Patent Grant
9841214
The present invention relates to the field of refrigeration engineering method, particularly to a passive type organic working fluid ejector refrigeration method.
Low temperature heat source usually refers to heat sources below 200° C. There are a variety and the huge amount of low temperature heat sources, including solar energy, geothermal energy and industrial waste heat. According to statistics, the solar radiation of two-thirds of the whole land area in China is greater than 5000 MJ per square meter. The geothermal energy in China can be equal to about 3.3 billion tons of standard coal. Since the low-temperature heat sources featured with a wide distribution and low quality it is difficult to be utilized by conventional energy conversion devices, resulting in that most of these energy vain discharged into the environment causing great waste and environmental pollution. Therefore, the exploration of technologies for rationally using these low temperature heat sources becomes such a hot topic in the field of energy technology. Organic working fluid power generation and ejector refrigeration system using organic working fluid is considered the most potential technology for the utilization of low temperature heat sources, which has a wide range of options, suitable cycle and high energy efficiency compared with the water vapor, when the heat source temperature is below 270° C.
The ejector refrigeration system appeared in the early 20th century, and there have been some applications. However, due to its low efficiency, bulky equipment and other reasons, it is gradually replaced by compact and more efficient compression refrigeration system. In recent years, however, the ejector refrigeration system again becomes a research focus in the field and attracts widespread concern. The ejector refrigeration system has several advantages. It does not contain moving parts and has a simple structure, reliable performance, easy maintenance, etc. The operating parameters of the refrigerant system are more suitable for low temperature heat sources such as solar energy, geothermal energy and industrial waste heat.
After searching for the existing literature, Huang B. J. et al published an article entitled “A solar ejector cooling system using refrigerant R141b” (B J Huang, J M. Chang “A solar ejector cooling system using refrigerant R141b.” Solar Energy, 1998 (64)1223-226). This paper presents a new ejector refrigeration system program, which uses a high-performance ejector refrigeration unit with heat recovery. One-dimensional mathematical model of ejector proposed by previous researchers was improved, and the ejector refrigeration performance of the system was calculated to obtain a good cooling effect. Zheng Bin et al published an article entitled “A combined power and ejector refrigeration cycle for low temperature heat sources” (Zheng Bin, Y W Weng. “A combined power and ejector refrigeration cycle for low temperature heat sources” Solar Energy, 2010 (84): 784-791). The combined cycle will adopt expander and ejector, improving the efficiency of using the low temperature waste heat sources according to the energy cascade principle. The system uses latent heat of vaporization working fluid for cooling and improves performance of cooling and power generation system. Currently, the similar ejector refrigeration system for low temperature heat source has been extensively studied. The researches focus primarily on mathematical modeling, optimization of the ejector, and the ejector's experimental performance.
The traditional method of cooling has to work with external power. It needs pump to provide pressurized working fluid which consumes a lot of power. In addition, the control process also requires an external power supply, resulting in reduced overall system efficiency and increasing construction and maintenance costs.
The object of the present invention is to overcome the above drawbacks of the prior art and to provide a non-active type organic working fluid ejector refrigeration method.
The purpose of the present invention can be achieved by the following technical solutions:
1. A method of the passive type organic working fluid ejector refrigeration comprises the following steps of:
2. The injector includes a nozzle, entrained flow inlet, receiving chamber, the mixing chamber and diffuser cavity. The nozzle and entrained flow inlet were in the receiving chamber. The receiving chamber, mixing chamber and the diffuser cavity connect sequentially.
3. The reservoir's position is 100-1000 mm higher than the relative position of the evaporator, in order to use gravity transport of liquid refrigerant.
4. The system uses gravity to transport liquid medium and uses the self-operated pressure regulator valve and self-operated thermostatic regulator valve to control the entire ejection refrigeration process.
5. The organic liquid medium is R245fa, R600, R600a, R141b or R142b.
6. The entrainment ratio of ejector is from 0.1 to 0.5. The mass flow rate of working fluid of the ejector is 0.01 to 2.0 kg/s. The working pressure is 0.8-2.5 MPa.
7. The working pressure of condenser is the condensation pressure of liquid refrigerant at 10° C.-38° C. namely temperature range of the cooling water or cooling air.
8. The working pressure of the refrigerant evaporator is the corresponding evaporation pressure of liquid refrigerant with an evaporation temperature of 5° C.-15° C.
The present invention can use the low-temperature heat sources including industrial waste heat, solar hot water, geothermal energy etc. The temperature ranges from 60° C. to 200° C. Since the low-temperature heat sources featured with a wide distribution and low quality, it is difficult to be utilized by conventional energy conversion devices, resulting in that most of these low temperature heat sources vain discharged into the environment causing great waste and environmental pollution.
Compared with the prior technology, the present invention uses the organic working fluid in the evaporator to absorb heat during evaporation, so the evaporator pressure and temperature increases. When the working fluid pressure reaches the design pressure of the ejector, the first self-operated pressure regulator valve at the outlet of evaporator opens. The working steam flows into the ejector and produces ejecting effect, so that the pressure of refrigerant drops in the refrigeration evaporator. The refrigerant in the refrigeration evaporator is gasified with phase transition and the steam at outlet of refrigeration evaporator is ejected to the ejector and mixed with steam in a mixing chamber. After the diffuser cavity, the steam flows into the condenser to condense. A part of condensed liquid refrigerant flows into the reservoir, and the other part after the self-operated thermostatic valve flows into the cooling evaporator to absorb heat of cooling water, thus the water temperature decreases to 10-12° C., completing the refrigeration cycle. With the consumption of working steam in the evaporator, the evaporator pressure gradually drops to the set value of self-operated pressure regulator valve. The first self-operated pressure regulator valve and a second self-operated pressure regulator valve closes automatically. The third self-operated pressure regulator valve automatically opens, and liquid refrigerant of the reservoir flows back into the evaporator by gravity. Then the third self-operated pressure regulator valve is closed again, and the second self-operated pressure regulator valve opens and the next circulation begins.
The ejector refrigeration device uses gravity for the liquid medium transmission. The system can operate without working fluid pump, relying on the heat absorption and evaporation of working fluid in a closed space to increase pressure. The work process is controlled by self-operated pressure regulator valve and self-operated thermostatic regulator valve to achieve cooling effect. The groundwater, river (sea) water or air can be used as cold source.
Combining with the accompanying drawings and specific embodiments, the present invention will be described in detail.
This embodiment uses refrigerant R600a as working fluid. The temperature of heat sources is 120° C. The output temperature of chilled water is 12° C. The specific implementation steps are as follows:
First, the third self-operated pressure regulator valve is opened, the liquid organic working fluid in reservoir flows into the evaporator by gravity, until liquid surface equilibrium. After the third self-operated pressure regulator valve is closed, 100 kg working fluid is closed in the evaporator.
The second step, the liquid refrigerant in the evaporator absorbs heat during evaporation. The working fluid temperature and pressure is increasing, and ultimately achieves 101° C. and 2 MPa, namely, the design parameters of the ejector.
The third step, the first self-operated pressure regulator valve at the outlet of evaporator opens automatically under certain pressure. The steam as the working fluid with the mass flow rate of 0.175 kg/s flows into the ejector and produces ejecting effect for the gas at the outlet of refrigeration evaporator.
The fourth step, the lead working fluid mixes with the entrain stream in the mixing chamber. The mixing fluid flows into the diffuser chamber and then discharges from the ejection outlet, into the condenser. The outlet pressure and temperature of ejector working fluid are 0.438 MPa and 64.2° C.
The fifth step, the working fluid vapor is condensed into liquid in the condenser, and then divided into two streams. One stream flows into the reservoir, and the other one is throttled into the refrigeration evaporator through self-operated pressure regulator valve, then absorbs heat from the chilled water. The water temperature is cooled down to 12° C., completing the refrigeration cycle. The mass flow rate of refrigerant in refrigeration circuit is 0.03 Kg/s. The corresponding evaporation pressure and evaporation temperature are 0.21 MPa and 10° C. This process is controlled by self-operated temperature regulator valve.
The sixth step, the cooling evaporator provides chilled water of 12° C., and the output cooling capacity is 12 kW. The steam at outlet of refrigeration evaporator entrained by the ejector into the ejector inlet and mixed with work steam.
The seventh step, in the work process, the liquid refrigerant in the evaporator absorbs heat and evaporates constantly. After about 570 seconds, the fluid evaporates completely, and the evaporation pressure of refrigerant rapidly declines.
The eighth step, when the working fluid pressure drops to the set pressure of first self-operated pressure regulator valve, the first self-operated pressure regulator valve and a second self-operated pressure regulator valve is closed. The third self-operated pressure regulator valve opens, and the saturated liquid refrigerant of reservoir flows into the evaporator by gravity.
The ninth step, when the working fluid injection process finishes, the third self-operated pressure regulator valve and the second self-operated pressure regulator valve close automatically. A certain quality of the working fluid is closed in the evaporator for a new circulation. In this case, the cooling COP is about 0.31 and the cooling capacity is up to about 12 kW.
This embodiment uses refrigerant R245fa as working fluid. The temperature of heat sources is 120° C. The output temperature of chilled water is 12° C. The specific implementation steps are as follows:
First, the third self-operated pressure regulator valve is opened, the liquid organic working fluid in reservoir flows into the evaporator by gravity, until liquid surface equilibrium. After the third self-operated pressure regulator valve is closed, 100 kg working fluid is closed in the evaporator.
The second step, the liquid refrigerant in the evaporator absorbs heat during evaporation. The working fluid temperature and pressure is increasing, and ultimately achieves 100° C. and 1.26 MPa, namely, the design parameters of the ejector.
The third step, the first self-operated pressure regulator valve at the outlet of evaporator opens automatically under certain pressure. The steam as the working fluid with the mass flow rate of 0.175 Kg/s flows into the ejector and produces ejecting effect for the gas at the outlet of refrigeration evaporator.
The fourth step, the lead working fluid mixes with the entrain stream in the mixing chamber. The mixing fluid flows into the diffuser chamber and then discharges from the ejection outlet, into the condenser. The outlet pressure and temperature of ejector working fluid are 0.197 MPa and 64.9° C.
The fifth step, the working fluid vapor is condensed into liquid in the condenser, and then divided into two streams. One stream flows into the reservoir, and the other is throttled into the refrigeration evaporator through self-operated pressure regulator valve, then absorbs heat from the chilled water. The water temperature is cooled down to 12° C., completing the refrigeration cycle. The mass flow rate of refrigerant in circuit is 0.0525 Kg/s. The corresponding evaporation pressure and evaporation temperature are 0.08 MPa and 10° C. This process controlled by self operated temperature regulator valve.
The sixth step, the cooling evaporator provides chilled water of 12° C., and the output cooling capacity is 13 kW. The steam at outlet of refrigeration evaporator entrained by the ejector into the ejector inlet and mixed with work steam.
The seventh step, in the work process, the liquid refrigerant in the evaporator absorbs heat and evaporates constantly. After about 570 seconds, the fluid evaporates completely, and the evaporation pressure of refrigerant rapidly declines.
The eighth step, when the working fluid pressure drops to the set pressure of first self-operated pressure regulator valve, the first self-operated pressure regulator valve and a second self-operated pressure regulator valve is closed. The third self-operated pressure regulator valve opens, and the saturated liquid refrigerant of reservoir flows into the evaporator by gravity.
The ninth step, when the working fluid injection process finishes, the third self-operated pressure regulator valve and the second self-operated pressure regulator valve close automatically. A certain quality of the working fluid is dosed in the evaporator for a new circulation. In this case, the cooling COP is about 0.35 and the cooling capacity is up to about 13 kW.
This embodiment uses refrigerant R600a as working fluid. The temperature of heat sources is 120° C. The output temperature of chilled water is 12° C. The specific implementation steps are as follows:
First, the third self-operated pressure regulator valve is opened, the liquid organic working fluid in reservoir flows into the evaporator by gravity, until liquid surface equilibrium. After the third self-operated pressure regulator valve is closed, 1000 kg working fluid is closed in the evaporator.
The second step, the liquid refrigerant in the evaporator absorbs heat during evaporation. The working fluid temperature and pressure is increasing, and ultimately achieves 100° C. and 0.68 MPa, namely, the design parameters of the ejector.
The third step, the first self-operated pressure regulator valve at the outlet of evaporator opens automatically under certain pressure. The steam as the working fluid with the mass flow rate of 1.75 kg/s flows into the ejector and produces ejecting effect for the gas at the outlet of refrigeration evaporator.
The fourth step, the lead working fluid mixes with the entrain stream in the mixing chamber. The mixing fluid flows into the diffuser chamber and then discharges from the ejection outlet, into the condenser. The outlet pressure and temperature of ejector working fluid are 0.104 MPa and 70.4° C.
The fifth step, the working fluid vapor is condensed into liquid in the condenser, and then divided into two streams. One stream flows into the reservoir, and the other is throttled into the refrigeration evaporator through self-operated pressure regulator valve, then absorbs heat from the chilled water. The water temperature is cooled down to 12° C., completing the refrigeration cycle. The mass flow rate of refrigerant in circuit is 0.525 kg/s. The corresponding evaporation pressure and evaporation temperature are 0.043 MPa and 10° C. The process is controlled by self operated temperature regulator valve.
The sixth step, the cooling evaporator provides cooling water of 12° C., and the output cooling capacity is 130 kW. The steam at outlet of refrigeration evaporator entrained by the ejector into the ejector inlet and mixed with work steam.
The seventh step, in the work process, the liquid refrigerant in the evaporator absorbs heat and evaporates constantly. After about 560 seconds, the fluid evaporates completely, and the evaporation pressure of refrigerant rapidly declines.
The eighth step, when the working fluid pressure drops to the set pressure of first self-operated pressure regulator valve, the first self-operated pressure regulator valve and a second self-operated pressure regulator valve is closed. The third self-operated pressure regulator valve opens, and the saturated liquid refrigerant of reservoir flows into the evaporator by gravity.
The ninth step, when the working fluid injection process finishes, the third self-operated pressure regulator valve and the second self-operated pressure regulator valve close automatically. A certain quality of the working fluid is closed in the evaporator for a new circulation. In this case, the cooling COP is about 0.35 and the cooling capacity is up to about 130 kW.
The apparatus of the passive type organic working fluid ejector refrigeration method is shown in
As shown in
Next, the components will be further described: the location of the reservoir 6 is 100-1000 mm higher than that of the evaporator 1, which can take advantage of gravity to transfer liquid medium. The liquid refrigerant is organic working fluid such as R245fa, R600, R600a, R141b or R142b. The ejection coefficient of ejector 3 is from 0.1 to 0.5.The mass flow of the ejector 3 is 0.01-2.0 kg/s with a working pressure of 0.8-2.5 MPa. The working pressure of condenser 4 is the condensation pressure of liquid refrigerant at 10° C.-38° C., namely temperature range of the cooling water or cooling air. The working pressure of the refrigerant evaporator 8 is the corresponding evaporation pressure of liquid refrigerant with a evaporation temperature of 5° C.˜15° C.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2013 1 0483106 | Oct 2013 | CN | national |
This application is a continuation-in-part of International Patent Application No. PCT/CN2013/085958 with an international filing date of Oct. 25, 2013, designating the United States, now pending, and further claims priority benefits to Chinese Patent Application No. 201310483106.7 filed Oct. 15, 2013. The contents of all of the aforementioned applications, including any intervening amendments thereto, are incorporated herein by reference.
| Number | Date | Country |
|---|---|---|
| 101871440 | Oct 2010 | CN |
| Number | Date | Country | |
|---|---|---|---|
| 20160025391 A1 | Jan 2016 | US |
| Number | Date | Country | |
|---|---|---|---|
| Parent | PCT/CN2013/085958 | Oct 2013 | US |
| Child | 14874432 | US |
