CN101589231B - Reciprocating compressor - Google Patents
Reciprocating compressor Download PDFInfo
- Publication number
- CN101589231B CN101589231B CN2007800489849A CN200780048984A CN101589231B CN 101589231 B CN101589231 B CN 101589231B CN 2007800489849 A CN2007800489849 A CN 2007800489849A CN 200780048984 A CN200780048984 A CN 200780048984A CN 101589231 B CN101589231 B CN 101589231B
- Authority
- CN
- China
- Prior art keywords
- moving link
- hush tube
- backflow
- section
- refrigeration agent
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 239000003795 chemical substances by application Substances 0.000 claims description 69
- 238000005057 refrigeration Methods 0.000 claims description 69
- 230000003068 static effect Effects 0.000 claims description 13
- 229910000831 Steel Inorganic materials 0.000 claims description 6
- 239000000463 material Substances 0.000 claims description 6
- 239000010959 steel Substances 0.000 claims description 6
- 239000003507 refrigerant Substances 0.000 abstract description 21
- 230000006835 compression Effects 0.000 abstract description 20
- 238000007906 compression Methods 0.000 abstract description 20
- 230000002265 prevention Effects 0.000 abstract 1
- 238000010992 reflux Methods 0.000 description 22
- 238000000034 method Methods 0.000 description 10
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000005219 brazing Methods 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000030279 gene silencing Effects 0.000 description 1
- 238000003475 lamination Methods 0.000 description 1
- 239000008188 pellet Substances 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000003584 silencer Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
- F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
- F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
- F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/123—Fluid connections
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
Abstract
The present invention relates to a reciprocating compressor wherein a moving member reciprocates linearly inside a stationary member to compress refrigerant, and more particularly, to a reciprocating compressor wherein a backflow of refrigerant is prevented before the refrigerant is introduced into a compression space. A reciprocating compressor according to the present invention includes a hollowstationary member, a moving member reciprocating linearly inside the stationary member, and having a suction hole in a blocked end so that refrigerant can be introduced therethrough, a sound attenuat ion duct extended lengthwise inside the moving member to guide introduced refrigerant, and a backflow prevention portion expanded from an end of the sound attenuation duct toward the moving member to prevent a backflow of the refrigerant. As the refrigerant does not flow backward before it flows into a compression space, it is possible to improve the compression efficiency.
Description
Technical field
The present invention relates to a kind of reciprocal compressor, wherein when moving link in static component point-blank during to-and-fro motion, in the compression volume that the inner space of refrigeration agent by moving link is inhaled into and is to limit between static component and moving link, compressed, more specifically, relate to a kind of reciprocal compressor, wherein, before refrigeration agent is introduced compression volume by the inner space from moving link, prevent the backflow of the refrigeration agent in the inner space of moving link.
Background technique
Usually, in reciprocal compressor, limit working gas to be drawn into wherein between piston and cylinder/compression volume from wherein emitting, and piston in cylinder point-blank to-and-fro motion with compressed refrigerant.
Because reciprocal compressor comprises the parts (such as crankshaft) that are converted into the straight reciprocating motion power of piston for the rotating force by drive motor, so this conversion of motion can cause very large mechanical loss.Recently developed linear compressor to overcome the above problems.
Especially, in linear compressor, piston is coupled directly to reciprocating linear electric motor point-blank, thereby has prevented the mechanical loss caused by conversion of motion.Therefore, linear compressor can improve compression efficiency simplified construction.In addition, regulate the power of input linear electric motor to control the operation of linear electric motor, make and produce than noise less in other compressor.Therefore linear compressor has been widely used in being arranged in the household electric appliance in the interior space, in refrigerator.
Fig. 1 shows the view of an example of conventional reciprocating formula compressor, and Fig. 2 shows the view of an example of the refrigeration agent suction passage of conventional reciprocating formula compressor.
With reference to Fig. 1 and 2, in the linear compressor of the example as conventional reciprocating formula compressor, the structure consisted of framework 1, static component 2, moving link 3, suction valve 4, bleed valve assembly 5, linear electric motor 6, motor cover 7, supporting element 8, body cover 9, damping spring (not shown) and muffler assembly 10 is arranged in the housing (not shown) to be subject to elastic support.
In detail, static component 2 forms the hollow shape with two open ends.One end of static component 2 is packed into and is fixed in framework 1, and its other end is by bleed valve assembly 5 sealings.Bleed valve assembly 5 comprises escape cock 5a, discharge cover 5b and escape cock spring 5c.When the vibration of the refrigeration agent of discharging from discharge cover 5b and noise are inhibited by the loop pipe (not shown), refrigeration agent is discharged into outside by the outflow tube (not shown) on the housing side.
Moving link 3 forms the hollow shape with a closed end.The closed end of moving link 3 inserts in static component 2.Limit compression volume P between static component 2 and moving link 3.Closed end at moving link 3 is formed with a plurality of inlet hole 3a, thereby can refrigeration agent be sucked to compression volume P by inlet hole 3a.Central authorities at the closed end of moving link 3 are formed with groove 3b, thereby thin suction valve 4 can be anchored on to groove 3b with bolt B.Here, inlet hole 3a can be formed at a side of the closed end of moving link 3 as shown in figure prejudicially, or can be formed at the central authorities of the closed end of moving link 3.If inlet hole 3a is formed on central authorities, suction valve 4 must with figure in differently be fixed to the edge of moving link 3.Yet, due to suction valve 4 and the moving link 3 of not too easily mechanically being coupled, so, for suction valve 4 is installed, be essential such as the special device of magnet.Therefore, as a rule, inlet hole 3a is formed at the closed end of moving link 3 prejudicially, and suction valve 4 mechanically is coupled in the central authorities of the closed end of moving link 3 by bolt etc.
The relative pressure of the compression volume P that suction valve 4 causes by the straight reciprocating motion by moving link 3 changes to open and seal the inlet hole 3a of moving link 3.
Linear electric motor 6 comprise cylindrical inner stator 6a, external stator 6b, permanent magnet 6c and connector element 6d, wherein cylindrical inner stator 6a is fixed to the outside of static component 2, external stator 6b is having default spacing with inner stator 6a in the radial direction, the end of external stator 6b is supported on framework 1 and the other end is supported on motor cover 7, permanent magnet 6c is arranged between inner stator 6a and external stator 6b with prepsetting gap, and connector element 6d is for being connected in permanent magnet 6c by moving link 3.
Motor cover 7 in axial direction supports external stator 6b with fixing external stator 6b, and motor cover 7 bolts are fixed to framework 1.Body cover 9 is coupled in motor cover 7.The supporting element 8 that is connected in the other end of moving link is arranged between motor cover 7 and body cover 9, in axial direction flexibly to be supported by resonant spring.
Supporting element 8 comprises supporting projections 8a, bolt hole 8b and opening portion, wherein supporting projections 8a packs spring into the supported spring flexibly of the moving direction along moving link 3, bolt B is fixed in the flange 3c on the other end that is formed on moving link 3 by bolt hole 8b, opening portion is formed at central authorities with the assembly 10 that fixes a silencer thereon.
Be formed with predetermined inlet hole on body cover 9, the refrigeration agent that makes the intake channel from the housing side introduce can pass through this inlet hole.
In this case, when linear electric motor 6 operation, moving link 3 and muffler assembly 10 to-and-fro motion point-blank be connected thereto.Suction valve 4 and escape cock 5a operate by the relative pressure variation of compression volume P.According to above operation, refrigeration agent is inhaled into compression volume P and is compressed in compression volume P through the inlet hole 3a of opening portion, muffler assembly 10 and the moving link 3 of the intake channel on the housing side, body cover 9, and is discharged into outside by the outflow tube on discharge cover 5b, loop pipe and housing side.
Muffler assembly 10 forms the moving direction longitudinal extension along moving link 3.Muffler assembly 10 not only guides the inhalation flow of refrigeration agent, and weakens the noise produced when refrigeration agent is inhaled into compression volume P by suction valve 4.When the refrigeration agent process has the hush tube 11 of small diameter and has larger-diameter resonant cavity 14, noise can be weakened according to acoustic characteristic.
In more detail, muffler assembly 10 comprises hush tube 11, the shell 12 of hollow, inside prolong pipe 13, resonant cavity 14 and assembly department 15, wherein hush tube 11 in the inside of moving link 3 longitudinal extension vertically, the shell 12 of hollow is formed at the outside of the other end of moving link 3, inside prolonging pipe 13 is formed in the entrance of shell 12, resonant cavity 14 limits the space than internal volume that has in shell 12, and resonant cavity 14 also has opening portion and makes refrigeration agent can pass through this opening portion, assembly department 15 radially extends and is fixed in bolt B the flange 3c of moving link 3.Here, muffler assembly 10 is fixed in the flange 3c of moving link 3 with supporting element 8 with bolt B.
The refrigeration agent that intake channel (not shown) by housing is introduced is through the predetermined inlet hole of body cover 9, directed through being formed in the entrance of shell 12 in prolong pipe 13, resonant cavity 14 and hush tube 11, and be inhaled into compression volume P by suction valve 4.The noise produced in this operating process is weakened by hush tube 11, resonant cavity 14 and by shell 12 and the Nei Yan pipe 13 secondary resonance chambeies that limit conversely, then is sent to enclosure interior.
If the length of hush tube 11 increases, the sectional area of hush tube 11 reduces, or the increase of the actual volume of resonant cavity 14, can improve noise reduction efficacy.Yet the length of hush tube 11 is subject to the restriction of the length of moving link 3.In addition, if the end of hush tube 11 is difficult to guide to through the refrigeration agent of hush tube 11 inlet hole 3a too near the closed end of moving link 3.Simultaneously, if the sectional area of hush tube 11 reduces, can produce the refrigeration agent suction loss.In addition, due to silencing apparatus 10, with moving link 3 to-and-fro motion point-blank in the space limited by body cover 9 and resonant spring, so increase the volume of resonant cavity 14, be limited.
Simultaneously, as mentioned above, when hush tube 11 is placed on the central interior of moving link 3 and closed end that inlet hole 3a is formed at moving link 3 prejudicially, although the major part of the refrigeration agent by hush tube 11 is introduced into the inlet hole 3a of moving link 3, but can touch the closed end to moving link 3 by some in the refrigeration agent of hush tube 11, and reverse flowing back to.When refrigeration agent flows back to, some refrigeration agents flow in the inner periphery of moving link 3 and the space between hush tube 11, thereby produce the flow of refrigerant loss.Consequently reduced compression efficiency.
Summary of the invention
Technical problem
Imagination the present invention is in order to solve the aforementioned problems in the prior.One object of the present invention is to provide a kind of reciprocal compressor, and it can reduce the backflow of the refrigeration agent of the inlet hole of introducing moving link from muffler assembly.
Another object of the present invention is to provide a kind of reciprocal compressor, and it can reduce the flow losses of the refrigeration agent of the inlet hole of introducing moving link from muffler assembly.
Another object of the present invention is to provide a kind of reciprocal compressor, and it can maximize by the length that increases as much as possible the hush tube of muffler assembly under specified criteria the noise reduction efficacy of muffler assembly.
Technological scheme
According to for realizing the present invention of these purposes, a kind of reciprocal compressor has been proposed, comprising: the static component of hollow; Moving link, described moving link is to-and-fro motion point-blank in described static component, and described moving link has inlet hole at closed end and makes refrigeration agent to introduce by described inlet hole; Hush tube, the described hush tube refrigeration agent that longitudinal extension is introduced with guiding in described moving link; Reaching refluxes prevents that section, described backflow from preventing that section from expanding to described moving link from the end of described hush tube, to prevent the backflow of described refrigeration agent.
Here, described inlet hole is formed on the closed end of described moving link eccentricly.
Preferably, reciprocal compressor comprises muffler assembly, and described muffler assembly comprises hush tube and the resonant cavity be connected with described hush tube, to weaken the noise due to the inflow generation of described refrigeration agent.
More preferably, described hush tube can be formed at the central interior of described moving link, and with the longitudinal direction longitudinal extension along described moving link, and described resonant cavity can be formed at the outside of described moving link to be connected with described hush tube.
According to a preferred aspect of the present invention, described backflow prevents that section from can form flange-shape, vertically expands to the internal surface of described moving link with the end from described hush tube; Can form funnel shape, in the described backflow in the end of described hush tube, prevent that the diameter of section from axial direction increasing; Perhaps, can form cup-shapedly, become to there is step with the end extended from described hush tube.
Preferably, described backflow prevents that section from can form as one by using plastic material and described hush tube, or is made and be soldered to the end of described hush tube by steel.
More preferably, reflux and prevent the end of section and the internal surface close contact of moving link.
The accompanying drawing explanation
Fig. 1 shows the view of an example of conventional reciprocating formula compressor.
Fig. 2 shows the view of an example of the refrigeration agent suction passage of conventional reciprocating formula compressor.
Fig. 3 to 5 shows the view according to the different mode of executions of the refrigeration agent suction passage of reciprocal compressor of the present invention.
Embodiment
Describe the preferred embodiment of the present invention in detail hereinafter with reference to accompanying drawing.
Fig. 3 to 5 shows the view according to the different mode of executions of the refrigeration agent suction passage of reciprocal compressor of the present invention.
With reference to Fig. 3, in the first mode of execution of the refrigeration agent suction passage of linear compressor, wherein this linear compressor is the example according to reciprocal compressor of the present invention, inlet hole 103a be formed on prejudicially on a closed end of moving link 103 be limited to the static component (not shown) and be connected with the compression volume P between moving link 103, and at the other end of moving link 103, supporting element 108 and muffler assembly 110 are installed.The hush tube 111 of muffler assembly 110 is placed in the central interior of moving link 103, and the end of hush tube 111 is formed with to reflux and prevents that section 116 is radially to expand.
In detail, moving link 103 forms piston-shaped, and is formed with prejudicially inlet hole 103a on its closed end.Central authorities at this closed end are formed with bolt slot 103b, make the thin suction valve (not shown) for opening and seal inlet hole 103a to be fixed in bolt slot 103b with bolt.
Here, at the open end of moving link 103, be formed with flange 103c radially to expand, and supporting element 108 and muffler assembly 110 are fixed in the flange 103c of moving link 103 with bolt B.
The same with prior art, supporting element 108 comprises supporting projections 108a and bolt hole 108b, and muffler assembly 110 comprise hush tube 111, shell 112, in prolong pipe 113, resonant cavity 114 and assembly department 115.Therefore omit its detailed description.
Backflow prevents that section 116 from forming flange shape and vertically expanding with the internal surface of the end orientation movements member 103 of the hush tube 111 from muffler assembly 110, i.e. radially expansion.Because backflow prevents that section 116 is for guiding towards inlet hole 103a through the refrigeration agent of hush tube 111, so the hush tube 111 of muffler assembly 110 can form than length of the prior art, hush tube 111 can form apart from the closed end of moving link 103 nearer.Result is, hush tube 111 is than relatively longer in prior art, thereby improved noise reduction performance.
In order to prevent that refrigeration agent through the hush tube 111 of muffler assembly 110 from touching to the closed end of moving link 103 and between the internal surface of moving link 103 and hush tube 111, flow back to, more preferably, reflux prevent section 116 from hush tube 111 expansions of muffler assembly 110 and with the internal surface close contact of moving link 103.
If hush tube 111 is made by plastic material, reflux and prevent that section 116 can be by being used plastic material casting together with hush tube 111.Simultaneously, if hush tube 111 is made by steel, reflux and prevent that section 116 from can be made separately by steel, and be fixed to the end of hush tube 111 by the welding process such as brazing.
Thereby the refrigeration agent of the hush tube 111 of process muffler assembly 110 moves along the central interior of moving link 103.Some refrigeration agents flow directly into the inlet hole 103a of moving link 103.Even other refrigeration agent touches to the closed end of moving link 103 and refluxes, refrigeration agent also can move along the internal surface of moving link 103, touches to refluxing and prevents section 116, and again along the flow of refrigerant direction, flow to inlet hole 103a.
That is, even some in the refrigeration agent of the hush tube 111 of process muffler assembly 110 reflux, but because internal surface and the backflow of moving link 103 prevents section 116 close contact each other, so can reduce the flow losses of refrigeration agent.
Simultaneously, with reference to Fig. 4, identical with above-mentioned the first mode of execution according to the second mode of execution of the refrigeration agent suction passage of reciprocal compressor of the present invention.Yet, refluxes and prevent that section 117 from forming the funnel shape that diameter increases along the flow of refrigerant direction in the end of the hush tube 111 of muffler assembly 110, and backflow prevents the end of section 117 and the internal diameter close contact of moving link 103.
Because backflow prevents that section 117 is for guiding towards inlet hole 103a through the refrigeration agent of hush tube 111, so the hush tube 111 of muffler assembly 110 can form than length of the prior art, hush tube 111 can form apart from the closed end of moving link 103 nearer.Thereby hush tube 111 is relatively longer than of the prior art, thereby has improved noise reduction performance.
Even the hush tube 111 of muffler assembly 110 is unlike length of the prior art, but expand gradually because backflow prevents section 117 radial direction along the hush tube 111 of muffler assembly 110 on the flow of refrigerant direction, so that the inlet hole 103a of moving link 103 and backflow prevent that section 117 from forming is located adjacent one another.
Backflow prevents that section 117 from can form as one by the hush tube 111 that uses plastic material and muffler assembly 110, or is made and be soldered to the hush tube 111 of muffler assembly 110 by steel.
Therefore, the refrigeration agent of the hush tube 111 of process muffler assembly 110 moves along the central interior of moving link 103.Some refrigeration agents flow directly into the inlet hole 103a of moving link 103.Even other refrigeration agent touches to the closed end of moving link 103 and refluxes, these refrigeration agents also can passive movement member 103 internal diameter and backflow prevent section's 117 guiding, converge in the refrigeration agent through hush tube 111, and flow to inlet hole 103a along the flow of refrigerant direction.
That is, even some in the refrigeration agent of the hush tube 111 of process muffler assembly 110 reflux, but because internal diameter and the backflow of moving link 103 prevents section 117 close contact each other, so can reduce the flow losses of refrigeration agent.
On the other hand, with reference to Fig. 5, identical with above-mentioned the second mode of execution according to the 3rd mode of execution of the refrigeration agent suction passage of reciprocal compressor of the present invention.Yet it is cup-shaped that backflow prevents that section 118 from forming, with the end extended of the hush tube 111 from muffler assembly 110, and backflow prevents the end of section 118 and the internal surface close contact of moving link 103.In the situation that the end that backflow prevents section 118 not with the internal surface close contact of moving link 103, preferably, reflux that it is longer to prevent that section 118 from forming along the flow of refrigerant direction, possess gap with the internal surface of moving link 103.
Even the hush tube 111 of muffler assembly 110 is unlike length of the prior art, but vertically expand and extend along the flow of refrigerant direction along the radial direction of the hush tube 111 of muffler assembly 110 because backflow prevents section 118, so that the inlet hole 103a of moving link 103 and backflow prevent that section 118 from forming is located adjacent one another.
Backflow prevents that section 118 from can form as one by the hush tube 111 that uses plastic material and muffler assembly 110, or is made and be soldered to the hush tube 111 of muffler assembly 110 by steel.
Therefore, some in the refrigeration agent of the hush tube 111 of process muffler assembly 110 flow directly into the inlet hole 103a of moving link 103.Even other refrigeration agent touches to the closed end of moving link 103 and refluxes, these refrigeration agents also can passive movement member 103 internal diameter and backflow prevent section's 118 guiding, converge in the refrigeration agent through hush tube 111, and 103 flow along the flow of refrigerant direction along moving link.
In addition, even some in the refrigeration agent of the hush tube 111 of process muffler assembly 110 reflux, but because internal surface and the backflow of moving link 103 prevents section 118 close contact each other, so can reduce the flow losses of refrigeration agent.
Simultaneously, the flow of back flow of refrigerant (flow rate) is closely related with the structure of refrigerant flow channel.It means with following formula.
That is, the flow Q of the refrigeration agent of backflow
hto pressure difference Δ P and gap h, be directly proportional, but prevent that with hush tube 111 and backflow the flow direction length L of section 116,117 or 118 is inversely proportional to, the pressure of the pressure that wherein pressure difference Δ P is the space that forms between hush tube 111 and moving link 103 and the export department that prevents section 116,117 or 118 of refluxing poor, the internal surface that gap h is moving link 103 and backflow prevent the gap between section 116,117 or 118.According to the present invention, based on above formula, reduce as much as possible the internal surface of moving link 103 and reflux to prevent the gap h between section 116,117 or 118, minimize thus the flow of the refrigeration agent of backflow.According to the present invention, preferably, reflux and prevent that the end of section 116,117 or 118 from contacting with minimum gaps h with the internal surface of moving link 103.
In addition, increase the length of hush tube 111 or increase the flow of refrigerant direction length along flow of refrigerant direction hush tube 111 ends, making refluxes prevents that section 116,117 or 118 can be positioned as close to the inlet hole 103a of moving link 103.Therefore, refrigeration agent refluxes less or does not reflux, and does not produce the flow of refrigerant loss.Thereby, as mentioned above, if the length of hush tube 111 increases, can improve noise reduction efficacy.
Result is, can be increased in the flow of the refrigeration agent circulated in each mode of execution according to reciprocal compressor of the present invention to improve compression efficiency, and and then improves Energy Efficiency Ratio (EER).According to test result, compared with prior art, the first EER to the 3rd mode of execution improves respectively 0.08,0.07 and 0.1.
With reference to mode of execution and accompanying drawing, describe the present invention in detail.Yet scope of the present invention is not limited to mode of execution and accompanying drawing, but is limited by appended claims.
Commercial Application
According to the present invention, in reciprocal compressor, even caused before the inlet hole of moving link the backflow that refrigeration agent occurs by the hush tube from muffler assembly at refrigeration agent, the backflow that refrigeration agent also can touch to the hush tube end that is formed at muffler assembly prevents section, and directed and again flow to the inlet hole of moving link.Thereby can suppress the backflow of refrigeration agent.In addition, between the hush tube due to the internal diameter at moving link and muffler assembly, being attached with refluxes prevents section, so prevented the flow losses of the refrigeration agent that backflow causes before refrigeration agent is introduced into compression volume.Therefore can increase the flow of refrigeration agent.In addition, increase the length of hush tube to improve noise reduction efficacy and then raising compression efficiency and efficiency.
Claims (9)
1. a reciprocal compressor comprises:
The static component of hollow;
Moving link, described moving link is to-and-fro motion point-blank in described static component, and described moving link has inlet hole at closed end and makes refrigeration agent to introduce by described inlet hole;
Hush tube, described hush tube bolt is fixed in the flange of described moving link, and the described hush tube refrigeration agent that longitudinal extension is introduced with guiding in described moving link, and described hush tube is near the closed end of described moving link; And
Backflow prevents section, and described backflow prevents that section from expanding to described moving link from the end of described hush tube,
Thereby, described backflow prevent section end can with the internal surface close contact of described moving link, wherein, prevent from through described hush tube and touch to the refrigeration agent of the closed end of described moving link flowing back between the internal surface of described moving link and described hush tube.
2. reciprocal compressor as claimed in claim 1, wherein, described inlet hole is formed on the closed end of described moving link prejudicially.
3. reciprocal compressor as claimed in claim 2, comprise muffler assembly, and described muffler assembly comprises hush tube and the resonant cavity be connected with described hush tube, to weaken the noise due to the inflow generation of described refrigeration agent.
4. reciprocal compressor as claimed in claim 3, wherein, described hush tube is formed at the central interior of described moving link, and with the longitudinal direction longitudinal extension along described moving link, and described resonant cavity is formed at the outside of described moving link to be connected with described hush tube.
5. reciprocal compressor as described as any one in claim 1 to 4, wherein, the described backflow section of preventing forms flange-shape, with the end from described hush tube, to the internal surface of described moving link, vertically expands.
6. reciprocal compressor as described as any one in claim 1 to 4, wherein, the described backflow section of preventing forms funnel shape, in the described backflow in the end of described hush tube, prevents that the diameter of section from axial direction increasing.
7. reciprocal compressor as described as any one in claim 1 to 4, wherein, the described backflow section of preventing forms cup-shaped, with the end extended from described hush tube, becomes to have step.
8. reciprocal compressor as described as any one in claim 1 to 4, wherein, described backflow prevents that section is by being used plastic material and described hush tube to form as one.
9. reciprocal compressor as described as any one in claim 1 to 4, wherein, described backflow prevents that section from being made and being soldered to the end of described hush tube by steel.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020070000328 | 2007-01-02 | ||
| KR10-2007-0000328 | 2007-01-02 | ||
| KR20070000328 | 2007-01-02 | ||
| PCT/KR2007/006759 WO2008082116A2 (en) | 2007-01-02 | 2007-12-21 | Reciprocating compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101589231A CN101589231A (en) | 2009-11-25 |
| CN101589231B true CN101589231B (en) | 2013-12-25 |
Family
ID=39589093
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007800489849A Expired - Fee Related CN101589231B (en) | 2007-01-02 | 2007-12-21 | Reciprocating compressor |
Country Status (3)
| Country | Link |
|---|---|
| KR (1) | KR20080063706A (en) |
| CN (1) | CN101589231B (en) |
| WO (1) | WO2008082116A2 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BR102012032343A2 (en) * | 2012-12-18 | 2014-09-02 | Whirlpool Sa | Suction Cap for a LINEAR ENGINE COMPRESSOR and LINEAR ENGINE COMPRESSOR |
| KR102073719B1 (en) * | 2013-10-04 | 2020-02-05 | 엘지전자 주식회사 | A linear compressor |
| KR102073715B1 (en) * | 2013-10-04 | 2020-02-05 | 엘지전자 주식회사 | A linear compressor |
| KR102259660B1 (en) * | 2016-10-11 | 2021-06-02 | 엘지전자 주식회사 | Linear compressor |
| KR101990401B1 (en) * | 2017-09-15 | 2019-06-18 | 엘지전자 주식회사 | Linear compressor |
| EP3869040B1 (en) * | 2018-01-12 | 2024-07-31 | LG Electronics Inc. | Linear compressor and refrigerator including same |
| KR102447354B1 (en) * | 2021-01-22 | 2022-09-26 | 엘지전자 주식회사 | Reciprocating compressor |
| KR102687563B1 (en) * | 2022-09-30 | 2024-07-24 | 엘지전자 주식회사 | Linear compressor |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3781140A (en) * | 1971-05-26 | 1973-12-25 | Coleman Co | Synchronous reciprocating electrodynamic compressor system |
| CN1443279A (en) * | 2001-04-06 | 2003-09-17 | Lg电子株式会社 | Suction gas guiding system for reciprocating compressor |
| CN1516785A (en) * | 2001-04-16 | 2004-07-28 | Lg������ʽ���� | Suction gas guiding system for reciprocating compressor |
| CN1648453A (en) * | 2003-12-31 | 2005-08-03 | Lg电子株式会社 | Reciprocating compressor having assembly structure of suction muffler |
| CN1769680A (en) * | 2004-11-03 | 2006-05-10 | Lg电子株式会社 | Linear compressor |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7156626B2 (en) * | 2001-10-12 | 2007-01-02 | Lg Electronics Inc. | Double side action type reciprocating compressor |
| KR100550536B1 (en) * | 2003-06-04 | 2006-02-10 | 엘지전자 주식회사 | Linear compressor |
-
2007
- 2007-12-21 WO PCT/KR2007/006759 patent/WO2008082116A2/en active Application Filing
- 2007-12-21 KR KR1020070135656A patent/KR20080063706A/en active Search and Examination
- 2007-12-21 CN CN2007800489849A patent/CN101589231B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3781140A (en) * | 1971-05-26 | 1973-12-25 | Coleman Co | Synchronous reciprocating electrodynamic compressor system |
| CN1443279A (en) * | 2001-04-06 | 2003-09-17 | Lg电子株式会社 | Suction gas guiding system for reciprocating compressor |
| CN1516785A (en) * | 2001-04-16 | 2004-07-28 | Lg������ʽ���� | Suction gas guiding system for reciprocating compressor |
| CN1648453A (en) * | 2003-12-31 | 2005-08-03 | Lg电子株式会社 | Reciprocating compressor having assembly structure of suction muffler |
| CN1769680A (en) * | 2004-11-03 | 2006-05-10 | Lg电子株式会社 | Linear compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101589231A (en) | 2009-11-25 |
| WO2008082116A3 (en) | 2009-07-30 |
| WO2008082116A2 (en) | 2008-07-10 |
| KR20080063706A (en) | 2008-07-07 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101589231B (en) | Reciprocating compressor | |
| EP3242027B1 (en) | Linear compressor | |
| KR102238334B1 (en) | Linear compressor | |
| US7770694B2 (en) | Resonator arrangement in an acoustic muffler for a refrigeration compressor | |
| US20040247457A1 (en) | Linear compressor | |
| EP3587813B1 (en) | Reciprocating compressor | |
| KR20150040027A (en) | A linear compressor | |
| CN110360081B (en) | Linear compressor | |
| KR101764027B1 (en) | A linear compressor | |
| EP3783223A1 (en) | Linear compressor | |
| KR102390176B1 (en) | Linear compressor | |
| KR20180093526A (en) | Linear compressor | |
| KR20050080657A (en) | Vibration reduction structure of reciprocating compressor | |
| US12044225B2 (en) | Linear compressor | |
| US11781540B2 (en) | Linear compressor | |
| KR20040021466A (en) | Reciprocating compressor | |
| KR20180039960A (en) | Linear compressor | |
| US7588424B2 (en) | Linear compressor unit | |
| KR100527587B1 (en) | Noise reducing structure of reciprocating compressor | |
| US11982266B2 (en) | Compressor | |
| KR102432487B1 (en) | Linear compressor | |
| KR20030073662A (en) | Reciprocating compressor | |
| KR101788597B1 (en) | Hermetic type compressor | |
| KR100550535B1 (en) | Linear compressor | |
| CN114687994A (en) | Linear compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20131225 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |