CN211950757U - Solar tower trough combined power generation system - Google Patents

Solar tower trough combined power generation system Download PDF

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Publication number
CN211950757U
CN211950757U CN202020257742.3U CN202020257742U CN211950757U CN 211950757 U CN211950757 U CN 211950757U CN 202020257742 U CN202020257742 U CN 202020257742U CN 211950757 U CN211950757 U CN 211950757U
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inlet
outlet
heat
transfer fluid
storage tank
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张�成
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Guangdong Ocean University
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Guangdong Ocean University
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    • YGENERAL 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
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02EREDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00Energy generation through renewable energy sources
    • Y02E10/40Solar thermal energy, e.g. solar towers
    • Y02E10/46Conversion of thermal power into mechanical power, e.g. Rankine, Stirling or solar thermal engines

Abstract

The utility model relates to a solar photothermal power technical field discloses a solar energy tower groove cogeneration system. The power generation system comprises a trough type heat collector, a tower type heat collector, a preheater, a superheater and a reheater; the outlet of the heating pipe of the trough type heat collector is connected with the heat transfer fluid inlet of the preheater; the heat transfer fluid outlet of the preheater is connected with the heating pipe inlet of the trough type heat collector; the outlet of the heating pipe of the tower type heat collector is respectively connected with the heat transfer fluid inlet of the superheater and the heat transfer fluid inlet of the reheater; and a heat transfer fluid outlet of the superheater and a heat transfer fluid outlet of the reheater are connected with a heating pipe inlet of the tower type heat collector. The utility model simultaneously utilizes the trough type heat collector and the tower type heat collector, and the trough type heat collector and the tower type heat collector work in respective optimal working temperature intervals, thereby improving the system efficiency and the field utilization rate of the tower type mirror field; the sectional heating of the working medium is realized, and the flow of the heat transfer fluid in each heat exchanger can be independently adjusted.

Description

Solar tower trough combined power generation system
Technical Field
The utility model relates to a solar photothermal power technical field especially relates to a solar tower groove cogeneration system.
Background
With the obvious problems of fossil energy consumption and environmental pollution, solar energy is widely considered as a clean energy source which has the most potential to replace the traditional fossil energy source in the future. Solar photo-thermal power generation generally adopts a heat collector to collect light and heat for power generation, and a reflector is used for collecting sunlight to a receiver for absorbing solar energy to generate heat and transferring the heat to synthetic oil, molten salt or air and other heat transfer fluids. The heat transfer fluid then provides heat, either directly or indirectly, to the power cycle system. Compared with solar photovoltaic power generation, solar photo-thermal power generation has the advantages of high energy density, stable power generation, good power grid compatibility, easy integration with the existing thermal power plant and the like, and is receiving more and more attention. The existing solar thermal power station adopts a single heat collector structure type: solar trough power generation or solar tower power generation.
The solar trough type power generation technology adopts a trough type paraboloid as a reflector, and the reflector tracks the sun in a single-shaft tracking mode in the daytime. The reflector reflects and concentrates sunlight onto the heating tube at the focal line. The heat transfer fluid flows through the heating tubes and absorbs heat generated by the concentrated sunlight for provision to the power generation system. The structural schematic diagram of the existing solar trough power generation system is shown in fig. 1, and the circulation loop of the heat transfer fluid is as follows: after the heat transfer fluid is heated by the trough collector 11, one part of the heat transfer fluid sequentially passes through the superheater 22 and the preheater 21, exchanges heat with the Rankine cycle flowing through the superheater 22 and the preheater 21 and then flows back to the trough collector 11, and the other part of the heat transfer fluid passes through the reheater 23 and exchanges heat with the Rankine cycle flowing through the reheater 23 and then flows back to the trough collector 11.
The solar tower power generation technology is a solar power generation technology which uses a receiver positioned at the top of a high tower to receive collected sunlight. It uses a large number of movable solar reflectors (called heliostats) each equipped with a tracking mechanism to accurately reflect sunlight in real time to a receiver located at the top of the tower. The tracking mechanism tracks the sun for two-axis tracking (east to west, up and down). The receiver absorbs concentrated solar radiation to convert the solar energy into heat, which is transferred by the heat transfer fluid to the thermodynamic cycle system for power generation. The structural schematic diagram of the existing solar tower power generation system is shown in fig. 2, and the circulation loop of the heat transfer fluid is as follows: after the heat transfer fluid is heated by the tower type heat collector 12, one part of the heat transfer fluid sequentially passes through the superheater 22 and the preheater 21, exchanges heat with the Rankine cycle flowing through the superheater 22 and the preheater 21 and then flows back to the tower type heat collector 12, and the other part of the heat transfer fluid passes through the reheater 23 and exchanges heat with the Rankine cycle flowing through the reheater 23 and then flows back to the tower type heat collector 12.
Solar trough power generation is the most mature and commercialized technology, but it has the following disadvantages: the light-gathering ratio is relatively low, the heat collection temperature of the receiver is relatively low, and the photo-thermal power generation efficiency is also relatively low. The solar tower type power generation technology has the advantages of high photo-thermal power generation efficiency and large-scale application, and has the defects of high investment cost, high system complexity, large heat absorber heat exchange temperature difference and large energy consumption of a molten salt heat preservation system.
In addition, the existing solar tower type power generation technology and solar trough type power generation technology have large temperature difference and large temperature difference between heat transfer fluid and Rankine cycle heat exchange processAnd (4) damage problem. This is because, for the groove-type power generation and tower-type power generation technologies, in the heat exchange process of the heat transfer fluid and the rankine cycle working medium, as shown in fig. 3, the rankine cycle working medium has phase change, but the heat transfer fluid has no phase change, so that the heat transfer temperature difference is large in the heat transfer process, and the heat transfer temperature difference is large in the heat transfer processThe damage is larger.
Under the existing solar trough power generation system shown in fig. 1 and the solar tower power generation system structure shown in fig. 2, since the heat transfer fluid can only flow through the heat exchangers (the preheater 21, the superheater 22 and the reheater 23) at a constant mass flow rate to realize heat exchange, as shown in fig. 4, the temperature difference Δ T at the pinch point isminUnder the fixed condition, if the mass flow of the heat transfer fluid is increased to reduce the slope of the heat transfer fluid curve, the heat exchange average temperature difference of the evaporation section is reduced, and the heat exchange average temperature difference of the preheating section is also increased; similarly, if the heat transfer fluid flow is decreased to increase the slope of the heat transfer fluid curve, the average heat transfer temperature difference in the preheating section is decreased while the average heat transfer temperature difference in the evaporation section is increased, thus resulting in a large temperature difference and a large heat transfer rateThe problem of damage is always unavoidable.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to provide a solar tower groove cogeneration system overcomes that what prior art existed leads to big difference in temperature and big because of heat transfer fluid can only flow through each heat exchanger with invariable mass flowAnd (4) the problem of damage.
To achieve the purpose, the utility model adopts the following technical proposal:
a solar cell cogeneration system, comprising: the heat collecting device and the heat exchange device;
the heat collecting device comprises: trough collectors and tower collectors;
the heat exchange device comprises: the system comprises a preheater, a superheater and a reheater, wherein the preheater or the superheater is also combined with an evaporator;
the outlet of the heating pipe of the trough type heat collector is connected with the heat transfer fluid inlet of the preheater through a first pipeline; the heat transfer fluid outlet of the preheater is connected with the heating pipe inlet of the trough type heat collector through a second pipeline;
a heating pipe outlet of the tower type heat collector is respectively connected with a heat transfer fluid inlet of the superheater and a heat transfer fluid inlet of the reheater through a third pipeline; and a heat transfer fluid outlet of the superheater and a heat transfer fluid outlet of the reheater are respectively connected with a heating pipe inlet of the tower type heat collector through a fourth pipeline.
Optionally, the system further comprises a heat storage device;
the heat storage device includes: the low-temperature heat storage tank, the medium-temperature heat storage tank and the high-temperature heat storage tank;
an inlet of the low-temperature heat storage tank is connected with the second pipeline through a first valve, and an outlet of the low-temperature heat storage tank is connected with the second pipeline through a second valve;
an inlet of the high-temperature heat storage tank is connected with the third pipeline through a third valve, and an outlet of the high-temperature heat storage tank is connected with the third pipeline through a fourth valve;
the first inlet of the medium-temperature heat storage tank is connected with the first pipeline through a fifth valve; a first outlet of the medium-temperature heat storage tank is connected with the first pipeline through a sixth valve; a second inlet of the medium-temperature heat storage tank is connected with the fourth pipeline through a fifth valve; and a second outlet of the medium-temperature heat storage tank is connected with the fourth pipeline through a sixth valve.
Optionally, the system further comprises a steam turbine, wherein the steam turbine comprises a high-pressure cylinder and a medium-low pressure cylinder;
a working medium outlet of the superheater is connected with a working medium inlet of the high-pressure cylinder;
a working medium outlet of the high-pressure cylinder is connected with a working medium inlet of the reheater;
a working medium outlet of the reheater is connected with a working medium inlet of the medium-low pressure cylinder;
a first working medium outlet of the medium and low pressure cylinder is connected with an inlet of a deaerator, and a second working medium outlet of the medium and low pressure cylinder is connected with an inlet of the deaerator through a condenser;
the outlet of the deaerator is connected with the working medium inlet of the preheater,
and the working medium outlet of the preheater is connected with the working medium inlet of the superheater.
Optionally, the design value of the outlet temperature of the heat transfer fluid of the trough collector is not equal to the design value of the inlet temperature of the heat transfer fluid of the tower collector.
Optionally, the heat transfer fluid flowing through the heat collecting device and the heat exchanging device includes: synthetic oil, molten salt, or air; rankine cycle working medium flowing through the heat exchange device comprises: water, CO2Or an organic working substance.
The utility model also provides another kind of solar tower groove cogeneration system, include: the heat collecting device, the heat storage device and the heat exchange device;
the heat collecting device comprises: trough collectors and tower collectors;
the heat storage device includes: the low-temperature heat storage tank, the medium-temperature heat storage tank and the high-temperature heat storage tank;
the heat exchange device comprises: the system comprises a preheater, a superheater and a reheater, wherein the preheater or the superheater is also combined with an evaporator;
an outlet of a heating pipe of the trough type heat collector is connected with a first inlet of the medium-temperature heat storage tank through a first pipeline; the first outlet of the medium-temperature heat storage tank is connected with the heat transfer fluid inlet of the preheater through a second pipeline; the heat transfer fluid outlet of the preheater is connected with the inlet of the low-temperature heat storage tank through a third pipeline; an outlet of the low-temperature heat storage tank is connected with an inlet of a heating pipe of the trough type heat collector through a fourth pipeline;
an outlet of a heating pipe of the tower type heat collector is connected with an inlet of the high-temperature heat storage tank through a fifth pipeline; an outlet of the high-temperature heat storage tank is respectively connected with a heat transfer fluid inlet of the superheater and a heat transfer fluid inlet of the reheater through a sixth pipeline; a heat transfer fluid outlet of the superheater and a heat transfer fluid outlet of the reheater are respectively connected with a second inlet of the medium-temperature heat storage tank through a seventh pipeline; and a second outlet of the medium-temperature heat storage tank is connected with an inlet of a heating pipe of the tower type heat collector through an eighth pipeline.
Optionally, the system further comprises a steam turbine, wherein the steam turbine comprises a high-pressure cylinder and a medium-low pressure cylinder;
a working medium outlet of the superheater is connected with a working medium inlet of the high-pressure cylinder;
a working medium outlet of the high-pressure cylinder is connected with a working medium inlet of the reheater;
a working medium outlet of the reheater is connected with a working medium inlet of the medium-low pressure cylinder;
a first working medium outlet of the medium and low pressure cylinder is connected with an inlet of a deaerator, and a second working medium outlet of the medium and low pressure cylinder is connected with an inlet of the deaerator through a condenser;
the outlet of the deaerator is connected with the working medium inlet of the preheater,
and the working medium outlet of the preheater is connected with the working medium inlet of the superheater.
Optionally, the design value of the outlet temperature of the heat transfer fluid of the trough collector is not equal to the design value of the inlet temperature of the heat transfer fluid of the tower collector.
Optionally, the heat transfer fluid flowing through the heat collecting device and the heat exchanging device includes: synthetic oil, molten salt, or air; rankine cycle working medium flowing through the heat exchange device comprises: water, CO2Or an organic working substance.
Compared with the prior art, the embodiment of the utility model provides a following beneficial effect has:
1) the embodiment of the utility model provides an adopted tower heat collector and slot type heat collector simultaneously, utilized the slot type heat collector to be used for collecting the lower heat of temperature, utilized the higher heat of tower heat collector to collect the temperature for tower heat collector and slot type heat collector can be worked in respective best operating temperature interval, are favorable to improving system efficiency, and the place utilization ratio in tower mirror field can also be improved in the joining of slot type heat collector, the lowering system cost.
2) The embodiment of the utility model realizes the segmented heating of Rankine cycle working medium by utilizing the tower type heat collector and the trough type heat collector; based on the sectional heating mode, the mass flow of the heat transfer fluid in each heat exchanger can be independently adjusted according to the requirement, so that the heat exchange temperature difference of each heat exchanger can be reduced, and the heat exchange process is reducedAnd the power generation efficiency of the power plant is improved.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings needed to be used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without inventive exercise.
Fig. 1 is a structural view of a conventional solar trough power generation system.
Fig. 2 is a structural view of a conventional solar tower power generation system.
Fig. 3 is a schematic diagram of heat transfer of a conventional tower power generation system and a conventional trough power generation system.
Fig. 4 is a schematic diagram of heat transfer when the mass flow rate of a heat transfer fluid is changed in the prior art.
Fig. 5 is a structural diagram of a solar tower-trough combined power generation system provided in the first embodiment of the present invention;
fig. 6 is a schematic diagram of heat transfer when the mass flow of the heat transfer fluid is changed according to an embodiment of the present invention.
Fig. 7 is another schematic diagram of heat transfer when the mass flow of the heat transfer fluid is changed according to an embodiment of the present invention.
Fig. 8 is a structural diagram of a solar tower-trough combined power generation system provided by the second embodiment of the present invention.
[ diagrammatic illustration ]
The heat collecting device 10: a trough collector 11 and a tower collector 12;
the heat exchange device 20: a preheater 21, a superheater 22, and a reheater 23;
the heat storage device 30: a low-temperature heat storage tank 31, a medium-temperature heat storage tank 32, and a high-temperature heat storage tank 33;
the steam turbine 40: a high pressure cylinder 41, a medium and low pressure cylinder 42, a condenser 43 and a deaerator 44.
Detailed Description
In order to make the technical solution of the embodiments of the present invention better understood, the technical solution of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, but not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by a person of ordinary skill in the art without creative efforts shall fall within the protection scope of the embodiments of the present invention.
The terms "comprises" and "comprising," and any variations thereof, in the description and claims of embodiments of the present invention and the above-described drawings, are intended to cover non-exclusive inclusions, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed, but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.
The utility model discloses a core thought does: the multi-heat-source temperature and the multi-heat-transfer-fluid flow are realized by adopting multi-stage heat storage, and the segmented heating of the preheating section, the evaporation section and the overheating section is realized, so that the problems of large temperature difference and large temperature difference in the heat transfer process of the heat transfer fluid and the Rankine cycle working medium are solvedAnd (4) damage problem.
Referring to fig. 5, an embodiment of the present invention provides a solar tower and trough combined power generation system, including: the heat collecting device 10 and the heat exchange device 20;
heat collecting device 10, comprising: a trough concentrator 11 and a tower concentrator 12.
Heat exchange device 20, comprising: a preheater 21, a superheater 22 and a reheater 23, and the preheater 21 or the superheater 22 is also associated with an evaporator function.
The outlet of the heating pipe of the trough collector 11 is connected with the heat transfer fluid inlet of the preheater 21 through a first pipeline; the heat transfer fluid outlet of the preheater 21 is connected with the heating pipe inlet of the trough collector 11 through a second pipeline.
Based on the partial structure, the heat transfer fluid flowing out of the heating pipe of the trough heat collector 11 firstly flows into the preheater 21 through the first pipeline, exchanges heat with the Rankine cycle working medium flowing through the preheater 21, and then enters the heating pipe of the trough heat collector 11 through the second pipeline to absorb heat, so that a first heat transfer fluid circulation loop is formed.
A heating pipe outlet of the tower type heat collector 12 is respectively connected with a heat transfer fluid inlet of the superheater 22 and a heat transfer fluid inlet of the reheater 23 through a third pipeline; the heat transfer fluid outlet of the superheater 22 and the heat transfer fluid outlet of the reheater 23 are respectively connected with the heating pipe inlet of the tower collector 12 through a fourth pipe.
Based on the structure, the heat transfer fluid flowing out of the heating pipe of the tower type heat collector 12 firstly passes through the third pipeline, one part of the heat transfer fluid flows into the superheater 22 to exchange heat with the Rankine cycle working medium flowing through the superheater 22, the other part of the heat transfer fluid flows into the reheater 23 to exchange heat with the Rankine cycle working medium flowing through the reheater 23, and after heat exchange is completed, the heat transfer fluid enters the heating pipe of the tower type heat collector 12 through the fourth pipeline to absorb heat, so that a second heat transfer fluid circulation loop is formed.
In the embodiment, a tower type heat collector 12 and a trough type heat collector 11 are adopted at the same time; wherein, the trough heat collector 11 is used for collecting heat with lower temperature and leading the heat transfer fluid flowing through the heating pipe to have the temperature T1Heating to a temperature T2The heat transfer fluid is used for exchanging heat with Rankine cycle working medium flowing through the preheater 21; the tower heat collector 12 is used for collecting heat with higher temperature and enabling the heat transfer fluid flowing through the heating pipe to have the temperature T2' heating to temperature T3The heat transfer fluid is used to exchange heat with the rankine cycle fluid flowing through the superheater 22.
It should be noted that the design value T of the outlet temperature of the heat transfer fluid of the trough collector2And the design value T of the inlet temperature of the heat transfer fluid of the tower type heat collector2' the two can be equal or unequal, and can be designed according to requirements. When the mass flow of the heat transfer fluid in each heat exchanger is reasonably adjusted, if T is2And T2' equal, a heat transfer curve as shown in FIG. 6 can be obtained, if T is2And T2' unequal results in a heat transfer curve as shown in FIG. 7, and in fact, these two cases are compared at T2And T2Under the unequal condition, the heat exchange temperature difference is smaller, and the heat exchange is realizedThe losses are also smaller.
Therefore, the embodiment can not only enable the tower type heat collector 12 and the trough type heat collector 11 to work in respective optimal working temperature range, which is beneficial to improving the system efficiency, but also improve the field utilization rate of the tower type mirror field and reduce the system cost due to the addition of the trough type heat collector 11. Moreover, the sectional heating of the preheating section, the evaporation section and the overheating section of the heat exchange part is realized; based on this staged heating approach, the mass flow rates of the heat transfer fluid in the respective heat exchangers (preheater 21, superheater 22, reheater 23) (as indicated by q1, q2, q3 in fig. 5) can be adjusted as needed.
Further, through the mass flow of heat transfer fluid in each heat exchanger of reasonable regulation, as shown in fig. 6 and 7 the embodiment of the utility model provides a with the contrast sketch map of heat transfer of current traditional scheme, all can reduce the heat transfer difference in temperature of each heat exchanger, reduce heat transfer process' sAnd the power generation efficiency of the power plant is improved. At the same time, a reasonable temperature of the heat transfer fluid can be selected to reduce the heat exchange process in the reheater 23And (4) loss.
In practical application, the heat transfer fluid temperatures at the heat transfer fluid inlet and the heat transfer fluid outlet of each heat exchanger can be preset according to actual requirements, so as to adjust the flow quality of the heat transfer fluid of each heat exchanger (if the slope of the heat transfer fluid curve in the current heat exchanger needs to be increased, the mass flow of the heat transfer fluid of the corresponding part is reduced, otherwise, the mass flow of the heat transfer fluid is increased), so as to reduce the heat exchange temperature difference of each heat exchanger and reduce the heat exchange temperature difference of each heat exchanger in the heat exchange processThe purpose of the damage is achieved.
It is noted that the Rankine cycle working medium can be water, and other media such as CO can be selected2Organic working media and the like; the heat transfer fluid may be synthetic oil, molten salt, air, or the like, and is not particularly limited.
In addition, the power generation system of the present embodiment may further include a heat storage device 30, and the heat storage device 30 includes: a low temperature heat storage tank 31, a medium temperature heat storage tank 32, and a high temperature heat storage tank 33.
Wherein the low temperature heat storage tank 31 includes an inlet and an outlet, the inlet is connected to the second pipe through the first valve, and the outlet is connected to the second pipe through the second valve, for storing the low temperature heat transfer fluid.
The high temperature heat storage tank 33 includes an inlet connected to the third pipe through a third valve and an outlet connected to the third pipe through a fourth valve for storing the heat transfer fluid at a high temperature.
The medium temperature heat storage tank 32 comprises two inlets and two outlets, wherein a first inlet of the medium temperature heat storage tank is connected with the first pipeline through a fifth valve, and a first outlet of the medium temperature heat storage tank is connected with the first pipeline through a sixth valve; the second inlet of the heat exchanger is connected with the fourth pipeline through a fifth valve, and the second outlet of the heat exchanger is connected with the fourth pipeline through a sixth valve, so that the heat exchanger is used for storing medium-temperature heat transfer fluid.
The application of the low-temperature heat storage tank 31, the medium-temperature heat storage tank 32 and the high-temperature heat storage tank 33 realizes three-stage heat storage, can realize automatic matching of the mass flow of the heat transfer fluid in the tower type heat collector 12 and the trough type heat collector 11, and is favorable for flexibly adjusting the mass flow of the heat transfer fluid flowing through each heat exchanger.
In addition, in the embodiment, the medium-temperature heat storage tank 32 can be used for buffering the heat transfer fluid, adjusting the flow rate of the heat transfer fluid, stabilizing the heat exchange temperature and flow rate in the heat exchanger, and facilitating the stable power generation of the system; the trough heat collector 11 is used for collecting medium-temperature heat transfer fluid, and a low-cost technology is provided for starting a system and performing heat preservation and condensation prevention.
As shown in fig. 5, the power generation system of the present embodiment further includes a steam turbine 40, and the steam turbine 40 includes a high pressure cylinder 41 and a medium pressure cylinder 42.
Wherein, the working medium outlet of the superheater 22 is connected with the working medium inlet of the high-pressure cylinder 41; a working medium outlet of the high-pressure cylinder 41 is connected with a working medium inlet of the reheater 23; the working medium outlet of the reheater 23 is connected with the working medium inlet of the medium and low pressure cylinder 42; a first working medium outlet of the medium and low pressure cylinder 42 is connected with an inlet of the deaerator 44, and a second working medium outlet of the medium and low pressure cylinder 42 is connected with an inlet of the deaerator 44 through the condenser 43; the outlet of the deaerator 44 is connected with the working medium inlet of the preheater 21, and the working medium outlet of the preheater 21 is connected with the working medium inlet of the superheater 22.
It should be noted that, the high pressure cylinder and the medium and low pressure cylinder may have steam extraction for heating the water supply and the deaerator, but for the sake of simplicity of description of the embodiment of the present invention, the steam extraction port for heating the water supply is not shown in the schematic diagram provided in fig. 5. In fact, the high pressure cylinder and the medium and low pressure cylinder may have more other steam extraction outlets, and the utility model discloses do not make the restriction.
The cycle process of the Rankine cycle working medium comprises the following steps: the Rankine cycle working medium which is preheated and is steam enters the superheater 22 to be heated into superheated steam, the superheated steam works in the high-pressure cylinder 41 of the steam turbine 40 to form low-pressure and low-temperature steam and enters the reheater 23, the reheater 23 reheats the part of steam into high-temperature steam, the high-temperature steam enters the medium-low pressure cylinder 42 of the steam turbine 40 to continue to work, one part of the high-temperature steam directly enters the deaerator 44, and the other part of the high-temperature steam enters the condenser 43 to be condensed into liquid and then enters the deaerator 44; after being deoxidized by the deaerator 44, the waste heat enters the preheater 21 for preheating, vaporization and evaporation, and then enters the superheater 22, so that a circulation loop of Rankine cycle working medium is formed.
It should be noted that the cycle-side structure of the rankine cycle working medium (including the internal connection structure of the heat exchange device 20 and the steam turbine 40) is not limited to the structure shown in fig. 5, and can be flexibly adjusted according to actual conditions, and is not particularly limited.
To sum up, the embodiment of the utility model provides an applied the heat collector and the tertiary heat-retaining of two kinds of different grade types, can realize carrying out the optimization strategy of real-time control to heat storage volume, heat transfer fluid flow, system operation mode etc. and improved the stability and the flexibility of system.
Example two
Referring to fig. 8, an embodiment of the present invention provides another solar tower and trough combined power generation system, including: the heat collecting device 10, the heat storage device 30 and the heat exchange device 20.
Heat collecting device 10, comprising: a trough concentrator 11 and a tower concentrator 12.
The heat storage device 30 includes: a low temperature heat storage tank 31, a medium temperature heat storage tank 32, and a high temperature heat storage tank 33. The low-temperature heat storage tank 31 and the high-temperature heat storage tank 33 both include an inlet and an outlet, and the medium-temperature heat storage tank 32 includes two inlets and two outlets.
Heat exchange device 20, comprising: a preheater 21, a superheater 22 and a reheater 23, and the preheater 21 or the superheater 22 is also associated with an evaporator function.
The outlet of the heating pipe of the trough collector 11 is connected with the first inlet of the medium temperature heat storage tank 32 through a first pipeline; a first outlet of the medium temperature heat storage tank 32 is connected with a heat transfer fluid inlet of the preheater 21 through a second pipeline; a heat transfer fluid outlet of the preheater 21 is connected with an inlet of the low-temperature heat storage tank 31 through a third pipeline; an outlet of the low-temperature heat storage tank 31 is connected with an inlet of a heating pipe of the trough collector 11 through a fourth pipeline.
The outlet of the heating pipe of the tower type heat collector 12 is connected with the inlet of the high-temperature heat storage tank 33 through a fifth pipeline; an outlet of the high-temperature heat storage tank 33 is connected with a heat transfer fluid inlet of the superheater 22 and a heat transfer fluid inlet of the reheater 23 through a sixth pipeline; a heat transfer fluid outlet of the superheater 22 and a heat transfer fluid outlet of the reheater 23 are respectively connected with a second inlet of the medium temperature heat storage tank 32 through seventh pipelines; a second outlet of the medium temperature heat storage tank 32 is connected with an inlet of the heating pipe of the tower type heat collector 12 through an eighth pipeline.
The difference from the first embodiment is that each heat storage tank in the second embodiment completely serves as a buffer device between the heat collecting device 10 and the heat exchanging device 20. However, the second embodiment also realizes two heat transfer fluid circulation loops to realize the segmented heating of the rankine cycle working medium, and the realization principle is the same as that of the first embodiment, and is not described herein again.
The above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; although the present invention has been described in detail with reference to the foregoing embodiments, it should be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; such modifications and substitutions do not depart from the spirit and scope of the present invention in its corresponding aspects.

Claims (9)

1. A solar cell cogeneration system, comprising: the heat collecting device and the heat exchange device;
the heat collecting device comprises: trough collectors and tower collectors;
the heat exchange device comprises: the system comprises a preheater, a superheater and a reheater, wherein the preheater or the superheater is also combined with an evaporator;
the outlet of the heating pipe of the trough type heat collector is connected with the heat transfer fluid inlet of the preheater through a first pipeline; the heat transfer fluid outlet of the preheater is connected with the heating pipe inlet of the trough type heat collector through a second pipeline;
a heating pipe outlet of the tower type heat collector is respectively connected with a heat transfer fluid inlet of the superheater and a heat transfer fluid inlet of the reheater through a third pipeline; and a heat transfer fluid outlet of the superheater and a heat transfer fluid outlet of the reheater are respectively connected with a heating pipe inlet of the tower type heat collector through a fourth pipeline.
2. The solar cell unified power generation system of claim 1, further comprising a heat storage device;
the heat storage device includes: the low-temperature heat storage tank, the medium-temperature heat storage tank and the high-temperature heat storage tank;
an inlet of the low-temperature heat storage tank is connected with the second pipeline through a first valve, and an outlet of the low-temperature heat storage tank is connected with the second pipeline through a second valve;
an inlet of the high-temperature heat storage tank is connected with the third pipeline through a third valve, and an outlet of the high-temperature heat storage tank is connected with the third pipeline through a fourth valve;
the first inlet of the medium-temperature heat storage tank is connected with the first pipeline through a fifth valve; a first outlet of the medium-temperature heat storage tank is connected with the first pipeline through a sixth valve; a second inlet of the medium-temperature heat storage tank is connected with the fourth pipeline through a fifth valve; and a second outlet of the medium-temperature heat storage tank is connected with the fourth pipeline through a sixth valve.
3. The solar cell combined power system of claim 1 or 2, further comprising a steam turbine, the steam turbine comprising a high pressure cylinder and a medium to low pressure cylinder;
a working medium outlet of the superheater is connected with a working medium inlet of the high-pressure cylinder;
a working medium outlet of the high-pressure cylinder is connected with a working medium inlet of the reheater;
a working medium outlet of the reheater is connected with a working medium inlet of the medium-low pressure cylinder;
a first working medium outlet of the medium and low pressure cylinder is connected with an inlet of a deaerator, and a second working medium outlet of the medium and low pressure cylinder is connected with an inlet of the deaerator through a condenser;
the outlet of the deaerator is connected with the working medium inlet of the preheater,
and the working medium outlet of the preheater is connected with the working medium inlet of the superheater.
4. The solar tower and trough combined power generation system of claim 1 or 2, wherein the design value of the heat transfer fluid outlet temperature of the trough collector is not equal to the design value of the heat transfer fluid inlet temperature of the tower collector.
5. The solar cell unified power generation system according to claim 1, wherein the heat transfer fluid flowing through said heat collection means and said heat exchange means comprises: synthetic oil, molten salt, or air; rankine cycle working medium flowing through the heat exchange device comprises: water, CO2Or an organic working substance.
6. A solar cell cogeneration system, comprising: the heat collecting device, the heat storage device and the heat exchange device;
the heat collecting device comprises: trough collectors and tower collectors;
the heat storage device includes: the low-temperature heat storage tank, the medium-temperature heat storage tank and the high-temperature heat storage tank;
the heat exchange device comprises: the system comprises a preheater, a superheater and a reheater, wherein the preheater or the superheater is also combined with an evaporator;
an outlet of a heating pipe of the trough type heat collector is connected with a first inlet of the medium-temperature heat storage tank through a first pipeline; the first outlet of the medium-temperature heat storage tank is connected with the heat transfer fluid inlet of the preheater through a second pipeline; the heat transfer fluid outlet of the preheater is connected with the inlet of the low-temperature heat storage tank through a third pipeline; an outlet of the low-temperature heat storage tank is connected with an inlet of a heating pipe of the trough type heat collector through a fourth pipeline;
an outlet of a heating pipe of the tower type heat collector is connected with an inlet of the high-temperature heat storage tank through a fifth pipeline; an outlet of the high-temperature heat storage tank is respectively connected with a heat transfer fluid inlet of the superheater and a heat transfer fluid inlet of the reheater through a sixth pipeline; a heat transfer fluid outlet of the superheater and a heat transfer fluid outlet of the reheater are respectively connected with a second inlet of the medium-temperature heat storage tank through a seventh pipeline; and a second outlet of the medium-temperature heat storage tank is connected with an inlet of a heating pipe of the tower type heat collector through an eighth pipeline.
7. The solar cell combined power system of claim 6, further comprising a steam turbine, said steam turbine including a high pressure cylinder and a medium to low pressure cylinder;
a working medium outlet of the superheater is connected with a working medium inlet of the high-pressure cylinder;
a working medium outlet of the high-pressure cylinder is connected with a working medium inlet of the reheater;
a working medium outlet of the reheater is connected with a working medium inlet of the medium-low pressure cylinder;
a first working medium outlet of the medium and low pressure cylinder is connected with an inlet of a deaerator, and a second working medium outlet of the medium and low pressure cylinder is connected with an inlet of the deaerator through a condenser;
the outlet of the deaerator is connected with the working medium inlet of the preheater;
and the working medium outlet of the preheater is connected with the working medium inlet of the superheater.
8. The solar tower and trough cogeneration system of claim 6, wherein the design heat transfer fluid outlet temperature of said trough collector is not equal to the design heat transfer fluid inlet temperature of said tower collector.
9. The solar cell combined power generation system of claim 6, wherein the heat transfer fluid flowing through the heat collection device and the heat exchange device comprises: synthetic oil, molten salt, or air; rankine cycle working medium flowing through the heat exchange device comprises: water, CO2Or an organic working substance.
CN202020257742.3U 2020-03-05 2020-03-05 Solar tower trough combined power generation system Active CN211950757U (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021174862A1 (en) * 2020-03-05 2021-09-10 广东海洋大学 Solar tower and trough combined power generation system

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021174862A1 (en) * 2020-03-05 2021-09-10 广东海洋大学 Solar tower and trough combined power generation system

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