CN210290143U - Compressor with parallel independent pump bodies and air conditioning system - Google Patents
Compressor with parallel independent pump bodies and air conditioning system Download PDFInfo
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- CN210290143U CN210290143U CN201921272015.8U CN201921272015U CN210290143U CN 210290143 U CN210290143 U CN 210290143U CN 201921272015 U CN201921272015 U CN 201921272015U CN 210290143 U CN210290143 U CN 210290143U
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- 238000004378 air conditioning Methods 0.000 title claims abstract description 46
- 239000007788 liquid Substances 0.000 claims abstract description 41
- 230000001502 supplementing effect Effects 0.000 claims description 2
- 239000007789 gas Substances 0.000 description 46
- 230000000694 effects Effects 0.000 description 16
- 238000007791 dehumidification Methods 0.000 description 7
- 238000001704 evaporation Methods 0.000 description 7
- 238000010438 heat treatment Methods 0.000 description 6
- 230000006835 compression Effects 0.000 description 5
- 238000007906 compression Methods 0.000 description 5
- 230000008020 evaporation Effects 0.000 description 5
- 238000005057 refrigeration Methods 0.000 description 5
- 239000003507 refrigerant Substances 0.000 description 4
- 238000003303 reheating Methods 0.000 description 4
- 238000009833 condensation Methods 0.000 description 3
- 230000005494 condensation Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 238000013461 design Methods 0.000 description 3
- 238000012545 processing Methods 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 239000013589 supplement Substances 0.000 description 2
- 238000013475 authorization Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 239000000567 combustion gas Substances 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000005485 electric heating Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000001603 reducing effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000029058 respiratory gaseous exchange Effects 0.000 description 1
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Abstract
The utility model discloses a take compressor and air conditioning system of parallel independent pump body, the compressor of the parallel independent pump body in area includes: the air suction end of the first air cylinder, the air suction end of the second air cylinder and the air suction end of the parallel air cylinder are respectively and independently connected with a liquid distributor, and the parallel switch valve is arranged on an air inlet pipe of the liquid distributor connected with the parallel air cylinder. The air conditioning system is in a double-suction single-row mode or a double-suction double-row mode, the double-suction single-row mode is used for dehumidifying through a low-temperature evaporator in a double evaporator and sensible heat of a high-temperature evaporator, and the double-suction double-row mode is used for guiding gas exhausted by a compressor and a second cylinder into a double condenser and then converging the gas into the same channel to enter the double evaporator for circulation. The utility model discloses effectively reduce the loss power consumption of compressor, promote compressor place air conditioning system's efficiency.
Description
Technical Field
The utility model relates to a compressor technical field especially relates to compressor and air conditioning system of the parallel independent pump body in area.
Background
The three-cylinder compressor is comparatively common one in the multi-cylinder compressor, current three-cylinder compressor adopts a jar varactor, doublestage increases the enthalpy structure, for example the utility model patent of publication number CN208651158U, it adds a varactor cylinder by two doublestage double-cylinders and constitutes, can understand that a double-cylinder structure has established ties a less varactor cylinder of volume, its double-cylinder doublestage is the cylinder of equidimension, similar with conventional double-cylinder double-stage compressor, possess and increase the enthalpy function (the tonifying qi mode of conventional doublestage increases the enthalpy compressor is offered the tonifying qi mouth through baffle or flange, reach the effect that the tonifying qi increases the enthalpy through sneaking gas in the cylinder), through the pressure of the varactor control mouth department of adjusting the varactor cylinder, can make the varactor cylinder open and stop, thereby realize the double-cylinder, the function of switching in order to accomplish the compressor of three-.
The cylinder body structure of the existing three-cylinder compressor is complex, so that the compressor is high in cost and has serious vibration problems, the start and stop of the variable-capacity cylinder cannot be flexibly switched, and when the compressor operates at low temperature and low frequency, the low-load performance advantage is not large, so that the APF (intermediate refrigeration) is not high enough, and the heating performance is poor. In addition, when the air conditioning system where the three-cylinder compressor is located operates, cooling, refrigerating and dehumidifying are completed in one system, so that the heat exchange efficiency of the evaporator is low, the air conditioning system cannot meet the refrigerating and dehumidifying and heating requirements of the area north of the Yangtze river basin, and serious hidden dangers are caused to the energy efficiency and after-sales experience of the air conditioning system.
Therefore, how to design a compressor and an air conditioning system with parallel independent pumps is a technical problem to be solved urgently in the industry.
SUMMERY OF THE UTILITY MODEL
In order to solve the defect that current multi-cylinder compressor performance is poor, the utility model provides a take compressor and air conditioning system of parallel independent pump body.
The utility model discloses a technical scheme be, the design takes the compressor of the parallel independent pump body, include: the shell, locate first cylinder and the second cylinder in the casing, still be equipped with the parallel cylinder of independent compression and tonifying qi in the casing, the parallel cylinder's end of breathing in is connected in series has the parallel ooff valve of control whether its operation is worked. The air suction ends of the first air cylinder, the second air cylinder and the parallel air cylinders are respectively and independently connected with a liquid distributor, and the parallel switch valve is arranged on an air inlet pipe of the liquid distributor connected with the parallel air cylinders.
Preferably, the liquid distributor connected with the first air cylinder is a first liquid distributor, the liquid distributor connected with the second air cylinder is a second liquid distributor, an intermediate pipe is connected between an air inlet pipe of the first liquid distributor and an air inlet pipe of the second liquid distributor, and the intermediate pipe is provided with a control switch valve.
Preferably, the first cylinder, the second cylinder and the parallel cylinder are sequentially arranged in the housing from top to bottom.
Preferably, the shell is provided with an exhaust port, and the exhaust ends of the first cylinder, the second cylinder and the parallel cylinder are communicated with the exhaust port.
Preferably, the shell is provided with an exhaust port, the exhaust ends of the first cylinder and the parallel cylinder are communicated with the exhaust port, and the exhaust end of the second cylinder is independently connected with an exhaust pipe extending out of the shell.
Preferably, the cylinder volume of the first cylinder is V1, the cylinder volume of the second cylinder is V2,
the range of (A) is 0.6 to 1.0.
Preferably, the cylinder volume of the first cylinder is V1, the cylinder volume of the second cylinder is V2, the cylinder volume of the parallel cylinder is V3,
the range of (A) is 0.1 to 0.4.
Preferably, the cylinder volume of the first cylinder is V1, the cylinder volume of the second cylinder is V2, the cylinder volume of the parallel cylinder is V3,
the range of (A) is 0.105 to 0.625.
Preferably, a variable-volume cylinder for supplying air to the parallel cylinders is arranged in the shell, the variable-volume cylinder is communicated with the parallel cylinders through an intermediate flow passage, and the intermediate flow passage is communicated in a single direction through the non-return device.
The utility model also provides an air conditioning system, it includes foretell compressor.
In an embodiment, the air conditioning system further comprises: the system comprises a condenser, a flash evaporator with three interfaces, a first evaporator, a second evaporator and a four-way valve with four ports; the exhaust port of the compressor is connected with the first port of the four-way valve; one end of the condenser is connected with a second port of the four-way valve, and the other end of the condenser is connected with a first interface of the flash evaporator; one end of the first evaporator is connected with the second interface of the flash evaporator, and the other end of the first evaporator is connected with the third port of the four-way valve; one end of the second evaporator is connected with the second interface of the flash evaporator, the other end of the second evaporator is provided with a first branch and a second branch in parallel, the first branch is connected with a first switch valve in series and is connected to an air inlet pipe of a liquid distributor connected with the first air cylinder, and the second branch is connected with a second switch valve in series and is connected with an air outlet of the compressor; the fourth port of the four-way valve is connected to the air inlet pipe of the liquid distributor connected with the second cylinder, and the third port of the flash evaporator is connected to the air inlet pipe of the liquid distributor connected with the parallel cylinder.
In another embodiment, the air conditioning system further comprises: the system comprises a first condenser, a second condenser, a flash evaporator with three interfaces, a first evaporator, a second evaporator and a four-way valve with four ports; the exhaust port of the compressor is connected with the first end of the four-way valve; one end of the first condenser is connected with the exhaust end of the second cylinder, and the other end of the first condenser is connected with the first interface of the flash evaporator; one end of the second condenser is connected with a second port of the four-way valve, and the other end of the second condenser is connected with a first interface of the flash evaporator; one end of the first evaporator is connected with the second interface of the flash evaporator, and the other end of the first evaporator is connected with the third port of the four-way valve; one end of the second evaporator is connected with the second interface of the flash evaporator, the other end of the second evaporator is provided with a first branch and a second branch in parallel, the first branch is connected with a first switch valve in series and is connected to an air inlet pipe of a liquid distributor connected with the first air cylinder, and the second branch is connected with a second switch valve in series and is connected with an air outlet of the compressor; the fourth port of the four-way valve is connected to the air inlet pipe of the liquid distributor connected with the second air cylinder, and the third port of the flash evaporator is connected to the air inlet pipe of the liquid distributor connected with the parallel air cylinder.
Compared with the prior art, the utility model discloses keep the twin-cylinder structure of doublestage enthalpy increase among the conventional three jar compressors, set up a parallel cylinder in addition in the compressor, this parallel cylinder compresses alone and the tonifying qi, and through the operation work or the uninstallation of parallel cylinder of parallel switch valve control, can adjust the operating condition of compressor in a flexible way as required, effectively reduces the loss power consumption of compressor, and it is big to improve the compressor vibration, promotes compressor place air conditioning system's efficiency.
Drawings
The invention is explained in more detail below with reference to exemplary embodiments and the accompanying drawings, in which:
fig. 1 is a schematic view of an internal structure of a compressor of the present invention;
FIG. 2 is a schematic view of the flow direction of the refrigerant in the middle double suction single row air conditioning system of the present invention;
FIG. 3 is a schematic view of the flow direction of the dehumidifying coolant of the mid-double suction single row air conditioning system of the present invention;
fig. 4 is a schematic view of the flow direction of the refrigerant in the double suction double row air conditioning system of the present invention.
Detailed Description
As shown in fig. 1 to 4, the present invention provides a compressor including: the casing, locate first cylinder 1 and second cylinder 2 in the casing, still be equipped with the parallel cylinder 3 of independent compression and tonifying qi in the casing, independent compression and tonifying qi of here mean that parallel cylinder 3 has independent working chamber and exhaust end, and the suction compression and the exhaust of working chamber do not all receive the influence of first cylinder 1, second cylinder 2, and the gas of parallel cylinder 3 combustion gas gets into in the casing in order to play the tonifying qi effect. The parallel switch valve 4 for controlling whether the parallel cylinder 3 operates or not is connected in series at the air suction end of the parallel cylinder 3, when the parallel switch valve 4 is opened, the parallel cylinder 3 operates independently, and gas exhausted from a working cavity of the parallel cylinder is fed into the shell to be mixed with gas exhausted from the first cylinder 1 and the second cylinder 2; when the parallel switch valve 4 is closed, the parallel cylinder 3 is unloaded and does not participate in refrigerant circulation. The switch of the parallel switch valve 4 can be adjusted according to actual requirements, and the parallel switch valve is flexible to use and convenient to control.
Specifically, the air suction ends of the first air cylinder 1, the second air cylinder 2 and the parallel air cylinder 3 are respectively and independently connected with a liquid distributor, the liquid distributor connected with the first air cylinder 1 is a first liquid distributor 5, the liquid distributor connected with the second air cylinder 2 is a second liquid distributor 6, the liquid distributor connected with the air suction end of the parallel air cylinder 3 is a parallel liquid distributor 7, a parallel switch valve 4 is arranged on an air inlet pipe of the parallel liquid distributor 7, an intermediate pipe is connected between the air inlet pipe of the first liquid distributor 5 and the air inlet pipe of the second liquid distributor 6, the intermediate pipe is provided with a control switch valve 8, when the control switch valve 8 is closed, the first air cylinder 1 and the second air cylinder 2 are respectively and independently compressed and supplied with air, and when the control switch valve 8 is switched on, the first air cylinder 1 and the second air cylinder 2 suck air with the same evaporation temperature to.
In a preferred embodiment, the first cylinder 1, the second cylinder 2 and the parallel cylinder 3 are sequentially arranged in the shell from top to bottom, the first cylinder 1 is a high-pressure cylinder, the second cylinder 2 is a low-pressure cylinder, and the cylinder volumes of the first cylinder 1, the second cylinder 2 and the parallel cylinder 3 are differentThe cylinder volume of the first cylinder 1 is V1, the cylinder volume of the second cylinder 2 is V2, the cylinder volume of the parallel cylinder 3 is V3,
the range of (A) is 0.6 to 1.0,
in the range of 0.1 to 0.4, when
When the ratio of (1) is between 0.105 and 0.625, the compressor has the optimal volume ratio, and the air supply pressure of the parallel cylinder 3 reaches the optimal pressure value. Through theoretical calculation of the volume ratios of the three cylinder bodies, the optimal volume ratio can be confirmed to enable the heating performance of the compressor to be optimal, the energy efficiency of the compressor can be improved by about 20% under the refrigerating working condition, the heating performance at minus 15 ℃ can be effectively improved under the dehumidifying and heating working condition, the mechanical refrigerating efficiency is improved to the maximum extent, and the problems of vibration and the like can be effectively solved while the energy efficiency of the compressor is improved.
The second cylinder 2 has two arrangement modes, as shown in fig. 2 and 4, the first mode is that the shell is provided with an exhaust port, exhaust ends of the first cylinder 1, the second cylinder 2 and the parallel cylinder 3 are communicated with the exhaust port, and gases exhausted by the first cylinder 1, the second cylinder 2 and the parallel cylinder 3 are mixed in the shell, and the first mode is suitable for a double-suction single-row mode of the air conditioning system; as shown in fig. 4, the second mode is that the housing is provided with an exhaust port, the exhaust ends of the first cylinder 1 and the parallel cylinder 3 are both communicated with the exhaust port, the exhaust gases discharged from the first cylinder 1 and the parallel cylinder 3 are mixed in the housing, the exhaust end of the second cylinder 2 is separately connected with an exhaust pipe extending out of the housing, the discharged gases are directly sent to a heat exchanger outside the compressor, in the second mode, the discharge end of the second cylinder 2 is connected with an exhaust gas separator 9, the refrigerant sent out by the discharge end passes through the exhaust gas separator 9 and then enters the heat exchanger outside the compressor, and the second mode is suitable for the double suction and double discharge mode of the air conditioning system.
In optional embodiment, be equipped with the varactor cylinder of supplying gas with parallel cylinder 3 in the casing, the varactor cylinder is located parallel cylinder's lower floor, and varactor cylinder and parallel cylinder 3 are through middle runner intercommunication, and middle runner passes through non return device one-way conduction, and the concrete structure and the theory of operation of non return device have been disclosed in detail in the utility model for CN208651158U in the authorization notice number, do not describe here any more. The optional embodiment is a scheme for realizing variable-capacity and double-stage enthalpy-increasing and parallel independent compression, can be switched among modes of double cylinders, three cylinders and four cylinders, can expand the operation range of the compressor, enables the compressor to operate under the environment condition in a wider range, and can effectively operate in the temperature environment in the range of-45-40 ℃ through theoretical calculation.
The utility model also provides an air conditioning system, it includes double evaporation ware and foretell compressor, be equipped with the ooff valve in air conditioning system's the part route, the optional solenoid valve of foretell ooff valve, closed state through changing each ooff valve, can change the gas flow path of single compressor in the air conditioning system pipeline, make air conditioning system inhale different or the same evaporating temperature's gas, independently compress in big or small jar of two temperatures, improve the refrigeration capacity, through double evaporation temperature evaporimeter, low temperature evaporimeter is used for the dehumidification, high temperature evaporimeter is used for handling sensible heat, the hierarchical processing load, the effect of improving circulation. Not only saves cost and space, but also can realize the effect of separating sensible heat and latent heat of the system while improving the refrigerating capacity. In addition, a double-suction double-row air conditioning system can be designed, the gas in the second cylinder 2 is guided into the double condensers, the gas exhausted from the exhaust port of the shell flows to the second condenser 20, the gas exhausted from the second cylinder 2 flows to the first condenser 19, and finally, the gas is converged to the same channel to enter the double evaporators for recirculation through the mutual heat exchange of the condensers, so that the refrigeration effect is further improved, and the APF value of the air conditioning system is effectively improved.
As shown in fig. 2 and 3, in an embodiment, the air conditioning system is in a double suction single row mode, and specifically, the air conditioning system further includes: a condenser 14, a flash evaporator 10 with three interfaces, a first evaporator 11, a second evaporator 12 and a four-way valve 13 with four ports, wherein the exhaust port of the compressor is connected with the first end of the four-way valve 13, one end of the condenser 14 is connected with the second port of the four-way valve 13, the other end of the first throttling valve 15 is connected in series with a first interface of the flash evaporator 10, one end of the first evaporator 11 is connected with a second interface of the flash evaporator 10, the other end of the first evaporator is connected with a third port of the four-way valve 13, one end of the second evaporator 12 is connected in series with a second throttling valve 16 and connected with a second interface of the flash evaporator 10, the other end of the second evaporator is provided with a first branch and a second branch in parallel, the first branch is connected in series with a first switch valve 17 and connected with an air inlet pipe of the first liquid separator 5, the second branch is connected in series with a second switch valve 18 and connected with an air outlet of the compressor, a fourth port of the four-way valve 13 is connected with an air inlet pipe of the second liquid separator.
The system is designed aiming at two environments of refrigeration in summer and dehumidification in rainy season, when summer is hot, a low-temperature evaporator of a double-evaporator of the air conditioning system is used for dehumidification, a high-temperature evaporator is used for processing sensible heat, the load is processed in a grading manner, the circulation efficiency is improved, the temperature and the humidity are controlled independently, and the refrigerating capacity is effectively improved; when the rainy season is wet, the gas flow path is changed, the low-temperature evaporator is used for reheating, the high-temperature evaporator is used for condensing and dehumidifying, the temperature and humidity are controlled, condensing and reheating are carried out, the dehumidifying capacity is effectively improved, the medium-pressure gas of the flash evaporator is output to the parallel cylinder 3, the gas discharged from the parallel cylinder 3 is mixed with the gas in the shell to achieve the effects of air supply and enthalpy increase, and the detailed description is respectively carried out below.
As shown in fig. 2, cooling-double suction single row mode in summer: closing the control switch valve 8 and the second switch valve 18, opening the first switch valve 17, at this time, the gas discharged by the compressor passes through the four-way valve 13 and the condenser 14, simultaneously opening the first throttle valve 15 and the second throttle valve 16, and sequentially performing throttling and pressure reduction effects, wherein one part of the gas passes through the first evaporator 11 through the flash evaporator 10, and the other part of the gas enters the second evaporator 12 through the second throttle valve 16, and correspondingly, the first evaporator 11 processes sensible heat to guide the gas to the second cylinder 2, the second evaporator 12 dehumidifies to guide the gas to the first cylinder 1, and the first cylinder 1 and the second cylinder 2 independently suck air to work, so that the air conditioning system is subjected to graded cooling, the temperature and humidity are independently controlled, the refrigerating capacity of the air conditioning system is remarkably improved, and the refrigerating effect is improved for hot environments in summer. Meanwhile, the parallel switch valve 4 can be opened and closed, whether the parallel cylinder 3 is unloaded or not is determined according to actual requirements, and when the parallel cylinder 3 operates and works, compressed gas is discharged into the cavity of the shell and mixed with gas compressed by the first cylinder 1 and the second cylinder 2, and the compressed gas is used as an effect of air supplement and enthalpy increase to improve the energy efficiency of the compressor and the air conditioning system.
As shown in fig. 3, the dehumidification-double suction single row mode in the rainy season: the control switch valve 8 and the second switch valve 18 are opened, the first switch valve 17 is closed, and at this time, the discharge gas of the compressor passes through the four-way valve 13 and the condenser 14, simultaneously opening a first throttle valve 15 and a second throttle valve 16 to sequentially perform throttling and pressure reducing effects, accumulating gas at a first evaporator 11 through a flash evaporator 10, reheating gas discharged by a compressor through a second evaporator 12, condensing and dehumidifying the gas mixture through the first evaporator 11, then entering a first cylinder 1 and a second cylinder 2 corresponding to a first liquid separator and a second liquid separator through a four-way valve 13 again, because the first switch valve 17 is closed, at this time, the double-temperature cylinder sucks the gas with the same evaporation temperature, the temperature and humidity double control, temperature adjustment and dehumidification and condensation reheating of the double-evaporator air conditioning system are realized, electric heating is not needed, the heating capacity of the air conditioning system is remarkably improved, and the treatment effect is improved for the plum rain season environment. Meanwhile, the parallel switch valve 4 can be opened and closed, whether the parallel cylinder 3 is unloaded or not is determined according to actual requirements, and when the parallel cylinder 3 operates and works, compressed gas is discharged into the cavity of the shell and mixed with gas compressed by the first cylinder 1 and the second cylinder 2, and the compressed gas is used as an effect of air supplement and enthalpy increase to improve the energy efficiency of the compressor and the air conditioning system.
In another embodiment, as shown in fig. 4, the air conditioning system is in a double suction, double row mode, which differs from the double suction, single row mode only in the vent flow path design and the added double condenser result, specifically the air conditioning system further comprises: a first condenser 19, a second condenser 20, a flash evaporator 10 with three interfaces, a first evaporator 11, a second evaporator 12 and a four-way valve 13 with four ports; the exhaust port of the compressor is connected with the first end of the four-way valve 13; one end of the first condenser 19 is connected with a first throttle valve 15 in series and is connected with a first connector of the flash evaporator 10, and the other end of the first condenser is connected with an exhaust pipe of the exhaust gas separator 9; one end of the second condenser 20 is connected with a first throttle valve 15 in series and is connected with a first interface of the flash evaporator 10, and the other end of the second condenser is connected with a second port of the four-way valve 13; one end of the first evaporator 11 is connected with the second interface of the flash evaporator 10, and the other end is connected with the third port of the four-way valve 13; one end of the second evaporator 12 is connected with a second throttling valve 16 in series and connected with a second connector of the flash evaporator 10, the other end of the second evaporator is provided with a first branch and a second branch in parallel, the first branch is connected with a first switch valve 17 in series and connected with an air inlet pipe of the first liquid separator 5, and the second branch is connected with a second switch valve 18 in series and connected with an air outlet of the compressor; a fourth port of the four-way valve 13 is connected with an air inlet pipe of the second liquid separator 6, and a third port of the flash evaporator 10 is connected with an air inlet pipe of the parallel liquid separator 7.
As shown in fig. 4, cooling-double suction double row mode in summer: closing the control switch valve 8 and the second switch valve 18, opening the first switch valve 17, at this time, the gas discharged from the compressor passes through the four-way valve 13 and the second condenser 20, the gas discharged from the second cylinder 2 passes through the first condenser 19, finally joins in the same pipeline and passes through the first throttle valve 15 and the flash evaporator 10, simultaneously opening the first throttle valve 15 and the second throttle valve 16, a part of the gas passes through the first evaporator 11 through the flash evaporator 10, a part of the gas enters the second evaporator 12 through the second throttle valve 16, correspondingly, the first evaporator 11 processes sensible heat and leads the gas to the second cylinder 2, the second evaporator 12 dehumidifies and leads the gas to the first cylinder 1, the first cylinder 1 and the second cylinder 2 independently suck and exhaust the gas to work, so that the air conditioning system of the double condensers enhances the heat exchange effect, further enhances the condensation dehumidification effect, and the air conditioning system of the double evaporators progressively cools down, the temperature and humidity are independently controlled, the refrigerating capacity of the air conditioning system is obviously improved, and the refrigerating effect is obviously improved in hot summer environments. Meanwhile, the parallel switch valve 4 can be opened and closed, whether the parallel cylinder 3 is unloaded or not is determined according to actual requirements, and when the parallel cylinder 3 operates and works, compressed gas is discharged into the cavity of the shell and mixed with gas compressed by the first cylinder 1 to serve as an effect of supplementing air and increasing enthalpy so as to improve the energy efficiency of the compressor and the air conditioning system.
The utility model provides a conventional three jar compressors with high costs and vibration big, the general problem of popularization effect, and can also solve low-load performance advantage not big, APF not enough high grade problem, combine air conditioning system's two evaporating temperature evaporimeters, the low temperature evaporimeter is used for the dehumidification, and the high temperature evaporimeter is used for handling the sensible heat, and the hierarchical processing load improves the circulation and imitates. The utility model discloses an air conditioning system not only can realize refrigeration in summer, double evaporation ware, step cooling, humiture independent control, can also realize that plum rainy season dehumidifies, warm and humid two accuse, the dehumidification that adjusts the temperature, the condensation is reheat, need not the electricity reheat.
The above description is only exemplary of the present invention and should not be taken as limiting the scope of the present invention, as any modifications, equivalents, improvements and the like made within the spirit and principles of the present invention are intended to be included within the scope of the present invention.
Claims (12)
1. A compressor with parallel independent pump bodies, comprising: the air compressor comprises a shell, a first air cylinder and a second air cylinder which are arranged in the shell, and is characterized in that the shell is also internally provided with a parallel air cylinder for independently compressing and supplementing air, and the air suction end of the parallel air cylinder is connected in series with a parallel switch valve for controlling whether the parallel air cylinder operates or not; the air suction ends of the first air cylinder, the second air cylinder and the parallel air cylinders are respectively and independently connected with a liquid distributor, and the parallel switch valve is arranged on an air inlet pipe of the liquid distributor connected with the parallel air cylinders.
2. The compressor according to claim 1, wherein the dispenser connected to the first cylinder is a first dispenser, the dispenser connected to the second cylinder is a second dispenser, and an intermediate pipe is connected between an intake pipe of the first dispenser and an intake pipe of the second dispenser, and the intermediate pipe is provided with a control switch valve.
3. The compressor of claim 1, wherein the first cylinder, the second cylinder, and the parallel cylinders are arranged in the housing in sequence from top to bottom.
4. The compressor of claim 1, wherein the housing is provided with a discharge port, and discharge ends of the first cylinder, the second cylinder, and the parallel cylinders are all in communication with the discharge port.
5. The compressor of claim 1, wherein the housing is provided with a discharge port, the discharge ends of the first cylinder and the parallel cylinders are communicated with the discharge port, and the discharge end of the second cylinder is separately connected with a discharge pipe extending outside the housing.
6. The compressor of claim 1, wherein the cylinder volume of the first cylinder is V1, the cylinder volume of the second cylinder is V2, and V1 ÷ V2 is in the range of 0.6 to 1.0.
7. The compressor of claim 1, wherein the cylinder volume of the first cylinder is V1, the cylinder volume of the second cylinder is V2, the cylinder volume of the parallel cylinders is V3, and the range of V3 ÷ (V1+ V2) is 0.1 to 0.4.
8. The compressor of claim 1, wherein the cylinder volume of the first cylinder is V1, the cylinder volume of the second cylinder is V2, the cylinder volume of the parallel cylinders is V3, and the range of V3 ÷ (V1+ V2+ V3) is 0.105 to 0.625.
9. The compressor as claimed in claim 1, wherein a variable capacity cylinder for supplying air to the parallel cylinders is provided in the housing, the variable capacity cylinder and the parallel cylinders are communicated through an intermediate flow passage, and the intermediate flow passage is unidirectionally communicated through a check device.
10. An air conditioning system, comprising: a compressor as claimed in any one of claims 1 to 9.
11. The air conditioning system as claimed in claim 10, further comprising: the system comprises a condenser, a flash evaporator with three interfaces, a first evaporator, a second evaporator and a four-way valve with four ports;
the exhaust port of the compressor is connected with the first port of the four-way valve;
one end of the condenser is connected with the second port of the four-way valve, and the other end of the condenser is connected with the first interface of the flash evaporator;
one end of the first evaporator is connected with the second interface of the flash evaporator, and the other end of the first evaporator is connected with the third port of the four-way valve;
one end of the second evaporator is connected with the second interface of the flash evaporator, the other end of the second evaporator is provided with a first branch and a second branch in parallel, the first branch is connected with a first switch valve in series and is connected to an air inlet pipe of a liquid separator connected with the first air cylinder, and the second branch is connected with a second switch valve in series and is connected with an air outlet of the compressor;
a fourth port of the four-way valve is connected to an air inlet pipe of a liquid distributor connected with the second air cylinder;
and a third interface of the flash evaporator is connected to an air inlet pipe of a liquid distributor connected with the parallel cylinder.
12. The air conditioning system as claimed in claim 10, further comprising: the system comprises a first condenser, a second condenser, a flash evaporator with three interfaces, a first evaporator, a second evaporator and a four-way valve with four ports;
the exhaust port of the compressor is connected with the first port of the four-way valve;
one end of the first condenser is connected with the exhaust end of the second cylinder, and the other end of the first condenser is connected with the first interface of the flash evaporator;
one end of the second condenser is connected with the second port of the four-way valve, and the other end of the second condenser is connected with the first interface of the flash evaporator;
one end of the first evaporator is connected with the second interface of the flash evaporator, and the other end of the first evaporator is connected with the third port of the four-way valve;
one end of the second evaporator is connected with the second interface of the flash evaporator, the other end of the second evaporator is provided with a first branch and a second branch in parallel, the first branch is connected with a first switch valve in series and is connected to an air inlet pipe of a liquid separator connected with the first air cylinder, and the second branch is connected with a second switch valve in series and is connected with an air outlet of the compressor;
a fourth port of the four-way valve is connected to an air inlet pipe of a liquid distributor connected with the second air cylinder;
and a third interface of the flash evaporator is connected to an air inlet pipe of a liquid distributor connected with the parallel cylinder.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921272015.8U CN210290143U (en) | 2019-08-07 | 2019-08-07 | Compressor with parallel independent pump bodies and air conditioning system |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110513290A (en) * | 2019-08-07 | 2019-11-29 | 珠海凌达压缩机有限公司 | Compressor with parallel independent pump bodies and air conditioning system |
| CN111594442A (en) * | 2020-05-12 | 2020-08-28 | 珠海凌达压缩机有限公司 | Compressor assembly, air conditioning system and control method of air conditioning system |
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2019
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110513290A (en) * | 2019-08-07 | 2019-11-29 | 珠海凌达压缩机有限公司 | Compressor with parallel independent pump bodies and air conditioning system |
| CN111594442A (en) * | 2020-05-12 | 2020-08-28 | 珠海凌达压缩机有限公司 | Compressor assembly, air conditioning system and control method of air conditioning system |
| CN111594442B (en) * | 2020-05-12 | 2024-05-14 | 珠海凌达压缩机有限公司 | Compressor assembly, air conditioning system and control method of air conditioning system |
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