and the other end of the support reed is connected with the inner wall surface of the back pressure cavity; wherein the other end of the support reed extends spirally towards the direction far away from the silencer.

Optionally, the support spring is arc-shaped, and the width of the support spring gradually decreases in a direction from the one end of the support spring to the other end of the support spring.

Optionally, the support spring is of an integral structure with the silencer.

Embodiments of the present disclosure also provide a stirling cooler comprising a linear compressor as described in any one of the above embodiments.

The linear compressor and the Stirling refrigerator provided by the embodiment of the disclosure can realize the following technical effects:

in the working process of the Stirling refrigerator, a compressor piston can perform reciprocating linear motion in a compressor cavity, so that gas working media in the compressor cavity are compressed and expanded. Because the back pressure cavity does not participate in the action of the front face of the compressor piston on the system acting refrigeration, the plate spring and the silencing device are both arranged in the back pressure cavity, the placement is convenient, and the normal work of the Stirling refrigerator can not be influenced. The silencing device is positioned in the back pressure cavity and can absorb the working noise of the Stirling refrigerator, so that a better silencing effect can be achieved. And set up silencing device, need not to change other parts of stirling refrigerator, utilize current back pressure chamber installation silencing device of stirling refrigerator, simple structure, the cost is lower, and the effect is showing.

The foregoing general description and the following description are exemplary and explanatory only and are not restrictive of the application.

Drawings

One or more embodiments are illustrated by way of example in the accompanying drawings, which correspond to the accompanying drawings and not in limitation thereof, in which elements having the same reference numeral designations are shown as like elements and not in limitation thereof, and wherein:

FIG. 1 is a schematic diagram of a Stirling cooler according to an embodiment of the present disclosure;

FIG. 2 is a schematic cross-sectional view of a Stirling cooler according to an embodiment of the present disclosure;

FIG. 3 is a structural schematic diagram of a perspective view of a shock-absorbing and sound-attenuating structure provided by the disclosed embodiment;

FIG. 4 is a structural schematic diagram of another perspective of a shock-absorbing and sound-attenuating structure provided by the embodiments of the present disclosure;

FIG. 5 is a schematic cross-sectional view of a shock-absorbing and sound-attenuating structure according to an embodiment of the present disclosure;

reference numerals:

10. a housing; 101. a back pressure chamber; 102. a magnet; 103. a coil; 104. a compressor piston; 105. an ejector; 106. a first plate spring; 107. a second plate spring; 20. a silencer device; 201. a porous body; 202. a cavity; 30. supporting the reed; 40. a hot end heat exchanger; 50. an outer fin; 60. a heat regenerator; 70. and a cold end heat exchanger.

Detailed Description

So that the manner in which the features and elements of the disclosed embodiments can be understood in detail, a more particular description of the disclosed embodiments, briefly summarized above, may be had by reference to the embodiments, some of which are illustrated in the appended drawings. In the following description of the technology, for purposes of explanation, numerous details are set forth in order to provide a thorough understanding of the disclosed embodiments. However, one or more embodiments may be practiced without these details. In other instances, well-known structures and devices may be shown in simplified form in order to simplify the drawing.

The terms "first," "second," and the like in the description and in the claims, and the above-described drawings of embodiments of the present disclosure, are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It should be understood that the data so used may be interchanged under appropriate circumstances such that embodiments of the present disclosure described herein may be made. Furthermore, the terms "comprising" and "having," as well as any variations thereof, are intended to cover non-exclusive inclusions.

In the embodiments of the present disclosure, the terms "upper", "lower", "inner", "middle", "outer", "front", "rear", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings. These terms are used primarily to better describe the disclosed embodiments and their examples and are not intended to limit the indicated devices, elements or components to a particular orientation or to be constructed and operated in a particular orientation. Moreover, some of the above terms may be used to indicate other meanings besides the orientation or positional relationship, for example, the term "on" may also be used to indicate some kind of attachment or connection relationship in some cases. The specific meanings of these terms in the embodiments of the present disclosure can be understood by those of ordinary skill in the art as appropriate.

In addition, the terms "disposed," "connected," and "secured" are to be construed broadly. For example, "connected" may be a fixed connection, a detachable connection, or a unitary construction; can be a mechanical connection, or an electrical connection; may be directly connected, or indirectly connected through intervening media, or may be in internal communication between two devices, elements or components. Specific meanings of the above terms in the embodiments of the present disclosure can be understood by those of ordinary skill in the art according to specific situations.

The term "plurality" means two or more, unless otherwise specified.

The term "and/or" is an associative relationship that describes objects, meaning that three relationships may exist. E.g., a and/or B, represents: a or B, or A and B.

It should be noted that, in the case of no conflict, the embodiments and features in the embodiments of the present disclosure may be combined with each other.

As shown in connection with fig. 1-5, embodiments of the present disclosure provide a stirling cooler including a housing 10, a linear compressor, a hot side heat exchanger 40, a regenerator 60, and a cold side heat exchanger 70. Wherein the housing 10 defines a cavity within which the linear compressor, hot side heat exchanger 40, regenerator 60 and cold side heat exchanger 70 are located.

The linear compressor comprises a magnet 102, a compressor piston 104, an ejector 105, a plate spring and a coil 103, wherein the compressor piston 104, the ejector 105 and the shell 10 jointly form a compressor cavity, the magnet 102 is arranged in the coil 103, and when the coil 103 is electrified with alternating current, the magnet 102 can reciprocate. The magnet 102 is coupled to the compressor piston 104 to effect reciprocating movement of the compressor piston 104 to produce the alternating oscillating gas. The magnet 102 is arranged inside the coil 103, and when the coil 103 is electrified with alternating current, the magnet 102 can perform reciprocating linear motion in the coil 103.

The compressor piston 104 and the discharger 105 do reciprocating linear motion, so that gas working media in the cavity are compressed and expanded, the gas working media form periodic pressure fluctuation, and the final pressure fluctuation is generally close to sine due to the sine of current.

The stirling cooler also includes an outer fin 50, the outer fin 50 being located outside the hot side heat exchanger 40. The gas of alternating oscillation generated by the compressor passes through the hot end heat exchanger 40, heat is discharged from the hot end heat exchanger 40, the hot end heat exchanger 40 cools the high-temperature oscillating gas from the compressor through cooling water or air, and then the heat is conducted to the outside of the refrigerator through the outer fins 50. The cooled oscillating gas enters the heat regenerator 60 to exchange heat with the filler inside the heat regenerator 60, so that the filler and the gas working medium exchange heat fully.

Alternatively, the filler filled inside regenerator 60 is typically a stainless steel wire mesh, metal balls, or the like having a higher specific heat capacity than helium. The pressure loss of gas passing can be reduced while the working medium and the filler are fully heat exchanged.

The gas eventually develops a linear temperature profile in regenerator 60. The working medium comes out of the heat regenerator 60 and enters the cold end heat exchanger 70, and the cooling capacity is provided for the external cooled working medium. The ejector 105 and the cold side heat exchanger 70 form a cavity 202 which plays a role of expansion of the working medium, and simultaneously consumes the expansion work to achieve the refrigeration effect.

In the first half of a period of the oscillating gas, the gas transfers heat to the filler in the heat regenerator 60, the temperature of the gas working medium is reduced, in the second half of the period, the gas absorbs heat from the seasoning in the heat regenerator 60, the temperature of the gas is increased, but because the heat absorbed and released by the gas in the period is unequal, a temperature gradient is finally generated in the axial direction of the heat regenerator 60, so that the cold end heat exchanger 70 connected with the heat regenerator 60 reaches a lower temperature.

The heat absorbed and released by the gas in the regenerator 60 is not equal, and part of the reason is that the cavity 202 between the cold side heat exchanger 70 and the ejector 105 forms an expansion chamber, and the gas transfers the expansion work to the ejector 105 and converts the expansion work into mechanical work to be carried away.

The compressor piston 104 and the housing 10 enclose a back pressure cavity 101, the compressor cavity includes the back pressure cavity 101, the back pressure cavity 101 is located on the back of the compressor piston 104, the plate spring is fixedly arranged in the back pressure cavity 101, and the plate spring is connected with the compressor piston 104.

The number of leaf springs is two, and two leaf springs include first leaf spring 106 and second leaf spring 107, and first leaf spring 106 and second leaf spring 107 set gradually along the direction of keeping away from compressor piston 104.

The gas working medium makes sinusoidal motion in the compressor chamber, passes through the outer heat exchanger, the regenerator 60 and other components, enters the cold end heat exchanger 70, and finally expands in the expansion chamber. It is worth noting that there is no one-way flow of gas from the compression chamber to the expansion chamber, which is always in a reciprocating sinusoidal motion, which can be considered as from the compression chamber to the expansion chamber. The compressor piston 104 realizes the active motion because the permanent magnet 102 is under the action of the electrified silicon steel sheet. The ejector 105 is passively moved by the combined action of the gas in the compression and expansion chambers. The compressor piston 104 is secured to the first plate spring 106 by a support structure for cantilever movement with the first plate spring 106. The ejector 105 is fixed to the second plate spring 107 by a link, and moves with the cantilever of the second plate spring 107.

The compressor piston 104 includes a piston body and a stem that is connected between the piston body and the first plate spring 106. The piston body is driven by the driving force generated by the alternating magnetic field to do linear reciprocating motion. The loop bar is connected between the piston body and the first plate spring 106, and the piston body drives the loop bar to perform linear reciprocating motion. The loop bar carries out linear reciprocating motion, and the loop bar is connected with first leaf spring 106, and the loop bar transmits the drive power of piston body to first leaf spring 106, and first leaf spring 106 produces deformation and absorbs drive power to reduce the vibrations of compressor piston 104.

Optionally, the first plate spring 106 is opened with a first fixing hole, and the loop bar is connected with the first fixing hole.

In some alternative embodiments, the ejector 105 includes an ejector 105 body and a connecting rod, one end of which is connected to the ejector 105 body and the other end of which is connected to the second leaf spring 107 through the compressor piston 104.

With this alternative embodiment, the ejector body performs the linear reciprocating motion, and one end of the connecting rod is connected to the ejector body, so that the ejector 105 drives the connecting rod to perform the linear reciprocating motion. The second plate spring 107 serves to fix the radial movement of the ejector 105 while ensuring its free axial reciprocation. The other end of the link is connected with the second plate spring 107 so that the second plate spring 107 provides a supporting force to the link to provide a supporting force to the ejector body. The second plate spring 107 pushes the ejector 105 through the link and ensures that the linear reciprocating motion of the ejector 105 maintains a phase difference with the motion of the compressor piston 104. The other end of the connecting rod passes through the compressor piston 104 and then is connected with the second plate spring 107, so that the space occupied by the installation of the second plate spring 107 is reduced, and the internal structural layout of the linear compression device is more reasonable.

Optionally, the second plate spring 107 is opened with a second fixing hole, and the connecting rod is connected with the second fixing hole.

The disclosed embodiment provides a linear compressor, as shown in fig. 2 to 4, the linear compressor includes a silencer 20, the silencer 20 is located in a back pressure chamber 101, and the silencer 20 is located on a side of a plate spring away from a compressor piston 104, and is used for absorbing noise generated when a stirling refrigerator operates.

In this embodiment, since the back pressure chamber 101 is located on the back side of the compressor piston 104, and since the back pressure chamber 101 does not participate in the effect of the compressor piston 104 on applying work to the system for refrigeration, the plate spring and the silencer 20 are both disposed in the back pressure chamber 101, which is convenient for placement, and the normal operation of the stirling refrigerator is not affected. The silencing device 20 is located in the back pressure cavity 101, and can absorb the working noise of the linear compressor and the Stirling refrigerator, so that a better silencing effect can be achieved. And set up silencing device 20, need not to change other parts of stirling refrigerator, utilize current back pressure chamber 101 of stirling refrigerator to install silencing device 20, simple structure, the cost is lower, and the effect is showing.

Alternatively, as shown in fig. 3 to 5, the silencer device 20 includes a sound-sensing portion and a sound-containing portion, which are communicated with each other. The sound sensing part and the sound capacity part form a resonance structure to play a role in eliminating noise.

Alternatively, as shown in fig. 5, the muffler device 20 includes a cavity 202 and a porous body 201, and the porous body 201 communicates with the cavity 202 for absorbing noise. In this embodiment, the porous structure is a sound sensing portion, the cavity 202 is a sound capacitance portion, and the porous medium and the cavity act together to perform a sound attenuation function.

Optionally, the resonant frequency of the muffler device 20 is greater than the frequency of noise in the operation of the Stirling cooler. Therefore, the porous medium can well absorb sound, and the performance of the refrigerator is improved.

Optionally, the porous body 201 comprises a conduit and a porous medium (not shown), the conduit being provided at an end of the cavity 202 facing the leaf spring and communicating with the cavity 202. The porous medium is filled in the pipeline.

In this embodiment, the porous medium can absorb noise flowing through the porous body 201, further improving the sound attenuation effect.

Optionally, the porous medium comprises a stainless steel mesh, metal pellets or a PET (Polyethylene terephthalate) Polyethylene terephthalate material. The porous medium of the embodiment has low cost and easy production, and the resonance frequency of the silencer 20 is set to be high, so that most of low-frequency noise generated by the normal operation of the Stirling refrigerator is absorbed, and the aim of silencing is fulfilled. And the porous medium has a substance with higher specific heat capacity, so that the pressure loss of gas passing can be reduced while the gas working medium and the porous medium are ensured to fully exchange heat.

Optionally, the porous medium has a porosity greater than 60%. The porosity is more than 60%, so that the higher the collision probability and the collision frequency after the sound waves enter the porous material, the faster the energy of the sound waves is consumed, and the better the corresponding sound absorption effect is.

Alternatively, as shown in FIG. 5, the conduit and the cavity 202 are each hollow and the cross-sectional area of the conduit is less than the cross-sectional area of the cavity 202, the conduit and the cavity 202 forming a Helmholtz resonance chamber. Optionally, the conduit is an elongate conduit.

Silencing mainly refers to the process of energy consumption in the process of transmission of sound waves in a medium. When the sound wave propagates to the surface of the medium, one part of the sound wave is reflected back, and the other part of the sound wave is absorbed by the medium and converted into mechanical energy for transmission or converted into heat energy for consumption. The silencing phenomenon is ubiquitous, but only materials with strong sound absorption capacity can be applied to practical occasions. The noise elimination principle has two principles, namely, sound energy is converted into heat energy through material friction; secondly, the sound energy is converted into mechanical energy (vibration) through material vibration, and then converted into heat energy. In this embodiment, the helmholtz resonator is a resonant sound absorbing structure. The cavity 202 is a resonance-generating cavity, and the cavity 202 is connected with the outside through a pipe, and sound waves enter the cavity 202 from the pipe, so that air in the pipe moves back and forth to compress air in the cavity 202, and an air spring is formed. When the frequency of the incident sound wave is consistent with the natural frequency of the resonator structure, the generated resonance amplitude is maximum, and the consumed energy is maximum, so that the aim of sound elimination is fulfilled.

The cavity 202 is a closed cavity 202, which can ensure that an air spring can be formed in the cavity 202.

Optionally, the resonant frequency of the muffler device 20 is greater than the operating frequency of the stirling cooler, and since the resonant frequency of the muffler device 20 is set to be higher, most of the noise generated by normal operation of low frequency is absorbed by the muffler device, so as to achieve the purpose of muffling. Thus, the porous medium 201 can achieve a good sound absorption effect, and the performance of the Stirling refrigerator is improved. In practical application, the operating frequency of the Stirling refrigerator is usually 60Hz, the resonant frequency of the silencer 20 is greater than 1kHz and far greater than the operating frequency of the Stirling refrigerator, and the purpose of silencing can be achieved.

Illustratively, the length of the porous body 201 may be 30mm and the inner diameter 40mm, the inner diameter of the cavity 202 100mm and the length of the cavity 202 30mm, such that the acoustic resonance frequency of the acoustic damping device 20 is greater than 1kHz.

Optionally, the silencer 20 is filled with a gas working medium, and the gas working medium may be helium gas or hydrogen gas. This can improve the efficiency of sound absorption. It should be noted that: the gas working medium can also be air. The gas working medium in the silencer 20 is consistent with the gas working medium in the compressor, so that the refrigerating effect of the Stirling refrigerator is improved. For example, when the internal working medium is helium or hydrogen, the gas working medium inside the silencer 20 is also helium or hydrogen.

Optionally, the movement of the gas working medium inside the silencer 20 is sinusoidal, and both the pressure fluctuation and the volume flow are sinusoidal. It should be noted that: the sinusoidal movement described in this application is not strictly sinusoidal and approaches to sinusoidal movement are also possible as alternative embodiments of the present application. Because the alternating current is sinusoidal, the magnetic field that produces is sinusoidal to the gaseous working medium of silencing device 20 inside motion receives Faraday's law of electromagnetic induction influence, and the motion is also sinusoidal, can further improve stirling refrigerator's refrigeration efficiency.

Optionally, the linear compressor further comprises an elastic member connected between the muffler device 20 and the inner wall surface of the back pressure chamber 101.

Here, the silencer 20 has a certain weight, which can be regarded as a weight block, and the weight block and the elastic member form a damping and silencing structure, so that the corresponding overall resonance frequency is increased, thereby deviating from the operating frequency of the refrigerator. The closer the running frequency and the resonant frequency are, the larger the amplitude of the whole machine is; correspondingly, the farther the deviation, the smaller the overall amplitude.

The resonance frequency is equal to the square of the division of the rigidity of the elastic part and the dynamic mass, after the elastic part with large rigidity is selected, the resonance frequency of the damping and noise elimination structure can reach very high and is far away from the frequency of dozens of hertz of operation, in the vibration process of the unit, as the damping and noise elimination structure is connected with the unit, the vibration energy can be transmitted to the damping and noise elimination structure, the damping and noise elimination structure can also generate vibration after absorbing the energy, and the vibration amplitude of the damping and noise elimination structure is very small, so that the aim of damping is achieved. During the work of the Stirling refrigerator, the silencing device 20 and the elastic piece form a damping and silencing structure, so that the damping can be realized through vibration, the silencing can also be realized through the silencing device 20, and a better damping and silencing effect can be achieved.

In one embodiment, as shown in fig. 3 and 4, the linear compressor further includes a support reed 30, and the support reed 30 is connected between the muffler device 20 and an inner wall surface of the back pressure chamber 101. The elastic member is a support spring 30.

In this embodiment, the support spring 30 connects the silencer 20 to the back pressure chamber 101, so that the support spring 30 and the silencer 20 can form a damping and silencing structure, the support spring 30 enables the whole damping and silencing structure to vibrate, and the damping can be realized by adjusting the vibration frequency.

In another embodiment, the elastic member may be a spring, and the spring is connected between the muffler device 20 and the inner wall surface of the back pressure chamber 101, so as to achieve the effect of damping.

In order to reduce the vibration of the whole Stirling refrigerator as much as possible, the resonance frequency of the shock absorption and noise elimination structure is far away from the operating frequency of the Stirling refrigerator.

In practical application, the resonance frequency of the damping and noise elimination structure is more than 1kHz, so that the normal operation frequency of the Stirling refrigerator can be deviated, and the damping and noise elimination effect is realized. For example, stirling cryocoolers typically operate at frequencies ranging from 1Hz to 60Hz. For example, the rigidity of the elastic part can be 100000N/m, the dynamic mass is 0.1kg, and the resonance frequency of the whole machine is greater than 1kHz.

Optionally, the supporting reeds 30 are connected to the outer side wall of the silencer 20, the number of the supporting reeds 30 is multiple, and the supporting reeds 30 are sequentially arranged on the outer side wall of the silencer 20 at intervals along the circumferential direction of the silencer 20.

In this embodiment, the plurality of supporting reeds 30 are disposed at intervals on the outer side wall of the silencer 20, so that the whole damping and silencing structure can be connected in the back pressure cavity 101 along the circumferential direction, and the connection stability in the circumferential direction is increased.

Alternatively, one end of the support reed 30 is connected to the outer side wall of the muffler device 20, and the other end of the support reed 30 is connected to the inner wall surface of the back pressure chamber 101; wherein the other end of the supporting spring 30 extends spirally away from the pipe.

In this embodiment, the support spring 30 extends spirally, which increases the size of the support spring 30 in the circumferential direction, and is convenient for increasing the connection area and stability between the support spring 30 and the cavity wall of the back pressure cavity 101. In addition, the damping effect of the damping and noise elimination structure can be ensured, and the used materials are fewer, so that the materials used for producing the damping and noise elimination structure are reduced, and the production cost is reduced.

Alternatively, the supporting spring 30 has an arc shape, and the width of the supporting spring 30 is gradually reduced in a direction from one end of the supporting spring 30 to the other end of the supporting spring 30.

In this embodiment, the width of the supporting reeds 30 is gradually reduced, so that the distance between the adjacent supporting reeds 30 is increased, and thus, in the movement process of the damping and noise elimination structure, the adjacent supporting reeds 30 do not interfere with each other, and it can be ensured that the supporting reeds 30 have enough space to move, so as to improve the damping effect. Similarly, the width of one end of the supporting reed 30 is larger, so that the strength of the supporting reed 30 can be ensured, and the connection stability of the damping and noise elimination structure and the cavity wall of the back pressure cavity 101 is improved.

Alternatively, each support spring 30 is crescent-shaped.

Optionally, the supporting spring 30 includes a plurality of concentric arc segments and/or eccentric arc segments connected in sequence, and the concentric arc segments and/or eccentric arc segments increase in sequence from one end of the supporting spring 30 to the other end of the supporting spring 30.

By adopting the optional embodiment, the concentric arc section and/or the eccentric arc section is sequentially enlarged from one end of the supporting reed 30 to the other end of the supporting reed 30, so that each supporting reed 30 extends spirally, the stress of each supporting reed 30 is reasonable, each supporting reed 30 is not easy to break, and the reliability and the service life of the damping and noise elimination structure are improved.

Optionally, the number of the concentric arc segments and/or the eccentric arc segments can be adjusted according to the practical application of the shock-absorbing and noise-eliminating structure.

Optionally, a support spring 30 is provided on the outer side wall of the porous body 201. Because the cross-sectional area of porous main part 201 is less than the cross-sectional area of cavity 202, support reed 30 locates the lateral wall of porous main part 201, can increase the radial and circumferential size of support reed 30, so not only can increase the stability of being connected of the chamber wall of shock attenuation noise cancelling structure and backpressure chamber 101, can also increase the frequency range of the resonant frequency of shock attenuation noise cancelling structure, be convenient for adjust the resonant frequency of shock attenuation noise cancelling structure, and then realize best shock attenuation effect.

Optionally, the support spring 30 is of unitary construction with the muffler device 20. In this embodiment, the supporting spring 30 and the silencing device 20 are integrally formed, so that the structural stability of the damping and silencing structure can be improved, and the service life of the damping and silencing structure can be prolonged.

Optionally, the cavity 202 and the porous body 201 are made of stainless steel, aluminum or other metal materials, and the metal cavity has high capacitance.

Alternatively, the supporting spring 30 is a thin sheet of metal, and the material may be stainless steel, metal, or the like.

It can be understood that: the shell of the silencing device 20 and the supporting spring plates 30 made of the materials can increase the strength of the shock-absorbing and noise-eliminating structure, so that the service life of the shock-absorbing and noise-eliminating structure is ensured.

Alternatively, the supporting spring 30 is fixedly connected to the wall of the back pressure chamber 101, for example, by welding. Therefore, the connection stability of the shock absorption and noise elimination structure can be further improved, and the stability of movement is ensured.

Embodiments of the present disclosure also provide a stirling cooler comprising the linear compressor of any one of the embodiments described above.

The stirling cryocooler provided by the embodiment of the present disclosure includes any one of the linear compressors, so that the stirling cryocooler has the beneficial effects of any one of the linear compressors, and details are not repeated herein.

The above description and drawings sufficiently illustrate embodiments of the disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The examples merely typify possible variations. Individual components and functions are optional unless explicitly required, and the sequence of operations may vary. Portions and features of some embodiments may be included in or substituted for those of others. The embodiments of the present disclosure are not limited to the structures that have been described above and shown in the drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims (10)

1. A linear compressor, characterized by comprising:

a housing defining a compressor cavity;

the compressor piston is movably positioned in the compressor cavity and encloses a back pressure cavity with the shell, and the compressor cavity comprises the back pressure cavity;

the plate spring is connected with the compressor piston and is positioned in the back pressure cavity;

and the silencing device is positioned in the back pressure cavity and on one side of the plate spring, which deviates from the compressor piston, and is used for absorbing noise.

2. The linear compressor of claim 1, wherein the muffler device comprises:

a cavity;

and the porous body is communicated with the cavity and is used for absorbing noise.

3. The linear compressor of claim 2, wherein the porous body comprises:

the pipeline is arranged at one end, facing the plate spring, of the cavity and communicated with the cavity;

and the porous medium is filled in the pipeline.

4. Linear compressor according to claim 3,

the cross-sectional area of the cavity is greater than the cross-sectional area of the conduit such that the cavity and the conduit form a helmholtz resonator.

5. The linear compressor of any one of claims 1 to 4, further comprising:

and the support reed is connected between the silencing device and the inner wall surface of the back pressure cavity.

6. Linear compressor according to claim 5,

the number of the supporting reeds is multiple, and the supporting reeds are sequentially arranged on the outer side wall of the silencing device at intervals along the circumferential direction of the silencing device.

7. Linear compressor according to claim 6,

one end of the supporting reed is connected with the outer side wall of the silencing device, and the other end of the supporting reed is connected with the inner wall surface of the back pressure cavity;

wherein the other end of the support reed extends spirally towards the direction far away from the silencer.

8. Linear compressor according to claim 7,

the support spring is arc-shaped, and the width of the support spring is gradually reduced along the direction from the one end of the support spring to the other end of the support spring.

9. Linear compressor according to claim 5,

the support reed and the silencing device are of an integrated structure.

10. A stirling cooler, comprising a linear compressor according to any one of claims 1 to 9.

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