CN113323876B - Air suction supercharging structure of compressor and compressor - Google Patents
Air suction supercharging structure of compressor and compressor Download PDFInfo
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- CN113323876B CN113323876B CN202110758187.1A CN202110758187A CN113323876B CN 113323876 B CN113323876 B CN 113323876B CN 202110758187 A CN202110758187 A CN 202110758187A CN 113323876 B CN113323876 B CN 113323876B
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- 238000000034 method Methods 0.000 claims abstract description 6
- 238000007789 sealing Methods 0.000 claims description 32
- 238000009434 installation Methods 0.000 claims description 6
- 230000002093 peripheral effect Effects 0.000 claims description 6
- 239000003507 refrigerant Substances 0.000 abstract description 9
- 230000001133 acceleration Effects 0.000 abstract description 2
- 230000029058 respiratory gaseous exchange Effects 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 30
- 230000000694 effects Effects 0.000 description 7
- 230000003068 static effect Effects 0.000 description 7
- 239000010687 lubricating oil Substances 0.000 description 5
- 230000002411 adverse Effects 0.000 description 4
- 238000000926 separation method Methods 0.000 description 4
- 230000003584 silencer Effects 0.000 description 4
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000007599 discharging Methods 0.000 description 2
- 239000008187 granular material Substances 0.000 description 2
- 230000000670 limiting effect Effects 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000003292 glue Substances 0.000 description 1
- 230000009931 harmful effect Effects 0.000 description 1
- 230000003116 impacting effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
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- 230000010349 pulsation Effects 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/005—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of dissimilar working principle
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- 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
- F04C29/02—Lubrication; Lubricant separation
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- 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
- F04C29/02—Lubrication; Lubricant separation
- F04C29/026—Lubricant separation
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- 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
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- 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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The utility model provides a compressor inhale pressure intensifying structure and compressor, the pressure intensifying structure of breathing in includes the intake pipe, the drainage tube, first cavity and second cavity, the one end of drainage tube and the gas vent intercommunication of compressor are in order to introduce exhaust gas, the other end and first cavity intercommunication, the one end of intake pipe inhales the admit air gas, the other end and second cavity intercommunication, make the admit air gas of compressor get into in the second cavity through the intake pipe, the outside of second cavity is located to first cavity cover, perhaps the outside of first cavity is located to second cavity cover, and exhaust gas flows in first cavity and can carry out the acceleration and/or pressure boost to the admit air gas in the second cavity. According to the method and the device, the intake air is pressurized by utilizing the energy of the exhaust air, so that the energy is saved, meanwhile, the intake air is pressurized, the suction amount of the refrigerant of the compressor is increased, and the refrigerating capacity of the compressor is improved; meanwhile, the exhaust noise of the compressor is reduced, and the vibration of the compressor is reduced.
Description
Technical Field
The disclosure relates to the technical field of compressors, in particular to a suction supercharging structure of a compressor and the compressor.
Background
With the high-speed development of economy in China, household multi-split air conditioners and commercial multi-split air conditioners are widely applied, and with the improvement of the requirements on environmental protection, energy conservation and the like in China and abroad, the requirements on compressors in air conditioning systems are stricter. Effective means for improving the efficiency of the compressor comprise increasing the refrigerating capacity of the compressor, reducing the air suction and exhaust losses of the compressor, reducing the oil discharge rate of the compressor and the like. At present, the exhaust airflow of the compressor directly impacts a silencer or an upper cover of a shell, the kinetic energy of the exhaust airflow is wasted, and meanwhile, the high-speed impact airflow can cause adverse effects such as vibration and noise of the compressor.
Because the compressor among the prior art has direct impact muffler or casing upper cover of exhaust air current, has wasted the kinetic energy of exhaust air current, and the high-speed air current of strikeing simultaneously can cause technical problems such as harmful effects such as vibration and noise of compressor, consequently this disclosure research design a compressor inhale pressure intensifying structure and compressor.
BRIEF SUMMARY OF THE PRESENT DISCLOSURE
Therefore, the technical problem to be solved by the present disclosure is to overcome the defects that in the prior art, the exhaust gas directly impacts the muffler or the upper cover of the housing, the kinetic energy of the exhaust gas is wasted, and meanwhile, the high-speed impacting gas flow can cause adverse effects such as vibration and noise of the compressor, so as to provide a suction supercharging structure of the compressor and the compressor.
In order to solve the above problems, the present disclosure provides a suction boosting structure of a compressor, including:
the exhaust gas compressor comprises an air inlet pipe, a drainage pipe, a first cavity and a second cavity, wherein one end of the drainage pipe can be communicated with an exhaust port of the compressor to introduce exhaust gas, the other end of the drainage pipe is communicated with the first cavity, so that the exhaust gas of the compressor enters the first cavity through the drainage pipe, one end of the air inlet pipe sucks intake gas, the other end of the air inlet pipe is communicated with the second cavity, so that the intake gas of the compressor enters the second cavity through the air inlet pipe, the first cavity is sleeved outside the second cavity, or the second cavity is sleeved outside the first cavity, and the exhaust gas flows in the first cavity to accelerate and/or pressurize the intake gas in the second cavity.
In some embodiments, further comprising a vortex shield, a vortex blade, and a plenum, the interior of the vortex shield forming the first cavity, at least a portion of the plenum being disposed within the vortex shield and the interior of the plenum forming the second cavity;
the vortex cover is internally provided with the vortex blades, the vortex blades are arranged on the periphery of the pressure increasing pipe and can be driven by exhaust gas to rotate, and the vortex blades can drive the pressure increasing pipe to integrally rotate.
In some embodiments, the swirl vanes are plural, and the plural swirl vanes are circumferentially spaced apart on the outer peripheral wall of the pressure increasing duct.
In some embodiments, the cross section of the vortex shield is a circular ring-shaped structure, and the opening where the draft tube meets the vortex shield is along the circumferential tangential direction of the vortex shield, so that the exhaust gas entering the vortex shield is along the circumferential tangential direction of the vortex shield; and/or the number of the vortex hoods is at least two, and the two vortex hoods can be spliced with each other to form the first cavity.
In some embodiments, the gas inlet device further comprises an axial flow blade, the axial flow blade is disposed inside the pressure increasing pipe, and the axial flow blade can be driven to rotate along with the rotation of the pressure increasing pipe, so that the inlet gas is accelerated and/or pressurized through the axial flow blade.
In some embodiments, the vortex cover is further provided with an exhaust hole, and the exhaust hole can exhaust the gas after passing through the vortex blade to the outside of the first cavity; and/or the presence of a gas in the gas,
the vortex cover is further provided with an oil return hole, the oil return hole is communicated with the first cavity, and oil passing through the vortex blade can be led out of the first cavity through the oil return hole.
In some embodiments, when the vortex cover is further provided with an exhaust hole, the exhaust hole is formed in the outer peripheral surface of the vortex cover and formed along the circumferential tangential direction of the vortex cover, and the flow area of the exhaust hole is larger than or equal to the area of the exhaust port;
when the vortex cover is also provided with an oil return hole, the oil return hole is close to the exhaust hole relative to an opening at the joint of the drainage tube and the vortex cover; the oil return hole is a plurality of.
In some embodiments, the axial end of the booster pipe is provided with a sealing ring groove, and a sealing ring is sleeved in the sealing ring groove; and/or the axial end part of the booster pipe is also provided with a bearing.
In some embodiments, when both the sealing ring and the bearing are included, the bearing is installed at an outer circumference of the sealing ring, the compressor further includes a fixed scroll including an air inlet hole for air intake, one axial end of the booster duct is inserted into the air intake pipe, and the other axial end of the booster duct is inserted into the air inlet hole; the bearing comprises a first bearing and a second bearing, the first bearing is located between the air inlet pipe and the booster pipe, and the second bearing is located between the air inlet pipe and the booster pipe.
In some embodiments, the bearings are tapered roller bearings, the first bearing is a first tapered roller bearing, the second bearing is a second tapered roller bearing, and the first tapered roller bearing and the second tapered roller bearing are installed in opposite directions.
The present disclosure also provides a compressor including the suction boosting structure of the compressor of any one of the preceding claims.
The suction supercharging structure of the compressor and the compressor have the following beneficial effects:
according to the air compressor, the first cavity and the second cavity are arranged, the exhaust of the compressor is introduced into the first cavity through the drainage tube, the suction of the compressor is introduced into the second cavity through the air inlet pipe, the first cavity and the second cavity are sleeved with each other, so that the exhaust air flows in the first cavity and can accelerate and/or pressurize the intake air in the second cavity, therefore, the energy (including speed and pressure) of the exhaust air is effectively utilized to drive the speed and/or pressure of the intake air to be increased, the exhaust kinetic energy and the like are utilized through the pressurizing device, the exhaust energy is utilized to pressurize the intake air, the energy is saved, the suction air is pressurized, the refrigerant suction amount of the compressor is increased, and the refrigerating capacity of the compressor is improved; meanwhile, the exhaust speed and pressure are reduced, so that the exhaust noise of the compressor can be effectively reduced, the vibration of the compressor is reduced, and the problems that the exhaust airflow directly impacts a silencer or an upper cover of a shell, the kinetic energy of the exhaust airflow is wasted, and the high-speed impact airflow can cause the adverse effects of the vibration, the noise and the like of the compressor are effectively solved; and utilize turbine blade and vortex cover shell structure etc. can also carry out certain oil-gas separation to the compressor exhaust gas, reduce the oil yield of compressor, accomplish to promote compressor performance, further promote compressor's performance and reliability.
Drawings
Fig. 1 is an assembly structural view of a suction supercharging structure of a compressor of the present disclosure;
FIG. 2 is an exploded view of the suction plenum of the compressor of the present disclosure;
FIG. 3 is a front cross-sectional view of a booster tube assembly in the suction boosting configuration of the compressor of the present disclosure;
FIG. 4 is a top view of a booster tube assembly in the suction boosting configuration of the compressor of the present disclosure;
FIG. 5 is a connection view of a half of the swirl hood and the draft tube in the suction plenum of the compressor of the present disclosure;
fig. 6 is a connection diagram of the other half of the swirl housing in the suction supercharging structure of the compressor of the present disclosure.
FIG. 7 is a cross-sectional view of the overall assembly of the scroll compressor of the present disclosure.
The reference numerals are represented as:
100. a first cavity; 200. a second cavity; 1. a lower cover assembly; 2. a housing assembly; 3. a stator assembly; 4. a junction box; 5. a counterbalance; 6. a main bearing; 7. a support; 8. a static scroll pan; 81. an air inlet; 82. an exhaust port; 9. a pressurizing assembly; 10. an upper cover assembly; 11. a movable plate; 12. a cross slip ring; 13. a crankshaft; 14. a rotor assembly; 15. a foot pad; 901. an air inlet pipe; 902. a drainage tube; 903. a vortex cover; 904. a seal ring; 905. a bearing; 906. a pressure increasing pipe; 906a, axial flow blades; 906b, swirl vanes; 906d, a sealing ring groove; 907. an exhaust hole; 908. an oil return hole; 909. and (4) opening.
Detailed Description
As shown in fig. 1 to 7, the present disclosure provides a suction boosting structure of a compressor, which includes:
an air inlet pipe 901, a drainage pipe 902, a first cavity 100 and a second cavity 200, wherein one end of the drainage pipe 902 can be communicated with an exhaust port 82 of a compressor to introduce exhaust gas, the other end is communicated with the first cavity 100, so that the exhaust gas of the compressor enters the first cavity 100 through the drainage pipe 902, one end of the air inlet pipe 901 sucks in intake gas, the other end is communicated with the second cavity 200, so that the intake gas of the compressor enters the second cavity 200 through the air inlet pipe 901, the first cavity 100 is sleeved outside the second cavity 200 or the second cavity 200 is sleeved outside the first cavity 100 (the second cavity 200 can be at least partially accommodated in the first cavity 100 or the first cavity 100 can be at least partially accommodated in the second cavity 200), and the exhaust gas flows in the first cavity 100 and can enter the intake gas in the second cavity 200 Line acceleration and/or pressurization.
According to the air compressor, the first cavity and the second cavity are arranged, the exhaust of the compressor is introduced into the first cavity through the drainage tube, the suction of the compressor is introduced into the second cavity through the air inlet pipe, the first cavity and the second cavity are sleeved with each other, so that the exhaust air flows in the first cavity and can accelerate and/or pressurize the intake air in the second cavity, therefore, the energy (including speed and pressure) of the exhaust air is effectively utilized to drive the speed and/or pressure of the intake air to be increased, the exhaust kinetic energy and the like are utilized through the pressurizing device, the exhaust energy is utilized to pressurize the intake air, the energy is saved, the suction air is pressurized, the refrigerant suction amount of the compressor is increased, and the refrigerating capacity of the compressor is improved; meanwhile, the exhaust speed and pressure are reduced, the exhaust noise of the compressor can be effectively reduced, the vibration of the compressor is reduced, and the problems that the exhaust airflow directly impacts the silencer or the upper cover of the shell, the kinetic energy of the exhaust airflow is wasted, and the high-speed impact airflow can cause the adverse effects of the vibration, the noise and the like of the compressor are effectively solved.
1. The utility model provides a high efficiency supercharging device that admits air and have its compressor, the compressor mainly comprises spare parts such as pump body subassembly, shafting subassembly, motor element, casing subassembly and the supercharging subassembly of newly-increased. The supercharging component comprises an exhaust drainage tube, a vortex cover, a supercharging pipe with an axial flow blade and a vortex blade, a bearing, a sealing ring and the like;
2. the gas discharged by the compressor is introduced into the vortex cover by the drainage tube, the gas pushes the turbine blades to rotate, the whole pressure increasing tube is driven to rotate, so that the gas sucked by the compressor is accelerated by the axial flow blades in the pressure increasing tube to increase the kinetic energy, and the increased energy is converted into pressure energy in a subsequent cavity according to the Bernoulli principle, so that the suction capacity of a refrigerant of the compressor is increased, and the cold quantity of the compressor is increased;
3. the compressor discharges high gas speed, the traditional mode is that energy is consumed by collision and the like on a silencer or an upper cover, so that the noise and the vibration of the compressor are reduced, the impact effect of gas on a shell and the like can be effectively reduced by utilizing the energy through drainage, and the conditions of the vibration, the noise and the like of the compressor are reduced;
4. the air current can carry a certain amount of lubricating oil when the compressor exhausts, cause the compressor to spit oily rate high, influence the compressor refrigerating output, lubricating oil gets into follow-up refrigeration plant and attaches to the heat transfer surface, improve the thermal resistance, reduce heat exchange efficiency, this disclosure utilizes modes such as drainage to make gas promotion vortex blade, the promotion in-process heavier oil drips the granule can be through the collision, modes such as vortex are separated out, in the oil gallery through vortex cover flows back to the compressor at last, thereby reduce the compressor and spit oily rate, improve compressor cold volume and refrigerating system efficiency.
The utility model provides a suction supercharging device and have its compressor, utilize exhaust kinetic energy etc. through supercharging device, carry out the pressure boost to the suction, increase compressor refrigerant suction capacity, improve compressor refrigerating output; meanwhile, the exhaust noise of the compressor is reduced, and the vibration of the compressor is reduced; the turbine blade and the vortex cover shell structure are used for exhausting oil-gas separation, the oil discharge rate of the compressor is reduced, the performance of the compressor is improved, the reliability of the compressor is improved, and the like.
Has the advantages that:
1. the exhaust energy of the compressor is utilized, the air suction is pre-pressurized, and the air suction amount of the compressor is increased;
2. the exhaust pressure pulsation of the compressor is reduced, the impact of air flow on the shell is reduced, and the noise and the vibration of the compressor are reduced;
3. the oil-gas separation can be carried out on the exhaust gas, the oil discharge rate of the compressor is reduced, and the performance and the reliability of the compressor are improved.
In some embodiments, a vortex cover 903, a vortex blade 906b and a booster duct 906 are further included, the vortex cover 903 is internally formed into the first cavity 100, at least part of the booster duct 906 is arranged inside the vortex cover 903, and the booster duct 906 internally forms the second cavity 200;
the swirl cover 903 is provided with the swirl vanes 906b inside, the swirl vanes 906b are arranged on the periphery of the pressure increasing pipe 906, the swirl vanes 906b can be driven by exhaust gas to rotate, and the swirl vanes 906b can drive the pressure increasing pipe 906 to integrally rotate.
The vortex cover can form a first cavity, the pressure pipe can form a second cavity, at least part of the pressure pipe is inserted into the vortex cover, and the vortex blades fixedly arranged on the periphery of the pressure pipe can enable the pressure pipe to be impacted by exhaust gas to form rotation so as to drive the pressure pipe to rotate.
In some embodiments, the swirl vanes 906b are provided in plurality, and the plurality of swirl vanes 906b are circumferentially spaced apart on the outer peripheral wall of the pressure inlet duct 906. This is the preferred form of construction of the swirl vane of this disclosure, and the plurality of swirl vanes that are distributed at intervals can be impacted by the air current and drive the booster duct to form rotary motion.
In some embodiments, the cross section of the vortex hood 903 is a circular ring structure, and the opening 909 where the draft tube 902 meets the vortex hood 903 is along the circumferential tangential direction of the vortex hood 903, so that the exhaust gas entering the vortex hood 903 is along the circumferential tangential direction of the vortex hood 903; and/or the number of the vortex flow covers 903 is at least two, and the two vortex flow covers 903 can be spliced with each other to form the first cavity 100. According to the vortex cover, the vortex cover is arranged to be of the annular structure, the opening at the joint of the drainage tube and the vortex cover faces the circumferential tangential direction of the vortex cover, the direction of airflow sprayed into the first cavity from the opening can be enabled to be along the circumferential tangential direction of the vortex cover, and therefore the vortex blades are effectively pushed to rotate. The structure through a plurality of vortex covers can make a plurality of vortex covers splice and form the first cavity that is located its inside to the vortex of a plurality of concatenations covers can make things convenient for the dismantlement and the installation of vortex cover, makes the pressure boost pipe effectively set up wherein.
In some embodiments, the gas turbine further includes an axial flow blade 906a, the axial flow blade 906a is disposed inside the pressure increasing duct 906, and the axial flow blade 906a can be driven to rotate along with the rotation of the pressure increasing duct 906, so as to accelerate and/or increase the pressure of the intake gas through the axial flow blade 906 a. The axial flow blades are arranged in the second cavity of the pressure increasing pipe, so that the axial flow blades can be fixed on the inner peripheral wall of the pressure increasing pipe, and the pressure increasing pipe can drive the axial flow blades inside the pressure increasing pipe to rotate when being impacted by exhaust gas and rotate, so that the speed and the pressure of the inlet gas in the second cavity inside the pressure increasing pipe are increased towards the inlet hole of the static vortex disc along the axial direction, the inlet speed and the inlet pressure are increased, and the air inflow is increased.
The vortex blade, the booster pipe and the axial flow blade are of an integrally fixed structure.
In some embodiments, the vortex cover 903 is further provided with an exhaust hole 907, and the exhaust hole 907 can exhaust the gas passing through the vortex blade 906b to the outside of the first cavity 100; and/or the presence of a gas in the gas,
the vortex cover 903 is further provided with an oil return hole 908, the oil return hole 908 is communicated with the first cavity 100, and oil passing through the vortex blade 906b can be led out of the first cavity 100 through the oil return hole 908.
The exhaust hole arranged on the vortex cover can effectively lead the exhaust gas which has released the exhaust energy out of the first cavity; the oil return hole formed in the vortex cover can be used for collecting and discharging oil in exhaust gas which releases energy, and gas-liquid separation can be generated after the exhaust gas rotates in the vortex blade, so that the oil in the exhaust gas can be effectively separated, the oil spitting rate of the compressor is reduced, the performance of the compressor is improved, and the performance and the reliability of the compressor are further improved.
In some embodiments, when the vortex cover 903 is further provided with an exhaust hole 907, the exhaust hole 907 is opened on the outer circumferential surface of the vortex cover 903 and is opened along the circumferential tangential direction of the vortex cover 903, and the flow area of the exhaust hole 907 is greater than or equal to the area of the exhaust port;
when the vortex cover 903 is further provided with an oil return hole 908, the oil return hole 908 is arranged close to the exhaust hole 907 relative to the opening where the draft tube 902 is connected with the vortex cover 903; the number of the oil return holes 908 is plural.
The exhaust holes in the vortex cover are formed along the circumferential tangential direction of the vortex cover, so that exhaust resistance can be reduced, and the air inlet in the vortex cover is along the tangential direction, and the flow direction of the air inlet after the vortex cover drives the vortex blades to rotate is still along the tangential direction, so that the exhaust resistance can be reduced, and exhaust noise can be reduced; the flow area of the exhaust hole is larger than or equal to the area of the exhaust port 82 on the fixed scroll of the compressor, so that the exhaust resistance can be further reduced, the useless work in the exhaust process of the compressor is reduced, and the exhaust flow loss is reduced.
In some embodiments, an axial end of the pressure inlet 906 is provided with a sealing ring groove 906d, and the sealing ring groove 906d is sleeved with the sealing ring 904; and/or the axial end of the booster duct 906 is further provided with a bearing 905. The air leakage prevention device can effectively ensure the effective sealing effect of the air at the two ends of the booster pipe through the arrangement of the sealing ring groove and the sealing ring, and prevent the air leakage between the exhaust air and the intake air; the pressure increasing pipe can be effectively supported to the air inlet pipe and the static vortex disc at the same position through the bearing, and the effective rotation of the pressure increasing pipe is guaranteed.
In some embodiments, when both the sealing ring 904 and the bearing 905 are included, the bearing 905 is preferably installed on the outer circumference of the sealing ring 904, the compressor further includes a fixed scroll 8, the fixed scroll 8 includes an air inlet hole 81 for air intake, one axial end of the pressure increasing pipe 906 is inserted into the air inlet pipe 901, and the other axial end of the pressure increasing pipe 906 is inserted into the air inlet hole 81; the bearings include a first bearing located between the intake duct 901 and the booster duct 906, and a second bearing located between the intake duct 81 and the booster duct 906. According to the air inlet pipe structure, one end of the pressure increasing pipe is inserted into the air inlet pipe, the other end of the pressure increasing pipe is inserted into the air inlet hole of the static scroll disk, air in the air inlet pipe can be guided into the air inlet hole of the static scroll disk, the first bearing can support the position between the air inlet pipe and the pressure increasing pipe, and the second bearing can support the position between the pressure increasing pipe and the air inlet hole.
In some embodiments, the bearing 905 is a tapered roller bearing, the first bearing is a first tapered roller bearing, and the second bearing is a second tapered roller bearing, and the first tapered roller bearing and the second tapered roller bearing are installed in opposite directions. The axial float of the pressure increasing pipe can be limited through the opposite installation directions of the two tapered roller bearings, and the axial limiting effect is achieved.
The present disclosure also provides a compressor, preferably a scroll compressor, comprising a suction plenum of the compressor of any one of the preceding claims.
Fig. 2 is an exploded view of the assembled pressurizing assembly, which mainly comprises: the device comprises an air inlet pipe 901, a drainage pipe 902, two vortex hoods 903, 4 wear-resistant sealing rings 904, two conical roller bearings 905 and a pressure increasing pipe 906; the overall structure of the booster pipe 906 is as shown in fig. 3-3, a sealing ring groove 906d is arranged on the upper portion and the lower portion of a main body pipe body, 6-10 vortex blades 906b are arranged on the outer portion, 6 streamline axial flow blades 906a are arranged inside the pipe body, a wear-resistant sealing ring 904 is arranged in the sealing ring grooves at two ends of the booster pipe 906 during installation, tapered roller bearings 905 are arranged at two ends, and the two installation directions are opposite to each other, so that the axial movement of the structure is limited; then the lower part of the booster pipe is arranged in a bearing groove of the static scroll disk 8, the upper part of the booster pipe is arranged in a bearing groove of an air inlet pipe 901, and the air inlet pipe 901 of the booster pipe is welded at an air inlet pipe hole of the upper cover component 10; the outer side of a sealing ring at the sealing position of the lower part of the pressure increasing pipe 906 and the outer wall surface of a sealing ring groove are attached to the wall surface of a suction hole of the static scroll disk 8 to form a good dynamic sealing structure; the outer side of a sealing ring at the upper part of a sealing part of the pressurizing pipe 906 and the outer wall surface of a sealing ring groove are attached to the wall surface of the air inlet pipe 901 to form a good dynamic sealing structure; as shown in fig. 5, the draft tube 902 and a half of the vortex cover 903 are integrally connected with the vortex cover 903 in a streamline shape, the draft direction is introduced in a circumferential tangential direction, the rear end of the draft tube is circular and is matched with an installation groove milled at an exhaust port of the fixed scroll 8, and the draft tube and the half of the vortex cover 903 are fixedly installed in an interference tight fit manner; the other half of the vortex cover 903 is shown in FIG. 6, and can be formed by fixing two vortex covers by spot welding or metal glue to form a complete vortex cover, and wrapping the vortex blades of the pressure increasing pipe 906 therein; the vortex cover 903 is provided with an exhaust hole 907 tangentially along the circumferential direction, the flow area of the exhaust hole is not smaller than that of the exhaust port 82 of the compressor, and 3-5 oil return holes for discharging separated lubricating oil are formed at the position, close to the exhaust hole, of the lowest position of the vortex cover 903.
In the working process of the compressor, compressed refrigerant gas is discharged from an exhaust port of the fixed scroll 8, and is introduced into the vortex cover 903 through the drainage pipe 902 to push the vortex blades 906b to rotate, so that the whole pressure increasing pipe 906 is driven to rotate, the rotation of the internal axial flow blades 906a accelerates the refrigerant gas in the air inlet pipe, so that the overall energy of the refrigerant gas is increased, and the increased energy reduces the speed in the subsequent chamber and is converted into pressure energy according to the Bernoulli principle, so that the suction capacity of the refrigerant of the compressor is increased, and the cold quantity of the compressor is increased; the speed of the gas discharged by the compressor is high, and the energy is utilized by the drainage of the drainage pipe 902, so that the impact effect of the gas on a shell and the like can be effectively reduced, and the conditions of vibration, noise and the like of the compressor are reduced; the air current can carry a certain amount of lubricating oil when the compressor exhausts, cause the compressor to tell the oil rate high, influence the compressor cold volume, lubricating oil gets into follow-up refrigeration plant and attaches to the heat transfer surface, improve the thermal resistance, reduce heat exchange efficiency, this disclosure makes gas promotion vortex blade through modes such as drainage tube 902 drainage, the heavier oil droplet granule of promotion in-process can be through colliding, modes such as whirl flows are separated out, collect in vortex cover 903, return oil hole through vortex cover 903 at last flows back in the compressor, thereby reduce the compressor and tell the oil rate, improve compressor cold volume and refrigerating system efficiency.
The above description is only exemplary of the present disclosure and should not be taken as limiting the disclosure, as any modification, equivalent replacement, or improvement made within the spirit and principle of the present disclosure should be included in the scope of the present disclosure. The foregoing is only a preferred embodiment of the present disclosure, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present disclosure, and these modifications and variations should also be regarded as the protection scope of the present disclosure.
Claims (11)
1. The utility model provides a compressor inhale air pressure boost structure which characterized in that: the method comprises the following steps:
an air inlet pipe (901), a drainage pipe (902), a first cavity (100) and a second cavity (200), one end of the draft tube (902) can communicate with a discharge port (82) of a compressor to introduce discharge gas, and the other end communicates with the first chamber (100), so that the discharge gas of the compressor enters the first cavity (100) through the draft tube (902), one end of the air inlet pipe (901) sucks in inlet air, the other end of the air inlet pipe is communicated with the second cavity (200), so that the inlet air of the compressor enters the second cavity (200) through the inlet pipe (901), the first cavity (100) is sleeved outside the second cavity (200), or the second cavity (200) is sleeved outside the first cavity (100), and the exhaust gas flowing in the first cavity (100) can accelerate and/or pressurize the intake gas in the second cavity (200).
2. The suction supercharging structure of a compressor according to claim 1, wherein:
the vortex cover (903) is internally formed into the first cavity (100), at least part of the booster pipe (906) is arranged inside the vortex cover (903), and the booster pipe (906) is internally formed into the second cavity (200);
the vortex cover (903) is internally provided with the vortex blades (906b), the vortex blades (906b) are arranged on the periphery of the pressure increasing pipe (906), the vortex blades (906b) can be driven by exhaust gas to rotate, and the vortex blades (906b) can drive the pressure increasing pipe (906) to integrally rotate.
3. The suction supercharging structure of a compressor according to claim 2, wherein:
the number of the swirl vanes (906b) is plural, and the plural swirl vanes (906b) are circumferentially spaced apart from each other on the outer peripheral wall of the pressure increasing duct (906).
4. The suction supercharging structure of a compressor according to claim 2, wherein:
the cross section of the vortex cover (903) is of a circular ring-shaped structure, and an opening at the joint of the drainage tube (902) and the vortex cover (903) is along the circumferential tangential direction of the vortex cover (903), so that exhaust gas entering the vortex cover (903) is along the circumferential tangential direction of the vortex cover (903); and/or the number of the vortex hoods (903) is at least two, and the two vortex hoods (903) can be spliced with each other to form the first cavity (100).
5. The suction supercharging structure of a compressor according to claim 2, wherein:
the gas inlet device is characterized by further comprising axial flow blades (906a), wherein the axial flow blades (906a) are arranged inside the pressure increasing pipe (906), the axial flow blades (906a) can be driven to rotate along with the rotation of the pressure increasing pipe (906), and then the inlet gas is accelerated and/or pressurized through the axial flow blades (906 a).
6. The suction supercharging structure of a compressor according to claim 2, wherein:
the vortex cover (903) is also provided with an exhaust hole (907), and the exhaust hole (907) can exhaust the gas passing through the vortex blades (906b) to the outside of the first cavity (100); and/or the presence of a gas in the gas,
the vortex cover (903) is further provided with an oil return hole (908), the oil return hole (908) is communicated with the first cavity (100), and oil passing through the vortex blade (906b) can be led out of the first cavity (100) through the oil return hole (908).
7. The suction supercharging structure of a compressor according to claim 6, wherein:
when the vortex cover (903) is further provided with an exhaust hole (907), the exhaust hole (907) is formed in the outer peripheral surface of the vortex cover (903) and formed along the circumferential tangential direction of the vortex cover (903), and the flow area of the exhaust hole (907) is larger than or equal to the area of the exhaust port;
when the vortex cover (903) is further provided with an oil return hole (908), the oil return hole (908) is arranged close to the exhaust hole (907) relative to an opening at the joint of the drainage tube (902) and the vortex cover (903); the oil return holes (908) are multiple.
8. The suction supercharging structure of a compressor according to claim 2, wherein:
a sealing ring groove (906d) is formed in the axial end part of the pressure increasing pipe (906), and a sealing ring (904) is sleeved in the sealing ring groove (906 d); and/or the axial end of the booster duct (906) is further provided with a bearing (905).
9. The suction-supercharging structure of a compressor according to claim 8, wherein:
when the compressor comprises a sealing ring (904) and a bearing (905) at the same time, the bearing (905) is installed on the periphery of the sealing ring (904), the compressor further comprises a fixed scroll (8), the fixed scroll (8) comprises an air inlet hole (81) for air inlet, one axial end of the pressure increasing pipe (906) is inserted into the air inlet pipe (901), and the other axial end of the pressure increasing pipe (906) is inserted into the air inlet hole (81); the bearings include a first bearing located between the intake duct (901) and the booster duct (906), and a second bearing located between the intake duct (81) and the booster duct (906).
10. The suction supercharging structure of a compressor according to claim 9, wherein:
the bearing (905) is a tapered roller bearing, the first bearing is a first tapered roller bearing, the second bearing is a second tapered roller bearing, and the installation directions of the first tapered roller bearing and the second tapered roller bearing are opposite.
11. A compressor, characterized by: suction plenum structure comprising a compressor according to any one of claims 1 to 10.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202110758187.1A CN113323876B (en) | 2021-07-05 | 2021-07-05 | Air suction supercharging structure of compressor and compressor |
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| CN202110758187.1A CN113323876B (en) | 2021-07-05 | 2021-07-05 | Air suction supercharging structure of compressor and compressor |
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| CN113323876B true CN113323876B (en) | 2022-03-08 |
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| CN103486047B (en) * | 2013-08-23 | 2016-02-10 | 珠海凌达压缩机有限公司 | Can turbo charged rotary compressor |
| US20170030352A1 (en) * | 2014-04-09 | 2017-02-02 | Bin Tang | Eccentric movable vane pump |
| US9458848B2 (en) * | 2014-08-02 | 2016-10-04 | Nelik I. Dreiman | Revolving piston rotary compressor with stationary crankshaft |
| CN111189265B (en) * | 2018-11-15 | 2021-07-06 | 上海海立电器有限公司 | Air suction supercharging structure and refrigerating system |
| CN110630498A (en) * | 2019-09-11 | 2019-12-31 | 河北昊方新能源科技有限公司 | Scroll refrigeration compressor with suction boosting |
| CN112065715B (en) * | 2020-08-19 | 2022-05-20 | 广州万宝集团压缩机有限公司 | Scroll compressor and thermoregulation device |
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