CN111852783B - Two-phase flow device for wind power heating - Google Patents
Two-phase flow device for wind power heating Download PDFInfo
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- CN111852783B CN111852783B CN202010670047.4A CN202010670047A CN111852783B CN 111852783 B CN111852783 B CN 111852783B CN 202010670047 A CN202010670047 A CN 202010670047A CN 111852783 B CN111852783 B CN 111852783B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
- F03D9/20—Wind motors characterised by the driven apparatus
- F03D9/28—Wind motors characterised by the driven apparatus the apparatus being a pump or a compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
- F03D9/10—Combinations of wind motors with apparatus storing energy
- F03D9/18—Combinations of wind motors with apparatus storing energy storing heat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
- F03D9/20—Wind motors characterised by the driven apparatus
- F03D9/22—Wind motors characterised by the driven apparatus the apparatus producing heat
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E70/00—Other energy conversion or management systems reducing GHG emissions
- Y02E70/30—Systems combining energy storage with energy generation of non-fossil origin
Abstract
The invention discloses a two-phase flow device for wind power heating, which converts mechanical energy of wind power into heat energy by utilizing the high-strength flow friction effect of gas-liquid two-phase slug flow of a vertical pipe (or an inclined pipe) under the condition of atmospheric liquid ratio, thereby realizing wind power heating; the main part of the device comprises a wind power impeller, a speed changer, a dynamic and static disc of a vortex compressor, a two-phase flow heat-generating pipe and a gas-liquid separator, and the auxiliary part comprises a connecting pipe and a valve. The wind power impeller and the speed changer are connected with a movable and static disc of the scroll compressor through a shaft, the wind power impeller and the speed changer replace a motor of the scroll compressor to drive the movable and static discs of the scroll compressor, and gas is pressurized by wind power. The pressurized gas enters the two-phase flow heating pipe to form gas-liquid two-phase slug flow with an atmospheric liquid ratio together with liquid in the two-phase flow heating pipe, wind energy is converted into heat energy by means of a high-strength friction effect, and a wind power heating way is expanded.
Description
Technical Field
The invention belongs to the technical field of wind energy utilization, and particularly relates to a two-phase flow device for wind power heating.
Background
Wind energy is a renewable clean energy, and the effective utilization of the wind energy is a great hot point for energy utilization. The wind energy reserve of China is huge, and the estimated wind energy available on land is about 25 ten thousand MW, and the wind energy available in sea areas is about 75 ten thousand MW. The monsoon caused by the rotation of the earth from the west to the east can continue wind energy for several months in certain regions, has the characteristic of continuous utilization of the wind energy in the daytime and at night, and has the advantages compared with the solar energy which can be only utilized in the daytime. Wind energy is the most common form of wind energy utilization, relying on wind turbines to convert wind energy into electrical energy, and wind induced heating is another form of wind energy utilization. The wind power heating technology directly converts wind energy into heat energy, and can be used for providing hot water for life, life heating at low temperature, crop greenhouse heating, aquaculture heating and the like. The wind power heating technology is not as complex as the wind power technology, the device structure is relatively simple, and the wind power heating technology has the technical characteristics of high wind energy utilization rate, strong wind condition adaptability and the like. With the increase of the demand of people on heat energy in daily life and agricultural production, the wind-driven heating technology has wide application prospect.
Five common methods of wind-induced heating are available. The first wind-driven heating method is to generate electricity by wind power and then heat electric energy by a resistance wire, and belongs to indirect heating. The second wind-driven heating method is to use a wind turbine to drive an air compressor to compress air and then release heat, and the principle of the method is that the expansion of gas is utilized to release heat, so that the efficiency of converting wind energy into heat energy is not high. The third wind-driven heating method is that a wind turbine drives a stirrer to rotate at a high speed and stir liquid to generate heat, and the principle of the method is that friction between the stirrer and the liquid generates heat, so that the efficiency of converting wind energy into heat energy is high, but the stirrer rotates at a high speed in the liquid for a long time, so that the rotating shaft is easily abraded and vibrates. The fourth wind-driven heating method is to generate heat by rubbing a solid material with wind, and the method has high efficiency of converting wind energy into heat energy, but the rubbing of the solid material inevitably causes the abrasion of the material, and the performance of the solid material is attenuated by long-time rubbing. The fifth wind heating method is to utilize wind to drive the hydraulic pump to operate, so that the hydraulic oil is ejected from the small holes at high speed, and the hydraulic pump is heated by friction and impact in the process to convert wind energy into heat energy. From the above, it can be seen that the five existing wind-powered heating methods have advantages and limitations. Therefore, there is a need to develop a new device to convert wind energy into heat energy and expand the way of wind power heating.
Disclosure of Invention
The invention aims to solve the problems in the prior art and provides a two-phase flow device for wind power heating.
The technical scheme adopted by the invention is as follows:
a two-phase flow device of wind power heating comprises a wind power impeller and a movable static disc of a vortex compressor, the two-phase flow heating pipe and the gas-liquid separator are connected, the wind power impeller is connected with the movable static disc of the vortex compressor and used for receiving wind power and driving the movable static disc of the vortex compressor to work, the two-phase flow heating pipe is arranged vertically or obliquely, a two-phase outflow port is arranged at the upper end of the two-phase flow heating pipe, an air inlet and a liquid inlet are arranged at the lower end of the two-phase flow heating pipe, the air inlet is positioned above the liquid inlet, a gas outlet of the movable static disc of the vortex compressor is connected with the air inlet, a gas adjusting valve is arranged on a connecting pipeline, the two-phase outflow port is connected with a gas-liquid two-phase inlet on the gas-liquid separator through a pipeline, a liquid backflow port and a liquid outward delivery port are arranged at the lower part of the gas-liquid separator, the liquid backflow port is connected with the liquid inlet, a liquid adjusting valve is arranged on the connecting pipeline, and a liquid supplementing port is also arranged on the gas-liquid separator.
Preferably, the gas outlet of the movable stationary plate of the scroll compressor is provided with a gas check valve for preventing backflow of the compressed gas.
Preferably, the two-phase outflow port is vertically higher than the gas-liquid two-phase inlet port, and the two-phase outflow port and the gas-liquid two-phase inlet port are communicated with each other through an inclined downcomer.
Preferably, the air inlet is lower than the liquid external delivery port in the vertical direction, the liquid backflow port is arranged at the bottom of the gas-liquid separator, the liquid dredging valve is connected to the liquid backflow port, the liquid supplementing port is lower than the gas-liquid two-phase inlet in the vertical direction, the liquid supplementing valve is connected to the liquid supplementing port, and the liquid backflow port is lower than the liquid external delivery port in the vertical direction.
Preferably, the top of the gas-liquid separator is provided with a gas outlet, the gas outlet is connected with a gas inlet of a movable static disc of the scroll compressor, and the gas-liquid separator is provided with a gas pressure balancing hole for balancing the internal pressure and the external pressure of the gas-liquid separator.
Preferably, the included angle between the axis of the two-phase flow heat pipe and the horizontal direction is greater than or equal to 30 degrees.
Preferably, the two-phase flow device adopting wind power to heat further comprises a speed changer, wherein the wind power impeller and the speed changer are connected through a first connecting shaft, and the speed changer is connected with the movable and static disc of the scroll compressor through a second connecting shaft.
Preferably, the two-phase flow device for wind power heating can be provided with one two-phase flow heating pipe or can be provided with more than two-phase flow heating pipes in parallel, when the more than two-phase flow heating pipes are arranged in parallel, the air inlets of all the two-phase flow heating pipes are connected with the air outlet of the movable stationary disc of the scroll compressor, and the connecting pipeline is provided with an air regulating valve; the two-phase outflow ports of all the two-phase flow heat-generating pipes are connected with the gas-liquid two-phase inlet on the gas-liquid separator through a pipeline; liquid inlets of all the two-phase flow heat-inducing pipes are connected with a liquid return port on the gas-liquid separator, and liquid regulating valves are arranged on the connecting pipelines;
or at least two wind-driven heat-induced two-phase flow devices are arranged, and liquid output ports of all the wind-driven heat-induced two-phase flow devices are converged through a pipeline.
The wind power heating method is carried out by the two-phase flow device for wind power heating, and comprises the following processes:
injecting liquid into the two-phase flow heating pipe and forming a liquid column;
pressurizing the gas by using a wind power impeller and a movable static disc of a vortex compressor;
the pressurized gas enters the two-phase flow heat pipe and forms gas-liquid two-phase slug flow with the liquid in the two-phase flow heat pipe to generate friction effect, so that the temperature of the gas-liquid two phase rises;
the gas phase and the liquid phase after the temperature rise enter a gas-liquid separator for gas-liquid separation;
liquid separated by the gas-liquid separator enters the two-phase flow heating pipe again from the liquid reflux port and the liquid inlet to form gas-liquid two-phase slug flow;
when the temperature of the liquid in the gas-liquid separator reaches a preset temperature, outputting the liquid from the liquid output port;
and supplementing liquid into the gas-liquid separator from the liquid supplementing port when the liquid level in the gas-liquid separator is lower than a preset value.
Preferably, the calculation process of the wind-induced heat quantity E is as follows:
E＝τ(1+S)QLg(ρm-ρh)Lp sinθ
the temperature rise Δ T of the liquid was calculated as follows:
wherein: tau is the time of wind power heating, S is the gas-liquid ratio, Q is the ratio of gas volume flow to liquid volume flowLIs a liquidG is the acceleration of gravity, pmIs the actual average density rho of the gas-liquid two-phase fluid in the two-phase flow heating pipehIs a homogeneous density of a gas-liquid two-phase flow, LpThe length of the two-phase flow heating pipe is theta, and the inclination angle of the two-phase flow heating pipe relative to the horizontal plane is theta; etaLIs the liquid endotherm, pLIs liquid density, CpLIs the isobaric specific heat, V, of a liquidLIs the total volume of liquid in the device.
The invention has the following beneficial effects:
the two-phase flow device for wind power heating utilizes the wind power impeller and the movable stationary disc of the vortex compressor to pressurize gas, the gas inlet on the two-phase flow heating pipe is positioned above the liquid inlet, and the two-phase flow heating pipe is vertically or obliquely arranged, so that the pressurized gas enters the two-phase flow heating pipe from the gas inlet and forms gas-liquid two-phase slug flow with a liquid column in the two-phase flow heating pipe, high-strength friction effect is generated, mechanical energy of wind power is converted into heat energy, and the gas-liquid two phases are heated; the gas regulating valve and the liquid regulating valve can be used for respectively controlling the flow of gas and liquid, so that the gas-liquid ratio in the two-phase flow heating pipe reaches a preset value, and further gas-liquid two-phase slug flow is formed; the gas-liquid separator can perform gas-liquid separation on gas-liquid two phases with increased temperature flowing out from the two-phase flow outlet on the two-phase flow heat-generating pipe, and the separated liquid can form gas-liquid two-phase slug flow again through the liquid reflux port and the liquid inlet on the two-phase flow heat-generating pipe, so that the internal energy is continuously accumulated and increased, and the heating purpose is achieved. Utilize the outer defeated mouth of liquid on the vapour and liquid separator, can use liquid discharge after the liquid temperature in the vapour and liquid separator reaches the default, utilize the fluid infusion mouth on the vapour and liquid separator, can carry out the fluid infusion when the volume of liquid is less than the default in the vapour and liquid separator, guarantee that there is sufficient liquid to carry out the thermal cycle in whole device. The two-phase flow device for wind power heating of the invention takes two-phase flow friction heating as a basic principle, can convert wind energy into internal energy of liquid and be used, expands the way of wind power heating, has higher conversion efficiency because the friction heating between gas phase and liquid phase is mainly carried out, and has no particularly high pressure and flow velocity, so that the friction of the heat pipe caused by the gas phase and liquid phase relative to the two-phase flow is small.
Furthermore, the outlet of the two-phase flow heating pipe is communicated with the inlet of the gas-liquid separator through the inclined descending pipe, and the inclined descending pipe can avoid liquid backflow to cause the outlet of the two-phase flow heating pipe to be blocked.
Further, the gas inlet is vertically lower than the liquid outer delivery port, which is advantageous in that the liquid level in the gas-liquid separator can be ensured to be higher than that of the gas inlet, so that the liquid in the gas-liquid separator can be supplied to the two-phase flow induced heat pipe by means of gravity, and the gas inlet is vertically lower than the liquid outer delivery port, so that the gas entering from the gas inlet can easily form a gas-liquid two-phase slug flow with the liquid column above the gas inlet. The liquid backflow port is arranged at the bottom of the gas-liquid separator, and the liquid dredging valve is connected to the liquid backflow port, so that liquid is convenient to replace, the liquid in the gas-liquid separator can be guaranteed to be fully used, the liquid flow in the gas-liquid separator is enhanced, and the temperature of the liquid in the gas-liquid separator is relatively uniform.
Furthermore, the top of the gas-liquid separator is provided with a gas outlet which is connected with a gas inlet of a movable static disc of the scroll compressor, and the gas separated by the gas-liquid separator is heated and carries heat, so that the gas carrying the heat is recycled by adopting the structure, the heat loss is reduced, and the time for the liquid to reach the preset temperature is shortened. The air pressure balance hole is utilized, so that when the movable static disc of the scroll compressor inhales air, the pressure between the air-liquid separator and the atmosphere can be balanced, and the movable static disc of the scroll compressor can be ensured to smoothly inhale air.
Furthermore, the included angle between the axis of the two-phase flow heat-generating pipe and the horizontal direction is more than or equal to 30 degrees, and sin theta is more than or equal to 0.5 correspondingly, so that the heat converted by friction dissipation in the inclined pipe is not less than 50% of that of the vertical pipe.
Further, at least two-phase flow heat generating pipes are arranged in parallel, and at least two-phase flow devices for wind power heat generation are arranged, so that the heat generating capacity of the whole device can be enhanced.
The wind power heating method is carried out by adopting the two-phase flow device for wind power heating, takes the two-phase flow friction heating as the basic principle, can convert wind energy into heat energy, provides a new way for utilizing wind energy, and has higher conversion efficiency.
Drawings
FIG. 1 is a schematic structural view of a two-phase flow device for wind-induced heating according to the present invention.
FIG. 2 is a temperature-time diagram of liquid heating in an embodiment of the present invention.
In the figure: 1-a wind power impeller; 2-a first connecting shaft; 3-a transmission; 4-a second connecting shaft; 5-suction pipe; 6-a movable and static disc of the scroll compressor; 7-gas check valve; 8-gas conveying pipe; 9-gas regulating valve; 10-an air inlet; 11-two-phase flow induced heat pipe; 12-a two-phase outflow; 13-inclined downcomer; 14-a gas-liquid separator; 15-liquid inlet; 16-liquid communicating pipe; 17-liquid regulating valve; 18-a liquid return port; 19-a gas-liquid two-phase inlet; 20-a gas outlet; 21-air pressure balancing holes; 22-fluid infusion port; 23-external liquid delivery port; 24-a lyophobic valve; 25-liquid delivery valve; 26-a fluid infusion valve; 27-thermal insulation material.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
Referring to fig. 1, the two-phase flow device of wind-driven heat generation of the present invention comprises a main component including a wind-driven impeller 1, a transmission 3, a movable stationary disc 6 of a scroll compressor, a two-phase flow heat generation pipe 11 and a gas-liquid separator 14, and an auxiliary component including a connecting pipe and a valve. The wind power impeller 1 is connected with the speed changer 3 through the first connecting shaft 2, the speed changer 3 is connected with the movable and static disc 6 of the scroll compressor through the second connecting shaft 4, the wind power impeller 1 and the speed changer 3 together replace a motor of the scroll compressor to drive the movable and static disc 6 of the scroll compressor, and air is pressurized by wind power. The pressurized gas enters the two-phase flow heat-generating pipe 11, and forms a gas-liquid two-phase slug flow with an atmospheric liquid ratio together with the liquid in the two-phase flow heat-generating pipe 11, and wind energy is converted into heat energy by virtue of a high-strength friction effect. The components of the movable static disc 6, the gas one-way valve 7, the gas pipe 8, the gas regulating valve 9, the two-phase flow heating pipe 11, the inclined downcomer 13, the gas-liquid separator 14 and the gas suction pipe 5 form a gas flow path, and the components of the two-phase flow heating pipe 11, the inclined downcomer 13, the gas-liquid separator 14, the liquid communicating pipe 16 and the liquid regulating valve 17 form a liquid flow path.
The gas-liquid separator 14 is provided with a gas-liquid two-phase inlet 19, a gas outlet 20, a liquid supplementing port 22, a liquid return port 18 and a liquid output port 23. The gas outlet 20 is arranged at the upper end of the gas-liquid separator 14 and is communicated with the movable and static disc 6 of the scroll compressor through the suction pipe 5. When the liquid level in the gas-liquid separator 14 is lower than the minimum liquid level set value, the liquid supplementing valve 26 is opened, and liquid supplementing is started to be performed on the gas-liquid separator 14 through the liquid supplementing opening 22; when the liquid level is higher than the maximum liquid level set value, the liquid supplementing valve 26 is closed, and liquid supplementing is stopped. The liquid return port 18 and the liquid external delivery port 23 are arranged at the lower part of the gas-liquid separator 14, the liquid return port 18 is communicated with the liquid inlet 15 of the two-phase flow heat-generating pipe 11, and the liquid in the gas-liquid separator 14 enters the two-phase flow heat-generating pipe 11 from the liquid inlet 15 to flow in a circulating way. And opening the liquid outward-conveying valve 25 on the liquid outward-conveying port 23 to convey the heated liquid outward.
The gas-liquid separator 14 is provided with a gas pressure balancing hole 21, and when the scroll compressor rotates and sucks air by the movable disc 6, the gas pressure balancing hole 21 is used for balancing the pressure between the gas-liquid separator 14 and the atmosphere.
The liquid in the two-phase flow heat-generating pipe 11 is gravity-fed by the liquid stored in the gas-liquid separator 14.
Gas single-phase valve 7 is installed to gas 6 export one side of moving quiet dish of scroll compressor on the gas-supply pipe 8, and gas single-phase valve 7 can prevent the gas after the pressure boost to 6 refluxes of moving quiet dish of scroll compressor.
A gas regulating valve 9 is arranged on one side of the gas inlet 10 on the gas pipe 8, and the gas regulating valve 9 is used for regulating the gas flow; the liquid communicating pipe 16 is provided with a liquid regulating valve 17 for regulating the flow of the liquid. By adjusting the gas flow and the liquid flow, a slug flow with an atmospheric liquid ratio is formed, a high-strength flow friction effect is generated, and the mechanical energy of wind power is converted into heat energy.
The two-phase flow heat-generating pipe 11 is a vertical pipe (sin theta is 1) or a large-angle inclined pipe (sin theta is more than or equal to 0.5), theta is an included angle between the two-phase flow heat-generating pipe 11 and a horizontal plane, and the two-phase flow outlet 12 is positioned at the upper end of the two-phase flow heat-generating pipe 11 and is communicated with the gas-liquid two-phase inlet 19 at the upper part of the gas-liquid separator 14. The lower part of the two-phase flow heat-generating pipe 11 is provided with an air inlet 10 and a liquid inlet 15, the air inlet 10 is positioned above the liquid inlet 15, the air inlet 11 is communicated with the movable stationary disc 6 of the scroll compressor through an air pipe 8, and the liquid inlet 15 is communicated with a liquid return port 18 at the lower part of the gas-liquid separator through a liquid connecting pipe 16. Corresponding to the same movable and static disc 6 and gas-liquid separator 14 of the scroll compressor, 1 two-phase flow heat-generating pipe 11 can be arranged, the connection mode of the two-phase flow heat-generating pipe 11, the movable and static disc 6 of the scroll compressor and the gas-liquid separator 14 can be repeated, and at least two-phase flow heat-generating pipes 11 are arranged in parallel to enhance the heat-generating capacity.
The energy loss of the gas-liquid two-phase flow of the pipeline, i.e. the heat converted by the mechanical energy dissipated by friction, not only includes the contribution of friction pressure drop, but also includes the contribution of a part of gravity pressure drop, and the heat converted by the mechanical energy dissipated by friction E1The calculation formula is as follows:
E1＝τ(1+S)QL(ΔPf+g(ρm-ρh)Lpsinθ)
in the formula: e1Heat (unit: J) converted for mechanical energy dissipation by friction, τ time (unit: S) for wind heating, S gas-liquid ratio (ratio of gas volume flow to liquid volume flow), QLIs the volume flow rate (unit: m) of the gas3·s-1)，ΔPfIs the friction pressure drop (unit: Pa) in the two-phase flow heat-generating pipe, and g is the gravity acceleration (unit: m.s)-2)，ρmIs the actual average density (unit: kg.m) of the gas-liquid two-phase fluid in the two-phase flow heating pipe-3)，ρhIs the homogeneous density (unit: kg. m) of gas-liquid two-phase flow-3)，LpThe length (unit: m) of the two-phase flow heating pipe, and theta is the inclination angle (unit: DEG) of the two-phase flow heating pipe relative to the horizontal plane.
Under the condition of atmospheric liquid ratio, high-intensity flow friction effect exists in gas-liquid two-phase slug flow in the vertical pipe and the large-angle inclined pipe. For example, the gas-liquid ratio S.gtoreq.50, at which point the gas-liquid ratioActual average density ρ of two-phase fluidmSpecific gas-liquid two-phase flow homogeneous density rhohMuch larger, frictional pressure drop Δ PfAnd g (rho)m-ρh)Lpsin θ is much smaller and thus negligible, and the mechanical energy dissipates the converted heat E by friction1(i.e., wind-induced thermal energy E) can be approximated as:
E＝τ(1+S)QLg(ρm-ρh)Lp sinθ
when the wind power heating heat quantity E is calculated, the ratio of the gas volume flow to the liquid volume flow, namely the gas-liquid ratio S, is calculated according to the following formula:
S＝QG/QL
wherein QGIs the volume flow rate (unit: m) of the gas3/s)。
Homogeneous density rho of gas-liquid two-phase flow when calculating heat quantity of wind power heatinghCalculated according to the following formula:
where ρ isGIs the gas density (unit: kg/m)3)，ρLIs the liquid density (unit: kg/m)3)。
Due to gas-liquid ratio S and density difference (ρ)m-ρh) The two-phase flow heating device is large, and for gas-liquid two-phase slug flow in a vertical pipe (sin theta is equal to or more than 1) and a large-angle inclined pipe (sin theta is equal to or more than 0.5), the heat E converted by mechanical energy through friction dissipation is also large, and the heat is absorbed by liquid, so that two-phase flow heating can be implemented.
According to the basic principle of two-phase flow heating, the high-strength friction effect of gas-liquid two-phase slug flow of the vertical pipe (or the large-angle inclined pipe) under the condition of atmospheric liquid ratio is utilized to heat the liquid, the mechanical energy of wind power is converted into heat energy, and the wind power heating is realized.
By combining the device and the principle, the two-phase flow method of wind power heating of the invention has the following concrete implementation steps:
s1, the wind power impeller 1 rotates under the action of wind power, the rotating speed is increased through the speed changer 3, the movable and static disc 6 of the scroll compressor is driven to rotate, the air is sucked from the gas-liquid separator 14 through the air suction pipe 5 and sent into the movable and static disc 6 of the scroll compressor, and the air is pressurized by the movable and static disc 6 of the scroll compressor and then output through the air conveying pipe 8.
S2, closing the lyophobic valve 24 and the liquid outward-conveying valve 25, opening the liquid supplementing valve 26, and beginning to supplement liquid to the gas-liquid separator 14 through the liquid supplementing opening 22; when the liquid level is higher than the maximum liquid level set value, the liquid supplementing valve 26 is closed, and liquid supplementing is stopped. The liquid regulating valve 17 on the liquid communicating pipe 16 is opened, the liquid in the gas-liquid separator 14 enters the two-phase flow heat-generating pipe 11 through the liquid communicating pipe 16, and the liquid is injected into the two-phase flow heat-generating pipe 11 to form a liquid column.
S3, opening the gas regulating valve 9 on the gas pipe 8, the pressurized gas enters the two-phase flow heat-generating pipe 11, and forms a gas-liquid two-phase flow with the liquid in the two-phase flow heat-generating pipe 11.
S4, regulating and controlling the gas flow and the liquid flow through the gas regulating valve 9 and the liquid regulating valve 17 to enable the gas-liquid ratio to be not less than 50, forming gas-liquid two-phase slug flow with the atmospheric liquid ratio, generating a high-strength flow friction effect, and converting the mechanical energy of wind power into heat energy;
the energy loss of the gas-liquid two-phase flow of the pipeline, namely the heat converted by the mechanical energy dissipation through friction, not only comprises the contribution of friction pressure drop, but also comprises the contribution of a part of gravity pressure drop, and the heat E caused by wind power is calculated according to the following method:
E＝τ(1+S)QLg(ρm-ρh)Lp sinθ
wherein: e is the heat (unit: J) of wind power heating, tau is the time (unit: S) of wind power heating, S is the gas-liquid ratio (the ratio of gas volume flow to liquid volume flow, no dimension), Q isLIs the volume flow (unit: m) of the liquid3·s-1) And g is the acceleration of gravity (unit: m.s-2)，ρmIs the actual average density (unit: kg.m) of the gas-liquid two-phase fluid in the two-phase flow heating pipe-3)，ρhIs the homogeneous density (unit: kg. m) of gas-liquid two-phase flow-3)，LpFor two-phase flow induced heating tube growthAnd (m), and theta is the inclination angle (m) of the two-phase flow heating pipe relative to the horizontal plane.
The temperature rise of the liquid was calculated as follows:
wherein: delta T is the temperature rise (unit:. degree. C.) of the liquid, etaLIs the liquid endotherm (dimensionless, related to the density, specific heat and gas-liquid ratio of the fluid), ρLIs the liquid density (unit: kg. m)-3)，CpLIs the isobaric specific heat (unit: J.kg) of the liquid-1·℃-1)，VLIs the total volume (unit: m) of liquid in the device3)。
S5, when the wind power heating time reaches a preset value after tau and the liquid temperature rise delta T, the liquid outward-conveying valve 25 is opened, and liquid with a preset temperature is output outwards; when the liquid level is lower than the minimum liquid level set value, the liquid outward delivery valve 25 is closed, the liquid supplementing valve 26 is opened, liquid supplementing is carried out on the gas-liquid separator 14 through the liquid supplementing opening 22, liquid is re-injected into the two-phase flow heating pipe 11 to form a liquid column, and the next wind heating process is started.
Examples
In the present embodiment, the two-phase flow heat generating pipe 11 is a vertical pipe (sin θ is 1) having a length of 2m and an inner diameter of 0.04 m. The liquid being water, density rhoL＝998kg·m-3Specific heat at constant pressure CpL＝4200J·kg-1·℃-1(ii) a The gas being air, density rhoG＝1.3kg·m-3Specific heat at constant pressure CpG＝1005J·kg-1·℃-1(ii) a The liquid delivery valve 25 and the lyophobic valve 24 are kept closed, the liquid supply valve 26 is opened, and 10 liters (0.01 m) of the liquid is supplied from the liquid supply port 22 to the gas-liquid separator 143) Then the liquid regulating valve 17 is opened, and a liquid column with a height of 0.9m is formed in the two-phase flow heat pipe 11. By adjusting the gas flow and the liquid flow, a slug flow with a gas-liquid ratio S of 100 is formed, a high-strength flow friction effect is generated, the mechanical energy of wind power is converted into heat energy, and the liquid heat absorption rate eta is measured and calculatedL＝0.97。
FIG. 2 shows the time τ required for heating a volume of 10 liters of water to 40 ℃ and the water flow rate QLThe relationship (2) of (c). For the sake of more intuitive understanding, the unit of time τ in fig. 2 is changed from s (seconds) to min (minutes), and the water flow rate Q is changedLUnit of (a) is composed of3·s-1Change to L.min-1(liter/min). FIG. 2 shows a two-phase flow heat pipe with a height of 2m and an inner diameter of 0.04m, with a gas-liquid ratio S of 100 and a liquid flow rate QL＝0.4L·min-1Under the condition (2), 10 liters of water can be heated to 40 ℃ in about 132 minutes; at a gas-liquid ratio S of 100 and a liquid flow rate QL＝6L·min-1Under the conditions of (1), 10 liters of water is heated to 40 ℃ in about 15 minutes.
If n identical two-phase flow heating pipes are used in parallel in the above embodiment, the time required for heating to 40 ℃ can be shortened to n times of the above time.
Claims (9)
1. A two-phase flow device for wind power heating is characterized by comprising a wind power impeller, a movable static disc of a vortex compressor, a two-phase flow heating pipe (11) and a gas-liquid separator (14), wherein the wind power impeller is connected with the movable static disc of the vortex compressor and is used for receiving wind power and driving the movable static disc of the vortex compressor to work, the two-phase flow heating pipe (11) is vertically or obliquely arranged, a two-phase outflow port (12) is arranged at the upper end of the two-phase flow heating pipe (11), a gas inlet (10) and a liquid inlet (15) are arranged at the lower end of the two-phase flow heating pipe (11), the gas inlet (10) is positioned above the liquid inlet (15), a gas outlet of the movable static disc of the vortex compressor is connected with the gas inlet (10) and is provided with a gas regulating valve (9) on a connecting pipeline, the two-phase flow outlet (12) is connected with a gas-liquid two-phase inlet (19) on the gas-liquid separator (14) through a pipeline, a liquid return port (18) and a liquid outer delivery port (23) are arranged at the lower part of the gas-liquid separator (14), the liquid reflux port (18) is connected with the liquid inlet (15), a liquid regulating valve (17) is arranged on the connecting pipeline, and a liquid supplementing port (22) is also arranged on the gas-liquid separator (14);
the wind heating method of the two-phase flow device comprises the following processes:
injecting liquid into the two-phase flow heat-generating pipe (11) and forming a liquid column;
pressurizing the gas by using a wind power impeller and a movable static disc of a vortex compressor;
the pressurized gas enters the two-phase flow heat pipe (11) and forms gas-liquid two-phase slug flow with the liquid in the two-phase flow heat pipe (11) to generate friction effect, so that the temperature of the gas-liquid two-phase rises;
the gas-liquid two phases with the increased temperature enter a gas-liquid separator (14) for gas-liquid separation;
liquid separated by the gas-liquid separator (14) reenters the two-phase flow heat pipe (11) from the liquid return port (18) and the liquid inlet (15) to form gas-liquid two-phase slug flow;
when the temperature of the liquid in the gas-liquid separator (14) reaches a preset temperature, outputting the liquid from the liquid output port (23);
and when the liquid level in the gas-liquid separator (14) is lower than a preset value, liquid is replenished into the gas-liquid separator (14) from the liquid replenishing port (22).
2. A two-phase aeolian heating device according to claim 1, characterised in that said gas outlet of said mobile stationary disc of said scroll compressor is provided with a gas non-return valve (7) for preventing backflow of said compressed gas.
3. A wind-powered thermal two-phase flow device according to claim 1, wherein the two-phase flow outlet (12) is vertically higher than the gas-liquid two-phase inlet (19), and the two-phase flow outlet (12) communicates with the gas-liquid two-phase inlet (19) through an inclined downcomer (13).
4. The two-phase wind-driven heating device according to claim 1, wherein the gas inlet (10) is vertically lower than the liquid outlet (23), the liquid return port (18) is arranged at the bottom of the gas-liquid separator (14), the liquid return port (18) is connected with a lyophobic valve (24), the liquid supplementing port (22) is vertically lower than the gas-liquid two-phase inlet (19), the liquid supplementing port (22) is connected with a liquid supplementing valve (26), and the liquid return port (18) is vertically lower than the liquid outlet (23).
5. The two-phase wind-driven thermal flow device according to claim 1, wherein the top of the gas-liquid separator (14) is provided with a gas outlet (20), the gas outlet (20) is connected with a gas inlet of a movable stationary disc of the scroll compressor, and the gas-liquid separator (14) is provided with a gas pressure balancing hole (21) for balancing the pressure inside and outside the gas-liquid separator (14).
6. A wind powered heat generating two phase flow device according to claim 1 wherein the angle of the axis of the two phase flow heat generating pipe (11) to the horizontal is greater than or equal to 30 °.
7. A wind-powered hot two-phase flow device according to claim 1, further comprising a transmission (3), wherein the wind-powered impeller (1) and the transmission (3) are connected by a first connecting shaft, and the transmission (3) is connected with the stationary plate of the scroll compressor by a second connecting shaft.
8. A wind powered heated two phase flow device according to claim 1 wherein:
the wind-driven heating two-phase flow device is provided with one two-phase flow heating pipe (11) or more than two-phase flow heating pipes (11) in parallel, when the two or more than two-phase flow heating pipes (11) are arranged in parallel, the air inlets (10) of all the two-phase flow heating pipes (11) are connected with the air outlet of the movable static disc of the vortex compressor, and the connecting pipeline is provided with an air regulating valve (9); the two-phase flow outlets (12) of all the two-phase flow heat-generating pipes (11) are connected with a gas-liquid two-phase inlet (19) on the gas-liquid separator (14) through a pipeline; liquid inlets (15) of all the two-phase flow heat-generating pipes (11) are connected with a liquid return port (18) on the gas-liquid separator (14), and liquid regulating valves (17) are arranged on connecting pipelines;
or at least two wind-powered heat-generating two-phase flow devices are arranged, and liquid external delivery ports (23) of all the wind-powered heat-generating two-phase flow devices are converged through a pipeline.
9. A wind powered heated two phase flow device according to claim 1 wherein:
the calculation process of the wind-induced heat quantity E is as follows:
E＝τ(1+S)QLg(ρm-ρh)Lpsinθ
the temperature rise Δ T of the liquid was calculated as follows:
wherein: tau is the time of wind power heating, S is the gas-liquid ratio, Q is the ratio of gas volume flow to liquid volume flowLIs the volume flow of the liquid, g is the acceleration of gravity, ρmIs the actual average density rho of the gas-liquid two-phase fluid in the two-phase flow heating pipehIs a homogeneous density of a gas-liquid two-phase flow, LpThe length of the two-phase flow heating pipe is theta, and the inclination angle of the two-phase flow heating pipe relative to the horizontal plane is theta; etaLIs the liquid endotherm, pLIs liquid density, CpLIs the isobaric specific heat, V, of a liquidLIs the total volume of liquid in the device.
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Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103206355A (en) * | 2013-05-06 | 2013-07-17 | 张学文 | Artificial density difference power generation system |
| CN106286173A (en) * | 2016-10-09 | 2017-01-04 | 符海龙 | Power cycle output intent and the system of heat energy is absorbed from air |
| CN108757069A (en) * | 2018-06-15 | 2018-11-06 | 刘芙蓉 | Biphase gas and liquid flow gravity heat engine |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8196395B2 (en) * | 2009-06-29 | 2012-06-12 | Lightsail Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
| CN102235332A (en) * | 2010-04-27 | 2011-11-09 | 李化成 | Solar photo-thermal vapor-liquid two-phase flow thermal expansion power generating system |
| CN102706036A (en) * | 2012-05-19 | 2012-10-03 | 合肥天鹅制冷科技有限公司 | Air source heating air conditioning hot water machine |
| US20160123639A1 (en) * | 2013-06-24 | 2016-05-05 | Mitsubishi Heavy Industries, Ltd. | Turbo refrigerator |
| CN103604254B (en) * | 2013-11-12 | 2016-07-06 | 清华大学 | A kind of built-in biphase gas and liquid flow flow dividing structure |
| CN205037796U (en) * | 2015-09-23 | 2016-02-17 | 北京石油化工学院 | Intensive condenser pipe of built -in small passageway of triangle -shaped |
| CN106568111A (en) * | 2015-10-09 | 2017-04-19 | 上海日立电器有限公司 | Carbon dioxide heat pump heating system |
| CN107702581B (en) * | 2017-10-31 | 2019-05-03 | 中国计量大学 | The observation device of biphase gas and liquid flow in the plate heat exchanger of adjustable mounting position |
| CN208966383U (en) * | 2018-10-22 | 2019-06-11 | 依科瑞德（北京）能源科技有限公司 | A kind of energy source station that wind energy is complementary with liquefied air energy storage |
| CN209354349U (en) * | 2018-11-30 | 2019-09-06 | 珠海凌达压缩机有限公司 | The quiet disk of a kind of screw compressor and with its screw compressor |
| CN109469620A (en) * | 2018-12-18 | 2019-03-15 | 珠海凌达压缩机有限公司 | A kind of compressor increasing enthalpy gas supplementary structure and horizontal enthalpy-increasing scroll compressor |
-
2020
- 2020-07-13 CN CN202010670047.4A patent/CN111852783B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103206355A (en) * | 2013-05-06 | 2013-07-17 | 张学文 | Artificial density difference power generation system |
| CN106286173A (en) * | 2016-10-09 | 2017-01-04 | 符海龙 | Power cycle output intent and the system of heat energy is absorbed from air |
| CN108757069A (en) * | 2018-06-15 | 2018-11-06 | 刘芙蓉 | Biphase gas and liquid flow gravity heat engine |
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