CN1536289A - Single-drive solar tracking system - Google Patents
Single-drive solar tracking system Download PDFInfo
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- CN1536289A CN1536289A CNA031094880A CN03109488A CN1536289A CN 1536289 A CN1536289 A CN 1536289A CN A031094880 A CNA031094880 A CN A031094880A CN 03109488 A CN03109488 A CN 03109488A CN 1536289 A CN1536289 A CN 1536289A
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/40—Solar thermal energy, e.g. solar towers
- Y02E10/47—Mountings or tracking
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Abstract
The present invention relates to a single drive sun tracking system. Said system includes fixed supporting frame, automatic angle-turning tracking mechanism, elevation regulating mechanism and time difference regulating mechanism. Said invention utilizes single drive to implement automatic angle-turning tracing, time difference regulation and elevation tracing of sun so as to simplify structure, and adopts standard transmission system equipment to raise its working reliability and applicability.
Description
Invention field
The present invention relates to a kind of single solar tracking system that drives that is mainly used in the helioplant.
Background technology
The sun tracing method that proposes in " sun tracing method and the device " of number of patent application 011241764 is widely used in solar tracking, the sun tracker that proposes is because of adopting two cover driven by servomotor and adopting the two-dimensional tracking that does not wait the tooth pitch gear to realize the sun, manufacturing process is very complicated, only be suitable for and require very accurately two-dimensional tracking, design stressed when being used for bigger system that its is adjusted groove time difference concentrated higher, need to strengthen gear diameter or select material preferably for use, and, there are certain applications only to need one dimension to follow the tracks of in the solar energy practical application, to adjust the groove and the elevation angle time difference and follow the tracks of to combine and be unfavorable for the occasion that needs one dimension to follow the tracks of, these have all improved cost and difficulty of processing relatively; In existing two-dimentional sun tracker or system, generally also be two cover control and driver elements, angle of rotation (hour angle) when following the tracks of too respectively and the elevation angle (declination angle), and it is unrelated, tracking mode mainly relies on sensor or signal picker, and shortcoming is to be subject to the operating accuracy of 16 fens visual angle width of the sun and sensor or signal picker and to environmental stability, tracking accuracy is lower, system reliability is poor, and control is complicated, cost is high.
Summary of the invention
Purpose of the present invention just provides a kind of single solar tracking system that drives, and to simplify drive mechanism, reduces manufacture difficulty, improves the functional reliability of drive mechanism and system controller.
Purpose of the present invention is achieved through the following technical solutions: comprise fixed rack, angle of rotation follower and the time difference regulating mechanism; Described angle of rotation follower comprises main working shaft, reducing gear, servomotor and system controller, the output of system controller connects servomotor, the servomotor output shaft is connected with the input of reducing gear is coaxial, the output of reducing gear is connected with main working shaft is coaxial, main working shaft rotating support is on fixed rack and parallel with the earth's axis, working cycles of angle of rotation follower is that rotated for 1 week 24 hours of mean solar time, and the servo-actuated of Continuous Drive master's working shaft changes in apparent motion on solar day hour angle; Every duration step by step of one of the described angle of rotation follower used step number of circulation be a mean solar day divide exactly the step number duration, adjust main working shaft intermittently, the angular variable when the solar day apparent motion of servo-actuated evenly; Difference regulating mechanism comprises screw rod, time difference adjusting module ring, time difference adjusting lever and the time difference transmission when described, time difference adjusting module ring is flexibly connected by a plurality of time difference adjusting modules and forms, the lateral surface of each time difference adjusting module have along time difference adjusting module anchor ring and with the circular arc thread groove of described screw engages; Have in the interior ring side of described time difference adjusting module ring along the time difference of anchor ring and adjust groove, the time difference on every time difference adjusting module is adjusted the hour angle arc length curve that groove was reflected in solar tracking system the time difference of the mean solar time of should module adjusting time interval and true solar time, it is continuous, closed and unduplicated that the time difference of each time difference adjusting module is adjusted groove, the hour angle arc length curve that the mean solar time in a whole time difference adjustment corresponding tropic year of groove and time difference true solar time are reflected in solar tracking system; Described time difference adjusting lever is fixed on the fixed rack, and its outer end is vertical inserts in the described time difference adjustment groove; The time difference regulating mechanism working cycles be 1 tropic year, screw drive time difference adjusting module ring rotated for 1 week, adjusted the mean solar time in 1 tropic year and the time difference of true solar time continuously; The system controller of described angle of rotation follower, servomotor, reducing gear and the time drive bevel gear of screw rod, time difference adjusting module ring, time difference transmission of difference regulating mechanism and the equal rotating support of driven wheel of differential on moving support, moving support is around main working shaft fine motion, described screw axial be main working shaft radially.
2Z-X type gear with small teeth difference power train or Harmonic Gears system is arranged in the described reducing gear, and the gearratio of reducing gear is more than or equal to 480.
Described reducing gear is made up of with intermeshing worm-and-wheel gear 2Z-XI gear with small teeth difference power train or Harmonic Gears system.
Described servomotor and system controller constitute a complete motion control ring, and system controller is in the angle of the set time of each fixing step duration position control servomotor rotational fixation.
The ridge of described time difference adjusting module ring thread groove add up to 487 with the product of described screw flight line number; Described time difference transmission is made up of intermeshing drive bevel gear and driven wheel of differential, drive bevel gear is connected with main working shaft is coaxial, driven wheel of differential is connected with screw coaxial, gearratio between the driving and driven bevel gear is 0.75, screw rod and the gearratio of adjusting between the ring are 487, and resultant gear ratio is 365.25.
The relative two sides of described time difference adjusting module ring respectively have along anchor ring and with the circular arc thread groove of described screw engages, screw rod is symmetrical arranged two.
Also comprise elevation angle guiding mechanism, it comprise the subtask axle, with the subtask axle be fixed together working face, few tooth difference power train, decide eccentric shaft, an end has the adjusting lever of striding the crack slide block, non-straight trough rail, subtask axle and main working shaft vertical hinge have with main working shaft corresponding gap of also slightly being wider than main working shaft along long to the centre at working face; An internal gear and the described main working shaft of few tooth difference power train are connected, compound planet gear is arranged on to be decided on the eccentric shaft, the outer rim of output inner gear connects an end of adjusting lever, the other end of adjusting lever is striden the crack slide block and is positioned at non-straight trough rail, and non-straight trough rail is divided into two parts and is hinged with an end of working face respectively; Describedly decide eccentric shaft and be fixed on the fixed rack, coaxial with main working shaft; The gearratio of described few tooth difference power train approximates 365; Few tooth difference speed reducing mechanism one-year age in the guiding mechanism of the elevation angle circles, cooperate by the machinery between adjusting lever, non-straight trough rail and the working face, drive working face 1 year positive and negative 23 ° 27 ' scope in circulation adjust once, adjust the working face servo-actuated and change in the declination angle of the sun.
Described few tooth difference transmission is the transmission of 2Z-XI type gear with small teeth difference, and the number of teeth is as follows: Z
1=62, Z2=64, Z
3=57, Z
4=59 or Z
1=57, Z
2=59, Z
3=62, Z
4=64, realize that gearratio is 365.80 or-364.80.
Two outer ends of the non-straight trough rail of described working face one end make progress in the same way or have a down dip, its COEFFICIENT K is 0.033-0.034 to the maximum, the value that plays the two ends COEFFICIENT K of non-straight trough rail from the intermediate point of non-straight trough rail changes between 0 to 0.033-0.034 continuously, Changing Pattern is that near sinusoidal changes, the ratio of the angle that the K value turns in every day actual measurement on the ecliptic for the earth and circumference 360 ° angles poor with the accumulative total between the standard circumference motion calculation angle, through calculating the back is arranged to non-straight trough rail continuously by sinusoidal rule track, constitute the accurate rail groove of non-straight trough rail, each offset point with straight center line apart from computing formula is: K * rail groove mid point is to the path length of subtask axle.
The present invention utilizes single angle of rotation tracking, time difference adjustment and elevation angle of realizing the sun of driving to follow the tracks of, and has simplified structure; The powertrain device of employing standard is carried out the deceleration of big speed ratio, realizes the driving power microminiaturization, has improved functional reliability, has reduced energy resource consumption; Adopt time difference module ring to realize time difference adjustment, reduced manufacture difficulty, saved material, also improved functional reliability.In addition, relatively independent elevation angle follower can separate with main system, and do not influence the angle of rotation follower and the time difference regulating mechanism work, and difference regulating mechanism can be also separable according to circumstances the time, so can carry out different combinations according to different needs, improve applicability.
Description of drawings
Fig. 1 is the whole schematic diagram that constitutes of the present invention.
Fig. 2 is the A-A cutaway view of Fig. 1.
Fig. 3 is the structural representation of working-spindle of the present invention, countershaft and working face, and wherein a figure is the c-c cutaway view of figure b, the vertical view of b figure a figure, the right view of c figure a figure.
Time difference adjusting module ring when Fig. 4 is of the present invention in the difference regulating mechanism and the structural representation of screw rod.
Fig. 5 is the B-B cutaway view of Fig. 4.
Fig. 6 is that module ring shown in Figure 4 launches its inboard structural representation of back.
Fig. 7 is the deviation curve figure of mean solar time in tropic year and true solar time.
The specific embodiment
Referring to Fig. 1-Fig. 7, comprise fixed rack 17, angle of rotation follower, the time difference regulating mechanism and elevation angle guiding mechanism.Described angle of rotation follower comprises main working shaft 11, reducing gear 2, servomotor 4 and system controller 3, the output of system controller 3 connects servomotor 4, servomotor 4 output shafts are connected with the input of reducing gear 2 is coaxial, the output of reducing gear 2 and main 11 coaxial connections of working shaft, main working shaft 11 rotating supports are on fixed rack 17 and parallel with the earth's axis, working cycles of angle of rotation follower is that rotated for 1 week 24 hours of mean solar time, and 11 servo-actuateds of Continuous Drive master's working shaft change in apparent motion on solar day hour angle.
Difference regulating mechanism is by screw rod 19 when described, time difference adjusting module ring 9, time difference adjusting lever 20 and time difference transmission constitute, described time difference transmission is made up of intermeshing drive bevel gear 7 and driven wheel of differential 8, initiatively tie up gear 7 and main 11 coaxial connections of working shaft, driven wheel of differential 8 and 19 coaxial connections of screw rod, main, gearratio between the driven wheel of differential is 0.75, gearratio between screw rod 19 and the adjusting module ring 9 is 487, time difference adjusting module ring 9 is flexibly connected by a plurality of time difference adjusting modules 91 and forms, the lateral surface of each time difference adjusting module 91 have along time difference adjusting module anchor ring and with the circular arc thread groove 92 of described screw rod 19 engagements, the ridge of this thread groove add up to 487 with the product of described screw rod 19 numbers of leads.Module ring 9 places in the guide groove 93 of an annular, drives module 91 and move along guide groove 93 circulations when screw rod 19 rotates.(referring to Fig. 4,5).
Have in the interior ring side of described time difference adjusting module ring 9 along the time difference of anchor ring and adjust groove 94, the time difference on every time difference adjusting module 91 is adjusted 94 pairs of grooves and should module adjust the hour angle arc length curve that the time difference of mean solar time of time interval and true solar time reflected in solar tracking system, it is continuous, closed and unduplicated that the time difference of each time difference adjusting module is adjusted groove 94, the hour angle arc length curve that the mean solar time in the whole time difference in adjustment 94 corresponding tropic years of groove and time difference true solar time are reflected in solar tracking system.(referring to Fig. 6,7).
Be fixed on the fixed rack 17 at described time difference adjusting lever 20, two quarter bends in its outer end are vertical to be inserted in the described time difference adjustment groove 94, the time difference regulating mechanism working cycles be about for 1 tropic year, screw drive time difference adjusting module ring rotated for 1 week, adjusted the mean solar time in 1 tropic year and the time difference of true solar time continuously.
The system controller 3 of described angle of rotation follower, servomotor 4, reducing gear 2 and the time drive bevel gear 7 of screw rod 19, time difference adjusting module ring 9, time difference transmission of difference regulating mechanism and driven wheel of differential 8 equal rotating supports on a moving support 1, moving support 1 is around main working shaft 11 fine motions, described screw rod 19 axially be main working shaft 11 radially, the gearratio that main working shaft 11 and the time difference are adjusted between the ring 9 is 365.25.
Be made up of 2Z-XI type gear with small teeth difference power train 21 and worm gear 22 worm screws 23 mechanisms in the described reducing gear 2, the output of few tooth difference power train 21 is connected with worm screw 23, and worm gear 22 is connected with main working shaft 11.Few tooth difference power train 21 also can adopt Harmonic Gears system, and the gearratio of reducing gear is more than or equal to 480.
Every duration step by step of one of the described angle of rotation follower used step number of circulation be a mean solar day divide exactly the step number duration, adjust main working shaft 11 intermittently, the angular variable when the solar day apparent motion of servo-actuated evenly.
Described servomotor 4 and system controller 3 constitute a complete motion control ring, and system controller 3 drives the angle of servomotor 4 rotational fixation in the position control of the set time of each fixing step duration.
Respectively there is the circular arc thread groove 92 with described screw rod 19 engagements the relative two sides of described time difference adjusting module ring 91, and screw rod 19 is symmetrical arranged two.
Described elevation angle guiding mechanism comprises working face 12, subtask axle 18, few tooth difference power train 16, decide eccentric shaft 21, adjusting lever 15 and adjusting lever 15 ends stride crack slide block 14, non-straight trough rail 13, subtask axle 18 is connected with working face 12, subtask 18 is connected on the main working shaft 11 with the unitary rotation of working face 12, having and main working shaft 11 corresponding gaps of also slightly being wider than main working shaft to the centre along long of working face 12; Few 16 1 internal gears of tooth difference power train 162 are connected with described main working shaft 11, compound planet gear 164 is arranged on and deciding on the eccentric shaft 161 that fixed rack 17 is fixedly linked, the outer rim of output inner gear 163 connects an end of adjusting lever 15, the other end of adjusting lever 15 is striden crack slide block 14 and is positioned at non-straight trough rail 13, and non-straight trough rail 13 is divided into two parts and is hinged with an end of working face 12 respectively.Few tooth difference speed reducing mechanism 16 one-year ages in the guiding mechanism of the elevation angle circle, and cooperate by the machinery between adjusting lever 15, non-straight trough rail 13 and the working face 12, make the adjusting range in 1 year of working face positive and negative 23 ° 27 ' between.(referring to Fig. 1).
Described few tooth difference power train 16 few tooth difference transmissions are the transmission of 2Z-XI type gear with small teeth difference, and the number of teeth is as follows: Z
1=62, Z
2=64, Z
3=57, Z
4=59 or Z
1=57, Z
2=59, Z
3=62, Z
4=64, realize that gearratio is 365.80 or-364.80; Also can be the few tooth difference transmission of single-stage, realize gearratio 365.
Two outer ends of the non-straight trough rail 13 of described working face 12 1 ends make progress in the same way or have a down dip, its COEFFICIENT K is 0.033-0.034 to the maximum, the value that plays the two ends COEFFICIENT K of non-straight trough rail 13 from the intermediate point of non-straight trough rail 13 changes between 0 to 0.033-0.034 continuously, Changing Pattern is that near sinusoidal changes, the ratio of the angle that the K value turns in every day actual measurement on the ecliptic for the earth and circumference 360 ° angles poor with the accumulative total between the standard circumference motion calculation angle, through calculating the back is arranged to non-straight trough rail 13 continuously by sinusoidal rule track, constitute the accurate rail groove of non-straight trough rail 13, each offset point with straight center line 131 apart from computing formula is: K * rail groove mid point is to the path length of subtask axle.(referring to figure three c).
The present invention also can be connected with many cover solar energy working faces by transmission, and can install on the face at any inclination angle.
The present invention can also only remove elevation angle guiding mechanism, keeps time difference adjustment function, and working face 12 directly is fixed on the main working shaft 11, can adjust working face 12 automatically, and the apparent motion of following the tracks of the sun achieves the high one dimension of precision and follows the tracks of.
The present invention can with the elevation angle and the time difference regulating mechanism remove the simplest sun tracker of formation, working face 12 directly is fixed on the working-spindle 11, not needing can be used for the occasion of accurate tracking.
Operation principle of the present invention is as follows:
The servo servomotor 4 of service system controller 3 controls rotates, and servo driven by servomotor 2Z-X little tooth difference speed reducer 2 becomes large torque through decelerator.After output to worm screw 6, worm screw 6 drives worm gears 5, further bigger deceleration with become high pulling torque and drive the main working shaft 11 that links to each other with worm gear 5 then, main working shaft 11 drives subtask axles 18 and rotates solar energy working faces 12, the tracking sun.Servo servomotor 4 speeds of service of system controller 3 control the speed on the main working shaft 11 of being reflected in equates in the unit interval with earth rotation speed or is close.
Coaxially on the worm gear 5 bevel gear 7 is set rotates with worm gear 5, bevel gear 7 drives bevel gear 8, bevel gear 8 drives screw rod 19, screw drive between the time difference mould preparation piece ring 9 in module guide groove 93, move, adjusting lever 20 on the fixed rack 17 is fixedly connected, adjustment groove 94 on the time difference adjusting module ring 9 is crooked, moving mutually and making support 1 generation is the swing of axle with main working shaft 11, this swing is synchronous with the time difference of its solar time and mean solar time, adjusted the time difference, made solar tracking not produce tracking error because of the time difference.The time difference is adjusted circulation in a year.
Main working shaft 11 rotates, the eccentric shaft 21 of the few tooth difference power train 16 in the elevation angle guiding mechanism that is fixedly linked with fixed rack 17 is motionless, main working shaft 11 is done in planetary gear servo-actuated in the elevation angle guiding mechanism that is fixedly linked with working shaft 11, compound planet gear 164 is done planetary motion, has driven the elevation angle of working face 12 by the adjusting lever 15 of output inner gear 163.
Few tooth difference speed reducing mechanism 16 in the guiding mechanism of the elevation angle, one-year age circles, by machinery cooperate to drive solar energy working face 12 one years positive and negative 23 ° 27 ' scope in circulation primary, adjusting 12 servo-actuateds of sun working face changes in the declination angle of the sun, make the different declination angular variables of solar tracking and produce tracking error, for small elevation angle tracking error, can look requiring to carry out necessary manual adjustment.
Claims (9)
1, a kind of single solar tracking system that drives is characterized in that: comprise fixed rack, angle of rotation follower and the time difference regulating mechanism; Described angle of rotation follower comprises main working shaft, reducing gear, servomotor and system controller, the output of system controller connects servomotor, the servomotor output shaft is connected with the input of reducing gear is coaxial, the output of reducing gear is connected with main working shaft is coaxial, main working shaft rotating support is on fixed rack and parallel with the earth's axis, working cycles of angle of rotation follower is that rotated for 1 week 24 hours of mean solar time, and the servo-actuated of Continuous Drive master's working shaft changes in apparent motion on solar day hour angle; Every duration step by step of one of the described angle of rotation follower used step number of circulation be a mean solar day divide exactly the step number duration, adjust main working shaft intermittently, the angular variable when the solar day apparent motion of servo-actuated evenly; Difference regulating mechanism comprises screw rod, time difference adjusting module ring, time difference adjusting lever and the time difference transmission when described, time difference adjusting module ring is flexibly connected by a plurality of time difference adjusting modules and forms, the lateral surface of each time difference adjusting module have along time difference adjusting module anchor ring and with the circular arc thread groove of described screw engages; Have in the interior ring side of described time difference adjusting module ring along the time difference of anchor ring and adjust groove, the time difference on every time difference adjusting module is adjusted the hour angle arc length curve that groove was reflected in solar tracking system the time difference of the mean solar time of should module adjusting time interval and true solar time, it is continuous, closed and unduplicated that the time difference of each time difference adjusting module is adjusted groove, the hour angle arc length curve that the mean solar time in a whole time difference adjustment corresponding tropic year of groove and time difference true solar time are reflected in solar tracking system; Described time difference adjusting lever is fixed on the fixed rack, and its outer end is vertical inserts in the described time difference adjustment groove; The time difference regulating mechanism working cycles be 1 tropic year, screw drive time difference adjusting module ring rotated for 1 week, adjusted the mean solar time in 1 tropic year and the time difference of true solar time continuously; The system controller of described angle of rotation follower, servomotor, reducing gear and the time drive bevel gear of screw rod, time difference adjusting module ring, time difference transmission of difference regulating mechanism and the equal rotating support of driven wheel of differential on moving support, moving support is around main working shaft fine motion, described screw axial be main working shaft radially.
2, single solar tracking system that drives according to claim 1, it is characterized in that: 2Z-X type gear with small teeth difference power train or Harmonic Gears system is arranged in the described reducing gear, and the gearratio of reducing gear is more than or equal to 480.
3, according to claim 1 and 2 described single solar tracking systems that drive, it is characterized in that: described reducing gear is made up of with intermeshing worm-and-wheel gear 2Z-XI gear with small teeth difference power train or Harmonic Gears system.
4, single solar tracking system that drives according to claim 1, it is characterized in that: described servomotor and system controller constitute a complete motion control ring, and system controller is in the angle of the set time of each fixing step duration position control servomotor rotational fixation.
5, single solar tracking system that drives according to claim 1 is characterized in that: the ridge of described time difference adjusting module ring thread groove add up to 487 with the product of described screw flight line number; Described time difference transmission is made up of intermeshing drive bevel gear and driven wheel of differential, drive bevel gear is connected with main working shaft is coaxial, driven wheel of differential is connected with screw coaxial, gearratio between the driving and driven bevel gear is 0.75, screw rod and the gearratio of adjusting between the ring are 487, and resultant gear ratio is 365.25.
6, according to claim 1 and 5 described single solar tracking systems that drive, it is characterized in that: the relative two sides of described time difference adjusting module ring respectively have along anchor ring and with the circular arc thread groove of described screw engages, screw rod is symmetrical arranged two.
7, single solar tracking system that drives according to claim 1, it is characterized in that: also comprise elevation angle guiding mechanism, it comprise the subtask axle, with the subtask axle be fixed together working face, few tooth difference power train, decide eccentric shaft, an end has the adjusting lever of striding the crack slide block, non-straight trough rail, subtask axle and main working shaft vertical hinge have with main working shaft corresponding gap of also slightly being wider than main working shaft along long to the centre at working face; An internal gear and the described main working shaft of few tooth difference power train are connected, compound planet gear is arranged on to be decided on the eccentric shaft, the outer rim of output inner gear connects an end of adjusting lever, the other end of adjusting lever is striden the crack slide block and is positioned at non-straight trough rail, and non-straight trough rail is divided into two parts and is hinged with an end of working face respectively; Describedly decide eccentric shaft and be fixed on the fixed rack, coaxial with main working shaft; The gearratio of described few tooth difference power train approximates 365; Few tooth difference speed reducing mechanism one-year age in the guiding mechanism of the elevation angle circles, cooperate by the machinery between adjusting lever, non-straight trough rail and the working face, drive working face 1 year positive and negative 23 ° 27 ' scope in circulation adjust once, adjust the working face servo-actuated and change in the declination angle of the sun.
8, single solar tracking system that drives according to claim 7, it is characterized in that: described few tooth difference transmission is the transmission of 2Z-XI type gear with small teeth difference, and the number of teeth is as follows: Z
1=62, Z
2=64, Z
3=57, Z
4=59 or Z
1=57, Z
2=59, Z
3=62, Z
4=64, realize that gearratio is 365.80 or-364.80.
9, single solar tracking system that drives according to claim 7, it is characterized in that: two outer ends of the non-straight trough rail of described working face one end make progress in the same way or have a down dip, its COEFFICIENT K is 0.033-0.034 to the maximum, the value that plays the two ends COEFFICIENT K of non-straight trough rail from the intermediate point of non-straight trough rail changes between 0 to 0.033-0.034 continuously, Changing Pattern is that near sinusoidal changes, the ratio of the angle that the K value turns in every day actual measurement on the ecliptic for the earth and circumference 360 ° angles poor with the accumulative total between the standard circumference motion calculation angle, through calculating the back is arranged to non-straight trough rail continuously by sinusoidal rule track, constitute the accurate rail groove of non-straight trough rail, each offset point with straight center line apart from computing formula is: K * rail groove mid point is to the path length of subtask axle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB031094880A CN100340822C (en) | 2003-04-10 | 2003-04-10 | Single-drive solar tracking system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB031094880A CN100340822C (en) | 2003-04-10 | 2003-04-10 | Single-drive solar tracking system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1536289A true CN1536289A (en) | 2004-10-13 |
| CN100340822C CN100340822C (en) | 2007-10-03 |
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ID=34319367
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB031094880A Expired - Fee Related CN100340822C (en) | 2003-04-10 | 2003-04-10 | Single-drive solar tracking system |
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| Country | Link |
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| CN (1) | CN100340822C (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102109228A (en) * | 2011-01-17 | 2011-06-29 | 崔长海 | Solar focusing ultrahigh-temperature air heating device |
| CN102141815A (en) * | 2011-03-14 | 2011-08-03 | 深圳市中兴新地通信器材有限公司 | Solar heliostat tracking system |
| CN102880192A (en) * | 2012-06-26 | 2013-01-16 | 王子延 | Single shaft driven double-shaft solar panel tracker |
| CN103488182A (en) * | 2012-06-12 | 2014-01-01 | 科基纳提克斯股份有限公司 | Adjusting device |
| CN104500658A (en) * | 2014-12-16 | 2015-04-08 | 湖南科技大学 | Built-in solar tracking azimuth driving device |
| CN106015474A (en) * | 2016-07-29 | 2016-10-12 | 洛阳理工学院 | Solar tracking gear assembly |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3882861T2 (en) * | 1987-09-21 | 1993-12-23 | Technology Network Inc | Automatic lighting device using sunlight with tracking device. |
| US5622078A (en) * | 1995-08-21 | 1997-04-22 | Mattson; Brad A. | Linear/helix movement support/solar tracker |
| JP2001135112A (en) * | 1999-11-10 | 2001-05-18 | Sanyo Electric Co Ltd | Tracking device and solar light collecting system |
| JP2001217445A (en) * | 2000-01-31 | 2001-08-10 | Honda Motor Co Ltd | Tracking solar power generating device and error correcting method for its built-in clock |
| CN1338600A (en) * | 2001-01-20 | 2002-03-06 | 聂洪军 | Method and equipment for tracking sun |
| CN2479443Y (en) * | 2001-04-26 | 2002-02-27 | 张维良 | Automatic sunlight-tracking means for solar range |
-
2003
- 2003-04-10 CN CNB031094880A patent/CN100340822C/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102109228A (en) * | 2011-01-17 | 2011-06-29 | 崔长海 | Solar focusing ultrahigh-temperature air heating device |
| CN102109228B (en) * | 2011-01-17 | 2012-12-12 | 崔长海 | Solar focusing ultrahigh-temperature air heating device |
| CN102141815A (en) * | 2011-03-14 | 2011-08-03 | 深圳市中兴新地通信器材有限公司 | Solar heliostat tracking system |
| CN102141815B (en) * | 2011-03-14 | 2014-04-09 | 深圳市中兴新地通信器材有限公司 | Solar heliostat tracking system |
| CN103488182A (en) * | 2012-06-12 | 2014-01-01 | 科基纳提克斯股份有限公司 | Adjusting device |
| CN102880192A (en) * | 2012-06-26 | 2013-01-16 | 王子延 | Single shaft driven double-shaft solar panel tracker |
| CN104500658A (en) * | 2014-12-16 | 2015-04-08 | 湖南科技大学 | Built-in solar tracking azimuth driving device |
| CN106015474A (en) * | 2016-07-29 | 2016-10-12 | 洛阳理工学院 | Solar tracking gear assembly |
| CN106015474B (en) * | 2016-07-29 | 2018-06-29 | 洛阳理工学院 | Solar tracking gear assembly |
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| Publication number | Publication date |
|---|---|
| CN100340822C (en) | 2007-10-03 |
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