CN204438288U - A kind of steam power plant cold source energy reclaims heating system - Google Patents
A kind of steam power plant cold source energy reclaims heating system Download PDFInfo
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Abstract
The utility model relates to steam power plant's cold source energy and reclaims field, specifically a kind of steam power plant cold source energy reclaims heating system, comprise steam turbine, condenser, first-degree heating network, secondary heat networks and cooling tower pipeline, wherein steam turbine is connected with described condenser, described condenser is connected with cooling tower pipeline with separate and switchable first-degree heating network, the one-level supply channel of described first-degree heating network is provided with heat supply initial station heater, recirculated water in first-degree heating network is once heated by described condenser, by described heat supply initial station heater post bake, secondary heat networks is provided with secondary heat exchange station, secondary heat exchange station effect described in circulating water temperature in the one-level water return pipeline of described first-degree heating network maintains optimal temperature of return water, the condensing water temperature of condenser is by maintaining normal level with the heat exchange of one-level water return pipeline.The utility model effectively can reclaim steam power plant's cold source energy for central heating, effectively eliminates various potential safety hazard simultaneously.
Description
Technical field
The utility model relates to steam power plant's cold source energy and reclaims field, and specifically a kind of steam power plant cold source energy reclaims heating system.
Background technology
China adopts cogeneration of heat and power central heating pattern to City Building heating from the sixties in last century, adopts cogeneration of heat and power technology to raising energy utilization rate, improves city environmental quality, provides amenities for the people etc. all to serve very important effect.
Cogeneration of heat and power is the successful model that thermal energy step utilizes, it utilizes high level heat to generate electricity, utilize relative Lowlevel thermal energy heat supply, the energy utilization rate in general pure condensate formula power plant is below 40%, and the power plant capacity usage ratio of cogeneration of heat and power can reach 60%, however, the low grade heat energy more than 30% is still had to be lost to air from cooling tower, this is cold source energy, in order to reclaim this cold source energy of 30% as far as possible, people are directly used for reclaiming cold source energy for resident's heating by adopting the cooling water of condenser not go up cooling tower, generally set up peak load calorifier in the outlet of condenser in prior art, by consuming a certain amount of low-pressure pumping steam of steam turbine, make peak load calorifier that the supply water temperature of recirculated water is promoted to 80 ~ 90 DEG C from 60 ~ 70 DEG C, but also make the return water temperature of recirculated water raise so simultaneously, even if having adjusted the flow of pumps for hot water supply net, the return water temperature of recirculated water also rises to 55 ~ 65 DEG C by 45 ~ 55 DEG C, similar with too high supply water temperature, too high heat supply network return water temperature is also serious potential safety hazard to steam turbine and condenser.
In addition, along with the continuous expansion in city, clean energy resource is short all the more, have also appeared in recent years and utilize heat pump techniques that the low grade heat energy of the cooling water of power plant is risen to high-grade heat energy to realize heat supply, reach the object of UTILIZATION OF VESIDUAL HEAT IN, this technical know-how is correct, also Multi-instance is had in reality, unfortunately its investment is large only, and economically see that its cost performance is unsuitable, enterprise pays much larger than income.
Utility model content
The purpose of this utility model is to provide a kind of steam power plant cold source energy to reclaim heating system, effectively reclaims steam power plant's cold source energy and is used for central heating, effectively eliminate various potential safety hazard simultaneously.
The purpose of this utility model is achieved through the following technical solutions:
A kind of steam power plant cold source energy reclaims heating system, it is characterized in that: comprise steam turbine, condenser, first-degree heating network, secondary heat networks and cooling tower pipeline, wherein the low pressure (LP) cylinder exhaust steam end of steam turbine is connected by the admission end of pipeline with described condenser, described condenser is connected with cooling tower pipeline with separate and switchable first-degree heating network, the one-level supply channel of described first-degree heating network is provided with heat supply initial station heater, recirculated water in first-degree heating network is once heated by described condenser, by described heat supply initial station heater post bake, secondary heat networks is provided with secondary heat exchange station, recirculated water in secondary heat networks is by described secondary heat exchange station and described first-degree heating network heat exchange, circulating water temperature in the one-level water return pipeline of described first-degree heating network maintains optimal temperature of return water by the effect of described secondary heat exchange station, described one-level water return pipeline is provided with heat exchanger, the condensing water temperature of condenser maintains normal level by described heat exchanger and the heat exchange of one-level water return pipeline.
It is 20 ~ 28KPa that described steam turbine exports back pressure, described steam turbine when summer not more exchanging rotor peak power be greater than 240MW.
Low pressure rotor in the low pressure (LP) cylinder of described steam turbine is 4 grades, and is 500 ~ 750mm as the movable vane of the new final stage rotor of the 4th grade and stator blade height, above described new final stage rotor, be provided with guide ring.
Described condenser bottom is provided with multiple rigid foundation, and the top of each rigid foundation is equipped with the expansion joint be connected with the low pressure (LP) cylinder of steam turbine.
Described expansion joint VCP amount is greater than 20mm, and level compensating amount is greater than 5mm.
One group of heat-exchange unit is set up in described secondary heat exchange station, or set up a branch road be connected with the one-level water return pipeline of first-degree heating network by the secondary water return pipeline of secondary heat networks, or while setting up one group of heat-exchange unit, set up a branch road be connected with the one-level water return pipeline of first-degree heating network by the secondary water return pipeline of secondary heat networks.
The optimal temperature of return water of described one-level water return pipeline is 38 ~ 42 DEG C; Condensing water temperature during normal level is below 49 DEG C.
Described cooling tower pipeline is provided with cooling tower, and the recirculated water output of described cooling tower and the pipeline cooled back between water end (W.E.) of condenser are provided with water circulating pump.
Described one-level supply channel is provided with pumps for hot water supply net, and the pipeline between the condensate water water side of described condenser and heat exchanger is provided with solidifying pump.
Described heat supply initial station heater is connected with steam turbine by bleed steam pipework.
Advantage of the present utility model and good effect are:
1, the utility model improves back pressure and exhaust temperature by the last two-stage rotor retrofit of steam turbine low pressure (LP) cylinder, the impact on unit generation ability in summer is reduced while reclaiming residual heat of electric power plant as far as possible, the utility model can realize switching between cooling tower pipeline and first-degree heating network simultaneously, during heat supply in winter, first-degree heating network runs, other non-heating period cooling tower pipelines run, and first-degree heating network exits.The utility model control condenser heating time operation back pressure at about 20 ~ 28kPa, ensure steam turbine when summer not more exchanging rotor peak power at more than 240MW.
2, condenser bottom of the present utility model is provided with multiple rigid foundation, each rigid foundation is equipped with expansion joint, can change due to back pressure and steam turbine exhaust temperature the thermal expansion effects brought by effective compensation condenser, ensure steam turbine security of operation.
3, the secondary water return pipeline of secondary heat networks to be connected with the one-level water return pipeline of first-degree heating network the optimal temperature of return water realizing the temperature of one-level water return pipeline to maintain 38 ~ 42 DEG C by setting up one group of heat-exchange unit at secondary heat exchange station or setting up a branch road by the utility model, ensures that power plant steam turbine and condenser normally run.
4, the utility model is provided with heat exchanger on one-level water return pipeline, the condensate water water side of condenser is connected with described heat exchanger by pipeline, and pass through the condensate water heat exchange of one-level water return pipeline and condenser, make the condensate water that temperature raises because condenser high back pressure runs again return to normal level temperature, ensure follow-up condensed water precision processing system and the security of operation of gland-sealing cooler.
Accompanying drawing explanation
Fig. 1 is structural representation of the present utility model,
Fig. 2 is the low pressure rotor structural representation of steam turbine of the prior art,
Fig. 3 is the low pressure rotor structural representation of steam turbine of the present utility model,
Fig. 4 is condenser scheme of installation of the prior art,
Fig. 5 is condenser scheme of installation of the present utility model,
Fig. 6 is the condenser mounting structure front view in Fig. 5,
Fig. 7 is A-A view in Fig. 6,
Fig. 8 is the secondary heat exchange station schematic diagram of prior art,
Fig. 9 is a kind of structural representation at secondary heat exchange station of the present utility model,
Figure 10 is the another kind of structural representation at secondary heat exchange station of the present utility model,
Figure 11 is another structural representation at secondary heat exchange station of the present utility model.
Wherein, 1 is steam turbine, 2 is pumps for hot water supply net, 3 is condenser, 4 is cooling tower, 5 is water circulating pump, 6 is solidifying pump, 7 is heat exchanger, 8 is gland-sealing cooler, 9 is one-level water return pipeline, 10 is heat supply initial station heater, 11 is one-level supply channel, 12 is secondary heat exchange station, 13 is heating housing estate, 14 is guide ring, 15 is new final stage rotor, 16 is expansion joint, 17 is admission end, 18 is heat supply network water side, 19 is heat supply network backwater end, 20 is cooling water outlet end, 21 for cooling back water end (W.E.), 22 is condensate water water side, 23 bleed steam pipeworks, 24 is original final stage rotor, 25 is elastic foundation, 26 is rigid foundation, 27 is the portion of being rigidly connected, 28 is heat-exchange unit, 29 is branch road, 25 is secondary water return pipeline.
Detailed description of the invention
Below in conjunction with accompanying drawing, the utility model is described in further detail.
As shown in Figure 1, the utility model comprises steam turbine 1, condenser 3, first-degree heating network, secondary heat networks and cooling tower pipeline, wherein condenser 3 is provided with multiple port, comprise admission end 17, heat supply network water side 18, heat supply network backwater end 19, cooling water outlet end 20, cool back water end (W.E.) 21 and condensate water water side 22, the low pressure (LP) cylinder exhaust steam end of described steam turbine 1 is connected by the admission end 17 of pipeline with described condenser 3, described condenser 3 is connected with cooling tower pipeline with first-degree heating network respectively, wherein the heat supply network water side 18 of condenser 3 is connected with the one-level supply channel 11 of first-degree heating network, the one-level water return pipeline 9 of first-degree heating network is connected with the heat supply network backwater end 19 of condenser 3, recirculated water in first-degree heating network completes first time heating by the low pressure (LP) cylinder exhausted spare heat absorbing steam turbine 1 when condenser 3, described one-level supply channel 11 is provided with pumps for hot water supply net 2 and heat supply initial station heater 10 successively, recirculated water in first-degree heating network is driven by pumps for hot water supply net 2 and circulates and regulate flow velocity, recirculated water in first-degree heating network completes post bake by described heat supply initial station heater 10, described heat supply initial station heater 10 is connected with steam turbine 1 by bleed steam pipework 23, the heating that namely heating steam in the heater 10 of described heat supply initial station derive from steam turbine 1 is drawn gas.Secondary heat networks is provided with secondary heat exchange station 12, the one-level supply channel 11 of described first-degree heating network is all connected with described secondary heat exchange station 12 with one-level water return pipeline 9, recirculated water in secondary heat networks completes heating by the heat absorbing first-degree heating network recirculated water when secondary heat exchange station 12, and heats to each heating housing estate 13 by pipeline.Cooling tower pipeline is provided with cooling tower 4, cooling water outlet end 20 on condenser 3 is connected by the recirculated water input of pipeline with described cooling tower 4, the recirculated water output of described cooling tower 4 is connected with the water end (W.E.) 21 that cools back on condenser 3 by pipeline, the pipeline cooling back between water end (W.E.) 21 of the recirculated water output of cooling tower 4 and condenser 3 is provided with and drives recirculated water and the water circulating pump 5 regulating flow velocity.
Steam turbine 1 in the utility model, for power plants generating electricity burden requirement, improves unit back pressuce by carrying out redesign to the last two-stage flow passage component of low pressure rotor, reduces the impact on unit generation ability in summer while reclaiming residual heat of electric power plant as far as possible.
As shown in Figure 2, original low pressure (LP) cylinder rotor is 5 grades, wherein the 5th grade blade is original final stage rotor 24, as shown in Figure 3, low pressure rotor in the utility model is 4 grades, wherein the structure of first 3 grades remains unchanged, original final stage rotor 24 is removed together with L O section, install guide ring 14 additional in L O section position simultaneously, guarantee steam passage is smooth, reduce the loss of inter-stage vapor flow, the 4th grade of rotor originally becomes new final stage rotor 15, the 4th grade of rotor height is originally 1000mm, after original final stage rotor 24 is removed, movable vane and the stator blade altitude range of new final stage rotor 15 become 500 ~ 750mm, concrete height needs design according to actual back pressure, the hub portion of new final stage rotor 15 is constant, by the moving vane blade root of original 1000mm height and stator blade groove according to moving vane blade root and the stator blade dividing plate of joining 500 ~ 750mm height.The back pressure of original steam turbine 1 is 16KPa, exhaust temperature is 55.7 DEG C, steam turbine power output is 330134kW (330MW), after redesigning, when every steam inlet condition is identical, the back pressure of the steam turbine 1 in the present embodiment is 26KPa, exhaust temperature is 66.5 DEG C, steam turbine power output is 260654kW (261MW), it is less on power output impact while back pressure and exhaust temperature improve, both high back pressure heating requirement in winter had been met, when normally running summer, if when unit is without large load (more than 300MW), on economy also without impact.
The utility model controls by control system the switching that the keying of condenser 3 inner valve and start and stop water circulating pump 5 and pumps for hot water supply net 2 realize cooling tower pipeline and first-degree heating network, and this is techniques well known.As shown in Figure 1, when steam turbine 1 is in the heating operating mode of high back pressure, described cooling tower pipeline is out of service, first-degree heating network brings into operation and the low pressure (LP) cylinder exhausted spare heat absorbing steam turbine 1 in condenser 3 completes heat exchange, in the present embodiment, the back pressure of condenser 3 rises to 26kPa by about 4.9kPa, namely the low pressure (LP) cylinder exhaust temperature of steam turbine 1 rises to 66.5 DEG C (saturation temperatures that back pressure is corresponding) by 30 ~ 40 DEG C, reach the object reclaiming residual heat of electric power plant as far as possible, when steam turbine 1 runs in non-heating period pure condensate operating mode, first-degree heating network is out of service, described cooling tower pipeline reruns, now the back pressure of condenser 3 returns to 4.9kPa level, because condenser 3 is changed greatly by the back pressure of bearing in non-heating period pure condensate change working to the process of heating operating mode and exhaust temperature, wherein condenser 3 bulk temperature is increased to about 66.5 DEG C, about 77 DEG C can be risen to time the highest, therefore condenser 3 all there will be thermal expansion effects at vertical direction and horizontal direction, the vertical direction of the condenser 3 in the present embodiment can increase the height of about 2 ~ 4.5mm, the one-sided swell increment of horizontal direction is between 1.2mm ~ 2mm, as shown in Figure 4, condenser 3 mounting structure of the prior art is that bottom is provided with elastic foundation 25, described elastic foundation 25 comprises many springs, top is provided with the portion that is rigidly connected 27 be connected with the low pressure (LP) cylinder of steam turbine 1, if condenser 3 still adopts mounting structure of the prior art, the spring on lower elastic basis 25 can be compressed the upper top power of the low pressure (LP) cylinder that can produce steam turbine 1, because the low pressure (LP) cylinder bearing in steam turbine 1 is non-floor bearing, the thrust that condenser after thermal expansion 3 pairs of low pressure (LP) cylinders produce will cause rotor absolute altitude to change, and then cause shafting vibration, therefore very big potential safety hazard can be there is, need to redesign the mounting structure of condenser 3.
These are as shown in Fig. 5 ~ 7, condenser 3 bottom of the present utility model is provided with multiple rigid foundation 26, the cross section of each rigid foundation 26 is L-type and top is equipped with expansion joint 16, described expansion joint 16 is expansion joint, expansion joint is techniques well known, expansion joint 16 VCP amount in the present embodiment is greater than 20mm, and level compensating amount is greater than 5mm.
When steam turbine 1 is in the heating operating mode of high back pressure, low pressure (LP) cylinder exhaust temperature rises to 66.5 DEG C by 30 ~ 40 DEG C, recirculated water in one-level supply channel 11 is after condenser 3 and heat supply initial station heater 10 heat, temperature reaches 90 ~ 95 DEG C, meets the heating requirement of each heating housing estate 13.As shown in Figure 8, the secondary heat exchange station 12 of prior art adopts two groups of heat-exchange unit 28, if still adopt the secondary heat exchange station 12 of prior art, circulating water temperature in one-level water return pipeline 9 also can raise after the heat exchange of secondary heat exchange station 12, in the present embodiment, the circulating water temperature of one-level water return pipeline 9 can be increased to 55 ~ 60 DEG C, too high first-degree heating network return water temperature forms serious potential safety hazard to steam turbine 1 and condenser 3, need redesign secondary heat exchange station 12, one-level return water temperature is made to maintain optimal temperature of return water, described optimal temperature of return water is 38 ~ 42 DEG C.
The utility model is by setting up one group of heat-exchange unit 28 at secondary heat exchange station 12, or set up a branch road 29 the secondary water return pipeline 30 of secondary heat networks is connected with the one-level water return pipeline 9 of first-degree heating network realizes one-level water return pipeline 9 temperature to be down to optimal temperature of return water, or the secondary heat networks side backwater end of the heat-exchange unit 28 of the radiator in secondary heat exchange station 12 is directly connected for water end (W.E.) with the secondary heat networks side of the heat-exchange unit 28 of underground heat realizes one-level water return pipeline 9 temperature to be down to optimal temperature of return water.
When secondary heat networks is all underground heat, the actual supply and return water temperature of first-degree heating network is in such cases: first latter stage 60 DEG C/36 DEG C, and the spike phase 90 DEG C/55 DEG C, the actual supply and return water temperature of secondary heat networks is: the coldest 42 DEG C/35 DEG C; 35 ~ 37 DEG C at ordinary times/28 ~ 32 DEG C.As shown in Figure 9, in this case the needs parallel connection of 12, secondary heat exchange station increases by one group of heat-exchange unit 28, the confession degree of rising again of spike phase is become 90 DEG C/40 DEG C, the flow and lift simultaneously adjusting circulating pump meets new working condition requirement, or while increase by one group of heat-exchange unit 28, as shown in figure 11, set up a branch road 29 the secondary water return pipeline 30 of secondary heat networks is connected with the one-level water return pipeline 9 of first-degree heating network one-level water return pipeline 9 temperature is down to optimal temperature of return water.
When secondary heat networks is all radiator, the actual supply and return water temperature of first-degree heating network is in such cases: first latter stage 60 DEG C/36 DEG C, and the spike phase 90 DEG C/55 DEG C, the actual supply and return water temperature of secondary heat networks is: the coldest 55 DEG C/43 DEG C; 46 ~ 49 DEG C at ordinary times/35 ~ 38 DEG C.As shown in Figure 10, in this case set up a branch road 29 in secondary heat exchange station 12 the secondary water return pipeline 30 of secondary heat networks is connected with the one-level water return pipeline 9 of first-degree heating network, the backwater of a part of secondary heat networks is made to enter in first-degree heating network, make the return water temperature of first-degree heating network reach optimal temperature of return water, whether the flow and lift simultaneously adjusting heat exchanger and circulating pump meets new working condition requirement.
When secondary heat networks is mixed by radiator and underground heat, and when the ratio of underground heat is more than 70%, the actual supply and return water temperature of first-degree heating network is in such cases: first latter stage 60 DEG C/36 DEG C, and the spike phase 90 DEG C/55 DEG C, the actual supply and return water temperature of secondary heat networks radiator is: the coldest 55 DEG C/43 DEG C; 46 ~ 49 DEG C at ordinary times/35 ~ 38 DEG C, the actual supply and return water temperature of secondary heat networks underground heat is: the coldest 42 DEG C/35 DEG C; 35 ~ 37 DEG C at ordinary times/28 ~ 32 DEG C.Secondary heat exchange station 12 increases a set of heat-exchange unit 28 in such cases, and the backwater of the first-degree heating network side of the heat-exchange unit 28 of radiator supplies water as the heat-exchange unit 28 first-degree heating network side of underground heat and enters, by heat exchange again, the return water temperature of first-degree heating network is down to optimal temperature of return water.
When secondary heat networks is mixed by radiator and underground heat, and when the ratio of underground heat is about 50%, the actual supply and return water temperature of first-degree heating network is in such cases: first latter stage 60 DEG C/36 DEG C, and the spike phase 90 DEG C/55 DEG C, the actual supply and return water temperature of secondary heat networks radiator is: the coldest 55 DEG C/43 DEG C; 46 ~ 49 DEG C at ordinary times/35 ~ 38 DEG C, the actual supply and return water temperature of secondary heat networks underground heat is: the coldest 42 DEG C/35 DEG C; 35 ~ 37 DEG C at ordinary times/28 ~ 32 DEG C.Secondary heat exchange station 12 increases a set of heat-exchange unit 28 in such cases, and the first-degree heating network side water supply of the first-degree heating network side backwater of the heat-exchange unit 28 of radiator as the heat-exchange unit 28 of underground heat is entered, by heat exchange again, the return water temperature of first-degree heating network is down to optimal temperature of return water, directly supplied water as the low temperature side of underground heat by the low temperature side heat supply backwater of the heat-exchange unit 28 of radiator enters secondary heat networks and runs simultaneously.
When condenser 3 high back pressure runs, the condensate water leaving water temperature of the condensate water water side 22 of condenser 3 is 65 DEG C ~ 75 DEG C by raising about 45 during nominal situation DEG C, condensing water temperature raises and all has a negative impact to follow-up condensed water precision processing system and gland-sealing cooler 8, as shown in Figure 1, the utility model is provided with heat exchanger 7 on the one-level water return pipeline 9 of first-degree heating network, described heat exchanger 7 is water-water heat exchanger, the condensate water water side 22 of condenser 3 is connected with described heat exchanger 7 by pipeline, pipeline between condensate water water side 22 and heat exchanger 7 is provided with the solidifying pump 6 driving condensate water to flow, by the one-level water return pipeline 9 of first-degree heating network and the condensate water heat exchange of condenser 3, condensate water maximum temperature is made to be reduced to less than 49 DEG C, do not affect follow-up condensed water precision processing system and gland-sealing cooler 8 normally works.
Operation principle of the present utility model is:
The utility model improves back pressure and exhaust temperature by the last two-stage rotor retrofit of the low pressure (LP) cylinder of steam turbine 1, the impact on unit generation ability in summer is reduced while reclaiming residual heat of electric power plant as far as possible, condenser 3 improves the heat supply temperature of first-degree heating network because back pressure raises, effective guarantee heating, the utility model is by being provided with multiple rigid foundation 26 in condenser 3 bottom simultaneously, each rigid foundation 26 is equipped with the thermal expansion effects that expansion joint 16 carrys out effective compensation condenser 3, ensure the security of operation of steam turbine 1, and the temperature of one-level water return pipeline 9 is maintained optimal temperature of return water by transforming secondary heat exchange station 12 by the utility model, by arranging heat exchanger 7 on one-level water return pipeline 9, the condensate water that temperature raises because condenser 3 high back pressure runs is made again to return to normal level temperature, ensure the security of operation of follow-up condensed water precision processing system and gland-sealing cooler.
Claims (10)
1. steam power plant's cold source energy reclaims heating system, it is characterized in that: comprise steam turbine (1), condenser (3), first-degree heating network, secondary heat networks and cooling tower pipeline, wherein the low pressure (LP) cylinder exhaust steam end of steam turbine (1) is connected with the admission end (17) of described condenser (3) by pipeline, described condenser (3) is connected with cooling tower pipeline with separate and switchable first-degree heating network, the one-level supply channel (11) of described first-degree heating network is provided with heat supply initial station heater (10), recirculated water in first-degree heating network is once heated by described condenser (3), by described heat supply initial station heater (10) post bake, secondary heat networks is provided with secondary heat exchange station (12), recirculated water in secondary heat networks is by described secondary heat exchange station (12) and described first-degree heating network heat exchange, circulating water temperature in the one-level water return pipeline (9) of described first-degree heating network maintains optimal temperature of return water by described secondary heat exchange station (12) effect, described one-level water return pipeline (9) is provided with heat exchanger (7), the condensing water temperature of condenser (3) maintains normal level by described heat exchanger (7) and one-level water return pipeline (9) heat exchange.
2. steam power plant according to claim 1 cold source energy reclaims heating system, it is characterized in that: described steam turbine (1) export back pressure be 20 ~ 28KPa, described steam turbine (1) when summer not more exchanging rotor peak power be greater than 240MW.
3. steam power plant according to claim 1 and 2 cold source energy reclaims heating system, it is characterized in that: the low pressure rotor in the low pressure (LP) cylinder of described steam turbine (1) is 4 grades, and be 500 ~ 750mm as the movable vane of the new final stage rotor (15) of the 4th grade and stator blade height, be provided with guide ring (14) in described new final stage rotor (15) top.
4. steam power plant according to claim 1 cold source energy reclaims heating system, it is characterized in that: described condenser (3) bottom is provided with multiple rigid foundation (26), the top of each rigid foundation (26) is equipped with the expansion joint (16) be connected with the low pressure (LP) cylinder of steam turbine (1).
5. steam power plant according to claim 4 cold source energy reclaims heating system, it is characterized in that: described expansion joint (16) VCP amount is greater than 20mm, and level compensating amount is greater than 5mm.
6. steam power plant according to claim 1 cold source energy reclaims heating system, it is characterized in that: in described secondary heat exchange station (12), set up one group of heat-exchange unit (28), or set up a branch road (29) be connected with the one-level water return pipeline (9) of first-degree heating network by the secondary water return pipeline (30) of secondary heat networks, or while setting up one group of heat-exchange unit (28), set up a branch road (29) be connected with the one-level water return pipeline (9) of first-degree heating network by the secondary water return pipeline (30) of secondary heat networks.
7. steam power plant according to claim 1 cold source energy reclaims heating system, it is characterized in that: the optimal temperature of return water of described one-level water return pipeline (9) is 38 ~ 42 DEG C; Condensing water temperature during normal level is below 49 DEG C.
8. steam power plant according to claim 1 cold source energy reclaims heating system, it is characterized in that: described cooling tower pipeline is provided with cooling tower (4), the recirculated water output of described cooling tower (4) and the pipeline cooled back between water end (W.E.) (21) of condenser (3) are provided with water circulating pump (5).
9. steam power plant according to claim 1 cold source energy reclaims heating system, it is characterized in that: described one-level supply channel (11) is provided with pumps for hot water supply net (2), the pipeline between the condensate water water side (22) of described condenser (3) and heat exchanger (7) is provided with solidifying pump (6).
10. steam power plant according to claim 1 cold source energy reclaims heating system, it is characterized in that: described heat supply initial station heater (10) is connected with steam turbine (1) by bleed steam pipework (23).
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105823110A (en) * | 2015-01-04 | 2016-08-03 | 沈阳扬波科技能源工程有限公司 | Thermal power plant cold source loss recovery heat supply system |
| CN108800976A (en) * | 2018-02-26 | 2018-11-13 | 西安热工研究院有限公司 | A kind of condensed water Water Level Regulating System and method being suitable for double back pressure thermal power plant units |
| CN114992691A (en) * | 2022-05-09 | 2022-09-02 | 杭州科晟能源技术有限公司 | High-efficient heating system |
-
2015
- 2015-01-04 CN CN201520002238.8U patent/CN204438288U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105823110A (en) * | 2015-01-04 | 2016-08-03 | 沈阳扬波科技能源工程有限公司 | Thermal power plant cold source loss recovery heat supply system |
| CN108800976A (en) * | 2018-02-26 | 2018-11-13 | 西安热工研究院有限公司 | A kind of condensed water Water Level Regulating System and method being suitable for double back pressure thermal power plant units |
| CN108800976B (en) * | 2018-02-26 | 2023-08-22 | 西安热工研究院有限公司 | Condensate water level adjusting system and method suitable for double back pressure heat supply unit |
| CN114992691A (en) * | 2022-05-09 | 2022-09-02 | 杭州科晟能源技术有限公司 | High-efficient heating system |
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