CN212457490U - Secondary throttling double-condensation refrigerating system and air conditioner - Google Patents
Secondary throttling double-condensation refrigerating system and air conditioner Download PDFInfo
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- CN212457490U CN212457490U CN202020650280.1U CN202020650280U CN212457490U CN 212457490 U CN212457490 U CN 212457490U CN 202020650280 U CN202020650280 U CN 202020650280U CN 212457490 U CN212457490 U CN 212457490U
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Abstract
The utility model provides a two condensation refrigerating system of secondary throttle, air conditioner, refrigerating system includes compressor and evaporimeter, one-level condenser and second grade condenser, first throttling arrangement and second throttling arrangement, the exit linkage of one-level condenser and compressor, the export of one-level condenser and the entry linkage of second grade condenser, and still be provided with first throttling arrangement on the pipeline between one-level condenser and second grade condenser, the exit linkage second throttling arrangement of second grade condenser, the evaporimeter is connected to second throttling arrangement's the other end. According to the utility model discloses can compare in a throttle refrigeration cycle system, under the condition of same evaporating pressure, superheat degree, super-cooled rate and refrigerant circulation volume, make full use of secondary condenser releases refrigerant latent heat and sensible heat after a throttle, greatly improved the heating capacity of system, refrigerating capacity, heating coefficient of performance and refrigeration coefficient of performance.
Description
Technical Field
The utility model relates to an air conditioning technology field, concretely relates to two condensation refrigerating system of secondary throttle, air conditioner.
Background
In the prior art, the air conditioner has a large proportion of energy consumption in total building energy consumption, and the trend of the air conditioner industry is about how to further improve the performance coefficient of the air conditioner and reduce the energy consumption of the air conditioner. The conventional primary throttling refrigeration cycle system has the defects of limited evaporation pressure and condensation pressure, small refrigerating capacity and heating capacity, low compression power consumption and difficult further improvement of the performance coefficient of the system. The once throttling refrigeration cycle adopts once throttling, and the throttling degree of the cycle mode is limited, so that the evaporation temperature cannot reach the low-temperature working condition, and the system cannot adapt to heating under the low-temperature working condition. In addition, a single condenser is adopted in the primary throttling refrigeration cycle system, so that the condensing pressure, the cooling water outlet temperature and the cooling air outlet temperature are single, the system function is single, and the diversification is insufficient.
The air conditioner in the prior art has the problems that a primary throttling refrigeration circulating system is influenced by the temperature of inflow water, the condensing pressure is insufficient, and the heating capacity is small; the primary throttling refrigeration cycle system has the problems of high evaporation pressure, small evaporation temperature difference and small heat absorption refrigeration capacity; the temperature range of the operating environment of the primary throttling refrigeration cycle system is small, and the primary throttling refrigeration cycle system cannot adapt to the heating under the working condition of low environment temperature; the problem of low performance coefficient of the primary throttling refrigeration cycle system; once throttle refrigeration cycle system condensing pressure, leaving water temperature, air-out temperature singleness lead to technical problem such as system function singleness, consequently the utility model discloses research design a two condensation refrigeration system of secondary throttle, air conditioner.
SUMMERY OF THE UTILITY MODEL
Therefore, the to-be-solved technical problem of the utility model lies in overcoming the defect that there is the problem that once throttle refrigeration cycle system heats/the refrigeration coefficient of performance is low in the air conditioner among the prior art to a two condensation refrigerating system of secondary throttle, air conditioner are provided.
In order to solve the above problem, the utility model provides a two condensation refrigerating system of secondary throttle, it includes:
compressor and evaporimeter still include one-level condenser and second grade condenser, first throttling arrangement and second throttling arrangement, the one-level condenser with the exit linkage of compressor, the export of one-level condenser with the entry linkage of second grade condenser, and be in the one-level condenser with still be provided with on the pipeline between the second grade condenser first throttling arrangement, the exit linkage of second grade condenser the second throttling arrangement, second throttling arrangement's the other end is connected the evaporimeter.
Preferably, still including letting in one-level inlet tube in the one-level condenser, the one-level inlet tube let in water in the one-level condenser and with the refrigerant pipeline in the one-level condenser carries out the heat transfer, the one-level outlet pipe is connected to the exit end of one-level condenser, be provided with first control valve on the one-level inlet tube.
Preferably, the condenser also comprises a second-stage water inlet pipe which can be communicated with the second-stage condenser, the second-stage water inlet pipe is communicated with water in the second-stage condenser and exchanges heat with a refrigerant pipeline in the second-stage condenser, the outlet end of the second-stage condenser is connected with a second-stage water outlet pipe, and a second control valve is arranged on the second-stage water outlet pipe.
Preferably, when the water-saving device comprises a first-stage water inlet pipe and a second-stage water outlet pipe, the water-saving device further comprises a bypass pipe, one end of the bypass pipe is communicated with the second-stage water outlet pipe, the other end of the bypass pipe is communicated with the first-stage water inlet pipe, and the bypass pipe is further provided with a third control valve.
Preferably, when a first control valve is included, the first control valve is a solenoid valve; and/or when a second control valve is included, the second control valve is a solenoid valve; and/or when a third control valve is included, the third control valve is a solenoid valve.
Preferably, the first-stage condenser can release heat and cool in an air cooling mode, and the second-stage condenser can release heat and cool in an air cooling mode.
Preferably, the wind heated by the secondary condenser can be conducted into the primary condenser to be subjected to secondary heating.
Preferably, the compressor includes a first compression unit and a second compression unit, the refrigeration system further includes a first intermediate heat exchanger and a first branch, the first intermediate heat exchanger is arranged on a pipeline between the secondary condenser and the second throttling device, one end of the first branch is connected to a pipeline between the secondary condenser and the first intermediate heat exchanger, the other end of the first branch is communicated into the first intermediate heat exchanger, meanwhile, an outlet pipeline of the first compression unit is also communicated into the first intermediate heat exchanger, an outlet of the first intermediate heat exchanger is communicated to an inlet of the second compression unit, a pipeline between the secondary condenser and the second throttling device penetrates through the first intermediate heat exchanger and exchanges heat with a refrigerant in the first intermediate heat exchanger, and a third throttling device is further arranged on the first branch pipeline;
or the compressor comprises a first compression unit, a second compression unit and a third compression unit, the air supplementing port is positioned between the first compression unit and the second compression unit, the refrigeration system further comprises a first intermediate heat exchanger and a first branch, the first intermediate heat exchanger is arranged on a pipeline between the first-stage condenser and the first throttling device, one end of the first branch is connected to a pipeline between the first-stage condenser and the first intermediate heat exchanger, the other end of the first branch is communicated into the first intermediate heat exchanger, an outlet pipeline of the second compression unit is also communicated into the first intermediate heat exchanger, an outlet of the first intermediate heat exchanger is communicated to an inlet of the third compression unit, a pipeline between the first-stage condenser and the first throttling device penetrates through the first intermediate heat exchanger and exchanges heat with refrigerant inside the first intermediate heat exchanger, and a third throttling device is also arranged on the first branch.
Preferably, the compressor comprises a first compression unit and a second compression unit, the refrigeration system further comprises a second intermediate heat exchanger and a second branch, the second intermediate heat exchanger is arranged on a pipeline between the second-stage condenser and the second throttling device, one end of the second branch is connected to a pipeline between the second-stage condenser and the second intermediate heat exchanger, the other end of the second branch penetrates through the second intermediate heat exchanger and is communicated to a pipeline between an outlet of the first compression unit and an inlet of the second compression unit, a pipeline between the second-stage condenser and the second throttling device penetrates through the second intermediate heat exchanger and exchanges heat with the second branch inside the second intermediate heat exchanger, and a fourth throttling device is further arranged on the second branch;
or, the compressor comprises a first compression unit, a second compression unit and a third compression unit, the air supplementing port is positioned between the first compression unit and the second compression unit, the refrigeration system further comprises a second intermediate heat exchanger and a second branch, the second intermediate heat exchanger is arranged on a pipeline between the first-stage condenser and the first throttling device, one end of the second branch is connected to a pipeline between the first-stage condenser and the second intermediate heat exchanger, the other end of the second branch penetrates through the second intermediate heat exchanger and is communicated to a pipeline between an outlet of the second compression unit and an inlet of the third compression unit, a pipeline between the first-stage condenser and the first throttling device penetrates through the second intermediate heat exchanger and exchanges heat with the second branch inside the second intermediate heat exchanger, and a fourth throttling device is also arranged on the second branch.
Preferably, the compressor comprises a first compression unit and a second compression unit, the refrigeration system further comprises a third branch, one end of the third branch is connected to a pipeline between the two-stage condenser and the second throttling device, the other end of the third branch is communicated to a pipeline between an outlet of the first compression unit and an inlet of the second compression unit, and the third branch is further provided with a fifth throttling device and a fourth control valve;
or, the compressor comprises a first compression unit, a second compression unit and a third compression unit, the air supplementing port is positioned between the first compression unit and the second compression unit, the refrigeration system further comprises a third branch, one end of the third branch is connected to a pipeline between the first-stage condenser and the first throttling device, the other end of the third branch is communicated to a pipeline between an outlet of the second compression unit and an inlet of the third compression unit, and the third branch is further provided with a fifth throttling device and a fourth control valve.
Preferably, the refrigeration system further includes a heat regenerator, the heat regenerator is disposed on a pipeline between the secondary condenser and the second throttling device, the pipeline between the secondary condenser and the second throttling device penetrates through the second intermediate heat exchanger, and a pipeline between the evaporator and the inlet of the compressor also penetrates through the heat regenerator and exchanges heat with a pipe section between the secondary condenser and the second throttling device, which penetrates through the heat regenerator.
The utility model also provides an air conditioner, it includes preceding arbitrary item refrigerating system.
The utility model provides a pair of refrigerating system, air conditioner have following beneficial effect:
1. the utility model discloses a set up two series connection's condenser, and set up throttling arrangement between two condensers to can effectively form secondary throttle and second grade condensation, the utility model discloses a two high low temperature systems of two condensation cycle of secondary throttle of throttle in the middle of two condensations compare in a throttle refrigeration cycle system, under the condition of same evaporating pressure, superheat degree, super-cooled rate and refrigerant circulation volume, make full use of second grade condenser release refrigerant latent heat and sensible heat after the throttle, greatly improved the heating capacity and the heating coefficient of performance of system.
2. The condensation heat dissipation capacity of the secondary throttling double-condensation circulating high-temperature and low-temperature system is larger, so that the evaporation heat absorption refrigerating capacity and the refrigerating performance coefficient are greatly improved compared with those of a primary throttling refrigerating circulating system.
3. Because the secondary throttling and double-condensing circulation high-low temperature system adopts secondary throttling, the operating environment temperature range of the secondary throttling and double-condensing circulation high-low temperature system is larger than that of the primary throttling and refrigerating circulation system, and the evaporation temperature can be lower, so that the secondary throttling and double-condensing circulation high-low temperature system is suitable for lower environment temperature to heat.
4. Because the secondary throttling double-condensation circulating high-low temperature system adopts double condensers, the condensing pressure of each condenser is different, the temperature of inlet and outlet water of each condenser can be freely controlled and adjusted, and the multifunctional working condition of water with different water temperatures can be realized.
5. Because the secondary throttling double-condensation circulating high-low temperature system adopts double condensers, the condensing pressure of each condenser is different, so that the air inlet and outlet temperature of each condenser can be freely controlled and adjusted, and the multifunctional working condition of heating at different air outlet temperatures can be realized;
6. the utility model discloses still increased complete intercooling's first intermediate heat exchanger device on the basis of two condensation cycle high low temperature systems of secondary throttle, compare in the two condensation cycle systems of solitary secondary throttle, the super-cooled degree of refrigerant before further having increased the entering evaporimeter, further strengthened refrigeration coefficient of performance or heating coefficient of performance, and still reduce the refrigerant temperature behind the one-level compression unit effectively, make its fully cooling to saturation temperature (the superheat degree is 0), can effectively reduce the exhaust superheat degree of compressor, and effectively reduce the compressor consumption;
7. the utility model discloses still increased incomplete intercooling's first intermediate heat exchanger device on the basis of two condensation cycle high low temperature systems of secondary throttle, compare in the two condensation cycle systems of solitary secondary throttle, further increased the super-cooled degree of refrigerant before getting into the evaporimeter, further strengthened refrigeration coefficient of performance or heating coefficient of performance, and still reduce the refrigerant temperature behind the one-level compression unit effectively, make its cooling (not fully cool to saturation temperature), can effectively reduce the exhaust superheat degree of compressor, and effectively reduce the compressor consumption;
8. the utility model discloses still increased the third branch road of middle hydrojet on the basis of two condensation cycle high low temperature systems of secondary throttle, compare in the two condensation cycle systems of independent secondary throttle, reduce the refrigerant temperature behind the one-level compression unit effectively, make its cooling (cool to saturation temperature or do not cool to saturation temperature), can effectively reduce the exhaust superheat degree of compressor, effectively reduce the compressor consumption, further strengthened refrigeration coefficient of performance or heating coefficient of performance;
9. the utility model discloses still increased the regenerator on the basis of two condensing cycle high low temperature systems of secondary throttle, compared in the two condensing cycle systems of solitary secondary throttle, can further increased the super-cooled rate of the refrigerant before getting into the evaporimeter, further strengthened refrigeration coefficient of performance or the coefficient of performance that heats, and can also improve the refrigerant superheat degree of breathing in before getting into the compressor induction port, prevent the compressor liquid attack, improve the reliability of compressor.
Drawings
FIG. 1 is a schematic view of a secondary throttling dual condensing cycle high and low temperature system of the present invention;
FIG. 2 is a pressure-enthalpy diagram of the secondary throttling dual-condensing cycle high-low temperature system of the present invention;
FIG. 3 is a graph of the pressure-enthalpy of the secondary throttling dual-condensing cycle high-low temperature system of the present invention compared with the existing primary throttling refrigeration cycle system;
FIG. 4 is a schematic view of the circulating high and low temperature system of the present invention with secondary throttling double condensation and complete intercooling;
fig. 5 is a pressure-enthalpy diagram of the secondary throttling double condensation and complete intercooling circulation high-low temperature system of the utility model;
FIG. 6 is a schematic view of the circulating high and low temperature system of the present invention with secondary throttling double condensation and incomplete intercooling;
fig. 7 is a pressure-enthalpy diagram of the secondary throttling double condensation and incomplete intermediate cooling circulating high-low temperature system of the present invention;
FIG. 8 is a schematic view of the secondary throttling double condensation and intermediate spraying circulation high and low temperature system of the present invention;
fig. 9 is a pressure-enthalpy diagram of the secondary throttling double condensation and intermediate spray circulation high and low temperature system of the present invention;
FIG. 10 is a schematic view of a secondary throttling double condensation and regenerative cycle high and low temperature system of the present invention;
fig. 11 is the pressure-enthalpy diagram of the secondary throttling double condensation and heat return cycle high and low temperature system of the present invention.
The reference numerals are represented as:
1. a compressor; 101. a first compression unit; 102. a second compression unit; 2. a first-stage condenser; 3. A first throttling device; 4. a secondary condenser; 5. a second throttling device; 6. an evaporator; 7. a second-stage water inlet pipe; 8. a secondary water outlet pipe; 9. a second control valve; 10. a bypass pipe; 11. a third control valve; 12. a first-stage water inlet pipe; 13. a first control valve; 14. a primary water outlet pipe; 15. a first intermediate heat exchanger; 16. a first branch; 17. a third throttling means; 18. a second intermediate heat exchanger; 19. a second branch circuit; 20. a fourth throttling device; 21. a third branch; 22. a fifth throttling device; 23. a fourth control valve; 24. a regenerator.
Detailed Description
As shown in fig. 1-3, the utility model provides a two condensation refrigerating system of secondary throttle, it includes:
1. The utility model discloses a set up two series connection's condenser, and set up throttling arrangement between two condensers to can effectively form secondary throttle and second grade condensation, the utility model discloses a two high low temperature systems of two condensation cycle of secondary throttle of throttle in the middle of two condensations compare in a throttle refrigeration cycle system, under the condition of same evaporating pressure, superheat degree, super-cooled rate and refrigerant circulation volume, make full use of second grade condenser release refrigerant latent heat and sensible heat after the throttle, greatly improved the heating capacity and the heating coefficient of performance of system.
2. The condensation heat dissipation capacity of the secondary throttling double-condensation circulating high-temperature and low-temperature system is larger, so that the evaporation heat absorption refrigerating capacity and the refrigerating performance coefficient are greatly improved compared with those of a primary throttling refrigerating circulating system.
3. Because the secondary throttling and double-condensing circulation high-low temperature system adopts secondary throttling, the operating environment temperature range of the secondary throttling and double-condensing circulation high-low temperature system is larger than that of the primary throttling and refrigerating circulation system, and the evaporation temperature can be lower, so that the secondary throttling and double-condensing circulation high-low temperature system is suitable for lower environment temperature to heat.
4. Because the secondary throttling double-condensation circulating high-low temperature system adopts double condensers, the condensing pressure of each condenser is different, the temperature of inlet and outlet water of each condenser can be freely controlled and adjusted, and the multifunctional working condition of water with different water temperatures can be realized.
5. Because the secondary throttling double-condensation circulating high-low temperature system adopts the double condensers, the condensing pressure of each condenser is different, the air inlet and outlet temperature of each condenser can be freely controlled and adjusted, and the multifunctional working condition of heating at different air outlet temperatures can be realized.
Preferably, still including letting in one-level inlet tube 12 in the one-level condenser 2, one-level inlet tube 12 let in water in the one-level condenser 2 and with the refrigerant pipeline in the one-level condenser 2 carries out the heat transfer, one-level outlet pipe 14 is connected to the exit end of one-level condenser 2 be provided with first control valve 13 on the one-level inlet tube 12. This is the utility model discloses a further preferred structural style can follow outside access-in water effectively through first order inlet pipe structural style to being heated and rising temperature in the one-level condenser, reaching the purpose of preparing the hot water, and discharging from the one-level outlet pipe, the water inlet passage of one-level inlet tube can effectively be controlled through the setting of first control valve.
Preferably, the system further comprises a second-stage water inlet pipe 7 capable of being communicated with the second-stage condenser 4, the second-stage water inlet pipe 7 is used for communicating water into the second-stage condenser 4 and exchanging heat with a refrigerant pipeline in the second-stage condenser 4, the outlet end of the second-stage condenser 4 is connected with a second-stage water outlet pipe 8, and a second control valve 9 is arranged on the second-stage water outlet pipe 8. This is the utility model discloses a further preferred structural style can follow outside access water effectively through the structural style of second grade inlet tube to being heated and rising temperature in the second grade condenser, reaching the purpose of preparing hot water (different with the hot water temperature of one-level condenser, second grade condensation pressure is lower, consequently prepares the hot water that the temperature is slightly low), and discharge from the second grade outlet pipe, the water route of second grade outlet pipe can effectively be controlled through the setting of second control valve.
Preferably, when the water heater comprises a first-stage water inlet pipe 12 and a second-stage water outlet pipe 8, the water heater further comprises a bypass pipe 10, one end of the bypass pipe 10 is communicated with the second-stage water outlet pipe 8, the other end of the bypass pipe 10 is communicated with the first-stage water inlet pipe 12, and the bypass pipe 10 is further provided with a third control valve 11. This is the utility model discloses a further preferred structural style, can be effectively with the leading-in one-level inlet tube of the hot water of second grade outlet pipe (temperature is slightly low) through the setting of bypass pipe to be prepared the hot water that the temperature is higher in the one-level condenser, form the two-stage and prepare hydrothermal purpose.
Preferably, when the first control valve 13 is included, the first control valve 13 is a solenoid valve; and/or when a second control valve 9 is included, the second control valve 9 is a solenoid valve; and/or when a third control valve 11 is included, said third control valve 11 is a solenoid valve. The solenoid valve is the preferred structural form of several control valves, can form more intelligent accurate control.
Preferably, the primary condenser 2 can release heat and cool in an air cooling mode, and the secondary condenser 4 can release heat and cool in an air cooling mode. This is another preferred structural style of the utility model, form the cooling to the secondary condenser through the form of forced air cooling to and promote the temperature of wind effectively, form hot-blast, in order to form and heat the room, and carry out work such as stoving.
Preferably, the first and second electrodes are formed of a metal,
the wind heated by the secondary condenser 4 can be conducted into the primary condenser 2 to be heated secondarily. Through the structure, air can be effectively accessed from the outside, so that the air is heated and warmed in the secondary condenser, the purpose of preparing hot air (different from the hot air temperature of the primary condenser, lower secondary condensation pressure and slightly lower temperature) is achieved, the purpose of heating the air step by step is achieved, and the requirements of environments with air (hot air) at different temperatures are met.
As shown in fig. 4 to 5, preferably, the compressor 1 comprises a first compression unit 101 and a second compression unit 102, the refrigeration system further comprises a first intermediate heat exchanger 15 and a first branch 16, the first intermediate heat exchanger 15 is arranged on the pipeline between the two-stage condenser 4 and the second throttling device 5, one end of the first branch 16 is connected to the pipeline between the two-stage condenser 4 and the first intermediate heat exchanger 15, the other end of the first branch opens into the first intermediate heat exchanger 15, the outlet pipeline of the first compression unit 101 also opens into the first intermediate heat exchanger 15, the outlet of the first intermediate heat exchanger 15 opens into the inlet of the second compression unit 102, the pipeline between the two-stage condenser 4 and the second throttling device extends through the first intermediate heat exchanger 15 and exchanges heat with the refrigerant inside the first intermediate heat exchanger 15, a third throttling device 17 is further arranged on the first branch 16;
alternatively, the compressor 1 comprises a first compression unit 101, a second compression unit 102 and a third compression unit 103, the air supplement port is positioned between the first compression unit 101 and the second compression unit 102, the refrigeration system further comprises a first intermediate heat exchanger 15 and a first branch 16, the first intermediate heat exchanger 15 is arranged on the pipeline between the first-stage condenser 2 and the first throttling device 3, one end of the first branch 16 is connected to the pipeline between the first-stage condenser 2 and the first intermediate heat exchanger 15, the other end of the first branch leads into the first intermediate heat exchanger 15, meanwhile, the outlet pipeline of the second compression unit 102 also leads into the first intermediate heat exchanger 15, the outlet of the first intermediate heat exchanger 15 is connected to the inlet of the third compression unit 103, the pipeline between the first-stage condenser 2 and the first throttling device 3 penetrates through the first intermediate heat exchanger 15, And exchanges heat with the refrigerant inside the first intermediate heat exchanger 15, and a third throttling device 17 is further provided on the first branch line 16.
The utility model discloses still increased the first middle heat exchanger device of complete intercooling on the basis of two condensation cycle high low temperature system of secondary throttle, compare in the two condensation cycle system of solitary secondary throttle, the super-cooled degree of refrigerant before the entering evaporimeter has further been increased, further strengthened refrigeration coefficient of performance or the coefficient of performance of heating, and still reduce the refrigerant temperature behind the one-level compression unit effectively, make its abundant cooling to saturation temperature (the superheat degree is 0), can effectively reduce the exhaust superheat degree of compressor, and effectively reduce the compressor consumption.
As shown in fig. 6 to 7, preferably, the compressor 1 includes a first compression unit 101 and a second compression unit 102, the refrigeration system also comprises a second intermediate heat exchanger 18 and a second branch 19, the second intermediate heat exchanger 18 being arranged on the line between the secondary condenser 4 and the second throttling device 5, one end of the second branch 19 is connected to a pipeline between the secondary condenser 4 and the second intermediate heat exchanger 18, the other end penetrates through the second intermediate heat exchanger 18 and is communicated to a pipeline between an outlet of the first compression unit 101 and an inlet of the second compression unit 102, a pipeline between the secondary condenser 4 and the second throttling device 5 penetrates through the second intermediate heat exchanger 18 and exchanges heat with the second branch 19 in the second intermediate heat exchanger 18, and a fourth throttling device 20 is further arranged on the second branch 19;
alternatively, the compressor 1 comprises a first compression unit 101, a second compression unit 102 and a third compression unit 103, the air supplement port is located between the first compression unit 101 and the second compression unit 102, the refrigeration system further comprises a second intermediate heat exchanger 18 and a second branch 19, the second intermediate heat exchanger 18 is arranged on the pipeline between the first-stage condenser 2 and the first throttling device 3, one end of the second branch 19 is connected to the pipeline between the first-stage condenser 2 and the second intermediate heat exchanger 18, the other end of the second branch 19 penetrates through the second intermediate heat exchanger 18 and is communicated to the pipeline between the outlet of the second compression unit 102 and the inlet of the third compression unit 103, the pipeline between the first-stage condenser 2 and the first throttling device 3 penetrates through the second intermediate heat exchanger 18 and exchanges heat with the second branch 19 inside the second intermediate heat exchanger 18, and a fourth throttling device 20 is also arranged on the second branch 19.
The utility model discloses still increased the first middle heat exchanger device of incomplete intercooling on the basis of the two condensation cycle high low temperature system of secondary throttle, compare in the two condensation cycle system of solitary secondary throttle, the super-cooled degree of refrigerant before the entering evaporimeter has further been increased, further strengthened refrigeration coefficient of performance or the coefficient of performance of heating, and still reduce the refrigerant temperature behind the one-level compression unit effectively, make its cooling (insufficient cooling to saturation temperature), can effectively reduce the exhaust superheat degree of compressor, and effectively reduce the compressor consumption.
As shown in fig. 8-9, preferably, the compressor 1 includes a first compression unit 101 and a second compression unit 102, the refrigeration system further includes a third branch 21, one end of the third branch 21 is connected to a pipeline between the two-stage condenser 4 and the second throttling device 5, and the other end is connected to a pipeline between an outlet of the first compression unit 101 and an inlet of the second compression unit 102, and a fifth throttling device 22 and a fourth control valve 23 are further disposed on the third branch 21;
or, the compressor 1 includes a first compression unit 101, a second compression unit 102 and a third compression unit 103, the refrigeration system further includes a third branch 21, one end of the third branch 21 is connected to a pipeline between the first-stage condenser 2 and the first throttling device 3, and the other end is connected to a pipeline between an outlet of the second compression unit 102 and an inlet of the third compression unit 103, and the third branch 21 is further provided with a fifth throttling device 22 and a fourth control valve 23.
The utility model discloses still increased the third branch road of middle hydrojet on the basis of two condensation circulation high low temperature systems of secondary throttle, compare in the two condensation circulation system of solitary secondary throttle, reduce the refrigerant temperature behind the one-level compression unit effectively, make its cooling (cooling to saturation temperature or do not cool to saturation temperature), can effectively reduce the exhaust superheat degree of compressor, effectively reduce the compressor consumption, further strengthened refrigeration coefficient of performance or heating coefficient.
As shown in fig. 10 to 11, preferably, the refrigeration system further includes a heat regenerator 24, the heat regenerator 24 is disposed on a pipeline between the secondary condenser 4 and the second throttling device 5, the pipeline between the secondary condenser 4 and the second throttling device 5 extends through the second intermediate heat exchanger 18, and a pipeline between the evaporator 6 and the inlet of the compressor 1 also extends through the heat regenerator 24 and exchanges heat with a pipe section between the secondary condenser 4 and the second throttling device 5 extending through the heat regenerator 24.
The utility model discloses still increased the regenerator on the basis of two condensing cycle high low temperature systems of secondary throttle, compared in the two condensing cycle systems of solitary secondary throttle, can further increased the super-cooled rate of the refrigerant before getting into the evaporimeter, further strengthened refrigeration coefficient of performance or the coefficient of performance that heats, and can also improve the refrigerant superheat degree of breathing in before getting into the compressor induction port, prevent the compressor liquid attack, improve the reliability of compressor.
The utility model also provides an air conditioner, it includes preceding arbitrary the two condensation refrigerating system of secondary throttle.
The utility model also provides a control method suitable for two condensing refrigerating system of arbitrary secondary throttle before being applicable to, wherein:
when the first control valve, the second control valve and the third control valve are included at the same time: and at least one of the first control valve, the second control valve and the third control valve is selectively controlled to act according to the requirements of different hot water temperatures.
The utility model discloses a set up two series connection's condenser, and set up throttling arrangement between two condensers to can effectively form secondary throttle and second grade condensation, the utility model discloses a two high low temperature systems of two condensation cycle of secondary throttle of throttle in the middle of two condensations compare in a throttle refrigeration cycle system, under the condition of same evaporating pressure, superheat degree, super-cooled rate and refrigerant circulation volume, make full use of second grade condenser release refrigerant latent heat and sensible heat after the throttle, greatly improved the heating capacity and the heating coefficient of performance of system.
2. The condensation heat dissipation capacity of the secondary throttling double-condensation circulating high-temperature and low-temperature system is larger, so that the evaporation heat absorption refrigerating capacity and the refrigerating performance coefficient are greatly improved compared with those of a primary throttling refrigerating circulating system.
3. Because the secondary throttling and double-condensing circulation high-low temperature system adopts secondary throttling, the operating environment temperature range of the secondary throttling and double-condensing circulation high-low temperature system is larger than that of the primary throttling and refrigerating circulation system, and the evaporation temperature can be lower, so that the secondary throttling and double-condensing circulation high-low temperature system is suitable for lower environment temperature to heat.
4. Because the secondary throttling double-condensation circulating high-low temperature system adopts double condensers, the condensing pressure of each condenser is different, the temperature of inlet and outlet water of each condenser can be freely controlled and adjusted, and the multifunctional working condition of water with different water temperatures can be realized.
5. Because the secondary throttling double-condensation circulating high-low temperature system adopts the double condensers, the condensing pressure of each condenser is different, the air inlet and outlet temperature of each condenser can be freely controlled and adjusted, and the multifunctional working condition of heating at different air outlet temperatures can be realized.
Preferably, the second control valve 9 is arranged on the secondary water outlet pipe 8, and the first control valve 13 is arranged on the primary water inlet pipe 12:
when water at a first temperature T1 and a second temperature T2 needs to be prepared at the same time, the first control valve 13 and the second control valve 9 are selected to be opened at the same time, and the third control valve 11 is closed at the same time;
when water with the first temperature T1 and the third temperature T3 needs to be prepared at the same time, the second control valve 9 and the third control valve 11 are selected to be opened at the same time, and the first control valve 13 is closed; wherein the second temperature T3> the second temperature T2> the first temperature T1;
when it is only necessary to make water at a third temperature T3, the third control valve 11 is selectively opened while the first control valve 13 and the second control valve 9 are closed.
The secondary throttling double-condensation circulation high-low temperature system is explained by combining the attached drawings 1-3 as follows:
referring to the attached figure 1, a schematic diagram of a secondary throttling double-condensation cycle high-low temperature system and a pressure-enthalpy diagram of a secondary throttling double-condensation cycle high-low temperature system are shown in the attached figure 2, a compressor sucks low-temperature superheated refrigerant b from an evaporator for compression, and compressed high-temperature high-pressure superheated refrigerant c is discharged into a primary condenser and condensed by cooling water into high-temperature high-pressure wet vapor refrigerant d; the high-temperature high-pressure wet vapor refrigerant d after primary condensation is throttled by a first throttling device to become a medium-temperature medium-pressure wet vapor refrigerant e; the medium-temperature medium-pressure wet vapor refrigerant e after primary throttling enters a secondary condenser and is condensed to medium-temperature medium-pressure supercooling refrigerant g by cooling water; the medium-temperature medium-pressure subcooled refrigerant g after secondary condensation is throttled by a second throttling device to form a low-temperature low-pressure wet vapor refrigerant h; the low-temperature low-pressure wet vapor refrigerant h after secondary throttling enters the evaporator to absorb heat to a low-temperature superheated refrigerant state b, so that a secondary throttling double-condensation cycle is completed.
Because two low temperature systems of two condensation circulations of secondary throttle have two condensers, the condensing pressure of each condenser is different, so the cooling method of condenser is various for the business turn over temperature of every condenser can freely be controlled and adjusted, can realize the multi-functional operating mode of different temperature water uses.
The first cooling method is to open the first control valve and open the second control valve simultaneously, and close the third control valve 11 simultaneously. The water inlet source temperature of the first-stage water inlet pipe and the water inlet source temperature of the second-stage water inlet pipe can be different, and the condensation temperature of the second-stage condenser is lower than that of the first-stage condenser, so that the water outlet temperature of the second-stage water outlet pipe is generally lower than that of the first-stage water outlet pipe, and therefore multifunctional working conditions that hot water at the first temperature T1 and the second temperature T2 is prepared to be used are achieved.
In the second cooling method, the second control valve and the third control valve are opened at the same time, and the first control valve is closed. The cooling water enters from the secondary water inlet pipe, after the cooling water is heated by the refrigerant of the secondary condenser, one part of the heated cooling water flows out from the secondary water outlet pipe for users to use, the other part of the heated cooling water enters into the primary condenser and is continuously heated by the refrigerant of the primary condenser, and the heated high-temperature hot water flows out from the primary water outlet pipe for users to use, so that the multifunctional working condition that the hot water with the first temperature T1 and the third temperature T3 is prepared for use is realized.
The third cooling mode is to open the third control valve and close the first control valve and the second control valve at the same time. And cooling water enters from the secondary water inlet pipe, and is heated into high-temperature hot water by the refrigerant of the secondary condenser and the refrigerant of the primary condenser, so that the high-flow requirement of the hot water at the third temperature T3 can be realized.
Referring to fig. 3, a pressure-enthalpy diagram of the secondary throttling double-condensation cycle high-low temperature system is compared with a pressure-enthalpy diagram of a conventional primary throttling refrigeration cycle system, and under the condition of the same evaporation pressure, superheat degree and refrigerant circulation volume, the condensation pressure of the primary throttling refrigeration cycle system is in the middle of two condensation pressures of the secondary throttling double-condensation cycle system. Compared with a primary throttling refrigeration cycle system, the compression power consumption of the secondary throttling double-condensation cycle system is increased by W ═ hc-hhThe secondary throttling double-condensation circulating high-low temperature system fully utilizes the latent heat of the refrigerant released by the secondary condenser after the primary throttlingSensible heat, more Q than the heating capacity of the primary throttling refrigeration cycle systemh＝hi-hfRefrigeration capacity is much Qc＝hj-hg. Compared with a primary throttling refrigeration cycle system, the secondary throttling double-condensation cycle system has the advantages that the amplification degree of the heating capacity and the refrigerating capacity is far greater than that of the compression power consumption, so that the secondary throttling double-condensation cycle high-low temperature system has higher heating capacity, refrigerating capacity, heating performance coefficient and refrigerating performance coefficient.
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. The foregoing is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, a plurality of modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.
Claims (12)
1. The utility model provides a two condensing refrigerating system of secondary throttle which characterized in that: the method comprises the following steps:
compressor (1) and evaporimeter (6), still include one-level condenser (2) and second grade condenser (4), first throttling arrangement (3) and second throttling arrangement (5), one-level condenser (2) with the exit linkage of compressor (1), the export of one-level condenser (2) with the entry linkage of second grade condenser (4) and be in one-level condenser (2) with still be provided with on the pipeline between second grade condenser (4) first throttling arrangement (3), the exit linkage of second grade condenser (4) second throttling arrangement (5), the other end of second throttling arrangement (5) is connected evaporimeter (6).
2. The secondary throttle dual-condensation refrigeration system according to claim 1, characterized in that:
still including letting in one-level inlet tube (12) in one-level condenser (2), one-level inlet tube (12) let in water in one-level condenser (2) and with the refrigerant pipeline in one-level condenser (2) carries out the heat transfer, one-level outlet pipe (14) is connected to the exit end of one-level condenser (2), be provided with first control valve (13) on one-level inlet tube (12).
3. The secondary throttle dual-condensation refrigeration system according to claim 1, characterized in that:
still including letting in second grade inlet tube (7) in second grade condenser (4), second grade inlet tube (7) let in water in second grade condenser (4) and with the refrigerant pipeline in second grade condenser (4) carries out the heat transfer, second grade outlet pipe (8) are connected to the exit end of second grade condenser (4) be provided with second control valve (9) on second grade outlet pipe (8).
4. The secondary throttling dual condensation refrigeration system of claim 3, wherein:
when the water purifier comprises a primary water inlet pipe (12) and a secondary water outlet pipe (8), the water purifier further comprises a bypass pipe (10), one end of the bypass pipe (10) is communicated with the secondary water outlet pipe (8), the other end of the bypass pipe is communicated with the primary water inlet pipe (12), and a third control valve (11) is further arranged on the bypass pipe (10).
5. The secondary throttle dual-condensation refrigeration system according to claim 4, characterized in that:
when a first control valve (13) is included, the first control valve (13) is an electromagnetic valve; and/or when a second control valve (9) is included, the second control valve (9) is a solenoid valve; and/or when a third control valve (11) is included, the third control valve (11) is a solenoid valve.
6. The secondary throttle dual-condensation refrigeration system according to claim 1, characterized in that:
the primary condenser (2) can release heat and cool in an air cooling mode, and the secondary condenser (4) can release heat and cool in an air cooling mode.
7. The secondary throttle dual-condensation refrigeration system according to claim 6, characterized in that:
the air heated by the secondary condenser (4) can be conducted into the primary condenser (2) to be heated secondarily.
8. The double-throttling double-condensing refrigeration system according to any one of claims 1 to 7, characterized in that:
the compressor (1) comprises a first compression unit (101) and a second compression unit (102), the refrigeration system further comprises a first intermediate heat exchanger (15) and a first branch (16), the first intermediate heat exchanger (15) is arranged on a pipeline between the secondary condenser (4) and the second throttling device (5), one end of the first branch (16) is connected to a pipeline between the secondary condenser (4) and the first intermediate heat exchanger (15), the other end of the first branch is communicated into the first intermediate heat exchanger (15), an outlet pipeline of the first compression unit (101) is communicated into the first intermediate heat exchanger (15), an outlet of the first intermediate heat exchanger (15) is communicated to an inlet of the second compression unit (102), and a pipeline between the secondary condenser (4) and the second throttling device penetrates through the first intermediate heat exchanger (15), The heat exchange is carried out between the refrigerant and the refrigerant in the first intermediate heat exchanger (15), and a third throttling device (17) is further arranged on the first branch (16);
or, the compressor (1) comprises a first compression unit (101), a second compression unit (102) and a third compression unit (103), the refrigeration system further comprises a first intermediate heat exchanger (15) and a first branch (16), the first intermediate heat exchanger (15) is arranged on a pipeline between the first-stage condenser (2) and the first throttling device (3), one end of the first branch (16) is connected to a pipeline between the first-stage condenser (2) and the first intermediate heat exchanger (15), the other end of the first branch leads into the first intermediate heat exchanger (15), an outlet pipeline of the second compression unit (102) is communicated to the first intermediate heat exchanger (15), an outlet of the first intermediate heat exchanger (15) is communicated to an inlet of the third compression unit (103), and a pipeline between the first-stage condenser (2) and the first throttling device (3) penetrates through the first intermediate heat exchanger (15), And exchanges heat with the refrigerant in the first intermediate heat exchanger (15), and a third throttling device (17) is arranged on the first branch (16).
9. The double-throttling double-condensing refrigeration system according to any one of claims 1 to 7, characterized in that:
the compressor (1) comprises a first compression unit (101) and a second compression unit (102), the refrigeration system further comprises a second intermediate heat exchanger (18) and a second branch (19), the second intermediate heat exchanger (18) is arranged on a pipeline between the secondary condenser (4) and the second throttling device (5), one end of the second branch (19) is connected to a pipeline between the secondary condenser (4) and the second intermediate heat exchanger (18), the other end of the second branch penetrates through the second intermediate heat exchanger (18) and is communicated to a pipeline between an outlet of the first compression unit (101) and an inlet of the second compression unit (102), a pipeline between the secondary condenser (4) and the second throttling device (5) penetrates through the second intermediate heat exchanger (18) and exchanges heat with the second branch (19) inside the second intermediate heat exchanger (18), a fourth throttling device (20) is further arranged on the second branch (19);
or, the compressor (1) comprises a first compression unit (101), a second compression unit (102) and a third compression unit (103), the refrigeration system further comprises a second intermediate heat exchanger (18) and a second branch (19), the second intermediate heat exchanger (18) is arranged on a pipeline between the first-stage condenser (2) and the first throttling device (3), one end of the second branch (19) is connected to a pipeline between the first-stage condenser (2) and the second intermediate heat exchanger (18), the other end of the second branch penetrates through the second intermediate heat exchanger (18) and is communicated to a pipeline between an outlet of the second compression unit (102) and an inlet of the third compression unit (103), and a pipeline between the first-stage condenser (2) and the first throttling device (3) penetrates through the second intermediate heat exchanger (18), And exchanges heat with the second branch (19) in the second intermediate heat exchanger (18), and a fourth throttling device (20) is further arranged on the second branch (19).
10. The double-throttling double-condensing refrigeration system according to any one of claims 1 to 7, characterized in that:
the compressor (1) comprises a first compression unit (101) and a second compression unit (102), the refrigeration system further comprises a third branch (21), one end of the third branch (21) is connected to a pipeline between the two-stage condenser (4) and the second throttling device (5), the other end of the third branch is communicated to a pipeline between an outlet of the first compression unit (101) and an inlet of the second compression unit (102), and a fifth throttling device (22) and a fourth control valve (23) are further arranged on the third branch (21);
or, the compressor (1) comprises a first compression unit (101), a second compression unit (102) and a third compression unit (103), the refrigeration system further comprises a third branch (21), one end of the third branch (21) is connected to a pipeline between the first-stage condenser (2) and the first throttling device (3), the other end of the third branch is communicated to a pipeline between an outlet of the second compression unit (102) and an inlet of the third compression unit (103), and a fifth throttling device (22) and a fourth control valve (23) are further arranged on the third branch (21).
11. The double-throttling double-condensing refrigeration system according to any one of claims 1 to 7, characterized in that:
the refrigerating system further comprises a heat regenerator (24), the heat regenerator (24) is arranged on a pipeline between the secondary condenser (4) and the second throttling device (5), the pipeline between the secondary condenser (4) and the second throttling device (5) penetrates through the heat regenerator (24), and a pipeline between the evaporator (6) and an inlet of the compressor (1) also penetrates through the heat regenerator (24) and exchanges heat with a pipeline between the secondary condenser (4) and the second throttling device (5) and penetrates through the heat regenerator (24).
12. An air conditioner, characterized in that:
comprising the double-throttling double-condensing refrigeration system of any of claims 1 to 11.
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| CN111550943A (en) * | 2020-04-26 | 2020-08-18 | 珠海格力电器股份有限公司 | Secondary throttling double-condensation refrigerating system, air conditioner and control method |
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