CN104132487A - Air source heat pump system of double-pressure control - Google Patents
Air source heat pump system of double-pressure control Download PDFInfo
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- CN104132487A CN104132487A CN201410353866.0A CN201410353866A CN104132487A CN 104132487 A CN104132487 A CN 104132487A CN 201410353866 A CN201410353866 A CN 201410353866A CN 104132487 A CN104132487 A CN 104132487A
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Abstract
The invention provides an air source heat pump system of double-pressure control. The air source heat pump system comprises a compressor, a reversing valve, an oil separator, a condenser, a liquid storage tank, a drying filter, a regenerator, an expansion valve, an evaporator, a gas-liquid separator, a controller, a sensor module and an electromagnetic valve module. According to the air source heat pump system of double-pressure control, by means of system control under low suction pressure, the temperature of a working medium on the high-pressure side can be lowered, the temperature and pressure of the working medium on the low-pressure side can be increased, and the pressure ratio of the compressor can be effectively lowered; meanwhile, as the working medium is overcooled, the evaporation heat absorption capacity after throttling is relatively increased, and increased power consumption of the compressor is basically compensated; in addition, by means of pressure control over the high-pressure side, the pressure of the high-pressure side can be effectively reduced, and the risk of system leakage is eradicated while system parts are protected.
Description
Technical field
The present invention relates to a kind of air source heat pump system, particularly relate to a kind of air source heat pump system of double pressure-controlled system.
Background technology
Teat pump boiler utilizes contrary Carnot's principle exactly, by medium, and the equipment heat from low temperature is delivered to the water of high temperature, the structure of Teat pump boiler comprises compressor, water tank, condenser, throttling arrangement, evaporimeter controller and respective line.The Teat pump boiler operation principle of this kind of structure is, heat catalysis (cold-producing medium) becomes the gas of HTHP to enter into condenser by pipeline through compressor compresses, in this heat of the water draw in cold condenser internal refrigeration storage agent of low temperature simultaneously, thereby the temperature increase of water, the liquid that converts high pressure to of condenser internal refrigeration storage agent, the highly pressurised liquid forming is through throttling arrangement step-down, lower the temperature into low-temperature refrigerant, low-temperature refrigerant is through evaporimeter endothermic gasification, get back to compressor, the gas that is compressed into HTHP through compressor again reenters condenser, so circulation, until the temperature of the water of water tank the inside is heated to the temperature that controller is set.This type of Teat pump boiler has avoided traditional solar product can not work at rainy weather or night, causes the defect that electric heater power consumption is large.
Yet, in air source heat pump system, variation along with ambient temperature, the duty of heat pump also changes thereupon, if ambient temperature is too low, the caloric receptivity of evaporimeter from external environment declines, working medium evaporating pressure is not enough, easily cause pressure of inspiration(Pi) too low, the problem that pressure ratio increases, result is the energy consumption that has increased system, mode for the current main flow of problems is between high and low pressure side, to increase magnetic valve, when low-pressure lateral pressure too low, for avoiding pressure ratio excessive, magnetic valve is opened, working medium directly enters low-pressure side by high-pressure side, but the evaporation endothermic amount that the problem that this measure brings is working medium reduces, although reduced compression ratio, but energy consumption still can increase.
In addition, increase along with environment temperature, the evaporation endothermic amount of system increases, the corresponding increase of evaporating pressure, as too high in environment temperature, evaporating temperature or evaporating pressure reach corresponding high value, cause compressor delivery pressure too high, too high pressure at expulsion may be brought certain damage effect for parts and the compressor itself of system, and more on high-tension side welds also can be revealed because hypertonia causes working medium.
In view of this, be necessary to provide in fact a kind of air source heat pump system of double pressure-controlled system, the air source heat pump system of this double pressure-controlled system can solve the problem of above-mentioned power consumption increase and working medium leakage.
Summary of the invention
For solving the problems of the technologies described above, the object of the present invention is to provide a kind of air source heat pump system of double pressure-controlled system, the air source heat pump system of this double pressure-controlled system can solve the problem of above-mentioned power consumption increase and working medium leakage.
For achieving the above object, technical scheme of the present invention is as follows:
The air source heat pump system of double pressure-controlled system of the present invention, it comprises a compressor, this compressor is connected with a gas-liquid separator; One fluid reservoir, this fluid reservoir one end is connected with a condenser, and the other end is connected with a device for drying and filtering; And an expansion valve, this expansion valve is connected with an evaporimeter, and the air source heat pump system of this double pressure-controlled system also comprises:
Reversal valve, this reversal valve comprises a high-pressure side import, high-pressure side outlet, low-pressure side outlet and low-pressure side import, and this high-pressure side import is connected with described compressor, and this high-pressure side outlet is connected with described oil eliminator, and this low-pressure side import is connected with described evaporimeter;
Oil eliminator, this oil eliminator comprises first row outlet and second row outlet, and this first row outlet is connected with described compressor, and second row outlet is connected with described condenser;
Magnetic valve module, this magnetic valve module is connected with the low-pressure side outlet of described reversal valve, and this magnetic valve module is connected with described gas-liquid separator;
Controller, this controller and described magnetic valve module are electrically connected; And
Sensor assembly, this sensor assembly and described controller are electrically connected, and this sensor assembly is connected with described compressor.
Preferably, described reversal valve is four-way change-over valve.
Preferably, the air source heat pump system of described double pressure-controlled system also comprises one the 4th magnetic valve, and the 4th magnetic valve and described expansion valve are in parallel.
Preferably, described the 4th magnetic valve is normally closed solenoid valve.
Preferably, the air source heat pump system of described double pressure-controlled system also comprises a regenerator, and this regenerator one end is connected with described device for drying and filtering, and the other end is connected with described expansion valve.
Preferably, described magnetic valve module comprises:
The first magnetic valve, this first magnetic valve one end is connected with the low-pressure side import of described reversal valve, and one end that the other end is connected with device for drying and filtering with described regenerator is connected;
The second magnetic valve, this second magnetic valve one end is connected with the outlet of described regenerator, and the other end is connected with described gas-liquid separator, and this second magnetic valve and described the 3rd magnetic valve and described regenerator are in series; And
The 3rd magnetic valve, the 3rd magnetic valve one end is connected with described the first magnetic valve, and the other end is connected with described the second magnetic valve, and the 3rd magnetic valve and described the first magnetic valve, the second magnetic valve and regenerator are in parallel.
Preferably, described the first magnetic valve is normally closed solenoid valve, and described the second magnetic valve is normally closed solenoid valve, and described the 3rd magnetic valve is normally open solenoid valve.
Preferably, described sensor assembly comprises:
The first pressure sensor, this first pressure sensor one end is connected with the outlet of described compressor, and the other end and described controller are electrically connected; And
The second pressure sensor, this second pressure sensor one end is connected with the import of described compressor, and the other end and described controller are electrically connected.
Preferably, described the first pressure sensor is high side pressure sensor, and described the second pressure sensor is low-pressure lateral pressure sensor.
The air source heat pump system of double pressure-controlled system of the present invention, when suction pressure of compressor is during lower than a setting value, by the second pressure sensor transmission of signal to controller, this controller sends signal after judging, the first magnetic valve and the second magnetic valve are opened, the 3rd closed electromagnetic valve, working medium through reversal valve after is out through the first magnetic valve, regenerator, after the second magnetic valve, enter again gas-liquid separator and carry out separation, in this process, by the system under low pressure of inspiration(Pi), control, can reduce working medium on high-tension side temperature and the temperature and pressure that is increased in low-pressure side, can effectively reduce the pressure ratio of compressor, simultaneously because working medium is excessively cold, evaporation endothermic amount after throttling increases relatively, substantially made up the power consumption that compressor increases thus, in addition, by on high-tension side pressure is controlled, can make high side pressure effectively reduce, at protection system parts simultaneously, also stopped the risk of system leak.
Accompanying drawing explanation
In order to be illustrated more clearly in the technical scheme in embodiment of the present invention technology, to the accompanying drawing of required use in embodiment technical description be briefly described below, apparently, accompanying drawing in the following describes is only some embodiments of the present invention, for those of ordinary skills, do not paying under the prerequisite of creative work, can also obtain according to these accompanying drawings other accompanying drawing.
Fig. 1 is structural representation of the present invention.
The specific embodiment
Below in conjunction with the accompanying drawing in the embodiment of the present invention, the technical scheme in the embodiment of the present invention is clearly and completely described, obviously, described embodiment is only the present invention's part embodiment, rather than whole embodiment.Embodiment based in the present invention, those of ordinary skills, not making the every other embodiment obtaining under creative work prerequisite, belong to the scope of protection of the invention.
In the present embodiment, consult shown in Fig. 1, the air source heat pump system of double pressure-controlled system of the present invention, it comprises compressor, the import of this compressor is connected with the outlet of gas-liquid separator; Fluid reservoir, the import of this fluid reservoir is connected with the outlet of condenser, and the outlet of fluid reservoir is connected with the import of device for drying and filtering; And expansion valve, the outlet of this expansion valve is connected with the import of evaporimeter; Reversal valve, this reversal valve comprises a high-pressure side import D, high-pressure side outlet E, low-pressure side import C and low-pressure side outlet S, this high-pressure side import is connected with the outlet of described compressor, this high-pressure side outlet is connected with the import of described oil eliminator, this low-pressure side import is connected with the outlet of described evaporimeter, in the present embodiment, this reversal valve is four-way change-over valve; Regenerator, the import of this regenerator is connected with the outlet of described device for drying and filtering, and the outlet of regenerator is connected with the import of described expansion valve; Oil eliminator, this oil eliminator comprises first row outlet and second row outlet, and this first row outlet is connected with the import of described compressor, and second row outlet is connected with the import of described condenser.
In Fig. 1, the air source heat pump system of this double pressure-controlled system also includes magnetic valve module, this magnetic valve module comprises the first magnetic valve, the second magnetic valve and the 3rd magnetic valve, wherein, this first magnetic valve is normally closed solenoid valve, the outlet of this first magnetic valve is connected with the outlet of the low-pressure side of described reversal valve, and the import of the first magnetic valve is connected with the import of described regenerator; The second magnetic valve is normally closed solenoid valve, and the import of this second magnetic valve is connected with the outlet of described regenerator, and the outlet of the second magnetic valve is connected with the import of described gas-liquid separator, and this second magnetic valve and described the 3rd magnetic valve and described regenerator are in series; The 3rd magnetic valve is normally open solenoid valve, the import of the 3rd magnetic valve is connected with the outlet of described the first magnetic valve, the outlet of the 3rd magnetic valve is connected with the outlet of described the second magnetic valve, and the 3rd magnetic valve and described the first magnetic valve, the second magnetic valve and regenerator are in parallel; In addition, expansion valve 8 is in parallel with the 4th magnetic valve, and the 4th magnetic valve is normally closed solenoid valve, after the two outlet converges, is connected with the import of evaporimeter 9.
In the present embodiment, the first magnetic valve and controller are electrically connected, and described the second magnetic valve and controller are electrically connected, and described the 3rd magnetic valve and controller are electrically connected, and the 4th magnetic valve and controller are electrically connected; In the present embodiment, compressor is connected with sensor assembly, wherein, sensor assembly comprises the first pressure sensor and the second pressure sensor, the first pressure sensor is high side pressure sensor and this first pressure sensor and the electric connection of described controller, the second pressure sensor is low-pressure lateral pressure sensor and this second pressure sensor and the electric connection of described controller, and in addition, the outlet of compressor is connected with the first pressure sensor; The import of compressor is connected with the second pressure sensor.
The normal heating mode stage: refrigerant becomes the working medium of HTHP after compressor compresses, through reversal valve 2, arrive oil eliminator 3, after minute oil, enter the working medium that becomes middle temperature high pressure after condenser 4 heat releases, the working medium that becomes low-temp low-pressure after fluid reservoir 5, device for drying and filtering 6, regenerator 7 carry out throttling by expansion valve 8 enters into evaporimeter 9, in evaporimeter 9, evaporation endothermic enters into gas-liquid separator 10 after by reversal valve 2 and carries out liquid phase separation, has then compressed one and heats circulation entering compressor 1.
The return-air low voltage control stage: when compressor 1 pressure of inspiration(Pi) is lower than when setting value, by the second pressure sensor 13 transmission of signals to controller 11, controller 11 sends control signal after judging, the first magnetic valve 15 and the second magnetic valve 16 are opened, the 3rd magnetic valve 14 cuts out, and the working medium through reversal valve 2 low-pressure sides outlets S after out enters gas-liquid separator 10 again and carries out separation after the first magnetic valve 15, regenerator 7, the second magnetic valve 16.In this process, high-pressure side working medium is being designated as △ h1 by the cooling heat of continuation after regenerator 7, the heat that enters the working medium absorption of regenerator 7 in low-pressure side is designated as △ h2, △ h1=△ h2, the difference that is inflated temperature after valve 8 throttlings and environment temperature due to high-pressure working medium after cold is large, heat exchange amount also increases and is designated as △ h3 thereupon, for the Temperature of Working after low-pressure side regenerator 7, rise, the power of compressor 1 also increases thereupon, value added is designated as △ h4, △ h3 ≈ △ h4, thus system when pressure ratio reduces, the efficiency of system does not reduce.
The exhaust high voltage control stage: when compressor 1 pressure at expulsion is when too high, by the first pressure sensor 12 transmission of signals to controller 11, controller 11 sends control signal after judging, the 4th magnetic valve 17 is opened, now part high-pressure side working medium directly enters low-pressure side through the 4th magnetic valve 17, thereby directly reduces on high-tension side pressure.
The air source heat pump system of double pressure-controlled system of the present invention; by the system under low pressure of inspiration(Pi), control; can reduce working medium on high-tension side temperature and the temperature and pressure that is increased in low-pressure side; can effectively reduce the pressure ratio of compressor; simultaneously because working medium is excessively cold; evaporation endothermic amount after throttling increases relatively; substantially made up the power consumption that compressor increases thus; in addition; by on high-tension side pressure is controlled; can make high side pressure effectively reduce, at protection system parts simultaneously, also stop the risk of system leak.
Above-mentioned explanation to the disclosed embodiments, makes professional and technical personnel in the field can realize or use the present invention.To the multiple modification of these embodiment, will be apparent for those skilled in the art, General Principle as defined herein can, in the situation that not departing from the spirit or scope of the present invention, realize in other embodiments.Therefore, the present invention will can not be restricted to these embodiment shown in this article, but will meet the widest scope consistent with principle disclosed herein and features of novelty.
Claims (9)
1. an air source heat pump system for double pressure-controlled system, it comprises a compressor, this compressor is connected with a gas-liquid separator; One fluid reservoir, this fluid reservoir one end is connected with a condenser, and the other end is connected with a device for drying and filtering; And an expansion valve, this expansion valve is connected with an evaporimeter, it is characterized in that, and the air source heat pump system of this double pressure-controlled system also comprises:
Reversal valve, this reversal valve comprises a high-pressure side import, high-pressure side outlet, low-pressure side outlet and low-pressure side import, and this high-pressure side import is connected with described compressor, and this high-pressure side outlet is connected with described oil eliminator, and this low-pressure side import is connected with described evaporimeter;
Oil eliminator, this oil eliminator comprises first row outlet and second row outlet, and this first row outlet is connected with described compressor, and second row outlet is connected with described condenser;
Magnetic valve module, this magnetic valve module is connected with the low-pressure side outlet of described reversal valve, and this magnetic valve module is connected with described gas-liquid separator;
Controller, this controller and described magnetic valve module are electrically connected; And
Sensor assembly, this sensor assembly and described controller are electrically connected, and this sensor assembly is connected with described compressor.
2. the air source heat pump system of the double pressure-controlled system of double pressure-controlled system according to claim 1, is characterized in that, described reversal valve is four-way change-over valve.
3. the air source heat pump system of double pressure-controlled system according to claim 1, is characterized in that, the air source heat pump system of described double pressure-controlled system also comprises one the 4th magnetic valve, and the 4th magnetic valve and described expansion valve are in parallel.
4. the air source heat pump system of double pressure-controlled system according to claim 3, is characterized in that, described the 4th magnetic valve is normally closed solenoid valve.
5. the air source heat pump system of double pressure-controlled system according to claim 1, is characterized in that, the air source heat pump system of described double pressure-controlled system also comprises a regenerator, and this regenerator one end is connected with described device for drying and filtering, and the other end is connected with described expansion valve.
6. the air source heat pump system of double pressure-controlled system according to claim 5, is characterized in that, described magnetic valve module comprises:
The first magnetic valve, this first magnetic valve one end is connected with the low-pressure side import of described reversal valve, and one end that the other end is connected with device for drying and filtering with described regenerator is connected;
The second magnetic valve, this second magnetic valve one end is connected with the outlet of described regenerator, and the other end is connected with described gas-liquid separator, and this second magnetic valve and described the 3rd magnetic valve and described regenerator are in series; And
The 3rd magnetic valve, the 3rd magnetic valve one end is connected with described the first magnetic valve, and the other end is connected with described the second magnetic valve, and the 3rd magnetic valve and described the first magnetic valve, the second magnetic valve and regenerator are in parallel.
7. the air source heat pump system of double pressure-controlled system according to claim 6, is characterized in that, described the first magnetic valve is normally closed solenoid valve, and described the second magnetic valve is normally closed solenoid valve, and described the 3rd magnetic valve is normally open solenoid valve.
8. the air source heat pump system of double pressure-controlled system according to claim 1, is characterized in that, described sensor assembly comprises:
The first pressure sensor, this first pressure sensor one end is connected with the outlet of described compressor, and the other end and described controller are electrically connected; And
The second pressure sensor, this second pressure sensor one end is connected with the import of described compressor, and the other end and described controller are electrically connected.
9. the air source heat pump system of double pressure-controlled system according to claim 8, is characterized in that, described the first pressure sensor is high side pressure sensor, and described the second pressure sensor is low-pressure lateral pressure sensor.
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Cited By (14)
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| CN105928252A (en) * | 2016-05-06 | 2016-09-07 | 宁波工程学院 | Heat pump |
| CN105928251A (en) * | 2016-05-06 | 2016-09-07 | 宁波工程学院 | Heat pump |
| CN105928275A (en) * | 2016-05-06 | 2016-09-07 | 宁波工程学院 | Heat pump |
| CN106322857A (en) * | 2016-09-21 | 2017-01-11 | 杭州佳力斯韦姆新能源科技有限公司 | Three-in-one high-pressure heat regenerator |
| CN106394181A (en) * | 2016-10-17 | 2017-02-15 | 重庆超力高科技股份有限公司 | R134a or 1234yf heat pump air-conditioning system and control method |
| CN106403334A (en) * | 2016-09-13 | 2017-02-15 | 克莱门特捷联制冷设备(上海)有限公司 | Refrigerating system capable of performing optimizing control on pressure ratio of water chilling unit |
| CN106394183A (en) * | 2016-10-17 | 2017-02-15 | 重庆超力高科技股份有限公司 | CO2 heat pump air conditioner system and control method thereof |
| CN106440591A (en) * | 2016-10-28 | 2017-02-22 | 珠海格力电器股份有限公司 | Air conditioner high pressure ratio control method, controller and air conditioner control system |
| CN108592452A (en) * | 2018-04-17 | 2018-09-28 | 西安交通大学 | A kind of CO2Air-conditioning heat pump removes defrosting system and its defrosting control method |
| CN109612157A (en) * | 2019-01-16 | 2019-04-12 | 江卫 | One kind is risen again formula energy saving heat pump system |
| CN112066568A (en) * | 2020-10-10 | 2020-12-11 | 衡阳晟达信息技术有限公司 | Pressure control type air energy water heater control system and control method thereof |
| CN112747391A (en) * | 2019-10-29 | 2021-05-04 | 青岛海尔空调电子有限公司 | Air conditioning unit and compressor cooling control method thereof |
| CN112944740A (en) * | 2021-03-22 | 2021-06-11 | 西安工业大学 | Air-conditioning temperature zone layered type variable porosity honeycomb structure heat regenerator |
| CN113915800A (en) * | 2021-09-27 | 2022-01-11 | 河南科技大学 | High-temperature double-source heat pump device |
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| CN105928251A (en) * | 2016-05-06 | 2016-09-07 | 宁波工程学院 | Heat pump |
| CN105928275A (en) * | 2016-05-06 | 2016-09-07 | 宁波工程学院 | Heat pump |
| CN105928252A (en) * | 2016-05-06 | 2016-09-07 | 宁波工程学院 | Heat pump |
| CN106403334A (en) * | 2016-09-13 | 2017-02-15 | 克莱门特捷联制冷设备(上海)有限公司 | Refrigerating system capable of performing optimizing control on pressure ratio of water chilling unit |
| CN106322857A (en) * | 2016-09-21 | 2017-01-11 | 杭州佳力斯韦姆新能源科技有限公司 | Three-in-one high-pressure heat regenerator |
| CN106394181A (en) * | 2016-10-17 | 2017-02-15 | 重庆超力高科技股份有限公司 | R134a or 1234yf heat pump air-conditioning system and control method |
| CN106394183A (en) * | 2016-10-17 | 2017-02-15 | 重庆超力高科技股份有限公司 | CO2 heat pump air conditioner system and control method thereof |
| CN106440591B (en) * | 2016-10-28 | 2019-01-22 | 珠海格力电器股份有限公司 | Air conditioner high pressure ratio control method, controller and air conditioner control system |
| CN106440591A (en) * | 2016-10-28 | 2017-02-22 | 珠海格力电器股份有限公司 | Air conditioner high pressure ratio control method, controller and air conditioner control system |
| CN108592452A (en) * | 2018-04-17 | 2018-09-28 | 西安交通大学 | A kind of CO2Air-conditioning heat pump removes defrosting system and its defrosting control method |
| CN109612157A (en) * | 2019-01-16 | 2019-04-12 | 江卫 | One kind is risen again formula energy saving heat pump system |
| CN112747391A (en) * | 2019-10-29 | 2021-05-04 | 青岛海尔空调电子有限公司 | Air conditioning unit and compressor cooling control method thereof |
| CN112066568A (en) * | 2020-10-10 | 2020-12-11 | 衡阳晟达信息技术有限公司 | Pressure control type air energy water heater control system and control method thereof |
| CN112944740A (en) * | 2021-03-22 | 2021-06-11 | 西安工业大学 | Air-conditioning temperature zone layered type variable porosity honeycomb structure heat regenerator |
| CN112944740B (en) * | 2021-03-22 | 2022-05-20 | 西安工业大学 | Air-conditioning temperature zone layered type variable porosity honeycomb structure heat regenerator |
| CN113915800A (en) * | 2021-09-27 | 2022-01-11 | 河南科技大学 | High-temperature double-source heat pump device |
| CN113915800B (en) * | 2021-09-27 | 2023-03-03 | 河南科技大学 | High-temperature double-source heat pump device |
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