CN212253218U - Low-temperature strong-heat air source heat pump system - Google Patents
Low-temperature strong-heat air source heat pump system Download PDFInfo
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- CN212253218U CN212253218U CN202021469795.8U CN202021469795U CN212253218U CN 212253218 U CN212253218 U CN 212253218U CN 202021469795 U CN202021469795 U CN 202021469795U CN 212253218 U CN212253218 U CN 212253218U
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Abstract
A low-temperature strong-heat air source heat pump system comprises a compressor, an air-cooled condenser, a one-way valve assembly, a flash tank, an economizer, a water-side heat exchanger and a gas-liquid separator; the air suction port of the compressor is connected with the gas-liquid separator, the exhaust port of the compressor is connected with the air-cooled condenser or the water-side heat exchanger through a four-way reversing valve, and the air supplement port of the compressor is connected with the air supplement loop and the liquid spraying loop; the air-cooled condenser is connected with the first-stage throttling electronic expansion valve through the one-way valve assembly; the first-stage throttling electronic expansion valve is connected with the flash tank through a drying filter A; the liquid outlet of the flash tank is connected with the main side inlet of the economizer, and the gas supplementing port of the flash tank is connected with the gas supplementing loop; the main side outlet of the economizer is respectively connected with the liquid spraying loop and the second-stage throttling electronic expansion valve; the second-stage throttle electronic expansion valve is connected with the economizer through a drying filter B, and the second-stage throttle electronic expansion valve is connected with the water side heat exchanger or the air-cooled condenser through a one-way valve assembly.
Description
Technical Field
The utility model relates to a heating ventilation air conditioning technology field, concretely relates to strong hot air source heat pump system of low temperature.
Background
An air source heat pump system is a renewable energy source utilization system which takes low-grade air as a cold and heat source, takes a refrigerant as a working medium, and consists of four devices, namely a compressor, an evaporator, a condenser and a throttling device, which are taken as main core components, and works according to inverse Carnot cycle to prepare cold and hot water.
The rapid development of global economy, energy shortage, aggravation of environmental pollution and global warming become problems concerned by the world, and particularly become a serious challenge facing the global refrigeration and air-conditioning industry; the method has the advantages of realizing efficient utilization of energy, low carbon and environmental protection and reducing energy consumption, and is particularly important. The air source heat pump is used as a renewable system form for preparing cold and hot water by virtue of the technical advantages of high efficiency, energy conservation, economy and environmental protection, and is rapidly developed in the field of building air conditioners in recent years.
However, in the conventional air source heat pump system, the refrigeration cycle working medium mainly comprises HCFC (HCFC-hydrochlorofluorocarbon), the most representative working medium is R22, but the refrigerant has serious damage to the ozone layer, and in order to reduce the damage to the ozone layer and the environment, the adjustment scheme for accelerating the elimination of HCFCs is passed in 9 months in 2007 and at the 19 th contracting meeting of the Montreal protocol; at present, HCFCs (R22) refrigerant in China is mainly substituted by Hydrofluorocarbon (HFCs) refrigerants such as R410A, R407C, R134a and the like, and the Hydrofluorocarbon (HFCs) refrigerant for substituting HCFCs has higher Global Warming Potential (GWP), and can only be used as a transition refrigerant in a short term under the current environment-friendly international environment; however, with the enhancement of the environmental protection consciousness all year round and the approval and signing of the global basic plus correction case, the refrigerant with high GWP is obviously not meeting the requirement of low GWP environmental protection in the refrigeration industry, and the search for the environment-friendly refrigerant with zero ODP and low GWP value becomes a common subject and social responsibility in the global refrigeration and air-conditioning industry in a period of time in the future, and is a global subject to be intensively solved by the union of global associates.
Therefore, the conventional air source heat pump system using R22 and R410A as working media faces the edge of limited use and elimination, is no longer suitable for long-term development of the air conditioning industry, and is already trending in the industry to search for a novel environment-friendly refrigerant with better energy conservation and environmental protection.
In addition to the above problems, the conventional air source heat pump has the following technical problems:
(1) the contradiction between heat supply and demand: the building heat demand is in linear inverse proportion to the outer ring temperature, the outer ring temperature is low, the heat demand is large, and the attenuation of the heating capacity of the conventional air source heat pump is obvious;
(2) limitation: in severe cold areas, a conventional air source heat pump system cannot be normally started and operated at the environment temperature of less than or equal to-15 ℃, the environment temperature of less than or equal to-20 ℃ and the COPH (chemical oxygen demand) is hardly more than 2.0 (the output water temperature is 41 ℃);
(3) under the working condition of high pressure ratio, the exhaust temperature of the compressor is continuously increased, the compression has overheating operation risk, the lubrication of the compressor is poor, the service life of the compressor is influenced, and the exhaust temperature is high, so that the compressor cannot be controlled within a reliable range by an effective control means and a method.
SUMMERY OF THE UTILITY MODEL
The utility model discloses to current technical problem, a low temperature strong hot air source heat pump system suitable for R32 working medium tonifying qi increases enthalpy second grade throttle is provided.
The utility model provides an above-mentioned technical problem's technical scheme as follows: a low-temperature strong-heat air source heat pump system comprises a compressor, a four-way reversing valve, an air-cooled condenser, a one-way valve assembly, a flash tank, an economizer, a water-side heat exchanger and a gas-liquid separator;
the air suction port of the compressor is connected with the gas-liquid separator, the exhaust port of the compressor is connected with the air-cooled condenser or the water-side heat exchanger through a four-way reversing valve, and the air supplement port of the compressor is connected with the air supplement loop and the liquid spraying loop;
the air-cooled condenser is connected with the first-stage throttling electronic expansion valve through the one-way valve assembly;
the first-stage throttling electronic expansion valve is connected with the flash tank through a drying filter A;
the liquid outlet of the flash tank is connected with the main side inlet of the economizer, and the gas supplementing port of the flash tank is connected with the gas supplementing loop;
the main side outlet of the economizer is respectively connected with the liquid spraying loop and the second-stage throttling electronic expansion valve;
and a drying filter B is arranged between the second-stage throttle electronic expansion valve and the economizer, and the second-stage throttle electronic expansion valve is connected with the water side heat exchanger or the air-cooled condenser through a one-way valve assembly.
The utility model has the advantages that: according to the air source heat pump system, the first-stage throttling electronic expansion valve and the second-stage throttling electronic expansion valve are adopted on the main circulation loop to achieve second-stage throttling depressurization, the air replenishing function of the flash tank is utilized, quasi second-stage compression is achieved, the flow of a refrigerant in the circulation loop is improved by 20%, the low-temperature heating capacity is improved by 10% -15%, and low-temperature intense heat is achieved, so that the system can efficiently and stably run at the severe cold temperature of-25 ℃, and the technical problems that the running range of a conventional air source heat pump is limited, the low-loop-temperature heating capacity is attenuated, and the energy efficiency is low are effectively solved.
On the basis of the technical scheme, the utility model discloses a reach the convenience of use and the stability of equipment, can also make following improvement to foretell technical scheme:
further, a main side outlet of the economizer is connected with an auxiliary side throttle expansion valve through a drying filter C, the auxiliary side throttle expansion valve is connected with an auxiliary side inlet of the economizer, and an auxiliary side outlet of the economizer is connected with a gas pipe between the four-way reversing valve and the gas-liquid separator.
The beneficial effect of adopting the further technical scheme is that: the secondary supercooling is realized by the aid of a downstream circulation mode of the economizer in a recycling mode, the inlet dryness of the evaporator is reduced, the unit circulation refrigerating capacity is increased, and the unit performance is effectively improved. Meanwhile, the auxiliary side of the economizer is circularly throttled by an electronic expansion valve, the middle air supplement pressure and the middle relative air supplement amount of the compressor are accurately controlled, and the heating performance of the unit under the low-temperature working condition is effectively improved.
Furthermore, an outlet at the auxiliary side of the economizer is provided with a temperature sensor, and the temperature sensor and the air suction pressure sensor are used for controlling the opening degree of the second-stage throttling electronic expansion valve.
The beneficial effect of adopting the further technical scheme is that: the PID control and the accurate pulse regulation of the second-stage throttle electronic expansion valve are realized by arranging the temperature sensor and the air suction pressure sensor together, the opening degree of the second-stage throttle electronic expansion valve is regulated in real time, the optimal flow dynamic matching is ensured, the flow regulation is more accurate, and the regulation range is wider.
Further, the air suction pressure sensor and the air suction temperature sensor are arranged on a connecting pipeline of the four-way reversing valve and the gas-liquid separator.
The beneficial effect of adopting the further technical scheme is that: the suction pressure sensor and the suction temperature sensor are arranged on the same pipeline, so that the influence of suction pressure drop on the accuracy of the calculated current superheat value can be avoided, and the accuracy of the main valve can be accurately controlled by comparing the calculated current superheat value with the target superheat value; meanwhile, the air suction temperature sensor is arranged before air separation, but not after air separation, the arrangement mode can effectively avoid the problems that when the low-ring-temperature unit is started, a large amount of liquid refrigerant stored in the air-liquid separator flows into the compressor through the air suction pipe, the detected air suction temperature is low, the calculated current superheat degree value is low, the opening of the electronic expansion valve is gradually reduced, liquid supply is insufficient during low-temperature starting, and low-ring-temperature starting frequent low-pressure alarm occurs.
Furthermore, a liquid spraying electromagnetic valve, a liquid spraying capillary tube and a liquid spraying one-way valve are arranged on the liquid spraying loop.
The beneficial effect of adopting the further technical scheme is that: when the current exhaust temperature is higher than a set protection value, the liquid spraying electromagnetic valve is closed, the liquid spraying cooling loop is conducted, the medium-pressure liquid refrigerant is throttled by the liquid spraying capillary tube and then mixed with the air supply circulating refrigerant to enter an air supply port of the compressor, wet spraying is carried out on the compressor, the exhaust temperature is reduced, particularly the problem that the exhaust temperature of an R32 working medium circulating system is too high is solved, the exhaust temperature of the compressor can be controlled within 125 ℃, and the compressor is prevented from being operated excessively; meanwhile, a one-way valve is arranged on the liquid spraying loop to prevent backflow.
Further, an air supply one-way valve is arranged on the air supply loop.
The beneficial effect of adopting the further technical scheme is that: the gas backflow can be prevented by arranging the gas supplementing one-way valve.
Furthermore, the second-stage throttle electronic expansion valve is connected in parallel with a bypass loop, and a bypass electromagnetic valve and a bypass capillary tube are arranged on the bypass loop.
The beneficial effect of adopting the further technical scheme is that: in a refrigeration running mode, the bypass electromagnetic valve is used as a passage when being electrified, the circulation quantity of a low-pressure side refrigerant is increased, the liquid supply quantity of the second-stage throttling electronic expansion valve is made up for the shortage, and the refrigerating capacity and the energy efficiency of a unit are improved; when in the heating mode, the bypass electromagnetic valve is powered off, and the bypass loop is not communicated; in the defrosting mode, the bypass electromagnetic valve is powered on, the circulation quantity of high-temperature refrigerants is increased, the defrosting speed can be increased, and the defrosting time is greatly shortened.
Further, the compressor is a scroll compressor, and the medium adopted by the low-temperature strong-heat air source heat pump system is R32 refrigerant.
The beneficial effect of adopting the further technical scheme is that: the R32 refrigerant has better heat exchange characteristic, the refrigerating capacity per unit volume is large, the filling amount of the system refrigerant is small, the system volume is reduced, and meanwhile, the system performance is obviously improved; and the GWP value of the HFCs-R32 is only 1/3 of R410A, the ODP value is 0, the refrigerant is energy-saving and environment-friendly, is an ideal substitute working medium for the traditional refrigerant in the middle and long term, and meets the development trend and the requirement of a novel refrigerant system in the refrigeration industry.
Furthermore, the air-cooled condenser is a red copper heat exchange tube with the tube diameter less than or equal to 7mm, and the economizer is a plate heat exchanger.
The beneficial effect of adopting the further technical scheme is that: the air-cooled condenser adopts a small-caliber heat exchanger, is more suitable for the flowing and heat exchange characteristics of R32, and improves the heat exchange performance; through setting up plate economizer can realize the secondary subcooling of middle pressure refrigerant before the second grade throttle, reduce the inlet dry-type and the flash gas before the throttle, improve evaporation side heat transfer performance.
Further, the check valve assembly includes four diaphragm type check valves.
The beneficial effect of adopting the further technical scheme is that: the one-way valve assembly plays a role in reversing the refrigerant in the system cycle, and the high-temperature and high-pressure refrigerant condensed in the refrigeration cycle and the heating cycle enters the flash tank after being throttled by the primary throttling electronic expansion valve.
Drawings
FIG. 1 is a schematic view of the present invention;
FIG. 2 is a flow chart of the cooling mode of the present application;
FIG. 3 is a flow chart of the heating mode of the present application;
FIG. 4 is a flow chart of the defrost mode of the present application;
figure 5 is a graph of the thermodynamic cycle pressure enthalpy p-h of the system of the present application.
The reference numbers are recorded as follows: the system comprises a compressor 1, a four-way reversing valve 2, a D interface 2-1, an E interface 2-2, an S interface 2-3, a C interface 2-4, an air-cooled condenser 3, a one-way valve component 4, a one-way valve A4-1, a one-way valve B4-2, a one-way valve C4-3, a one-way valve D4-4, a first-stage throttling electronic expansion valve 5, a drying filter A6, a flash generator 7, an economizer 8, a drying filter B9, a second-stage throttling electronic expansion valve 10, a bypass electromagnetic valve 11, a bypass throttling capillary tube 12, a water-side heat exchanger 13, a gas-liquid separator 14, a drying filter C15, an auxiliary-side throttling expansion valve 16, a liquid-spraying electromagnetic valve 17, a liquid-spraying capillary tube 18, a liquid-spraying one-way valve 19, a gas-supplementing one-way valve 20, a temperature-discharging sensor 21, A gas supply circuit 26 and a liquid spraying circuit 27.
Detailed Description
The principles and features of the present invention are described below in conjunction with the following drawings, the examples given are only intended to illustrate the present invention and are not intended to limit the scope of the present invention.
A low-temperature strong-heat air source heat pump system (see figures 1 to 5) comprises a compressor 1, a four-way reversing valve 2, an air-cooled condenser 3, a one-way valve assembly 4, a flash tank 7, an economizer 8, a water-side heat exchanger 13 and a gas-liquid separator 14;
an air suction port of the compressor 1 is connected with the gas-liquid separator 14, an air exhaust port is connected with the air-cooled condenser 3 or the water-side heat exchanger 13 through a D interface 2-1 of the four-way reversing valve 2, and an air supplement port of the compressor 1 is connected with an air supplement loop 26 and a liquid spraying loop 27; and a coil of the compressor 1 is cooled by a suction working medium, and oil is returned by utilizing the velocity of return air. And a temperature exhaust sensor 21 is arranged on a pipeline connecting the compressor 1 and the four-way reversing valve 2. And a fin temperature sensor 25 is arranged on the air-cooled condenser 3. The liquid spraying loop 27 is connected with the air supplementing loop 26 in parallel, and the liquid spraying loop 27 and the air supplementing loop 26 are mixed and then connected with an air supplementing port of the compressor 1.
As shown in fig. 5, the thermodynamic cycle of the existing primary throttling, air-filling and enthalpy-increasing air source heat pump system: 1 → 2 → 3 → 4 → 5 → 6 → 7' → 8' → 9' → 1
The application discloses a second grade throttle, tonifying qi increase enthalpy low temperature strong heat air source heat pump system thermodynamic cycle:
thermal cycling with spray circulation closed:
thermal cycling with spray circulation loop open:
according to the low-temperature strong-heat air source heat pump system, a system circulating working medium is throttled from a high-pressure Pc state to a medium-pressure Pi two-phase state through a first-stage throttling electronic expansion valve 5 and then enters a flash generator 7 to be divided into a saturated gas state and a saturated liquid state, the saturated medium-pressure gas in the upper space of the flash generator 7 enters a gas supplementing port of a compressor 1 through a gas supplementing loop 26, a saturated medium-pressure liquid refrigerant at the lower part of the flash generator 7 enters a main side of an economizer 8 in a medium-low pressure section to circulate, and is throttled to a low-pressure P0 gas-liquid two-phase state through a second-stage throttling electronic expansion valve 10 after being subjected to.
This application is through the peculiar system form of the secondary subcooling that the liquid was got to the medium pressure tonifying qi of second grade throttle, flash tank and well low pressure section plate economizer low reaches for the evaporation side obtains lower entry quality of dryness and entry enthalpy value, thereby has increased evaporation side entry and exit enthalpy difference, compares current once throttle tonifying qi enthalpy increase air source heat pump system, analyzes from the thermodynamic theory, this application evaporation side enthalpy difference increase ^ h (9') -h11 > 0, shows promptly: compared with the existing one-time throttling air-supplying enthalpy-increasing system, the system can absorb more heat in the environment under the same environment temperature and evaporation pressure, and the system form is more efficient; theoretical analysis and experimental tests verify that compared with the existing air source heat pump system for once air supply and enthalpy increase, the low-temperature heating capacity of the air source heat pump system is improved by 10% -15% under the low-temperature working condition, the energy efficiency is improved by 3% -5%, the low-temperature strong heat and the low-temperature high efficiency are realized in the true sense, and the effect is obvious;
meanwhile, the economizer in the middle of the application adopts a downstream liquid taking mode, the inlet dryness of the low-pressure side throttling electronic expansion valve is lower, the content of flash gas behind the valve is reduced, and the heat exchange coefficient and the heat exchange performance of an evaporation side are improved.
The air-cooled condenser 3 is connected with a first-stage throttling electronic expansion valve 5 through the one-way valve assembly 4; the first-stage throttling electronic expansion valve 5 is an electronic expansion valve, and the electronic expansion valve is selected and a thermostatic expansion valve can be selected.
The first-stage throttle electronic expansion valve 5 is connected with the flash tank 7 through a dry filter A6; the liquid outlet of the flash tank 7 is connected with the main side inlet of the economizer 8, and the gas supplementing port of the flash tank 7 is connected with the gas supplementing loop 26.
Primary side circulation: the primary side outlet of the economizer 8 is connected with a secondary throttling electronic expansion valve 10 through a dry filter B9;
the second stage throttle electronic expansion valve 10 is connected with the water side heat exchanger 13 or the air-cooled condenser 3 through the one-way valve assembly 4.
The water side heat exchanger 13 is a dry shell-and-tube heat exchanger or a U-shaped heat exchange tube, and adopts a spiral baffle plate, but the form of the water side heat exchanger is not limited thereto, and the plate heat exchanger is also applicable.
The water side heat exchanger 13 adopts the U-shaped heat exchange tube, so that lubricating oil can return to the compressor more conveniently, the oil storage rate of the low-pressure side of the system is reduced, the compressor is fully lubricated, and the problem that the compressor is damaged due to insufficient lubrication in the process of overheating operation is effectively prevented; and meanwhile, the spiral baffle plate is adopted, so that the disturbance of the water side can be increased, the heat exchange coefficient and the heat exchange effect of the water side are improved, and the performance of the unit is further improved.
The auxiliary side of the economizer 8 circulates: the main side outlet of the economizer 8 is connected with an auxiliary side throttle expansion valve 16 through a dry filter C15, the auxiliary side throttle expansion valve 16 is connected with an auxiliary side inlet of the economizer 8, the auxiliary side outlet of the economizer 8 is connected with a gas pipe between the four-way reversing valve 2 and the gas-liquid separator 14, and the gas suction port of the compressor 1 is connected through the gas-liquid separator 14. And an air pipe for connecting the four-way reversing valve 2 with the gas-liquid separator 14 is provided with an air suction pressure sensor 22 and an air suction temperature sensor 23.
The drying filter A6, the drying filter B9 and the drying filter C15 are red copper drying filters.
And a temperature sensor 24 is arranged at the outlet of the auxiliary side of the economizer 8, and the temperature sensor 24 and the suction pressure sensor 22 are used for controlling the opening degree of the second-stage throttling electronic expansion valve 10.
A liquid spraying circulation loop: the main side outlet of the economizer 8 is connected with a liquid spraying loop 27, the liquid spraying loop 27 is connected with the air replenishing loop 26 in parallel, and the liquid spraying loop 27 and the air replenishing loop 26 are mixed and then are connected with an air replenishing port of the compressor 1.
The liquid spraying loop 27 is provided with a liquid spraying electromagnetic valve 17, a liquid spraying capillary 18 and a liquid spraying one-way valve 19 which are connected in series. The liquid spraying electromagnetic valve 17 on the liquid spraying loop 27 is controlled through target exhaust temperature and return difference, when the current exhaust temperature is not less than the target protection exhaust temperature, the liquid spraying electromagnetic valve 17 is opened, and the liquid spraying loop 27 is opened; when the current exhaust temperature is less than or equal to (target exhaust temperature-return difference set value), the liquid spraying electromagnetic valve 17 is closed, and the liquid spraying loop 27 is closed. The system can be operated efficiently and stably at the ambient temperature of-25 ℃.
The air supply loop 26 is provided with an air supply one-way valve 20.
By coupling the liquid spraying loop 27 in parallel with the air supply loop 26, under the working condition of high pressure ratio, wet spraying is formed by opening the liquid spraying loop 27, the exhaust temperature of the system can be effectively reduced, compared with a conventional air source heat pump system and the existing primary throttling air supply enthalpy increasing system, the method can enable the compressor 1 to be closer to isentropic compression, the exhaust end point of the compressor 1 is leftwards moved to a point 4 'from a point 4 of a thermodynamic cycle pressure enthalpy p-h diagram of a system shown in a figure 5 and is closer to the isentropic compression end point 4s, the exhaust temperature is reduced to a T4' from a T4, two technical problems of quick rising of the exhaust temperature when the temperature is started at a limit low temperature and high temperature and overhigh temperature under the working condition of high pressure ratio are effectively solved, the expansion and application of the low-temperature air source heat pump system in severe cold areas are possible, the system is particularly suitable for R32 working media, and the characteristic of overhigh temperature discharge, the exhaust temperature of the compressor can be controlled in a reasonable interval, the compressor is prevented from operating excessively, and the high efficiency and stability of the system are guaranteed.
The second-stage throttle electronic expansion valve 10 is connected in parallel with a bypass loop, and a bypass electromagnetic valve 11 and a bypass throttle capillary tube 12 are arranged on the bypass loop.
The compressor 1 is a scroll compressor, and a medium adopted by a low-temperature strong hot air source heat pump system in a circulating mode is R32 refrigerant. The scroll compressor has the function of air supplement and enthalpy increase of a low-pressure cavity cooling zone, and the circulating medium of the low-temperature strong hot air source heat pump system is not limited to an R32 refrigerant and is also suitable for conventional refrigerants such as R22 and R410A. This application is through being applied to the accurate second grade compressor tonifying qi of second grade throttle with R32 working medium and increasing on the heat pump circulation system of enthalpy, heat transfer characteristic and the hot thing characteristic to R32 working medium have carried out the adaptability design, little pipe footpath design is all adopted to flash tank 7 and air-cooled condenser 3, flow path optimal design, the good flow characteristic and the heat transfer characteristic of full play R32 working medium, two ware heat exchanger performance promote 3% ~ 5%, the system size reduces, the cost drops into and reduces about 5%.
The air-cooled condenser 3 is a red copper heat exchange tube with the tube diameter less than or equal to 7mm, and the economizer 8 is a plate heat exchanger.
The check valve assembly 4 comprises four diaphragm type check valves.
The low-temperature strong-heat air source heat pump system has three circulation function modes of a refrigeration function, a heating function and a defrosting function:
the refrigeration mode is operated: the four-way reversing valve 2 is not powered, the D interface 2-1 is communicated with the C interface 2-4, and the E interface 2-2 is communicated with the S interface 2-3; high-temperature and high-pressure superheated refrigerant gas generated by compression of a compressor 1 enters an air-cooled condenser 3 through a four-way reversing valve 2 for cooling and condensation, liquid refrigerant after condensation and cooling is subjected to reversing and flow guiding effects through a one-way valve assembly 4, the liquid refrigerant passes through a one-way valve C4-3 of the one-way valve assembly 4, is throttled and decompressed by a first-stage throttling electronic expansion valve 5 to be in a medium-temperature and medium-pressure gas-liquid two-phase state and enters a flash tank 7, saturated gas enters an air supplementing port of the compressor 1 through an air supplementing one-way valve 20, residual saturated liquid refrigerant in the flash tank 7 enters a main circulation loop of a plate economizer 8, exchanges heat with an auxiliary circulation loop to realize secondary supercooling, is throttled and decompressed by a second-stage throttling electronic expansion valve 10 and a bypass loop, is subjected to heat absorption and evaporation refrigeration by a one-way valve B4-2 through a one-way valve B4-2, and the The compressor 14 returns to the suction port of the compressor 1 and performs compression again.
When the exhaust temperature is high, the liquid spraying electromagnetic valve 17 of the liquid spraying loop 27 is electrified, the liquid spraying loop 27 is conducted, medium-pressure liquid refrigerant enters the air supplement port of the compressor 1 through the liquid spraying one-way valve 19 after being throttled and depressurized by the liquid spraying capillary tube 18 to form wet spraying, the exhaust temperature is effectively reduced, and the alarm shutdown caused by over-high exhaust temperature of the system is prevented.
The heating operation mode is as follows: the four-way reversing valve 2 is electrified, the D interface 2-1 is communicated with the E interface 2-2, and the S interface 2-3 is communicated with the C interface 2-4; high-temperature and high-pressure superheated refrigerant gas generated by compression of a compressor 1 enters a water-side heat exchanger 13 through a four-way reversing valve 2 for cooling and condensation, the condensed and cooled liquid refrigerant is subjected to reversing and flow guiding effects through a one-way valve assembly 4, is throttled and decompressed into a medium-temperature and medium-pressure gas-liquid two-phase state by a first-stage electronic expansion valve 5 through a one-way valve D4-4 of the one-way valve assembly 4 and enters a flash tank 7, saturated gas enters a gas supplementing port of the compressor through a gas supplementing one-way valve 20, the residual saturated liquid refrigerant in the flash tank 7 enters a main circulation loop of a plate economizer 8, is subjected to secondary supercooling after being subjected to heat exchange with an auxiliary circulation loop, is throttled and decompressed through a second-stage throttling electronic expansion valve 10, and enters an air-cooled condenser 3 through; the evaporated gas enters the gas-liquid separator 14 through the C interface 2-4 and the S interface 2-3 of the four-way reversing valve 2, returns to the air suction port of the compressor 1 and is compressed again.
When the exhaust temperature is high, the working state of the liquid spraying loop is consistent with the refrigeration mode; in the heating mode, the bypass electromagnetic valve 11 on the bypass circuit connected in parallel with the second-stage throttle electronic expansion valve 10 is not powered, and the circuit is in a closed state.
The defrosting mode comprises the following steps: the working process is basically the same as the refrigeration mode, but only the condensing fan above the air-cooled condenser 3 is in a closed state, meanwhile, the liquid spraying electromagnetic valve 17 is not electrified, and the liquid spraying loop 27 is closed.
The above description is only for the preferred embodiment of the present invention, and is not intended to limit the present invention, and any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention should be included within the protection scope of the present invention.
Claims (10)
1. A low-temperature strong-heat air source heat pump system is characterized by comprising a compressor (1), a four-way reversing valve (2), an air-cooled condenser (3), a one-way valve assembly (4), a flash tank (7), an economizer (8), a water-side heat exchanger (13) and a gas-liquid separator (14);
an air suction port of the compressor (1) is connected with the gas-liquid separator (14), an air exhaust port of the compressor is connected with the air-cooled condenser (3) or the water-side heat exchanger (13) through a four-way reversing valve (2), and an air supplement port of the compressor (1) is connected with an air supplement loop (26) and a liquid spraying loop (27);
the air-cooled condenser (3) is connected with a first-stage throttling electronic expansion valve (5) through the one-way valve component (4);
the first-stage throttle electronic expansion valve (5) is connected with the flash tank (7) through a dry filter A (6);
the liquid outlet of the flash evaporator (7) is connected with the main side inlet of the economizer (8), and the gas supplementing port of the flash evaporator (7) is connected with the gas supplementing loop (26);
the main side outlet of the economizer (8) is respectively connected with a liquid spraying loop (27) and a second-stage throttling electronic expansion valve (10);
and a drying filter B (9) is arranged between the second-stage throttle electronic expansion valve (10) and the economizer (8), and the second-stage throttle electronic expansion valve (10) is connected with the water side heat exchanger (13) or the air-cooled condenser (3) through a one-way valve assembly (4).
2. A cold high-heat air source heat pump system according to claim 1, characterized in that the primary side outlet of the economizer (8) is connected to a secondary side throttle expansion valve (16) through a dry filter C (15), the secondary side throttle expansion valve (16) is connected to the secondary side inlet of the economizer (8), and the secondary side outlet of the economizer (8) is connected to the gas pipe between the four-way reversing valve (2) and the gas-liquid separator (14).
3. The low-temperature strong-heat air source heat pump system according to claim 2, characterized in that the secondary side outlet of the economizer (8) is provided with a temperature sensor (24), and the temperature sensor (24) and a suction pressure sensor (22) are used for controlling the opening degree of the second-stage throttling electronic expansion valve (10).
4. The low-temperature strong-heat air source heat pump system according to claim 3, wherein the suction pressure sensor (22) is arranged on a connecting pipeline between the four-way reversing valve (2) and the gas-liquid separator (14).
5. The low-temperature strong-heat air source heat pump system according to claim 1, wherein the liquid spraying loop (27) is provided with a liquid spraying solenoid valve (17), a liquid spraying capillary tube (18) and a liquid spraying check valve (19).
6. The low-temperature strong-heat air source heat pump system according to claim 1, wherein the air supply loop (26) is provided with an air supply check valve (20).
7. The low-temperature strong-heat air source heat pump system according to claim 1, wherein the second-stage throttle electronic expansion valve (10) is connected in parallel with a bypass circuit, and a bypass solenoid valve (11) and a bypass capillary tube (12) are arranged on the bypass circuit.
8. A strong hot air source heat pump system at low temperature according to claim 1, characterized in that the compressor (1) is a scroll compressor, and the medium adopted by the air source heat pump system is R32 refrigerant.
9. The low-temperature strong-heat air source heat pump system according to claim 1, wherein the air-cooled condenser (3) is a red copper heat exchange tube with a tube diameter less than or equal to 7mm, and the economizer (8) is a plate heat exchanger.
10. A high-heat air source heat pump system at cryogenic temperature according to claim 1, characterized in that the check valve assembly (4) comprises four diaphragm check valves.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021469795.8U CN212253218U (en) | 2020-07-23 | 2020-07-23 | Low-temperature strong-heat air source heat pump system |
Applications Claiming Priority (1)
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