CN105298801A - Linear compressor - Google Patents
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- CN105298801A CN105298801A CN201510272331.5A CN201510272331A CN105298801A CN 105298801 A CN105298801 A CN 105298801A CN 201510272331 A CN201510272331 A CN 201510272331A CN 105298801 A CN105298801 A CN 105298801A
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- cylinder barrel
- refrigeration agent
- framework
- sealed member
- rake
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Abstract
The invention provides a linear compressor. The linear compressor can enable a gas bearing to easily work between a cylinder and a piston of the linear compressor. The linear compressor comprises a housing, a cylinder, a framework, a piston, an exhaust valve, a flow space part, a sealing recess and a sealing part, wherein the housing is provided with a suction part; the cylinder is arranged in the housing and form the compression space for a refrigerating fluid; the framework is combined with the outside of the cylinder; the piston can perform reciprocating motion in the axial direction in the cylinder; the exhaust valve is arranged at one side of the cylinder, and selectively exhausts the refrigerating fluid compressed in the compression space; the flow space part is formed between the cylinder and the framework, and enables at least part of the exhausted refrigerating fluid to flow; the sealing recess communicates with the flow space part; and the sealing part is arranged in the sealing recess movably, and can seal the separated space between the framework and the cylinder.
Description
Technical field
The present invention relates to Linearkompressor (linearcompressor).
Background technique
Cooling system is the system of instigating refrigerant circulation and producing cold air, repeatedly performs the compression of refrigeration agent, condensation, expansion and evaporation process.For this reason, described cooling system comprises compressor, condenser, expansion gear and vaporizer.Described cooling system can be arranged on as in the refrigerator of household appliances or air conditioner.
Generally speaking, compressor (Compressor) receives power from the power generation arrangement such as electric motor or turbo machine to compress air or refrigeration agent or other various working gass and improve the mechanical device of pressure, is widely used in described household appliances or whole industry.
This compressor can be roughly divided into: between piston (Piston) and cylinder barrel (Cylinder), be formed with the compression volume sucking, discharge working gas, and the reciprocating compressor (Reciprocatingcompressor) that piston compresses refrigeration agent while straight reciprocating motion is carried out in cylinder barrel inside; The compression volume sucking, discharge working gas is formed between the roller (Roller) and cylinder barrel of eccentric rotary, and to the rotary compressor (Rotarycompressor) that refrigeration agent compresses while roller carries out eccentric rotary along inner wall of cylinder; And be formed with the compression volume sucking, discharge working gas between revolution scroll (Orbitingscroll) and fixed scroll (Fixedscroll), and to the scroll compressor (Scrollcompressor) that refrigeration agent compresses while described revolution scroll carries out rotating along fixed scroll.
Recently, in described reciprocating compressor, especially have developed a lot of Linearkompressor, this Linearkompressor makes piston directly be connected with the drive motor carrying out linear reciprocating motion, thus do not produce the mechanicalness loss caused by motion conversion, can compression efficiency be improved, and be configured to simple structure.
Usually, Linearkompressor is configured to the enclosure interior closed, and piston sucks refrigeration agent by linear motor and compressed rear discharge while cylinder barrel inside is with the mode movement of linear reciprocating motion.
Described linear motor is configured to permanent magnet between inner stator and external stator, and permanent magnet is configured to carry out straight reciprocating motion by the mutual electromagnetic force between permanent magnet and interior (or outer) stator.And along with described permanent magnet drives under the state linked with piston, piston sucks refrigeration agent and discharge after compress while linear reciprocating motion is carried out in cylinder barrel inside.
About Linearkompressor in the past, the applicant had once applied for patent (hereinafter referred to as existing document) and had obtained mandate.
Existing document 1: No. 10-1307688, Korean patent No., authorizes day: on September 5th, 2013, denomination of invention: Linearkompressor
Linearkompressor disclosed in above-mentioned existing document comprises the housing 110 holding multiple part.The height of the above-below direction of described housing 110, as shown in Fig. 2 of existing document, is formed high a little.
And possessing in the inside of described housing 110 can to the fuel feeding assembly 900 for oil supply between cylinder barrel 200 and piston 300.
In addition, when linear compressor application in refrigerator, described Linearkompressor can be arranged on the machine room on the downside of the rear being positioned at refrigerator.
Recently, the internal storage space of increase refrigerator becomes the problem that Consumer mainly pays close attention to.In order to increase the internal storage space of described refrigerator, need the volume reducing described machine room, in order to reduce the volume of described machine room and the size reducing described Linearkompressor becomes major subjects.
But the Linearkompressor disclosed in existing document occupies relatively large volume, exist and be not suitable for the problem being applied to the refrigerator that will increase internal storage space.
Need the major part of compressor to make small size to reduce the size of described Linearkompressor, but likely produce the problem of the degradation of the penalty of compressor in the case.
In order to solve the problem of the degradation of described compressor, the operation frequency increasing compressor can be considered.But the operation frequency of compressor is higher, the frictional force caused by oil being circulated in compressor inside is larger, occurs the problem that the performance of compressor reduces.
Summary of the invention
The present invention proposes for addressing this is that, and its object is to provides a kind of Linearkompressor that gas bearing can be made easily to work between the cylinder barrel and piston of Linearkompressor.
The Linearkompressor of one embodiment of the invention comprises: housing, and it is provided with sucting; Cylinder barrel, it is positioned at the inside of described housing, forms the compression volume of refrigeration agent; Framework, it is combined with the outside of described cylinder barrel; Piston, it is arranged in the mode that can move back and forth vertically in the inside of described cylinder barrel; Expulsion valve, it is positioned at the side of described cylinder barrel, discharges compression volume at described refrigeration agent selectively by the refrigeration agent compressed; Flowing space portion, it is formed between described cylinder barrel and described framework, for the flow of refrigerant at least partially in the refrigeration agent of being discharged by described expulsion valve; Sealing recess, it is communicated with described flowing space portion; And sealed member, it, the mode of movement can be arranged at described sealing recess, is closed the space of separating between described framework and described cylinder barrel.
Further, it is characterized in that, the radial direction height of described sealing recess is greater than the diameter of described sealed member.
Further, it is characterized in that, the axial length of described sealing recess is greater than the diameter of described sealed member.
Further, it is characterized in that, with the flow direction of described refrigeration agent for benchmark, the flow section of described sealing recess is greater than the flow section in described flowing space portion.
Further, it is characterized in that, described sealing recess is formed between the outer circumferential face of described cylinder barrel and the inner peripheral surface of described framework.
Further, described framework comprises recess forming portion, and this recess forming portion forms at least one side of described sealing recess, from the inner peripheral surface radial direction depression laterally of described framework.
Further, described cylinder barrel comprises the first rake, and this first rake is formed in the position corresponding with described recess forming portion, and the direction that the external diameter to described cylinder barrel reduces extends.
Further, it is characterized in that, described sealed member moves along described first rake.
Further, described framework comprises the second rake, this second rake from described recess forming portion to inward side to extending obliquely.
Further, also comprise spray nozzle part, this spray nozzle part is formed at the outer circumferential face of described cylinder barrel, the inner peripheral surface side of the refrigeration agent in described flowing space portion to described cylinder barrel is guided.
The feature of the Linearkompressor of another embodiment of the present invention is, comprising: housing, and it is provided with sucting; Cylinder barrel, it is positioned at the inside of described housing, forms the compression volume of refrigeration agent; Framework, it surrounds the outside of described cylinder barrel; Piston, it is arranged in the mode that can move back and forth vertically in the inside of described cylinder barrel; Expulsion valve, it is positioned at the side of described cylinder barrel, discharges compression volume at described refrigeration agent selectively by the refrigeration agent compressed; Flowing space portion, it is formed between the outer circumferential face of described cylinder barrel and the inner peripheral surface of described framework, flows for from the part of refrigerant the refrigeration agent that described expulsion valve is discharged; And sealing recess, it has the sectional area larger than described flowing space portion, is provided with sealed member.When the refrigeration agent in described flowing space portion acts on described sealed member, described sealed member moves to the position sealed the space between described framework and described cylinder barrel.
Further, it is characterized in that, when the refrigeration agent in described flowing space portion does not act on described sealed member, described sealed member is to not moving the position that the space between described framework and described cylinder barrel seals.
Further, described sealing recess comprises: recess forming portion, and its inner peripheral surface from described framework caves in; And first rake, it is formed at the outer circumferential face of described cylinder barrel.
And, it is characterized in that, described framework comprises the second rake extended obliquely from described recess forming portion, when the refrigeration agent in described flowing space portion acts on described sealed member, described sealed member moves to the position sealed the space of separating between described first rake and described second rake.
The present invention has following beneficial effect:
According to above-mentioned the present invention, the size of the compressor comprising inner body can be reduced, thus the size of the machine room of refrigerator can be reduced, therefore there is the advantage of the internal storage space that can increase refrigerator.
Further, by increasing the operation frequency of compressor, can preventing from causing performance to reduce because of diminishing of inner body, in addition, by applying gas bearing between cylinder barrel and piston, there is the advantage that can reduce the frictional force that oil produces.
And, so that the mode of movement sealed member for sealing the re-frigerant flowing spaces between cylinder barrel and framework can be arranged, described sealed member utilizes the pressure of refrigeration agent to seal the interval between cylinder barrel and framework in compressor operating process, thus can improve functional reliability.
And the recess of configuration sealed member is greater than described sealed member, thus enables described sealed member move, there is the advantage that sealed member can be utilized to reduce to put on the size of the power of framework or cylinder barrel.Therefore, it is possible to prevent the cylinder barrel be made up of aluminium material from deforming.
Further, according to the structure of described recess, can reduce the interference caused by sealed member when assembling cylinder barrel and framework, therefore, the assembling with cylinder barrel and framework becomes easy effect.
Further, possess multiple filtrating equipment in the inside of compressor, thus there is the advantage that can prevent comprising foreign matter or oil component in the pressurized gas (or Exhaust Gas) of the outer side inflow of piston from the nozzle of cylinder barrel.
Especially, absorbing silencer possesses the first filter, thus can prevent the foreign matter comprised in refrigeration agent from flowing into pressing chamber, and possess the second filter in the connecting part of cylinder barrel and framework, thus can prevent by the refrigerant gas that compresses the foreign matter that comprises or oil component flow to the gas inflow part of cylinder barrel.
And the gas inflow part of cylinder barrel possesses the 3rd filter, can prevent foreign matter or oil component from flowing into the nozzle of cylinder barrel from described gas inflow part.
As mentioned above, utilize multiple filtrating equipments that compressor and exsiccator possess, the foreign matter that can comprise the pressurized gas worked as bearing or oil component filter, therefore, it is possible to prevent the phenomenon that the spray nozzle part causing cylinder barrel because of foreign matter or oil component blocks.
By the phenomenon preventing the spray nozzle part of described cylinder barrel from blocking, between cylinder barrel and piston, the effect of gas bearing effectively can be realized, therefore, it is possible to prevent the wearing and tearing of cylinder barrel and piston.
Accompanying drawing explanation
Fig. 1 is the sectional view of the structure of the Linearkompressor representing the embodiment of the present invention.
Fig. 2 is the sectional view of the structure of the absorbing silencer representing the embodiment of the present invention.
Fig. 3 is the sectional view being configured with the state of the second filter representing the embodiment of the present invention.
Fig. 4 is the exploded perspective view representing the cylinder barrel of the embodiment of the present invention and the structure of framework.
Fig. 5 is the sectional view representing the cylinder barrel of the embodiment of the present invention and the bonding state of piston.
Fig. 6 is the exploded perspective view of the structure of the cylinder barrel representing the embodiment of the present invention.
The figure that Fig. 7 amplifies Fig. 5 " A ".
Fig. 8 is the sectional view representing the cylinder barrel of the embodiment of the present invention and the bonding state of framework.
The figure that Fig. 9 amplifies Fig. 8 " B ".
Figure 10 is the sectional view of the flow of refrigerant state of the Linearkompressor representing the embodiment of the present invention.
Figure 11 is the figure of the mobile status of sealed member when representing that the Linearkompressor of the embodiment of the present invention drives.
Embodiment
Hereinafter, with reference to the accompanying drawings of specific embodiments of the invention.It should be noted that, technological thought of the present invention is not limited to the disclosed embodiments, and the those skilled in the art understanding technological thought of the present invention can easily propose other embodiments at identical technological thought range content.
Fig. 1 is the sectional view of the structure of the Linearkompressor representing the embodiment of the present invention.
With reference to Fig. 1, the Linearkompressor 100 of the embodiment of the present invention comprises: the housing 101 of substantially cylindrical shape, be combined with the side of described housing 101 first cover 102, be combined with the opposite side of described housing 101 second cover 103.As an example, described Linearkompressor 100 is transversely placed, and described first cover 102 is combined with the right side of described housing 101, and described second cover 103 is combined with the left side of described housing 101.
Just in the broadest sense, described first cover 102 and the second cover 103 can be understood as a structure of described housing 101.
Described Linearkompressor 100 comprises: be arranged on the cylinder barrel 120 of the inside of described housing 101, carry out the piston 130 of linear reciprocating motion in the inside of described cylinder barrel 120 and described piston 130 provided to the motor sub-assembly 140 as linear motor of driving force.
When described motor sub-assembly 140 drives, described piston 130 can to move back and forth at a high speed.Operation frequency according to the Linearkompressor 100 of the present embodiment is roughly 100Hz.
Specifically, described Linearkompressor 100 comprises: the sucting 104 that refrigeration agent is flowed into and making in the inside of described cylinder barrel 120 by the discharge portion 105 that the refrigeration agent that compresses is discharged.Described sucting 104 and described first covers 102 and is combined, and described discharge portion 105 and described second is covered 103 and is combined.
The refrigeration agent sucked by described sucting 104 flow to the inside of described piston 130 via absorbing silencer 150.Noise can be reduced in the process of described absorbing silencer 150 at refrigeration agent.Described absorbing silencer 150 is bonded by the first baffler 151 and the second baffler 153.The inside being positioned at described piston 130 at least partially of described absorbing silencer 150.
The piston main body 131 that described piston 130 comprises substantially cylindrical shape and the piston flange portion 132 radially extended from described piston main body 131.Described piston main body 131 moves back and forth in the inside of described cylinder barrel 120, and described piston flange portion 132 moves back and forth in the outside of described cylinder barrel 120.
Described piston 130 can be made up of the aluminium material (aluminum or aluminum alloy) as nonmagnetic material.Because described piston 130 is made up of aluminium material, therefore, it is possible to the magnetic flux preventing described motor sub-assembly 140 from producing is delivered to described piston 130 and the phenomenon of External leakage to described piston 130.Described piston 130 can utilize forging method to be formed.
In addition, described cylinder barrel 120 can be made up of the aluminium material (aluminum or aluminum alloy) as nonmagnetic material.The material constituent ratio of described cylinder barrel 120 and piston 130 and kind and composition ratio can be identical.
Because described cylinder barrel 120 is made up of aluminium material, therefore, it is possible to the magnetic flux preventing described motor sub-assembly 140 from producing is delivered to described cylinder barrel 120 and the phenomenon of External leakage to described cylinder barrel 120.And described cylinder barrel 120 can utilize extruded rod processing method to be formed.
And because described piston 130 is made up of identical material (aluminium) with cylinder barrel 120, therefore thermal expansion coefficient is mutually the same.At Linearkompressor 100 run duration, described housing 100 inside forms high temperature (about 100 DEG C) environment, because described piston 130 is identical with the thermal expansion coefficient of cylinder barrel 120, therefore described piston 130 can be out of shape with identical volume production heat-dissipating with cylinder barrel 120.
Its result, can prevent from piston 130 and cylinder barrel 120 from producing thermal distortion with size different from each other or direction and produce with described cylinder barrel 120 between piston 130 moving period interfering.
Described cylinder barrel 120 be configured to hold described absorbing silencer 150 at least partially with described piston 130 at least partially.
The compression volume P utilizing described piston 130 pairs of refrigeration agents to compress is formed in the inside of described cylinder barrel 120.And, be formed with the inlet hole 133 making refrigeration agent flow into described compression volume P at the front part of described piston 130, be provided with the suction valve 135 opening described inlet hole 133 selectively in the front of described inlet hole 133.The joining hole be combined with the bonded block of regulation is formed in the substantially central portion of described suction valve 135.
Be provided with in the front of described compression volume P: form the discharge space of refrigeration agent or the discharge cover 160 of discharge duct of discharging from described compression volume P and to be combined with described discharge cover 160 and for discharging selectively at described compression volume P by the discharge valve assembly 161,162,163 of refrigeration agent compressed.
Described discharge valve assembly 161,162,163 comprises: when time more than the pressure of described compression volume P is for head pressure open and make refrigeration agent flow into the discharge space of described discharge cover 160 expulsion valve 161, be arranged on described expulsion valve 161 and discharge between cover 160 and the limiting component 163 valve spring 162 of elastic force being provided vertically and the amount of deformation of described valve spring 162 is limited.
At this, described compression volume P can be understood as the space be formed between described suction valve 135 and described expulsion valve 161.And described suction valve 135 is formed in the side of described compression volume P, described expulsion valve 161 is arranged on the opposite side of described compression volume P and the opposition side of described suction valve 135.
Described " axis " can be understood as the transverse direction in the direction and Fig. 3 that described piston 130 moves back and forth.Be defined as in described " axis " in " front " towards the described direction of discharge portion 105 and the direction of flow of refrigerant from described sucting 104, its opposite direction is defined as at " rear ".
On the contrary, so-called " radial direction " can be understood as the longitudinal direction in the direction vertical with the direction that described piston 130 moves back and forth and Fig. 1.
Described limiting component 163 is arranged on described discharge cover 160, and described valve spring 162 is arranged on the rear of described limiting component 163.And described expulsion valve 161 is combined with described valve spring 162, the rear quadrate part of described expulsion valve 161 or the back side are configured to be supported by the front surface of described cylinder barrel 120.
As an example, described valve spring 162 can comprise leaf spring (platespring).
Described piston 130 carries out in the process of linear reciprocating motion in the inside of described cylinder barrel 120, when the pressure of described compression volume P is lower than described head pressure and below suction pressure, described suction valve 135 is opened, thus refrigeration agent is inhaled into described compression volume P.On the contrary, when the pressure of described compression volume P becomes more than suction pressure described above, under the state that described suction valve 135 cuts out, the refrigeration agent of described compression volume P is compressed.
In addition, when the pressure of described compression volume P becomes more than described head pressure, described valve spring 162 deforms and described expulsion valve 161 is opened, and refrigeration agent is discharged from described compression volume P, is discharged to the discharge space of discharging cover 160.
Then, ring pipe 165 is flow at the refrigeration agent of the discharge spatial flow of described discharge cover 160.Described ring pipe 165 is combined with described discharge cover 160 and extends to described discharge portion 105, and the compressed refrigerant in described discharge space is guided to described discharge portion 105.As an example, described ring pipe 165 has the shape along prescribed direction winding, and spirally (round) extends, and is combined with described discharge portion 105.
Described Linearkompressor 100 also comprises the framework 110 be combined with the outside of described cylinder barrel 120.Described framework 110 is the structures for fixing described cylinder barrel 120, and other bonded block can be utilized to be combined with described cylinder barrel 200.Described framework 110 is configured to surround described cylinder barrel 120.That is, described cylinder barrel 120 can be configured to the inner side being contained in described framework 110.And described discharge cover 160 can be combined with the front surface of described framework 110.
In addition, the gas refrigerant at least partially in the high-pressure gas refrigerant of being discharged by the expulsion valve 161 opened, the segment space that can be combined with framework 110 via described cylinder barrel 120, the outer circumferential face effluent to described cylinder barrel 120 moves.
And refrigeration agent (flow into the inside of described cylinder barrel 120 via the gas inflow part 122 be formed on described cylinder barrel 120 with reference to Fig. 7 and spray nozzle part 123 (with reference to Fig. 7).The flow of refrigerant flowed into, to the space between described piston 130 and cylinder barrel 120, can make the outer circumferential face of described piston 130 separate from the inner peripheral surface of described cylinder barrel 120.Therefore, the refrigeration agent of described inflow can play the function of " gas bearing " for reducing the friction that described piston 130 produces with cylinder barrel 120 during moving back and forth.
Described motor sub-assembly 140 comprises: to be fixed on described framework 110 and be configured to surround described cylinder barrel 120 external stator 141,143,145, to the internal separation of described external stator 141,143,145 and the inner stator 148 configured and the permanent magnet 146 in described external stator 141, space between 143,145 and inner stator 148.
Described permanent magnet 146 can utilize and mutual electromagnetic force between described external stator 141,143,145 and inner stator 148 carries out straight reciprocating motion.And described permanent magnet 146 can be made up of the single magnet with a magnetic pole, or be combined by multiple magnet with three magnetic poles and form.
Described permanent magnet 146 can utilize connecting member 138 to be combined with described piston 130.Specifically, described connecting member 138 to be combined with described piston flange portion 132 and to extend towards the bending of described permanent magnet 146.Along with described permanent magnet 146 moves back and forth, described piston 130 can move back and forth vertically together with described permanent magnet 146.
And described motor sub-assembly 140 also comprises the fixed component 147 for being fixed on by described permanent magnet 146 on described connecting member 138.Described fixed component 147 can be mixed with resin (resin) and form by glass fibre or carbon fiber.Described fixed component 147 is arranged to the inner side and the outside that surround described permanent magnet 146, can maintain the bonding state of described permanent magnet 146 and described connecting member 138 securely.
Described external stator 141,143,145 comprises coil winding 143, and 145 and stator core 141.
The coil 145 that described coil winding 143,145 comprises coil carrier 143 and reels along the circumferencial direction of described coil carrier 143.The cross section of described coil 145 can be polygonal shape, can be hexagonal shape as an example.
Described stator core 141 is along the circumferential direction stacked and form by multiple lamination (lamination), and is configured to surround described coil winding 143,145.
The side of described external stator 141,143,145 is provided with stator case 149.One sidepiece of described external stator 141,143,145 is supported by described framework 110, and the other side is supported by described stator case 149.
Described inner stator 148 is fixed on the periphery of described framework 110.And described inner stator 148 is along the circumferential direction stacked and form in the outside of described framework 110 by multiple lamination.
The back cover 170 that described Linearkompressor 100 also comprises the support 137 for supporting described piston 130 and is combined with described support 137 elasticity.
Described support 137 utilizes the bonded block of regulation to be combined with described piston flange portion 132 and described connecting member 138.
The front of covering 170 is in the rear combined with suction guide portion 155.Described suction guide portion 155 is guided to make the mode being flowed into described absorbing silencer 150 by the refrigeration agent of described sucting 104 suction.
The mode that described Linearkompressor 100 comprises making described piston 130 carry out resonance motion have adjusted multiple springs 176 of each natural frequency.
Described multiple spring 176 comprises the first spring be supported between described support 137 and stator case 149 and the second spring be supported between described support 137 and back cover 170.
Described Linearkompressor 100 also comprises the both sides that are arranged on described housing 101 and makes the leaf spring 172,174 that the inner body of described compressor 100 is supported by described housing 101.
Described leaf spring 172,174 comprises and to cover 102 the first leaf springs 172 be combined with described first and cover 103 the second leaf springs 174 be combined with described second.Can be configured to as an example, described first leaf spring 172 is inserted into described housing 101 and first and covers 102 parts be combined, and described second leaf spring 174 is inserted into described housing 101 and second and covers 103 parts be combined.
Fig. 2 is the sectional view of the structure of the absorbing silencer representing the embodiment of the present invention.
With reference to Fig. 2, the first filter 310 that the absorbing silencer 150 of the embodiment of the present invention comprises the first baffler 151, the second baffler 153 be combined with described first baffler 151 and supported by described first baffler 151 and the second baffler 153.
Described first baffler 151 and the second baffler 153 are formed with the flowing space portion for flow of refrigerant therein.Specifically, described first baffler 151 discharge portion 105 direction described in side direction in described sucting 104 extends, the inside extending to described suction guide portion 155 at least partially of described first baffler 151.And described second baffler 153 extends to the inside of described piston main body 131 from described first baffler 151.
Described first filter 310 can be understood as and is arranged on described flowing space portion and the structure of filtering foreign matter.Described first filter 310 is made up of the magnetic material of tool, easily filters the foreign matter comprised in refrigeration agent especially metal dirt.
As an example, described first filter 310 is made up of stainless steel (stainlesssteel) material, has the magnetic of regulation, can prevent phenomenon of getting rusty.
Can be configured to as another example, described first filter 310 applies the magnetic material of tool, or at the surface attachment magnet of described first filter 310.
Described first filter 310 by netted (mesh) type constitution with multiple filtering hole, can have roughly discoid shape.And described filtering hole can have diameter or the width of below prescribed level.As an example, described prescribed level can be about 25 μm.
Described first baffler 151 and the second baffler 153 can utilize press mode to assemble.And described first filter 310 can be inserted into the pressing part of described first baffler 151 and the second baffler 153 and assemble.
As an example, the side in described first baffler 151 and the second baffler 153 is formed with groove portion, and on the opposing party, comprises the jut inserting described groove portion.
Under the state of the both sides of described first filter 310 between described groove portion and jut, described first filter 310 is supported by first, second baffler 151,153 described.
Specifically, under the state of described first filter 310 between first, second baffler 151,153 described, when described first baffler 151 and the second baffler 153 move to direction close to each other and are pressed into, the both sides of described first filter 310 are inserted between described groove portion and jut and are fixed.
As mentioned above, by arranging the first filter 310 on described absorbing silencer 150, to foreign matter more than prescribed level in the refrigeration agent sucked via described sucting 104, described first filter 310 can be utilized to filter, thus can prevent from playing in the refrigeration agent of function as the gas bearing between piston 130 and cylinder barrel 120 comprising foreign matter and flowing in described cylinder barrel 120.
Further, because described first filter 310 is securely fixed in the pressing part of first, second baffler 151,153 described, therefore, it is possible to prevent the phenomenon be separated from described absorbing silencer 150.
Fig. 3 is the sectional view being configured with the state of the second filter representing the embodiment of the present invention, and Fig. 4 is the exploded perspective view representing the cylinder barrel of the embodiment of the present invention and the structure of framework.
With reference to Fig. 3 and Fig. 4, the Linearkompressor 100 of the embodiment of the present invention is comprised and to be arranged between framework 110 and cylinder barrel 120 and the second filter 320 for filtering the high-pressure gas refrigerant of being discharged by expulsion valve 161.
Described second filter 320 can be positioned at the part or junction plane that described framework 110 is combined with cylinder barrel 120.
Specifically, the described cylinder barrel 120 cylinder barrel main body 121 that comprises substantially cylindrical shape and the cylinder barrel flange part 125 that radially extends from described cylinder barrel main body 121.
Described cylinder barrel main body 121 comprises the gas inflow part 122 that discharged gas refrigerant flows into.Described gas inflow part 122 can be formed as outer circumferential face along described cylinder barrel main body 121 with the shaped depressions of circular.
And described gas inflow part 122 can be provided with multiple.Multiple gas inflow part 122 comprises gas inflow part 122a, the 122b (with reference to Fig. 6) that are positioned at and are close to a side position from the axial centre portion of described cylinder barrel main body 121 and is positioned at the gas inflow part 122c (with reference to Fig. 6) being close to opposite side position from described axial centre portion.
Described cylinder barrel flange part 125 possesses and the connecting part 126 that described framework 110 is combined.Described connecting part 126 can be configured to externally give prominence in direction from the outer circumferential face of described cylinder barrel flange part 125.Described connecting part 126 can utilize the bonded block of regulation to be combined with the cylinder barrel joining hole 118 of described framework 110.
Described cylinder barrel flange part 125 comprises the attachment face 127 be arranged on described framework 110.Described attachment face 127 can be the back part of the cylinder barrel flange part 125 radially extended from described cylinder barrel main body 121.
Described framework 110 comprises: surround described cylinder barrel main body 121 chassis body 111 and along described chassis body 111 extend radially and with the cover connecting part 115 that described discharge cover 160 is combined.
The multiple cover joining hole 116 inserted for the bonded block be combined with described discharge cover 160 and the multiple cylinder barrel joining holes 118 inserted for the bonded block be combined with described cylinder barrel flange part 125 are formed in described cover connecting part 115.Described cylinder barrel joining hole 118 is formed in the position of caving in a little from described cover connecting part 115.
Described framework 110 possesses the recess 117 rearward caving in from described cover connecting part 115 and supply the insertion of described cylinder barrel flange part 125.That is, described recess 117 can be configured to the outer circumferential face surrounding described cylinder barrel flange part 125.The degree of depth of the depression of described recess 117 can be corresponding with the front and back width of described cylinder barrel flange part 125.
The re-frigerant flowing spaces of regulation can be formed between the inner peripheral surface and the outer circumferential face of described cylinder barrel flange part 125 of described recess 117.The high-pressure gas refrigerant of discharging from described expulsion valve 161 via described re-frigerant flowing spaces, and flows towards the outer circumferential face of described cylinder barrel main body 121.Described second filter 320 is arranged in described re-frigerant flowing spaces, can filter refrigeration agent.
Specifically, be formed with step-like assembly department in the rearward end of described recess 117, the second filter 320 of annular can be installed at described assembly department.
Under the state that described assembly department is installed described second filter 320, when described cylinder barrel 120 and described framework 110 in conjunction with time, described cylinder barrel flange part 125 is from described second filter 320 of front pushing of described second filter 320.That is, described second filter 320 can be fixed between the assembly department of described framework 110 and the attachment face 127 of described cylinder barrel flange part 125.
Described second filter 320 can be configured to, and the foreign matter that can cut through in the high-pressure gas refrigerant of expulsion valve 161 discharge of opening flows into the gas inflow part 122 of described cylinder barrel 120, the oil component comprised in adsorption refrigerating agent.
As an example, described second filter 320 can comprise the nonwovens or absorption cloth that are made up of PET (PolyethyleneTerephthalate, PETG) fiber.Described PET has the advantage of heat resistance and mechanical strength.And, the foreign matter of in refrigeration agent more than 2 μm can be cut off.
Have passed through the high-pressure gas refrigerant of the flowing space between the inner peripheral surface of described recess 117 and the outer circumferential face of described cylinder barrel flange part 125 through described second filter 320, refrigeration agent is filtered in the process.
Described Linearkompressor 100 also comprises sealed member 200, and sealing parts 200, between the outer circumferential face and the inner peripheral surface of described chassis body 111 of described cylinder barrel main body 121, seal the space between described cylinder barrel 120 and framework 110.Between the outer circumferential face and the inner peripheral surface of described chassis body 111 of described cylinder barrel main body 121, be formed with the sealing recess 220 (with reference to Fig. 9) for holding described sealed member 200.
Described sealed member 200 can have ring-shaped (O shape circle).
Described sealed member 200 can configure in the mode of surrounding the first rake 128 periphery being positioned at the rear quadrate part of described cylinder barrel main body 121, and can move along described first rake 128.
Fig. 5 is the sectional view representing the cylinder barrel of the embodiment of the present invention and the bonding state of piston, and Fig. 6 is the figure that the figure of the structure of the cylinder barrel representing the embodiment of the present invention, Fig. 7 amplify Fig. 5 " A ".
With reference to Fig. 5 to Fig. 7, the cylinder barrel 120 of the embodiment of the present invention comprises: have substantially cylindrical shape and the cylinder barrel main body 121 forming the first body end 121a and the second body end 121b and the cylinder barrel flange part 125 extended from the second body end 121b of described cylinder barrel main body 121 to radial outside.
Described first body end 121a and the second body end 121b is with the both side ends of axial centre portion 121c described cylinder barrel main body 121 for benchmark is formed of described cylinder barrel main body 121.Described first body end 121a specifies the rear end of described cylinder barrel main body 121, and described second body end 121b specifies the front ends of described cylinder barrel main body 121.
Described cylinder barrel main body 121 is formed the multiple gas inflow part 122 for the flow of refrigerant at least partially in the high-pressure gas refrigerant of being discharged by described expulsion valve 161.The 3rd filter 330 as " filter element " can be configured with in described multiple gas inflow part 122.
Described multiple gas inflow part 122 is configured to from the outer circumferential face of described cylinder barrel main body 121 depression prescribed depth and width.Described refrigeration agent can flow into the inside of described cylinder barrel main body 121 by described multiple gas inflow part 122 and spray nozzle part 123.
And the refrigeration agent flowed into, between the outer circumferential face and the inner peripheral surface of cylinder barrel 120 of described piston 130, plays the effect of gas bearing to the action of described piston 130.That is, due to the pressure of the refrigeration agent of described inflow, the outer circumferential face of described piston 130 maintains the state separated from the inner peripheral surface of described cylinder barrel 120.
Described multiple gas inflow part 122 comprises: be positioned at and be close to the first gas inflow part 122a and the second gas inflow part 122b of a side position from the axial centre portion 121c of described cylinder barrel main body 121 and be positioned at the 3rd gas inflow part 122c being close to opposite side position from described axial centre portion 121c.
Described first, second gas inflow part 122a, 122b with the axial centre portion 121c of described cylinder barrel main body 121 for benchmark is positioned at position closer to described second body end 121b, described 3rd gas inflow part 122c with the axial centre portion 121c of described cylinder barrel main body 121 for benchmark is positioned at position closer to described first body end 121a.
That is, described multiple gas inflow part 122 with the axial centre portion 121c of described cylinder barrel main body 121 for baseline configuration has asymmetrical number.
With reference to Fig. 1, with regard to the internal pressure of described cylinder barrel 120, compared with the first body end 121a side of the suction side near refrigeration agent, near higher by the pressure of the second body end 121b side of the discharge side of refrigeration agent that compresses, thus by forming in described second body end 121b side the function that more gas inflow part 122 strengthens gas bearing, form relatively few gas inflow part 122 in described first body end 121a side.
Described cylinder barrel main body 121 also comprises the spray nozzle part 123 that the inner peripheral surface direction from described multiple gas inflow part 122 to described cylinder barrel main body 121 extends.Described spray nozzle part 123 is formed as having the width less than described gas inflow part 122 or size.
Described spray nozzle part 123 can be formed multiple along the gas inflow part 122 extended with circle.And multiple spray nozzle part 123 is mutually separated and configures.
Described spray nozzle part 123 comprises the entrance part 123a linked with described gas the inflow part 122 and export department 123b linked with the inner peripheral surface of described cylinder barrel main body 121.Described spray nozzle part 123 is formed as having specific length from entrance part 123a towards described export department 123b.
After the refrigeration agent flowing into described gas inflow part 122 is filtered in described 3rd filter 330, flow to the entrance part 123a of described spray nozzle part 123, and flow along described spray nozzle part 123 to the inner peripheral surface direction of described cylinder barrel 120.And refrigeration agent flow into the inner space of described cylinder barrel 120 by described export department 123b.
Described piston 130 utilizes the pressure of the refrigeration agent of discharging from described export department 123b, carries out the action of separating from the inner peripheral surface of described cylinder barrel 120, namely floats from the inner peripheral surface of described cylinder barrel 120.That is, the pressure of the refrigeration agent supplied to the inner side of described cylinder barrel 120 provides buoyancy or floating pressure to described piston 130.
Described cylinder barrel 120 also comprises the first rake 128 extended obliquely rearward from described cylinder barrel main body 121.The direction that described first rake 128 can reduce gradually to the external diameter of described cylinder barrel 120 is formed obliquely.
Therefore, the external diameter being formed with the cylinder barrel 120 of described first rake 128 can be less than the external diameter of described cylinder barrel main body 121.
Fig. 8 is the sectional view representing the cylinder barrel of the embodiment of the present invention and the bonding state of framework, the figure that Fig. 9 amplifies Fig. 8 " B ".
With reference to Fig. 8 and Fig. 9, between the cylinder barrel 120 and framework 110 of the embodiment of the present invention, be formed with the flowing space portion 210 for the flow of refrigerant at least partially in the refrigeration agent of being discharged by described expulsion valve 161.
Described flowing space portion 210 rearward can extend from the space between the cover connecting part 115 of described framework 110 and the cylinder barrel flange part 125 of described cylinder barrel 120, and extends to the space between the rear quadrate part of described chassis body 111 and the first body end 121a of described cylinder barrel main body 121.
In described flowing space portion 210, the refrigeration agent of flowing can via described gas inflow part 122 and spray nozzle part 123, and the inner peripheral surface side to described cylinder barrel 120 flows.
Described Linearkompressor 100 comprises sealing recess 220, and sealing recess 220 is communicated with described flowing space portion 210, for arranging sealed member 200.
Described sealing recess 220 is the spaces that can arrange described sealed member 200, is formed between the inner peripheral surface of described chassis body 111 and the outer circumferential face of described cylinder barrel main body 121.And described sealing recess 220 can be formed at the rear quadrate part of described framework 110 and cylinder barrel 120.With the flow direction of refrigeration agent for benchmark, the flow section of described sealing recess 220 is greater than the flow section in described flowing space portion 210.
Specifically, comprise recess forming portion 112 at the rear quadrate part of chassis body 111, this recess forming portion 112 is configured to cave in outside radial direction from the inner peripheral surface of described chassis body 111.Described recess forming portion 112 forms at least one side of described sealing recess 212.
And, described chassis body 111 also comprise from described recess forming portion 112 rearward in the second rake 113 of extending obliquely of side direction.
Described cylinder barrel main body 121 comprises the first rake 128 for the formation of described sealing recess 220.Described first rake 128 forms at least one side of described sealing recess 220.
Described first rake 128 rearward extends inner side obliquely from the first body end 121a of described cylinder barrel main body 121.And described first rake 128 can extend to the position corresponding with the inner side of described second rake 113 from the inner side of described recess forming portion 112.
According to the sunk structure of described recess forming portion 112 and the leaning structure of described first rake 128, the radial direction height of described sealing recess 220 can be greater than the diameter of described sealed member 200.And the axial length of described sealing recess 220 can be greater than the diameter of described sealed member 200.
That is, described sealing recess 220 can have described sealed member 200 and not interfere with described chassis body 111 or cylinder barrel main body 121 and can the size of degree of movement.
On the other hand, the interval in the space of separating between the rear quadrate part of described first rake 128 and the rear quadrate part of described second rake 113 or distance are less than the diameter of described sealed member 200.Therefore, at Linearkompressor 100 duration of work, when refrigeration agent rearward flows along described flowing space portion 210, described sealed member 200 rearward moves under the effect of the pressure of described refrigeration agent, closes the space of described separation.
As mentioned above, because described sealed member 200 is closed described flowing space portion 210 between described cylinder barrel 120 and framework 110, therefore, it is possible to prevent the refrigrant leakage in described flowing space portion 210 to the outside of described framework 110.
And, described sealed member 200 is the mode of movement can be arranged on described sealing recess 220, when compressor is produced the flowing of refrigeration agent by driving in described flowing space portion 210, described sealed member 200 pressurizes to described cylinder barrel 120 and described framework 110, therefore, it is possible to prevent the distortion of the cylinder barrel 120 produced by the plus-pressure of described sealed member 200.
Below, the flowing state of Linearkompressor duration of work refrigeration agent and the effect of sealed member are described.
Figure 10 is the sectional view of the flow of refrigerant state of the Linearkompressor representing the embodiment of the present invention, and Figure 11 is the figure of the mobile status of sealed member when representing that the Linearkompressor of the embodiment of the present invention drives.
First, with reference to Figure 10, the flowing of the refrigeration agent in the Linearkompressor of the present embodiment is described.
With reference to Figure 10, refrigeration agent flows into the inside of housing 101 by sucting 104, and flow to the inside of absorbing silencer 150 by sucking guide portion 155.
Then, refrigeration agent, via the first baffler 151 of described absorbing silencer 150, flows into the second baffler 153, and flow to the inside of piston 130.In the process, the suction noise of refrigeration agent can be reduced.
In addition, refrigeration agent is while via the first filter 310 be arranged in described absorbing silencer 150, and foreign matter more than prescribed level (25 μm) is filtered.
The refrigeration agent being present in the inside of described piston 130 through described absorbing silencer 150, when suction valve 135 is opened, is inhaled into compression volume P by inlet hole 133.
When the refrigerant pressure of described compression volume P becomes more than head pressure, expulsion valve 161 is opened, refrigeration agent is discharged to the discharge space of discharging cover 160 by the expulsion valve 161 opened, and flow to discharge portion 105 by the ring pipe 165 be combined with described discharge cover 160, be discharged to the outside of compressor 100.
In addition, be present in the refrigeration agent at least partially in the refrigeration agent in the discharge space of described discharge cover 160, can flow in the space between the framework 110 of cylinder barrel 120 and described flowing space portion 210.Specifically, refrigeration agent via the cylinder barrel flange part 125 of recess 117 inner peripheral surface and described cylinder barrel 120 that are formed at framework 110 outer circumferential face between the flowing space, the outer circumferential face towards cylinder barrel main body 121 flows.
Now, refrigeration agent can through the second filter 320 between the attachment face 127 and the assembly department 113 of framework 110 of described cylinder barrel flange part 125, and the foreign matter in the process more than prescribed level (2 μm) is filtered.And the oil component in refrigeration agent is adsorbed by described second filter 320.
The refrigeration agent that have passed through described second filter 320 flow into multiple gas inflow part 122 of the outer circumferential face being formed at cylinder barrel main body 121.Then, refrigeration agent is while the 3rd filter 330 possessed through described gas inflow part 122, and the foreign matter more than prescribed level (1 μm) comprised in refrigeration agent is filtered, and the oil component comprised in refrigeration agent is adsorbed.
The refrigeration agent that have passed through described 3rd filter 330 flow into the inside of cylinder barrel 120 by spray nozzle part 123, between the inner peripheral surface and the outer circumferential face of piston 130 of described cylinder barrel 120, work (gas bearing) in the mode making described piston 130 separate from the inner peripheral surface of described cylinder barrel 120.
Now, the entrance part 123a diameter of described spray nozzle part 123 is larger than the diameter of export department 123b, therefore with the flow direction of refrigeration agent for benchmark, the flow of refrigerant sectional area in described spray nozzle part 123 reduces gradually.As an example, the diameter of described entrance part 123a is the value of more than the twice of export department 123b diameter.
As mentioned above, high-pressure gas refrigerant is roundabout and play bearing effect to reciprocating piston 130, therefore, it is possible to reduce the wearing and tearing between piston 130 and cylinder barrel 120 to the inside of described cylinder barrel 120.And, owing to not using the oil for bearing, therefore, even if described compressor 100 high speed operation also can not produce the frictional loss caused by oil.
Further, the path of the refrigeration agent of the internal flow of compressor 100 possesses multiple filter, thus the foreign matter comprised in refrigeration agent can be removed, therefore, it is possible to improve the reliability of the refrigeration agent worked as gas bearing.Therefore, it is possible to prevent the phenomenon producing wearing and tearing because of the foreign matter comprised in refrigeration agent on piston 130 or cylinder barrel 120.
And, utilize described multiple filter to remove the oil component comprised in refrigeration agent, thus the frictional loss that caused by oil component can be prevented.
On the other hand, in described flowing space portion 210, the refrigeration agent of flowing acts on described sealed member 200.That is, the pressure of described refrigeration agent acts on described sealed member 200, and described sealed member 200 moves from described sealing recess 220 between the first rake 128 of described cylinder barrel 120 and the second rake 113 of described framework 110.
Then, described sealed member 200 is close to described cylinder barrel 120 and framework 110, closes the space of separating between described cylinder barrel 120 and framework 110, as an example, closes the space between described first rake 128 and the second rake 113.Therefore, it is possible to prevent the refrigeration agent in described flowing space portion 210 by the spatial leaks separated between described cylinder barrel 120 and framework 110 to outside.
On the other hand, when the driving of described Linearkompressor 100 is interrupted, the pressure acting on the refrigeration agent of described sealed member 200 is removed, and the clinging force therefore between described sealed member 200 and described cylinder barrel 120 and framework 110 dies down.As a result, described sealed member 200 is in the state that can move freely in described sealing recess 220, as an example, is in the state (represented by dashed line) separated from described first rake 128 and the second rake 113.
According to this effect, only can be close to cylinder barrel 120 and framework 110 by sealed member 200 during driving at compressor 100, and carry out the sealing in described flowing space portion 210, therefore, it is possible to reduce the power putting on described cylinder barrel 120 from described sealed member 200.Thus, the distortion of described cylinder barrel 120 can be prevented.
And described sealed member 200 is in and in the state of described sealing recess 220 movement, therefore, when assembling described cylinder barrel 120 with framework 110, can prevents the interference effect of described sealed member 200.As a result, described cylinder barrel 120 becomes easy with the assembling of framework 110.
Claims (14)
1. a Linearkompressor, is characterized in that, comprising:
Housing, is provided with sucting;
Cylinder barrel, is positioned at the inside of described housing, forms the compression volume of refrigeration agent;
Framework, is combined with the outside of described cylinder barrel;
Piston, is arranged in the mode that can move back and forth vertically in the inside of described cylinder barrel;
Expulsion valve, is positioned at the side of described cylinder barrel, discharges compression volume at described refrigeration agent selectively by the refrigeration agent compressed;
Flowing space portion, is formed between described cylinder barrel and described framework, for the flow of refrigerant at least partially in the refrigeration agent of being discharged by described expulsion valve;
Sealing recess, is communicated with described flowing space portion; And
Sealed member, the mode of movement can be arranged at described sealing recess, closes the space of separating between described framework and described cylinder barrel.
2. Linearkompressor according to claim 1, is characterized in that,
The radial direction height of described sealing recess is formed as the diameter being greater than described sealed member.
3. Linearkompressor according to claim 1, is characterized in that,
The axial length of described sealing recess is formed as the diameter being greater than described sealed member.
4. Linearkompressor according to claim 1, is characterized in that,
With the flow direction of described refrigeration agent for benchmark, the flow section of described sealing recess is greater than the flow section in described flowing space portion.
5. Linearkompressor according to claim 1, is characterized in that,
Described sealing recess is formed between the outer circumferential face of described cylinder barrel and the inner peripheral surface of described framework.
6. Linearkompressor according to claim 5, is characterized in that,
Described framework comprises recess forming portion,
This recess forming portion forms at least one side of described sealing recess, from the inner peripheral surface radial direction depression laterally of described framework.
7. Linearkompressor according to claim 6, is characterized in that,
Described cylinder barrel comprises the first rake,
This first rake is formed in the position corresponding with described recess forming portion, and the direction that the external diameter to described cylinder barrel reduces extends.
8. Linearkompressor according to claim 7, is characterized in that,
Described sealed member moves along described first rake.
9. Linearkompressor according to claim 6, is characterized in that,
Described framework comprises the second rake,
This second rake from described recess forming portion to inward side to extending obliquely.
10. Linearkompressor according to claim 1, is characterized in that,
Also comprise spray nozzle part, this spray nozzle part is formed at the outer circumferential face of described cylinder barrel, the inner peripheral surface side of the refrigeration agent in described flowing space portion to described cylinder barrel is guided.
11. 1 kinds of Linearkompressors, is characterized in that, comprising:
Housing, is provided with sucting,
Cylinder barrel, is positioned at the inside of described housing, forms the compression volume of refrigeration agent,
Framework, surrounds the outside of described cylinder barrel,
Piston, is arranged in the mode that can move back and forth vertically in the inside of described cylinder barrel,
Expulsion valve, is positioned at the side of described cylinder barrel, discharges compression volume at described refrigeration agent selectively by the refrigeration agent compressed,
Flowing space portion, is formed between the outer circumferential face of described cylinder barrel and the inner peripheral surface of described framework, flows for from the part of refrigerant the refrigeration agent that described expulsion valve is discharged, and
Sealing recess, has the sectional area larger than described flowing space portion, is provided with sealed member;
When the refrigeration agent in described flowing space portion acts on described sealed member, described sealed member moves to the position sealed the space between described framework and described cylinder barrel.
12. Linearkompressors according to claim 11, is characterized in that,
When the refrigeration agent in described flowing space portion does not act on described sealed member, described sealed member is to not moving the position that the space between described framework and described cylinder barrel seals.
13. Linearkompressors according to claim 11, is characterized in that,
Described sealing recess comprises:
Recess forming portion, caves in from the inner peripheral surface of described framework, and
First rake, is formed at the outer circumferential face of described cylinder barrel.
14. Linearkompressors according to claim 13, is characterized in that,
Described framework comprises the second rake extended obliquely from described recess forming portion,
When the refrigeration agent in described flowing space portion acts on described sealed member, described sealed member moves to the position sealed the space of separating between described first rake and described second rake.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020140077506A KR102306857B1 (en) | 2014-06-24 | 2014-06-24 | A linear compressor |
| KR10-2014-0077506 | 2014-06-24 |
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| Publication Number | Publication Date |
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| CN105298801A true CN105298801A (en) | 2016-02-03 |
| CN105298801B CN105298801B (en) | 2017-10-24 |
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| CN201510272331.5A Active CN105298801B (en) | 2014-06-24 | 2015-05-25 | Linearkompressor |
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| CN (1) | CN105298801B (en) |
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| CN107339224A (en) * | 2016-05-03 | 2017-11-10 | Lg电子株式会社 | Linearkompressor |
| CN107339215A (en) * | 2016-05-03 | 2017-11-10 | Lg电子株式会社 | Linearkompressor |
| CN110360081A (en) * | 2018-04-10 | 2019-10-22 | Lg电子株式会社 | Linearkompressor |
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Also Published As
| Publication number | Publication date |
|---|---|
| KR20160000300A (en) | 2016-01-04 |
| CN105298801B (en) | 2017-10-24 |
| KR102306857B1 (en) | 2021-09-30 |
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