CN105221345A - A kind of cogeneration type compressed-air energy-storage system and controlling method thereof - Google Patents

Abstract

The present invention relates to a kind of cogeneration type compressed-air energy-storage system, comprise cogeneration units and adiabatic compression air energy-storage units; Cogeneration units comprises thermoelectricity unit boiler, the output terminal of thermoelectricity unit boiler is provided with the first branch road and the second branch road, described first branch road is connected with the input end of heat user by steam turbine, described second branch road is connected with the input end of heat user by thermoelectricity unit steam converter valve, and described steam turbine is connected with generator; The output terminal of described heat user is connected with the input end of thermoelectricity unit boiler by the second vapor-water heat exchanger; Described adiabatic compression air energy-storage units comprises the compressor, the second vapor-water heat exchanger, gas holder, the first vapor-water heat exchanger, turbine expansion equipment, first clutch, generator motor, the second clutch that connect successively, and described second clutch is connected with compressor; Described heat user is in parallel with the first vapor-water heat exchanger, and the input pipeline of heat user and the first vapor-water heat exchanger is also provided with steam regulation valve.

Description

A kind of cogeneration type compressed-air energy-storage system and controlling method thereof

Technical field

The invention belongs to clean energy resource technical field of comprehensive utilization, relate to a kind of cogeneration type compressed-air energy-storage system and controlling method thereof.

Background technique

Along with Wind Power In China develops scale continuous enlargement, wind-electricity integration runs and dissolve in market becomes the key factor of restriction Wind Power Development.China's wind-powered electricity generation compares and concentrates on three northern areas of China, winter, nighttime wind speed was very large, but night, electrical load requirement was lower, because the heat supply in winter phase is for ensureing heating demand, cogeneration units majority operates in the pattern of " electricity determining by heat ", and particularly for the back pressure type thermoelectricity unit existed a large amount of in thermoelectricity plant, it exports hotspot stress and fixes, be difficult to participate in peak regulation, seriously when causing low ebb abandon wind phenomenon.

Along with the development of energy storage technology, utilize energy storage to carry out " peak load shifting " wind-powered electricity generation, store unnecessary wind-powered electricity generation when electric load low ebb at night, discharge during electric load peak by day, become the effective means of the digestion capability improving wind-powered electricity generation.Particularly compressed air energy storage technology has that energy storage cost is low because of it, environmental friendliness, becomes without the advantage of phase transformation loss the extensive energy storage technology received much concern in recent years.

The method utilizing compressed-air energy storage to improve wind electricity digestion at present all only relates to the storage of single electric energy, and the hotspot stress of existing cogeneration units can not regulated to combine by energy storage, to improve the peak modulation capacity of thermoelectricity unit self, the stored energy capacitance needed under reducing wind-powered electricity generation of dissolving on an equal basis.This is the deficiencies in the prior art part.

Therefore, a kind of cogeneration type compressed-air energy-storage system of design and controlling method thereof are provided, to solve the problems of the technologies described above, are necessary.

Summary of the invention

The object of the invention is to, for the defect that above-mentioned prior art exists, provide a kind of cogeneration type compressed-air energy-storage system of design and controlling method thereof, to solve the problems of the technologies described above.

For achieving the above object, the present invention provides following technological scheme:

A kind of cogeneration type compressed-air energy-storage system, comprises cogeneration units and adiabatic compression air energy-storage units, it is characterized in that:

Described cogeneration units comprises thermoelectricity unit boiler, the output terminal of described thermoelectricity unit boiler is provided with the first branch road and the second branch road, described first branch road is connected with the input end of heat user by steam turbine, described second branch road is connected with the input end of heat user by thermoelectricity unit steam converter valve, and described steam turbine is connected with generator; The output terminal of described heat user is connected with the input end of thermoelectricity unit boiler by the second vapor-water heat exchanger;

Described adiabatic compression air energy-storage units comprises the compressor, the second vapor-water heat exchanger, gas holder, the first vapor-water heat exchanger, turbine expansion equipment, first clutch, generator motor, the second clutch that connect successively, and described second clutch is connected with compressor;

Described heat user is in parallel with the first vapor-water heat exchanger, and the input pipeline of heat user and the first vapor-water heat exchanger is also provided with steam regulation valve.

Preferably, described first vapor-water heat exchanger connects the steam output circuit of the high pressure airline before entering turbine expansion equipment and steam turbine; Thus steam-turbine heat can be utilized to heat the gas before entering turbine expansion equipment.

Preferably, the first described branch road is metallic conduit; Adopt metallic conduit can not only realize the conducting of current, and not perishable.

Preferably, the first described branch road is stainless steel pipeline; Anticorrosive, long service life.

Preferably, the first described branch road is outward for being enclosed with thermal insulation layer; The first branch road can either be protected, and effectively can delay the cooling rate of hot water in the first branch road.

Preferably, the second described branch road is metallic conduit; Adopt metallic conduit can not only realize the conducting of current, and not perishable.

Preferably, the second described branch road is stainless steel pipeline; Anticorrosive, long service life.

Preferably, the second described branch road is wrapped with thermal insulation layer; The second branch road can either be protected, and effectively can delay the cooling rate of hot water in the second branch road.

A controlling method for cogeneration type compressed-air energy-storage system, comprises the following steps:

Step (1): obtain wind-powered electricity generation prediction output power, thermal load demands prediction data and the electrical load requirement prediction data in next scheduling time section T;

Step (2): the wind power equivalence coal consumption amount of dissolving according to the coal consumption amount of t back pressure type thermoelectricity unit, t and compressed-air energy-storage system t equivalence power consumption arrange system goal function;

Step (3): arrange constraint conditio, according to system goal function and the constraint conditio of step (2), solves any time adiabatic compression air energy-storage units and the optimum output power of cogeneration units; Described constraint conditio comprises electric load Constraints of Equilibrium, heat load balance constraint, cogeneration units process constraint, unit ramping rate constraints and adiabatic compression air energy-storage units capacity-constrained;

The concrete steps of described step (2) are:

Heat supply coal consumption amount for back pressure type cogeneration units is expressed as the quadratic form of generated output:

$C_1(i,t)=a_i{\left(p_{e1,i}^t\right)}^2+b_i{p}_{e1,i}^t+c_i;$

In formula: C ₁(i, t) represents the coal consumption amount of t back pressure type thermoelectricity unit, a _i, b _i, c _ifor the coal consumption coefficient of back pressure type thermoelectricity unit i; be the generated output of i-th back pressure type thermoelectricity unit in t;

T dissolve wind-powered electricity generation consume equivalent coal consumption amount C ₂(t) be

C ₂(t)＝0；

If adiabatic compression air energy-storage units energy storage efficiency is η, then adiabatic compression air energy-storage units t equivalence power consumption C ₃(t) be:

$C_3\left(t\right)=(1-\mathrm{\η})C_{ave}{p}_{e3}^t;$

C in formula _avefor whole unit of cells power averaging energy consumption, for adiabatic compression air energy-storage units is at the generated output of t;

P _e1represent back pressure thermoelectricity unit generated output, p _e2represent the wind power of dissolving, p _e3represent adiabatic compression air energy-storage units generated output;

Setting up system goal function is:

$C\left(t\right)=\underset{t=1}{\overset{T}{\Σ}}\{\underset{i=1}{\overset{n}{\Σ}}{C}_1(i,t)p_{e1,i}^t+C_2\left(t\right)p_{e2}^t+C_3\left(t\right)p_{e3}^t\};$

Wherein, the total consumption of coal amount that C (t) is whole system, C ₁(i, t) represents the coal consumption amount of t back pressure type thermoelectricity unit, C ₂t wind power equivalence coal consumption amount that () is dissolved for t, C ₃t () is adiabatic compression air energy-storage units t equivalence power consumption, represent the electric power of i-th thermoelectricity unit in t, represent the wind-powered electricity generation electric power of dissolving in t, represent the electric power of adiabatic compression air energy-storage units t;

The electric load Constraints of Equilibrium of described step (3) and heat load balance constraint:

$\left\{\begin{array}{c}\underset{i=1}{\overset{n}{\Σ}}{P}_{e1,i}^t+P_{e2}^t+P_{e3}^t=P_{De}^t\\ P_{h1,i}^t+c_v{p}_{e3}^t\≥P_{Dh}^t\end{array}\right.;$

In formula for t equivalent electric load power, for t heat load power, c _vfor adiabatic compression air energy-storage units hotspot stress;

The cogeneration units units limits of described step (3):

$\left\{\begin{array}{c}{P}_{e1,i}^t=c_m{P}_{h,i}^t+K_i\\ P_{e1,\min ,i}\≤P_{e1,i}^t\≤P_{e1,\max ,i}\end{array}\right.;$

Wherein, c _mrepresent the hotspot stress of cogeneration units, K _ifor constant, P _{e1, min, i}gain merit for cogeneration units i is minimum and exert oneself, P _{e1, max, i}be respectively maximum the gaining merit of cogeneration units i to exert oneself;

The unit ramping rate constraints of described step (3):

$\left\{\begin{array}{c}{P}_i^t-P_i^{t-1}\≤P_{up,i}\\ P_i^{t-1}-P_i^t\≤P_{down,i}\end{array}\right.$

P _{up, i}for cogeneration units i upwards ramping rate constraints, P _{down, i}for the downward ramping rate constraints of cogeneration units i;

The adiabatic compression air energy-storage units capacity-constrained of described step (3):

$\underset{t=1}{\overset{n}{\Σ}}{p}_{e3}^t\≤S;$

In formula, n≤T, S are energy storage rated capacity;

According to objective function and constraint conditio, solve any time adiabatic compression air energy-storage units and the optimum output power of cogeneration units.

Beneficial effect of the present invention is, the high pressure-temperature air that described compressor exports carries out heat exchange by the backwater end of the second vapor-water heat exchanger and thermoelectricity unit boiler by the road, thus heats before entering thermoelectricity unit boiler heat supply backwater;

Adiabatic compression air energy-storage units and cogeneration units carry out the coupling of electric energy and heat energy, to cogeneration units heat supply, can absorb the heat energy of cogeneration units during the generating of release air during adiabatic compression air energy-storage units compressed-air energy storage.In addition, design principle of the present invention is reliable, and structure is simple, has application prospect widely.

As can be seen here, the present invention compared with prior art, has substantive distinguishing features and progress, and its beneficial effect implemented also is apparent.

Accompanying drawing explanation

Fig. 1 is the structural representation of a kind of cogeneration type compressed-air energy-storage system provided by the invention.

Wherein, 1.1-thermoelectricity unit boiler, 1.2-first branch road, 1.3-second branch road, 1.4-steam turbine, 1.5-heat user, 1.6-thermoelectricity unit steam converter valve, 2.1-compressor, 2.2 second vapor-water heat exchangers, 2.3 gas holder, 2.4 first vapor-water heat exchangers, 2.5-turbine expansion equipment, 2.6-first clutch, 2.7-generator motor, 2.8 second clutches, 2.9-steam regulation valve.

Embodiment

Below in conjunction with accompanying drawing, also by specific embodiment, the present invention will be described in detail, and following examples are explanation of the invention, and the present invention is not limited to following mode of execution.

As shown in Figure 1, a kind of cogeneration type compressed-air energy-storage system provided by the invention, comprises cogeneration units and adiabatic compression air energy-storage units;

Described cogeneration units comprises thermoelectricity unit boiler 1.1, the output terminal of described thermoelectricity unit boiler 1.1 is provided with the first branch road 1.2 and the second branch road 1.3, described first branch road 1.2 is connected with the input end of heat user 1.5 by steam turbine 1.4, described second branch road 1.3 is connected with the input end of heat user 1.5 by thermoelectricity unit steam converter valve 1.6, and described steam turbine 1.4 is connected with generator; The output terminal of described heat user 1.5 is connected with the input end of thermoelectricity unit boiler 1.1 by the second vapor-water heat exchanger 2.2;

Described adiabatic compression air energy-storage units comprises compressor 2.1, second vapor-water heat exchanger 2.2, gas holder 2.3, first vapor-water heat exchanger 2.4, turbine expansion equipment 2.5, first clutch 2.6, generator motor 2.7, the second clutch 2.8 that connect successively, and described second clutch 2.8 is connected with compressor 2.1;

Described heat user 1.5 is in parallel with the first vapor-water heat exchanger 2.4, and the input pipeline of heat user 1.5 and the first vapor-water heat exchanger 2.4 is also provided with steam regulation valve 2.9.

In the present embodiment, described first vapor-water heat exchanger 2.4 connects the steam output circuit of the high pressure airline before entering turbine expansion equipment 2.5 and steam turbine; Thus steam-turbine heat can be utilized to heat the gas before entering turbine expansion equipment.

In the present embodiment, the first described branch road 1.2 is metallic conduit; Adopt metallic conduit can not only realize the conducting of current, and not perishable.

In the present embodiment, the first described branch road 1.2 is stainless steel pipeline; Anticorrosive, long service life.

In the present embodiment, the first described branch road 1.2 is outer for being enclosed with thermal insulation layer; The first branch road can either be protected, and effectively can delay the cooling rate of hot water in the first branch road.

In the present embodiment, the second described branch road 1.3 is metallic conduit; Adopt metallic conduit can not only realize the conducting of current, and not perishable.

In the present embodiment, the second described branch road 1.3 is stainless steel pipeline; Anticorrosive, long service life.

In the present embodiment, the second described branch road 1.3 is wrapped with thermal insulation layer; The second branch road can either be protected, and effectively can delay the cooling rate of hot water in the second branch road.

The present embodiment also provides a kind of controlling method of cogeneration type compressed-air energy-storage system, comprises the following steps:

Step (1): obtain wind-powered electricity generation prediction output power, thermal load demands prediction data and the electrical load requirement prediction data in next scheduling time section T;

Step (2): the wind power equivalence coal consumption amount of dissolving according to the coal consumption amount of t back pressure type thermoelectricity unit, t and compressed-air energy-storage system t equivalence power consumption arrange system goal function;

Step (3): arrange constraint conditio, according to system goal function and the constraint conditio of step (2), solves any time adiabatic compression air energy-storage units and the optimum output power of cogeneration units; Described constraint conditio comprises electric load Constraints of Equilibrium, heat load balance constraint, cogeneration units process constraint, unit ramping rate constraints and adiabatic compression air energy-storage units capacity-constrained;

The concrete steps of described step (2) are:

Heat supply coal consumption amount for back pressure type cogeneration units is expressed as the quadratic form of generated output:

$C_1(i,t)=a_i{\left(p_{e1,i}^t\right)}^2+b_i{p}_{e1,i}^t+c_i;$

In formula: C ₁(i, t) represents the coal consumption amount of t back pressure type thermoelectricity unit, a _i, b _i, c _ifor the coal consumption coefficient of back pressure type thermoelectricity unit i; be the generated output of i-th back pressure type thermoelectricity unit in t;

T dissolve wind-powered electricity generation consume equivalent coal consumption amount C ₂(t) be

C ₂(t)＝0；

If adiabatic compression air energy-storage units energy storage efficiency is η, then adiabatic compression air energy-storage units t equivalence power consumption C ₃(t) be:

$C_3\left(t\right)=(1-\mathrm{\η})C_{ave}{p}_{e3}^t;$

C in formula _avefor whole unit of cells power averaging energy consumption, for adiabatic compression air energy-storage units is at the generated output of t;

P _e1represent back pressure thermoelectricity unit generated output, p _e2represent the wind power of dissolving, p _e3represent adiabatic compression air energy-storage units generated output;

Setting up system goal function is:

$C\left(t\right)=\underset{t=1}{\overset{T}{\Σ}}\{\underset{i=1}{\overset{n}{\Σ}}{C}_1(i,t)p_{e1,i}^t+C_2\left(t\right)p_{e2}^t+C_3\left(t\right)p_{e3}^t\};$

Wherein, the total consumption of coal amount that C (t) is whole system, C ₁(i, t) represents the coal consumption amount of t back pressure type thermoelectricity unit, C ₂t wind power equivalence coal consumption amount that () is dissolved for t, C ₃t () is adiabatic compression air energy-storage units t equivalence power consumption, represent the electric power of i-th thermoelectricity unit in t, represent the wind-powered electricity generation electric power of dissolving in t, represent the electric power of adiabatic compression air energy-storage units t;

The electric load Constraints of Equilibrium of described step (3) and heat load balance constraint:

$\left\{\begin{array}{c}\underset{i=1}{\overset{n}{\Σ}}{P}_{e1,i}^t+P_{e2}^t+P_{e3}^t=P_{De}^t\\ P_{h1,i}^t+c_v{p}_{e3}^t\≥P_{Dh}^t\end{array}\right.;$

In formula for t equivalent electric load power, for t heat load power, c _vfor adiabatic compression air energy-storage units hotspot stress;

The cogeneration units units limits of described step (3):

$\left\{\begin{array}{c}{P}_{e1,i}^t=c_m{P}_{h,i}^t+K_i\\ P_{e1,\min ,i}\≤P_{e1,i}^t\≤P_{e1,\max ,i}\end{array}\right.;$

Wherein, c _mrepresent the hotspot stress of cogeneration units, K _ifor constant, P _{e1, min, i}gain merit for cogeneration units i is minimum and exert oneself, P _{e1, max, i}be respectively maximum the gaining merit of cogeneration units i to exert oneself;

The unit ramping rate constraints of described step (3):

$\left\{\begin{array}{c}{P}_i^t-P_i^{t-1}\≤P_{up,i}\\ P_i^{t-1}-P_i^t\≤P_{down,i}\end{array}\right.$

P _{up, i}for cogeneration units i upwards ramping rate constraints, P _{down, i}for the downward ramping rate constraints of cogeneration units i;

The adiabatic compression air energy-storage units capacity-constrained of described step (3):

$\underset{t=1}{\overset{n}{\Σ}}{p}_{e3}^t\≤S;$

In formula, n≤T, S are energy storage rated capacity;

According to objective function and constraint conditio, solve any time adiabatic compression air energy-storage units and the optimum output power of cogeneration units.

The preferred embodiment of the present invention is only above; but the present invention is not limited thereto; any those skilled in the art can think there is no creationary change, and some improvements and modifications done without departing from the principles of the present invention, all should drop in protection scope of the present invention.

Claims (9)

1. a cogeneration type compressed-air energy-storage system, comprises cogeneration units and adiabatic compression air energy-storage units, it is characterized in that:

Described cogeneration units comprises thermoelectricity unit boiler, the output terminal of described thermoelectricity unit boiler is provided with the first branch road and the second branch road, described first branch road is connected with the input end of heat user by steam turbine, described second branch road is connected with the input end of heat user by thermoelectricity unit steam converter valve, and described steam turbine is connected with generator; The output terminal of described heat user is connected with the input end of thermoelectricity unit boiler by the second vapor-water heat exchanger;

Described adiabatic compression air energy-storage units comprises the compressor, the second vapor-water heat exchanger, gas holder, the first vapor-water heat exchanger, turbine expansion equipment, first clutch, generator motor, the second clutch that connect successively, and described second clutch is connected with compressor;

Described heat user is in parallel with the first vapor-water heat exchanger, and the input pipeline of heat user and the first vapor-water heat exchanger is also provided with steam regulation valve.

2. a kind of cogeneration type compressed-air energy-storage system according to claim 1, is characterized in that: described first vapor-water heat exchanger connects the steam output circuit of the high pressure airline before entering turbine expansion equipment and steam turbine.

3. a kind of cogeneration type compressed-air energy-storage system according to claim 1 and 2, is characterized in that: the first described branch road is metallic conduit.

4. a kind of cogeneration type compressed-air energy-storage system according to claim 3, is characterized in that: the first described branch road is stainless steel pipeline.

5. a kind of cogeneration type compressed-air energy-storage system according to claim 4, is characterized in that: the first described branch road is outward for being enclosed with thermal insulation layer.

6. a kind of cogeneration type compressed-air energy-storage system according to claim 5, is characterized in that: the second described branch road is metallic conduit.

7. a kind of cogeneration type compressed-air energy-storage system according to claim 6, is characterized in that: the second described branch road is stainless steel pipeline.

8. a kind of cogeneration type compressed-air energy-storage system according to claim 7, is characterized in that: the second described branch road is wrapped with thermal insulation layer.

9. a controlling method for cogeneration type compressed-air energy-storage system, comprises the following steps:

Step (1): obtain wind-powered electricity generation prediction output power, thermal load demands prediction data and the electrical load requirement prediction data in next scheduling time section T;

Step (2): the wind power equivalence coal consumption amount of dissolving according to the coal consumption amount of t back pressure type thermoelectricity unit, t and compressed-air energy-storage system t equivalence power consumption arrange system goal function;

Step (3): arrange constraint conditio, according to system goal function and the constraint conditio of step (2), solves any time adiabatic compression air energy-storage units and the optimum output power of cogeneration units; Described constraint conditio comprises electric load Constraints of Equilibrium, heat load balance constraint, cogeneration units process constraint, unit ramping rate constraints and adiabatic compression air energy-storage units capacity-constrained;

The concrete steps of described step (2) are:

Heat supply coal consumption amount for back pressure type cogeneration units is expressed as the quadratic form of generated output:

$C_1(i,t)=a_i{\left(p_{e1,i}^t\right)}^2+b_i{p}_{e1,i}^t+c_i;$

In formula: C ₁(i, t) represents the coal consumption amount of t back pressure type thermoelectricity unit, a _i, b _i, c _ifor the coal consumption coefficient of back pressure type thermoelectricity unit i; be the generated output of i-th back pressure type thermoelectricity unit in t;

T dissolve wind-powered electricity generation consume equivalent coal consumption amount C ₂(t) be

C ₂(t)＝0；

If adiabatic compression air energy-storage units energy storage efficiency is η, then adiabatic compression air energy-storage units t equivalence power consumption C ₃(t) be:

$C_3\left(t\right)=(1-\mathrm{\η})C_{ave}{p}_{e3}^t;$

C in formula _avefor whole unit of cells power averaging energy consumption, for adiabatic compression air energy-storage units is at the generated output of t;

P _e1represent back pressure thermoelectricity unit generated output, p _e2represent the wind power of dissolving, p _e3represent adiabatic compression air energy-storage units generated output;

Setting up system goal function is:

$C\left(t\right)=\underset{t=1}{\overset{T}{\Σ}}\{\underset{i=1}{\overset{n}{\Σ}}{C}_1(i,t)p_{e1,i}^t+C_2\left(t\right)p_{e2}^t+C_3\left(t\right)p_{e3}^t\};$

Wherein, the total consumption of coal amount that C (t) is whole system, C ₁(i, t) represents the coal consumption amount of t back pressure type thermoelectricity unit, C ₂t wind power equivalence coal consumption amount that () is dissolved for t, C ₃t () is adiabatic compression air energy-storage units t equivalence power consumption, represent the electric power of i-th thermoelectricity unit in t, represent the wind-powered electricity generation electric power of dissolving in t, represent the electric power of adiabatic compression air energy-storage units t;

The electric load Constraints of Equilibrium of described step (3) and heat load balance constraint:

$\left\{\begin{array}{c}\underset{i=1}{\overset{n}{\Σ}}{P}_{e1,i}^t+P_{e2}^t+P_{e3}^t=P_{De}^t\\ P_{h1,i}^t+c_v{p}_{e3}^t\≥P_{Dh}^t\end{array}\right.;$

In formula for t equivalent electric load power, for t heat load power, c _vfor adiabatic compression air energy-storage units hotspot stress;

The cogeneration units units limits of described step (3):

$\left\{\begin{array}{c}{P}_{e1,i}^t=c_m{P}_{h,i}^t+K_i\\ P_{e1,\min ,i}\≤P_{e1,i}^t\≤P_{e1,\max ,i}\end{array}\right.;$

Wherein, c _mrepresent the hotspot stress of cogeneration units, K _ifor constant, P _{e1, min, i}gain merit for cogeneration units i is minimum and exert oneself, P _{e1, max, i}be respectively maximum the gaining merit of cogeneration units i to exert oneself;

The unit ramping rate constraints of described step (3):

$\left\{\begin{array}{c}{P}_i^t-P_i^{t-1}\≤P_{up,i}\\ P_i^{t-1}-P_i^t\≤P_{down,i}\end{array}\right.$

P _{up, i}for cogeneration units i upwards ramping rate constraints, P _{down, i}for the downward ramping rate constraints of cogeneration units i;

The adiabatic compression air energy-storage units capacity-constrained of described step (3):

$\underset{t=1}{\overset{n}{\Σ}}{p}_{e3}^t\≤S;$

In formula, n≤T, S are energy storage rated capacity;

According to objective function and constraint conditio, solve any time adiabatic compression air energy-storage units and the optimum output power of cogeneration units.