CN106352586A - Double machine head heat source tower heat pump unit - Google Patents

Abstract

The invention discloses a double machine head heat source tower heat pump unit which comprises a refrigerating system A and a refrigerating system B which are the same. Each refrigerating system comprises a compressor, a condenser, a drying filter, an economizer solenoid valve, a thermostatic expansion valve, a liquid spray solenoid valve, an economizer, an electronic expansion valve and an evaporator. An air outlet of the compressor is connected with the refrigerating fluid input end of the condenser, the refrigerating fluid output end of the condenser is connected with the drying filter, the drying filter is connected with an air suction port of the compressor through the liquid spray solenoid valve, the main side refrigerating fluid input end of the economizer is connected with the drying filter, the main side refrigerating fluid output end is connected with the refrigerating fluid input end of the evaporator, the refrigerating fluid output end of the evaporator is connected with the air suction port of the compressor, the auxiliary side refrigerating fluid output end of the economizer is connected with an economizer port of the compressor, and the auxiliary side refrigerating fluid input end is connected with the drying filter through the thermostatic expansion valve and the economizer solenoid valve, and the performance of the whole unit is improved.

Description

A double-head heat source tower heat pump unit

technical field

The invention relates to a double-head heat source tower heat pump unit.

Background technique

Air conditioners are major building energy consumers. How to effectively reduce air conditioner energy consumption and improve energy utilization efficiency is the focus of research in the air conditioner industry. my country's hot-summer and cold-winter regions along the Yangtze River Basin are characterized by hot summers, cold and humid winters, and relatively high air humidity. At present, there are mainly three traditional ways of cooling/heating ("/" means "or") in this area: water-cooled chiller + boiler, water/ground source heat pump and air-cooled heat pump.

Among them, the air-cooled heat pump can realize cooling/heating at the same time, but the energy efficiency of cooling/heating is relatively low; High investment limit; water-cooled chiller + boiler cooling/heating mode, its operating efficiency is high in summer, while boiler heating is used in winter, and the utilization rate of primary energy is low.

The heat source tower heat pump system is produced on the basis of fully considering the climate environment in hot summer and cold winter regions and the advantages and disadvantages of the three existing cooling/heating methods. It can achieve efficient cooling in summer and efficient heating in winter without Restricted by the geographical environment, the initial investment is relatively low, and it is an ideal air-conditioning system for hot summer and cold winter regions. However, the existing design of the heat source tower heat pump system has the following deficiencies during use:

First, the chiller has no heating function. Although it can meet the requirements to a certain extent by simply changing the control system, its heating efficiency is very low under the heating condition of the heat source tower heat pump, especially when the ambient temperature is low. And the heat supply is also seriously insufficient.

Second, the heating conditions of the existing mature water/ground source heat pumps are quite different from those of heat source tower heat pumps. They operate under the conditions of heat source tower heat pumps, especially when the ambient temperature is low. Very poor ability.

Therefore, according to the characteristics of the heat source tower heat pump system, developing a high-efficiency heat pump unit suitable for the operation of the heat source tower heat pump system is a problem that researchers are focusing on at present.

Contents of the invention

In view of the above problems, the present invention provides a double-head heat source tower heat pump unit, which greatly improves the heating efficiency and heating capacity of the heat source tower heat pump unit during winter operation, and at the same time improves the performance of the compressor, thereby improving the performance of the entire unit.

In order to achieve the above-mentioned technical purpose and achieve the above-mentioned technical effect, the present invention is realized through the following technical solutions:

A double-head heat source tower heat pump unit is characterized in that it includes two sets of the same refrigeration system A and refrigeration system B, and each refrigeration system includes a compressor, a condenser, a dry filter, an economizer solenoid valve, and a thermal expansion valve , liquid injection solenoid valve, economizer, electronic expansion valve and evaporator, the exhaust port of the compressor is connected with the refrigerant input end of the condenser and the refrigerant output end of the condenser is connected with the dry filter, the dry The filter is connected to the suction port of the compressor through the liquid injection solenoid valve, the main side refrigerant input end of the economizer is connected to the dry filter and the main side refrigerant output end is connected to the refrigerant input of the evaporator through the electronic expansion valve The refrigerant output end of the evaporator is connected to the suction port of the compressor, the auxiliary refrigerant output end of the economizer is connected to the economizer port of the compressor, and the auxiliary refrigerant input end is expanded by thermal expansion. The valve and economizer solenoid valves are connected to the filter drier.

Preferably, the water-side output end of the evaporator of the refrigeration system A is connected to the water-side input end of the evaporator of the refrigeration system B, and the water-side output end of the condenser of the refrigeration system B is connected to the water-side input end of the condenser of the refrigeration system A connected.

Preferably, a ball valve is arranged between the refrigerant output end of the condenser and the dry filter.

Preferably, a throttle valve is arranged between the liquid injection solenoid valve and the suction port of the compressor.

The beneficial effects of the present invention are:

First, the unit is equipped with two sets of the same refrigeration system A and refrigeration system B. When the load is low, one compressor can be turned off to realize the operation of a single compressor under high load, and the two compressors can be turned on at the same time when the load is high. The performance coefficient of the compressor is high, thereby improving the performance coefficient of the whole unit.

Second, the two compressors are mutually redundant, and when one of them fails, the normal operation of the system can be ensured.

Third, the heat source tower heat pump unit adopts the low-temperature liquid injection technology to increase enthalpy and the economizer heat exchange technology, which greatly improves the heating efficiency and heating capacity of the heat source tower heat pump unit during winter operation.

Fourth, Refrigeration System A and Refrigeration System B adopt a series counter-flow condenser and evaporator, and the heat transfer coefficient of the water side is higher, which can reduce the heat exchange effect on the evaporator when the heating condition of the heat source tower heat pump unit is switched to antifreeze influences.

Fifth, Refrigeration System A and Refrigeration System B use series counter-flow condensers and evaporators, and the ratio of condensation pressure to evaporation pressure corresponding to each refrigeration system is greatly reduced compared with traditional refrigeration systems, so that the performance The coefficient has been greatly improved.

Description of drawings

Fig. 1 is a structural schematic diagram of a heat pump unit with double heads heat source tower of the present invention;

The meanings of the marks in the accompanying drawings are as follows:

1: Compressor A; 2: Shell and tube condenser A; 2-1: Shell and tube condenser A refrigerant input end; 2-2: Shell and tube condenser A refrigerant output end; 2-3: Shell Tube condenser A water side input; 2-4: Shell and tube condenser A water side output; 3: Ball valve A; 4: Dry filter A; 5: Economizer solenoid valve A; 6: Thermal expansion valve A; 7: Liquid injection solenoid valve A; 8: Throttle valve A; 9: Economizer A; 9-1: Economizer A main side refrigerant input end; 9-2: Economizer A main side refrigerant output end ;9-3: Refrigerant input port on the auxiliary side of economizer A; 9-4: Refrigerant output port on the auxiliary side of economizer A; 10: Electronic expansion valve A; 11: Shell-and-tube evaporator A; 11-1: Shell Tube evaporator A refrigerant input end; 11-2: Shell and tube evaporator A refrigerant output end; 11-3: Shell and tube evaporator A water side input end; 11-4: Shell and tube evaporator A Water side output end; 12: compressor B; 13: shell and tube condenser B; 13-1: shell and tube condenser B refrigerant input end; 13-2: shell and tube condenser B refrigerant output end; 13-3: Water side input end of shell and tube condenser B; 13-4: Water side output end of shell and tube condenser B; 14: Ball valve B; 15: Dry filter B; 16: Economizer solenoid valve B; 17: Thermal expansion valve B; 18: Liquid injection solenoid valve B; 19: Throttle valve B; 20: Economizer B; 20-1: Refrigerant input end of the main side of economizer B; Side refrigerant output port; 20-3: Economizer B secondary refrigerant input port; 20-4: Economizer B secondary refrigerant output port; 21: Electronic expansion valve B; 22: Shell and tube evaporator B; 22-1: Shell and tube evaporator B refrigerant input end; 22-2: Shell and tube evaporator B refrigerant output end; 22-3: Shell and tube evaporator B water side input end; 22-4: Shell Tube evaporator B water side output.

detailed description

The technical scheme of the present invention will be described in further detail below in conjunction with the accompanying drawings and specific embodiments, so that those skilled in the art can better understand the present invention and implement it, but the examples given are not intended to limit the present invention.

A double-head (two compressors) heat source tower heat pump unit, as shown in Figure 1, includes two sets of the same refrigeration system A and refrigeration system B, refrigeration system A and refrigeration system B are independent of each other, each set of refrigeration The system includes compressor, condenser, filter drier, economizer solenoid valve, thermal expansion valve, liquid injection solenoid valve, economizer, electronic expansion valve and evaporator.

The exhaust port of the compressor is connected to the refrigerant input end of the condenser and the refrigerant output end of the condenser is connected to a drier filter, and the drier filter is connected to the suction port of the compressor through a liquid injection solenoid valve, The main side refrigerant input end of the economizer is connected with the drier filter and the main side refrigerant output end is connected with the refrigerant input end of the evaporator through the electronic expansion valve, and the refrigerant output end of the evaporator is connected with the compressor The suction port is connected, the auxiliary side refrigerant output end of the economizer is connected to the economizer interface of the compressor, and the auxiliary side refrigerant input end is connected to the dry filter through the thermal expansion valve and the economizer electromagnetic valve.

Preferably, the water-side output end of the evaporator of the refrigeration system A is connected to the water-side input end of the evaporator of the refrigeration system B, and the water-side output end of the condenser of the refrigeration system B is connected to the water-side input end of the condenser of the refrigeration system A connected.

Preferably, a ball valve is arranged between the refrigerant output end of the condenser and the dry filter, and a throttle valve is arranged between the liquid injection solenoid valve and the suction port of the compressor.

A detailed description will be given below in conjunction with accompanying drawing 1. In Fig. 1, the condenser is a shell-and-tube condenser, the evaporator is a shell-and-tube evaporator, and refrigeration system A and refrigeration system B are connected by connecting pipes. It should be noted that, in order to facilitate the distinction, add A or B after the name of each component to distinguish, which correspond to the components of refrigeration system A and refrigeration system B respectively, that is, refrigeration system A includes compressor A1, shell-and-tube condenser A2, ball valve A3, dry filter A4, economizer solenoid valve A5, thermal expansion valve A6, liquid injection solenoid valve A7, throttle valve A8, economizer A9, electronic expansion valve A10 and shell-and-tube evaporator A11, refrigeration system B includes compressor B12, shell and tube condenser B13, ball valve B14, dry filter B15, economizer solenoid valve B16, thermal expansion valve B17, liquid injection solenoid valve B18, throttle valve B19, economizer B20, electronic expansion valve B21 and shell and tube evaporator B22.

For refrigeration system A:

The high-temperature and high-pressure refrigerant gas is discharged from the exhaust port of the compressor A1 into the refrigerant input port 2-1 of the shell-and-tube condenser A, and the high-temperature and high-pressure refrigerant gas is condensed into a normal-temperature and high-pressure refrigerant liquid, which passes through the shell and tube condenser The refrigerant output port 2-2 of the tubular condenser A and the ball valve A3 flow into the dry filter A4.

The normal temperature and high pressure refrigerant is divided into three paths at the outlet of the drying filter A4: a part of the refrigerant flows into the suction port of the compressor A1 through the liquid injection solenoid valve A7 and the throttle valve A8; The expansion valve A6 enters the refrigerant input port 9-3 on the auxiliary side of the economizer A, and then flows into the economizer port of the compressor A1 through the refrigerant output port 9-4 on the auxiliary side of the economizer A; most of the refrigerant passes through the main side of the economizer A The side refrigerant input port 9-1 and the main side refrigerant output port 9-2 of the economizer A flow into the electronic expansion valve A10, and the normal temperature and high pressure refrigerant liquid throttling becomes a low temperature and low pressure gas-liquid mixture and enters the shell and tube evaporator A for refrigeration The low-temperature and low-pressure refrigerant liquid boils in the evaporator and turns into low-temperature and low-pressure refrigerant gas, and then flows back to the suction of the compressor A1 through the refrigerant output port 11-2 of the shell-and-tube evaporator A. mouth.

For refrigeration system B:

The high-temperature and high-pressure refrigerant gas is discharged from the exhaust port of the compressor B12 into the refrigerant input port 13-1 of the shell-and-tube condenser B, and the high-temperature and high-pressure refrigerant gas is condensed into a normal-temperature and high-pressure refrigerant liquid, which passes through the shell and tube condenser The refrigerant output port 13-2 of the tubular condenser B and the ball valve B14 flow into the dry filter B15.

The normal temperature and high pressure refrigerant is divided into three paths at the outlet of the drying filter B15: a part of the refrigerant flows into the suction port of the compressor B12 through the liquid injection solenoid valve B18 and the throttle valve B19; The expansion valve B17 enters the refrigerant input port 20-3 on the auxiliary side of the economizer B, and then flows into the economizer interface of the compressor B12 through the refrigerant output port 20-4 on the auxiliary side of the economizer B; most of the refrigerant passes through the economizer B main The side refrigerant input port 20-1 and the main side refrigerant output port 20-2 of the economizer B flow into the electronic expansion valve B21, and the normal temperature and high pressure refrigerant liquid throttling becomes a low temperature and low pressure gas-liquid mixture and enters the shell and tube evaporator B for refrigeration The low-temperature and low-pressure refrigerant liquid boils in the evaporator and turns into low-temperature and low-pressure refrigerant gas, and then flows back to the suction of the compressor B12 through the refrigerant output port 22-2 of the shell-and-tube evaporator B mouth.

Chilled water flows in through the water-side input port 11-3 of the shell-and-tube evaporator A, and the water-side output port 11-4 of the shell-and-tube evaporator A is connected to the water-side input port 22-3 of the shell-and-tube evaporator B through pipes. Water flows out through shell and tube evaporator B water side output port 22-4. The evaporator A11 and the evaporator B22 are connected in series and countercurrent to achieve high evaporation temperature, high system performance coefficient and increased heat transfer in the system where the compressor A1 is located.

The cooling water flows in through the input port 13-3 of the water side of the shell and tube condenser B, and the output port 13-4 of the water side of the shell and tube condenser B is connected with the input port 2-3 of the water side of the shell and tube condenser A through pipes, cooling The water flows out through the shell and tube condenser A water side output port 2-4. Condenser A2 and condenser B13 are connected in series and countercurrent to achieve low condensation temperature and high system performance coefficient of the system where compressor B12 is located.

An economizer is installed at the outlet of the condenser to improve the performance coefficient and heating capacity of the heat source tower heat pump unit in a low temperature environment, and a liquid injection solenoid valve and a liquid injection throttle valve are installed at the condenser outlet to improve the performance of the heat source tower heat pump unit in a low temperature environment Heating capacity.

The beneficial effects of the present invention are:

First, the unit is equipped with two sets of the same refrigeration system A and refrigeration system B. When the load is low, one compressor can be turned off to realize the operation of a single compressor under high load, and the two compressors can be turned on at the same time when the load is high. The performance coefficient of the compressor is high, thereby improving the performance coefficient of the whole unit.

Second, the two compressors are mutually redundant, and when one of them fails, the normal operation of the system can be ensured.

Third, the heat source tower heat pump unit adopts the low-temperature liquid injection technology to increase enthalpy and the economizer heat exchange technology, which greatly improves the heating efficiency and heating capacity of the heat source tower heat pump unit during winter operation.

Fourth, Refrigeration System A and Refrigeration System B adopt a series counter-flow condenser and evaporator, and the heat transfer coefficient of the water side is higher, which can reduce the heat exchange effect on the evaporator when the heating condition of the heat source tower heat pump unit is switched to antifreeze influences.

Fifth, Refrigeration System A and Refrigeration System B use series counter-flow condensers and evaporators, and the ratio of condensation pressure to evaporation pressure corresponding to each refrigeration system is greatly reduced compared with traditional refrigeration systems, so that the performance The coefficient has been greatly improved.

The above are only preferred embodiments of the present invention, and are not intended to limit the patent scope of the present invention. Any equivalent structure or equivalent process transformation made by using the description of the present invention and the contents of the accompanying drawings, or directly or indirectly used in other related technical fields , are all included in the scope of patent protection of the present invention in the same way.

Claims (6)

1. a kind of Double-head heat source tower heat pump unit is it is characterised in that include two sets of identical refrigeration systems a and refrigeration system b, Often set refrigeration system include compressor, condenser, device for drying and filtering, economizer electromagnetic valve, heating power expansion valve, hydrojet electromagnetic valve, Economizer, electric expansion valve and vaporizer, the air vent of described compressor is connected and condenses with the cold-producing medium input of condenser The output of condenser of device is connected with device for drying and filtering, and described device for drying and filtering passes through the air entry of hydrojet electromagnetic valve and compressor It is connected, the master cold-producing medium input of described economizer is connected with device for drying and filtering and master output of condenser is swollen by electronics Swollen valve is connected with the cold-producing medium input of vaporizer, and the output of condenser of described vaporizer is connected with the air entry of compressor, The auxiliary side output of condenser of described economizer is connected with the economizer interface of compressor and auxiliary side cold-producing medium input passes through heat Power expansion valve is connected with device for drying and filtering with economizer electromagnetic valve.

2. a kind of Double-head heat source tower heat pump unit according to claim 1 is it is characterised in that the evaporation of refrigeration system a The water side outfan of device is connected with the water side input of the vaporizer of refrigeration system b, the water side output of the condenser of refrigeration system b End is connected with the water side input of the condenser of refrigeration system a.

3. a kind of Double-head heat source tower heat pump unit according to claim 1 is it is characterised in that the cold-producing medium of condenser is defeated Go out and be provided with ball valve between end and device for drying and filtering.

4. a kind of Double-head heat source tower heat pump unit according to claim 1 is it is characterised in that hydrojet electromagnetic valve and compression It is provided with choke valve between the air entry of machine.

5. a kind of Double-head heat source tower heat pump unit according to claim 1 is it is characterised in that described condenser is package Formula condenser.

6. a kind of Double-head heat source tower heat pump unit according to claim 5 is it is characterised in that described vaporizer is package Formula vaporizer.