CN113007097B - Flange structure, compressor and air conditioner - Google Patents
Flange structure, compressor and air conditioner Download PDFInfo
- Publication number
- CN113007097B CN113007097B CN202110322086.XA CN202110322086A CN113007097B CN 113007097 B CN113007097 B CN 113007097B CN 202110322086 A CN202110322086 A CN 202110322086A CN 113007097 B CN113007097 B CN 113007097B
- Authority
- CN
- China
- Prior art keywords
- silencing
- amortization
- compressor
- flange
- main
- 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.)
- Active
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0021—Systems for the equilibration of forces acting on the pump
- F04C29/0035—Equalization of pressure pulses
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
- F04C29/065—Noise dampening volumes, e.g. muffler chambers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
- F04C29/068—Silencing the silencing means being arranged inside the pump housing
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
Abstract
The utility model relates to a compressor technical field in general, concretely, relate to a flange structure, a compressor and air conditioner, flange structure adopts two-layer amortization structure, first amortization spare surrounds with the flange body and forms main amortization chamber and vice amortization chamber, second amortization spare surrounds with first amortization spare and forms second amortization chamber, double-deck amortization structure has prolonged the refrigerant flow path after the compressor exhaust, second amortization chamber carries out the secondary amortization to the refrigerant, thereby reduce the exhaust noise of compressor, first main amortization chamber combines the effect that has the reduction broadband and reduce specific peak frequency with vice amortization chamber, further improve the noise reduction effect, the refrigerant gets into flange structure from first circulation passageway, get into second amortization chamber after main amortization chamber and vice amortization chamber fall noise, then flow flange structure is flowed out from the second circulation passageway, arrange to the compressor in, flange structure has reduced the air current noise, the flow loss of gaseous refrigerant reduces, optimize the compressor performance.
Description
Technical Field
The present application relates generally to the field of compressor technology, and more particularly, to a flange structure, a compressor, and an air conditioner.
Background
The compressor is the "heart" of the air conditioning system and the refrigerant is "blood". The compressor compresses low-temperature low-pressure refrigerant into high-temperature high-pressure steam, releases heat in the condenser to become liquid, throttles the liquid into a low-temperature low-pressure gas-liquid mixture through the expansion valve, enters the evaporator, absorbs heat in the evaporator to evaporate, and then enters the compressor to compress, so that one cycle is completed.
In the existing double-cylinder rotor compressor assembly, a lower silencer arranged in the compressor plays a key role in vibration reduction and noise reduction. At present, a lower silencer is arranged in the compressor, refrigerant of the compressor is discharged through an exhaust port and then enters the silencer connected with a lower flange of the compressor, however, the existing silencer only has one silencing cavity, and the silencing cavity can only eliminate airflow noise with specific frequency, but can not eliminate noise with other frequency bands, so that the overall noise of the exhaust of the compressor is still larger.
Disclosure of Invention
In the summary, a series of concepts in a simplified form are introduced, which will be further described in detail in the detailed description. This summary is not intended to identify key features or essential features of the claimed subject matter, nor is it intended to be used as an aid in determining the scope of the claimed subject matter.
In order to solve the technical problem that the noise reduction effect of the existing compressor is poor, the main aim of the application is to provide a flange structure, a compressor and an air conditioner.
In order to achieve the purpose of the invention, the application adopts the following technical scheme:
the utility model provides a flange structure, includes flange body, first amortization spare and second amortization spare, the flange body has been seted up the axial and has been run through first circulation passageway and the second circulation passageway of flange body, first amortization spare install in the flange body, and with the flange body surrounds and forms main amortization chamber and vice amortization chamber, vice amortization chamber intercommunication main amortization chamber, main amortization chamber with first circulation passageway intercommunication, the second amortization spare install in the flange body, and with form the second amortization chamber between the first amortization spare, the second amortization chamber respectively with main amortization chamber with second circulation passageway intercommunication.
Further, in some embodiments of the present application, the flange body is at least axially stacked with two first silencing members, and a sandwich silencing cavity is formed between two adjacent first silencing members.
Further, in some embodiments of the present application, the main silencing chamber is provided with a communication channel for communicating with the second silencing chamber.
Further, in some embodiments of the present application, the cross-sectional area of the communication channel is defined as S 1 The cross-sectional area of the first flow channel is defined as S 2 ；
Wherein S is more than 0.2 and less than 1 /S 2 ＜0.6。
Further, in some embodiments of the present application, the cross-sectional area of the communication channel is defined as S 1 The cross-sectional area of the second flow channel is defined as S 3 ；
Wherein S is more than 0.6 and less than 1 /S 3 ＜2。
Further, in some embodiments of the present application, the volume of the main silencing chamber is defined as V 1 The volume of the second silencing cavity is defined as V 2 ；
Wherein 0.8 < V 1 /V 2 ＜2。
Further, in some embodiments of the present application, a plurality of the auxiliary silencing chambers are independently provided.
Further, in some embodiments of the present application, the plurality of the auxiliary silencing chambers are distributed along a circumferential direction of the flange body.
A compressor is provided with the flange structure.
Further, in some embodiments of the present application, the compressor further includes a pump body assembly and an upper flange mounted above the pump body assembly, and the flange structure is mounted below the pump body assembly.
An air conditioner is provided with the compressor.
According to the technical scheme, the flange structure, the compressor and the air conditioner have the advantages that:
the flange structure adopts two-layer amortization structure in this application, first amortization piece surrounds with the flange body and forms main amortization chamber and vice amortization chamber, second amortization piece surrounds with first amortization piece and forms the second amortization chamber, thereby prolonged the refrigerant flow path after the compressor is exhausted, the amortization path has been prolonged promptly, the second amortization chamber carries out the secondary amortization to the refrigerant, the exhaust noise of compressor has been reduced, main amortization chamber and vice amortization chamber combine have the effect that reduces the broadband and reduce specific peak frequency, further improve the noise reduction effect of two-layer amortization structure, the in-process of making an uproar falls, the refrigerant gets into flange structure from first circulation passageway, get into the second amortization chamber after main amortization chamber and vice amortization chamber fall the noise, then flow flange structure from second circulation passageway outflow flange, the casing chamber in the compressor is arranged to, flange structure wholly has reduced the air current noise, the flow loss of gaseous refrigerant is reduced, the air current pulsation that the compressor is exhausted and is produced is reduced, the compressor performance is optimized.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the invention and together with the description, serve to explain the principles of the invention.
In order to more clearly illustrate the embodiments of the invention or the technical solutions of the prior art, the drawings which are used in the description of the embodiments or the prior art will be briefly described, and it will be obvious to a person skilled in the art that other drawings can be obtained from these drawings without inventive effort.
Fig. 1 is a schematic diagram of a compressor according to an exemplary embodiment.
Fig. 2 is a partially enlarged structural schematic diagram of fig. 1, shown according to an exemplary embodiment.
Fig. 3 is a schematic diagram of a pump body structure according to an exemplary embodiment.
Fig. 4 is a schematic partial cross-sectional view of a pump body structure according to an exemplary embodiment.
Fig. 5 is a first schematic view of a pump body structure including a first silencer according to an exemplary embodiment.
Fig. 6 is another schematic view of a pump body structure including a first structure of a first silencer according to an exemplary embodiment.
Fig. 7 is a schematic view showing a pump body structure including a first silencer and a second structure according to an exemplary embodiment.
Fig. 8 is a schematic view showing a pump body structure including a third structure of the first muffler according to an exemplary embodiment.
Fig. 9 is a schematic view of a second silencer of a pump body structure according to an exemplary embodiment.
FIG. 10 is a V illustrated in accordance with an exemplary embodiment 1 /V 2 The ratio is plotted against compressor noise and performance.
FIG. 11 is an illustration of S according to an exemplary embodiment 1 /S 2 The ratio is plotted against compressor noise and performance.
FIG. 12 is an illustration of S according to an exemplary embodiment 1 /S 3 The ratio is plotted against compressor noise and performance.
Wherein reference numerals are as follows:
100-a flange body; 200-a first silencing member; 300-a second muffler; 400-knockout; 500-pump body assembly; 600-crank shaft; 700-upper flange; 800-motor assembly;
110-shaft holes; 120-a first flow-through channel; 130-a second flow-through channel;
210-a main silencing chamber; 220-a secondary sound deadening chamber; 230-grooves; 240-communication channels;
310-a second sound attenuation chamber.
Detailed Description
For the purposes of making the objects, technical solutions and advantages of the embodiments of the present application more clear, the technical solutions of the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is apparent that the described embodiments are some embodiments of the present application, but not all embodiments. All other embodiments, which can be made by those skilled in the art without making any inventive effort, based on the embodiments herein, are intended to be within the scope of the present application, and therefore the following detailed description of the embodiments of the invention provided in the accompanying drawings is not intended to limit the scope of the invention as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
In the existing double-cylinder rotor compressor assembly, a lower silencer is built in, refrigerant enters the silencer connected with a lower flange of the compressor, a silencing cavity is formed in the silencer, and an expansion structure of the silencer has a reducing effect on partial exhaust noise. In order to solve the technical problem that the silencing effect of the existing compressor is poor, this application provides a flange structure, compressor and air conditioner, this compressor is installed to the air conditioner, this flange structure is installed to the compressor, the flange structure adopts two-layer amortization structure, first amortization piece 200 and flange body 100 surround and form main amortization chamber 210 and vice amortization chamber 220, main amortization chamber 210 and vice amortization chamber 220 intercommunication, second amortization piece 300 and first amortization piece 200 surround and form second amortization chamber 310, the refrigerant gets into main amortization chamber 210 through first circulation passageway 120, make an uproar falls under the effect of main amortization chamber 210 and vice amortization chamber 220, refrigerant inflow second amortization chamber 310 in main amortization chamber 210, then flow out from second circulation passageway 130 to the refrigerant, the flow path of refrigerant has been prolonged, reduce the exhaust noise of compressor, main amortization chamber 210 has the effect of reducing the wide frequency, vice amortization chamber 220 has the effect of reducing specific peak frequency, the effect of reducing the noise of making an uproar of flange structure, the flow loss of gaseous refrigerant is reduced, optimize the compressor performance.
Fig. 1 is a schematic diagram of a compressor according to an exemplary embodiment. Fig. 2 is a partially enlarged structural schematic diagram of fig. 1, shown according to an exemplary embodiment.
The compressor includes flange body 100, first amortization piece 200, second amortization piece 300, knockout 400, pump body subassembly 500, bent axle 600, go up flange 700 and motor element 800, pump body subassembly 500 and bent axle 600 assembly, bent axle 600 connection motor element 800, go up flange 700 and flange body 100 and be connected with bent axle 600 assembly respectively, go up flange 700 and install in the upper portion of pump body subassembly 500, flange body 100 installs in the lower part of pump body subassembly 500, go up flange 700 and flange body 100 respectively with body subassembly two compression chamber about forming, two compression chamber communicate with the suction structure of knockout 400 respectively, lower amortization chamber communicates with the first flow channel 120 of flange body 100. The first silencing member 200 and the second silencing member 300 are respectively installed on the back side of the flange body 100, a first layer of silencing structure is formed between the first silencing member 200 and the flange body 100, the first layer of silencing structure comprises a main silencing cavity 210 and a secondary silencing cavity 220, the main silencing cavity 210 is communicated with the secondary silencing cavity 220, the first flow channel 120 is communicated with the main silencing cavity 210, the second silencing member 300 is connected with the flange body 100, the second silencing member 300 is arranged on the outer side of the first silencing member 200 and forms a second layer of silencing structure with the first silencing member 200, the second layer of silencing structure comprises a second silencing cavity 310, and the second flow channel 130 is communicated with the second silencing cavity 310.
The refrigerant enters the pump body assembly 500 from the liquid separator 400 to be compressed, the refrigerant is compressed into a high-temperature high-pressure gaseous refrigerant, the high-temperature high-pressure gaseous refrigerant enters the main silencing cavity 210 through the first flow channel 120, the auxiliary silencing cavity 220 is communicated with the main silencing cavity 210, the high-pressure gaseous refrigerant flows from the main silencing cavity 210 to the auxiliary silencing cavity 220 and then flows back to the main silencing cavity from the auxiliary silencing cavity 220, the main silencing cavity 210 serves as an expansion silencing structure, the effect of broadband noise reduction is achieved, the auxiliary silencing cavity 220 serves as a Helmholtz type resonant cavity to reduce a specific peak value, the optimal silencing effect is achieved, the high-pressure gaseous refrigerant in the main silencing cavity enters the second silencing cavity 310 from the communication channel 240, and finally is discharged from the second flow channel 130. In this application, form double-deck amortization structure on this flange body 100, carry out twice amortization to high-pressure gaseous refrigerant, effectively reduce compressor exhaust noise, first layer amortization structure has main amortization chamber 210 and vice amortization chamber 220, can effectively reduce the air current noise, and reasonable design main amortization chamber 210 and second amortization chamber 310 can reduce gaseous refrigerant's flow loss, the compressor performance of optimization.
On the basis of the principle, the application understands with this way that first silencing piece 200 is provided with two or more, a plurality of first silencing pieces 200 connect gradually to the axial range upon range of setting at flange body 100 forms the intermediate layer amortization chamber between two adjacent first silencing pieces 200, and the intermediate layer amortization chamber also has main amortization chamber and vice amortization chamber, because the communication channel 240 has been seted up to every first silencing piece 200, the communication channel dislocation set of two adjacent first silencing pieces, two adjacent intermediate layer amortization chambeies are through the communication channel intercommunication, thereby realize carrying out multiple amortization to pump body subassembly 500 exhaust gas, further flange structure's improvement amortization effect.
Fig. 3 is a schematic diagram of a pump body structure according to an exemplary embodiment. Fig. 4 is a schematic partial cross-sectional view of a pump body structure according to an exemplary embodiment.
Fig. 3 is a schematic front view of the flange body 100, the front surface of the flange body 100 faces the pump body assembly 500, the middle portion of the flange body is provided with a shaft hole 110, the shaft hole 110 is used for being matched with the crankshaft 600, the first flow channel 120 and the second flow channel 130 respectively penetrate through the flange body 100 in the axial direction, in this embodiment, the first flow channel 120 and the second flow channel 130 respectively penetrate through the holes of the flange body 100 in the axial direction, one first flow channel 120 is provided, two second flow channels 130 are provided, the two second flow channels 130 are close to each other relative to the first flow channel 120, interference between air inlet and air outlet of the flange structure is avoided, and installation of the flange body 100 is facilitated.
Under the understanding of those skilled in the art, in combination with the air intake and exhaust amount and the noise reduction requirement of the compressor, the number of the first flow channels 120 and the second flow channels 130 can be reset, so that the flange structure achieves the best noise reduction effect.
In fig. 4, the first silencing member 200 and the second silencing member 300 are sequentially installed on the back side of the flange body 100, and the second silencing member 300 covers the first silencing member 200, and the bottom of the first silencing member 200 is provided with a communication channel 240, so that the main silencing cavity 210 is communicated with the second silencing cavity 310 through the communication channel 240. In this embodiment, the communication channel 240 includes a through hole formed at the bottom of the first silencing member 200, the refrigerant in the main silencing cavity 210 can enter the second silencing cavity 310 through the communication channel 240, and under the understanding of those skilled in the art, according to the exhaust noise reduction requirement of the compressor, one, two or more communication channels 240 can be provided, when the number of the communication channels 240 increases, the amount of refrigerant flowing from the main silencing cavity 210 to the second silencing cavity 310 in unit time can be increased, so as to reduce the flow loss of the gaseous refrigerant.
Fig. 5 is a first structural schematic view of a pump body structure including the first silencer 200 according to an exemplary embodiment, fig. 6 is another view schematically illustrating a pump body structure including the first silencer 200 according to an exemplary embodiment, fig. 7 is a second structural schematic view of a pump body structure including the first silencer 200 according to an exemplary embodiment, fig. 8 is a third structural schematic view of a pump body structure including the first silencer 200 according to an exemplary embodiment, and fig. 9 is a second structural schematic view of a pump body structure 300 according to an exemplary embodiment.
Referring to fig. 5 and 6, a main silencing cavity 210 and a sub silencing cavity 220 are formed between the first silencing member 200 and the flange body 100, the communication channel 240 includes two through holes formed at the bottom of the main silencing cavity 210, the first silencing member 200 is provided with a groove 230 for communicating the main silencing cavity 210 with the sub silencing cavity 220, the main silencing cavity 210 plays a role in broadband noise reduction, and the sub silencing cavity 220 plays a role in reducing a specific peak value as a helmholtz type resonant cavity.
Helmholtz type resonant cavity muffling formula:
in the formula, f r -a muffling frequency in Hz; c-sound propagation velocity in m/s 2 The method comprises the steps of carrying out a first treatment on the surface of the V-the volume of the auxiliary silencing cavity 220, unit m 3 ；S 0 Cross-sectional area of groove 230, unit m 2 ；L k The length of the groove 230, the unit m, on the basis of the present application, the volume of the auxiliary silencing cavity 220 and the shape and size of the groove 230 can be adjusted according to the formula, so that the auxiliary silencing cavity 220 can be silencing against specific frequency, thereby achieving the optimal silencing effect, in the present application, the main silencing cavity 210 and the auxiliary silencing cavity 220 are simultaneously formed in the first silencing piece 200, the refrigerant passes through the auxiliary silencing cavity 220 from the main silencing cavity 210 and returns to the main silencing cavity 210, and finally enters the second silencing cavity 310 through the communication channel 240, thereby slowing down the flow speed of the refrigerant in the flange structure, optimizing the flow path of the refrigerant in the flange structure, and reducing the high-pressure gaseous coldThe auxiliary silencing cavity 220 can slow down the flow speed of the refrigerant in the flange structure due to abnormal noise caused by high-speed movement of the refrigerant in the flange structure, and the auxiliary silencing cavity 220 is used as a Helmholtz type resonant cavity, so that noise can be reduced, pressure fluctuation of the refrigerant can be reduced, pressure pulsation is reduced, flow loss of the refrigerant is reduced, and performance of the compressor is improved.
In this embodiment, it can be further understood that a plurality of auxiliary silencing cavities 220 are provided, the plurality of auxiliary silencing cavities 220 are distributed along the circumferential direction of the flange body 100, and a groove 230 is provided between each auxiliary silencing cavity 220 and the main silencing cavity 210, because the auxiliary silencing cavities 220 can reduce the flow velocity of the refrigerant, the flow velocity of the refrigerant in one auxiliary silencing cavity 220 farthest from the main silencing cavity 210 is slowest, the size of the groove 230 between each auxiliary silencing cavity 220 and the main silencing cavity 210 is changed according to the helmholtz type resonant cavity silencing formula, so that silencing of different frequencies is realized, and the silencing effect of the flange structure is improved.
In this application, on the basis of the above principle, the communication channel 240 may also adopt other structural forms, referring to fig. 7, the first silencing member 200 is provided with a notch corresponding to the main silencing cavity 210, the notch may be in a semicircular, crescent or polygonal structure, and after the first silencing member 200 is assembled with the flange body 100, the notch of the first silencing member 200 and the outer wall of the flange body 100 enclose to form the communication channel 240. Referring to fig. 8, according to the diameter of the portion of the flange body 100 for the engagement with the first sound attenuating member 200, an annular communication passage 240 is formed between the first sound attenuating member 200 and the flange body 100.
Referring to fig. 4 in conjunction with fig. 9, the second sound-deadening member 300 is substantially plum-blossom-shaped, and the second sound-deadening member 300 is provided with a concave cavity for forming the second sound-deadening chamber 310, the outline of the concave cavity being larger than the outline of the first sound-deadening member 200, so that the second sound-deadening chamber 310 is formed between the first sound-deadening member 200 and the second sound-deadening member 300 when the second sound-deadening member 300 is covered outside the first sound-deadening member 200.
FIG. 10 is a V illustrated in accordance with an exemplary embodiment 1 /V 2 The ratio is plotted against compressor noise and performance.
In this embodiment, the volume of the main silencing chamberDefined as V 1 The volume of the second sound deadening chamber 310 is defined as V 2 Wherein 0.8 < V 1 /V 2 When the ratio is too large or too small, the morphology of the two-layer silencing structure changes, and the noise eliminating effect becomes weak, as shown in FIG. 10, when 0.8 < V 1 /V 2 And when the noise is less than 2, the performance and the noise optimization effect of the compressor are in a good state.
V 1 、V 2 Is not easy to be arranged too large, V 1 、V 2 The installation space of the pump body assembly 500 inside the compressor can be influenced by the arrangement too much, the effective oil quantity of the compressor is reduced, the oil shortage phenomenon of the compressor is easy to occur, the noise elimination effect is reduced if the design is too small, and meanwhile, the performance of the compressor can be obviously reduced easily.
FIG. 11 is an illustration of S according to an exemplary embodiment 1 /S 2 FIG. 12 is a graph showing the relationship between ratio and compressor noise and performance, S according to an exemplary embodiment 1 /S 3 The ratio is plotted against compressor noise and performance.
In the present embodiment, the sum of the cross-sectional areas of the communication passages 240 is defined as S 1 Taking the design of two communication channels 240 as an example in FIG. 6, S 1 The cross-sectional area of the first communication passage 120 is defined as S, which is the sum of the cross-sections of the two communication passages 240 2 And 0.2 < S 1 /S 2 < 0.6, defining the cross-sectional area of the second flow passage 130 as S 3 Wherein 0.6 < S 1 /S 3 ＜2，S 1 And S is equal to 2 Ratio of (2) and S 1 And S is equal to 3 The ratio of (2) affects the pulsation and flow loss of the air flow in the flange structure, and the noise elimination effect is reduced when the ratio is too large, and the performance of the compressor is significantly reduced when the ratio is too small, as shown in fig. 11-12, when 0.2 < S 1 /S 2 < 0.6 and 0.6 < S 1 /S 3 When the pressure is less than 2, the performance and the noise optimization effect of the compressor are in a good state, and simultaneously, the refrigerant discharged from the compression cavity smoothly passes through the main silencing cavity 210, the auxiliary silencing cavity 220 and the second silencing cavity 310, so that the air flow pulsation is reduced, the flow loss is reduced, and the performance of the compressor is improved.
According to realityVerification and simulation contrast verification show that V 1 、V 2 、S 1 、S 2 S and S 3 The values are mutually influenced in terms of noise reduction, and V is more than 0.8 and less than V 1 /V 2 ＜2，0.2＜S 1 /S 2 ＜0.6，0.6＜S 1 /S 3 Any one of the three relations less than 2, or any two of the three relations are satisfied at the same time, or the three relations are satisfied at the same time, the noise of the compressor in operation is greatly reduced, and the performance is also obviously improved.
The embodiment also provides a compressor, and the compressor is provided with the flange structure.
The embodiment also provides an air conditioner, and the air conditioner is provided with the compressor.
In summary, the present application provides a flange structure, a compressor and an air conditioner, the flange structure includes a flange body 100, a first silencing member 200 and a second silencing member 300, a main silencing cavity 210 and an auxiliary silencing cavity 220 are formed between the first silencing member 200 and the flange body 100, a refrigerant passes through the auxiliary silencing cavity 220 from the main silencing cavity 210 and returns to the main silencing cavity 210, the flow speed of the refrigerant in the flange body 100 can be slowed down, the refrigerant flow path is optimized, the abnormal noise caused by the high-pressure gaseous refrigerant moving at a high speed in the flange structure is reduced, a second silencing cavity 310 is formed between the second silencing member 300 and the first silencing member 200, the refrigerant passes through a communication channel 240 and enters the second silencing cavity 310 after returning to the main silencing cavity 210 from the auxiliary silencing cavity 220, the double-layer silencing structure further reduces the exhaust noise of the compressor, and is set to be 0.8 < V 1 /V 2 ＜2，0.2＜S 1 /S 2 ＜0.6，0.6＜S 1 /S 3 In the relation of < 2, the refrigerant discharged from the compression chamber smoothly passes through the main silencing chamber 210, the auxiliary silencing chamber 220 and the second silencing chamber 310, so that air flow pulsation generated by the exhaust of the compressor is reduced, flow loss is reduced, and the performance of the compressor is improved.
It should be noted that in this document, relational terms such as "first" and "second" and the like are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Moreover, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one … …" does not exclude the presence of other like elements in a process, method, article, or apparatus that comprises the element.
The foregoing is only a specific embodiment of the invention to enable those skilled in the art to understand or practice the invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the general inventive concept. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (9)
1. A flange structure, comprising:
a flange body (100) provided with a first circulation channel (120) and a second circulation channel (130) which axially penetrate through the flange body (100);
the first silencing piece (200) is arranged on the flange body (100) and is surrounded with the flange body (100) to form a main silencing cavity (210) and an auxiliary silencing cavity (220), the auxiliary silencing cavity (220) is a Helmholtz type resonant cavity, the auxiliary silencing cavity (220) is communicated with the main silencing cavity (210) through a groove (230) arranged on the first silencing piece (200), the main silencing cavity (210) is communicated with the first circulating channel (120), and the cross section area of the groove (230) is smaller than that of the auxiliary silencing cavity (220); and
a second silencing member (300) mounted on the flange body (100) and forming a second silencing cavity (310) with the first silencing member (200), wherein the second silencing cavity (310) is respectively communicated with the main silencing cavity (210) and the second circulation channel (130);
the first silencing piece (200) is provided with a communication channel (240) used for communicating the main silencing cavity (210) with the second silencing cavity (310), and the communication channel (240) comprises two through holes formed in the bottom of the main silencing cavity (210);
the sum of the cross-sectional areas of the two communication channels (240) is defined as S 1 The cross-sectional area of the first flow channel (120) is defined as S 2 ；
Wherein S is more than 0.2 and less than 1 /S 2 ＜0.6。
2. Flange structure according to claim 1, wherein the flange body (100) is provided with at least two first silencing members (200) in an axial stack, and wherein an intermediate silencing chamber is formed between adjacent two first silencing members (200).
3. Flange structure according to claim 1, characterized in that the sum of the cross-sectional areas of two of said communication channels (240) is defined as S 1 The cross-sectional area of the second flow channel (130) is defined as S 3 ；
Wherein S is more than 0.6 and less than 1 /S 3 ＜2。
4. The flange structure according to claim 1, wherein the volume of the main sound attenuation chamber (210) is defined as V 1 The volume of the second silencing chamber (310) is defined as V 2 ;
Wherein 0.8 < V 1 /V 2 ＜2。
5. Flange structure according to claim 1, characterized in that the secondary sound-deadening chamber (220) is provided independently in plurality.
6. The flange structure according to claim 5, wherein a plurality of the sub-muffler chambers (220) are distributed along a circumferential direction of the flange body (100).
7. A compressor, characterized in that a flange structure according to any one of claims 1-6 is installed.
8. The compressor of claim 7, further comprising a pump body assembly (500) and an upper flange (700) mounted above the pump body assembly (500), the flange structure being mounted below the pump body assembly (500).
9. An air conditioner, characterized in that the compressor of claim 8 is installed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110322086.XA CN113007097B (en) | 2021-03-25 | 2021-03-25 | Flange structure, compressor and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110322086.XA CN113007097B (en) | 2021-03-25 | 2021-03-25 | Flange structure, compressor and air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113007097A CN113007097A (en) | 2021-06-22 |
| CN113007097B true CN113007097B (en) | 2023-05-12 |
Family
ID=76407331
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110322086.XA Active CN113007097B (en) | 2021-03-25 | 2021-03-25 | Flange structure, compressor and air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113007097B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113638862A (en) * | 2021-09-08 | 2021-11-12 | 松下·万宝(广州)压缩机有限公司 | Compressor pump body and compressor |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0649796U (en) * | 1992-12-17 | 1994-07-08 | 株式会社東芝 | Rotary compressor |
| KR20050097340A (en) * | 2004-04-01 | 2005-10-07 | 엘지전자 주식회사 | Muffler for hermetic type compressor |
| CN1763378A (en) * | 2004-10-21 | 2006-04-26 | 乐金电子(天津)电器有限公司 | Compressors muffler with resonance cavity |
| CN202991397U (en) * | 2012-11-22 | 2013-06-12 | 广东美芝制冷设备有限公司 | Silencer of compressor and compressor with same |
| CN104481885B (en) * | 2014-12-02 | 2017-02-22 | 广东美芝制冷设备有限公司 | Compressor |
| JP2018031303A (en) * | 2016-08-25 | 2018-03-01 | 三菱重工サーマルシステムズ株式会社 | Compressor |
| CN207131585U (en) * | 2017-07-26 | 2018-03-23 | 安徽美芝精密制造有限公司 | Bearing assembly and compressor |
| CN110685887A (en) * | 2019-10-15 | 2020-01-14 | 珠海凌达压缩机有限公司 | Silencer and compressor comprising same |
-
2021
- 2021-03-25 CN CN202110322086.XA patent/CN113007097B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN113007097A (en) | 2021-06-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPS6211200B2 (en) | ||
| CN211008996U (en) | Silencer, compressor and refrigerator | |
| CN104481885B (en) | Compressor | |
| CN113007097B (en) | Flange structure, compressor and air conditioner | |
| CN113357129B (en) | Exhaust noise reduction structure, compressor and refrigeration equipment | |
| CN110821782A (en) | Silencer, compressor and refrigerator | |
| CN110067733A (en) | A kind of noise elimination structure and its sound reduction method of compressor | |
| CN210118237U (en) | Noise elimination structure of compressor | |
| CN111765086A (en) | Compression pump body assembly, compressor and air conditioner | |
| CN115288980A (en) | Muffler and compressor | |
| CN112483396A (en) | Compressor pump body and compressor | |
| CN112177885A (en) | Silencer, compressor and refrigerator | |
| CN111946593A (en) | Air suction silencer and compressor with same | |
| CN114763754A (en) | Silencer | |
| CN114576167A (en) | Compressor body | |
| CN219868163U (en) | Indoor unit of air conditioner | |
| CN210565113U (en) | Pump body subassembly, compressor and air conditioner | |
| CN219101599U (en) | Exhaust silencing structure and compressor | |
| CN212296875U (en) | Compression pump body assembly, compressor and air conditioner | |
| CN214742064U (en) | Compressor pump body and compressor | |
| CN218722426U (en) | Gas-liquid separator, compressor assembly and air conditioner with compressor assembly | |
| CN217421325U (en) | Large-displacement silencer | |
| CN218598327U (en) | Silencer, compressor assembly and household appliance | |
| CN213743898U (en) | Suction muffler with honeycomb hole structure and compressor | |
| CN113217341B (en) | Sound deadening structure, compressor and refrigerator with same |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |