Double-crank-throw crankshaft double-fluted-disc rope transmission mechanism for solar tracker

Abstract

The invention discloses a double-crank crankshaft double-fluted-disc rope transmission mechanism for a solar tracker, and belongs to the technical field of solar photovoltaic supports. The device is composed of a double-crank crankshaft, a double-fluted-disc traction wheel, a transmission rope, a semicircular swing beam dragged by the transmission rope, a stand column used for installing the mechanisms and the like. When the device is engaged at the same time, passive self-locking can be realized, and the external force torsional moment of the photovoltaic array can be directly digested by each stand column. The device is high in comprehensive transmission ratio, a single motor can drive a plurality of stand column assemblies to operate, the photovoltaic array can be designed to be longer, the construction cost and the later cleaning cost of equipment are effectively reduced, external force borne by the photovoltaic array in severe weather such as strong wind can be evenly shared by the stand columns, the safety and stability of the support are improved, and the service life of the photovoltaic array is prolonged. The overall structure is simple, the cost performance is high, and the technical problems that a traditional flat single-shaft photovoltaic support is too few in transmission points and poor in photovoltaic array stability are effectively solved.

Description

Technical Field

[0001] This invention relates to the field of solar photovoltaic support technology, and more specifically to a hyperboloid crankshaft double-tooth disc rope transmission mechanism for a solar tracker. Background Technology

[0002] The flat single-axis photovoltaic tracking bracket can automatically follow the movement of the sun and rotate to keep the sunlight and photovoltaic array at the smallest incident angle. The flat single-axis photovoltaic tracking bracket has only one rotation axis parallel to the ground. Although it cannot make the sunlight and photovoltaic array completely perpendicular, it can keep the straight line of the sunlight projection on the photovoltaic array always in the north-south direction.

[0003] Compared to fixed supports, photovoltaic panels receive stronger sunlight most of the time, resulting in higher power generation. Traditional single-axis photovoltaic (PV) supports consist of a main beam mounted on top of several columns arranged in a north-south direction, connected by bearings and a transmission mechanism. The PV array is then installed on the main beam. Due to cost constraints, it's difficult to install a transmission mechanism between each column and the main beam. Some columns only use bearings to support the main beam, allowing it to rotate freely on columns without transmission mechanisms. This leads to a problem of insufficient transmission points in traditional tracking supports. Fewer transmission points mean greater spacing between them, resulting in lower stiffness of the main beam in the torsional direction, increased free length of the PV array, and poorer overall stability. Installing a transmission mechanism on each column to minimize the free length of the PV array and maximize its torsional stiffness is the safest approach for ensuring safe operation of the tracking support.

[0004] Therefore, a double-crank crankshaft double-tooth disc rope transmission mechanism suitable for flat single-axis photovoltaic tracking brackets is needed, which can be deployed on each column to solve the technical problems of insufficient transmission points, insufficient rigidity of photovoltaic array in torsional direction, and poor stability of traditional flat single-axis photovoltaic brackets. Summary of the Invention

[0005] The purpose of this invention is to provide a transmission mechanism that is simple in structure, driven simultaneously by connected transmission shafts, has a large transmission ratio, saves costs, and is highly practical: a double-crankshaft double-tooth disc rope transmission mechanism.

[0006] The specific technical solution of this invention is as follows:

[0007] A double-crankshaft double-tooth disc rope transmission mechanism for a solar tracker includes a double-crankshaft, a double-tooth disc traction wheel, a transmission rope, a semi-circular swing beam, and a column for mounting the various components.

[0008] The double-crank crankshaft, double-toothed traction wheel, and semi-circular swing beam are mounted on the column in a fixed or rotatable manner. The double-toothed traction wheel is pulled and held by a pair of transmission ropes at both ends of the semi-circular swing beam. The double-crank crankshaft, double-toothed traction wheel, semi-circular swing beam, and column together form the column assembly.

[0009] When the column assembly is used in a single-axis tracking bracket, it is arranged in a row along the north-south direction. The rotation axis of the double-crankshaft faces due south and due north, and the semi-circular swing beam extends in the east and west directions in the horizontal state. The double-crankshaft is directly driven by a motor and transmission mechanism to reciprocate, or the double-crankshaft is connected to the double-crankshaft of another column assembly through a transmission shaft to achieve reciprocating rotation at the same speed and angle.

[0010] The double-toothed traction wheel is sleeved on the shaft body below the double-crank crankshaft. The double-crank crankshaft includes two cranks. The two cranks alternately mesh with the tooth grooves of the double-toothed traction wheel. One end of the pair of transmission ropes is fixed to the double-toothed traction wheel. When the transmission ropes reciprocate, the pair of transmission ropes are in a state where one is retracted and the other is released, and the lengths of the retracted and released ropes are the same but the directions are opposite.

[0011] The other end of the transmission rope is fixed to both ends of the semi-circular swing beam. The winding and unwinding action of the transmission rope drives the semi-circular swing beam to reciprocate around its own bearing as the rotation center. The bracket structure for installing the photovoltaic array is mounted on the semi-circular swing beam. With the reciprocating rotation of the semi-circular swing beam, the solar tracking action of the single-axis photovoltaic array is realized.

[0012] Preferably, the two cranks are equidistant from the center, face opposite directions, and have an included angle of 180°; the north-south center distance of the two cranks is the same as the tooth spacing between the two teeth of the double-toothed traction wheel; the tooth spacing is the same as the pitch of the adjacent tooth grooves on the pitch circle of the two teeth of the double-toothed traction wheel; the center distance of the two cranks is the perpendicular distance between the center lines of the two cranks; and the pitch of the tooth grooves on the pitch circle is the perpendicular distance of a straight line perpendicular to the tooth disk drawn through the intersection of the center lines of the adjacent tooth grooves of the two teeth and the pitch circle of the tooth disk.

[0013] Preferably, the double-toothed traction wheel is an integral structure, comprising two toothed discs of the same size and a cylindrical rope winding wheel. The two toothed discs are respectively fixed at both ends of the rope winding wheel, and the tooth spacing between the two toothed discs is the same as the north-south distance between the two cranks of the double crankshaft.

[0014] The two toothed discs have the same number of teeth and tooth groove specifications. When combined as a whole, they deflect the pitch angle of adjacent tooth grooves on the pitch circle. The pitch angle of the tooth groove on the pitch circle is 360° divided by the number of teeth of the toothed disc and then divided by 2. Furthermore, the center line of any tooth groove of any toothed disc is aligned with the center line of the tooth of the other toothed disc.

[0015] Preferably, one end of the pair of transmission ropes is fixed to the winding wheel of the double-toothed traction wheel and wound around it several times, and the other end is led out upwards in a crisscross pattern, then pulled up symmetrically along the semicircular part of the semicircular swing beam and fixedly connected to the semicircular swing beam. The transmission ropes are wound in a crisscross pattern.

[0016] Preferably, the semi-circular swing beam is an integral structure, including a crossbeam, a bearing sleeve, and a semi-circular grooved component. The bearing sleeve is located in the middle of the crossbeam and is a bearing used to support the rotation of the semi-circular swing beam.

[0017] The semi-circular grooved component is connected to the crossbeam, which allows the transmission rope to be tensioned. The bracket structure for installing the photovoltaic array is fixedly connected to the integrated semi-circular swing beam structure.

[0018] Preferably, at least three shafts or bushings are arranged vertically from top to bottom on the column. The uppermost shaft or bushing is used to locate the rotation center of the semi-circular swing beam, the middle shaft or bushing is used to locate the rotation center of the double-crank crankshaft, and the lowermost shaft or bushing is used to locate the rotation center of the double-toothed traction wheel. The three rotation center lines are all oriented north-south and are parallel to each other.

[0019] Preferably, the two cranks of the double-crank crankshaft correspond one-to-one with the two teeth of the double-tooth traction wheel, and are in an alternating or simultaneous meshing engagement state. Each rotation of the double-crank crankshaft drives each tooth of the double-tooth traction wheel to rotate one tooth. The double-crank crankshaft and the double-tooth traction wheel are in a transmission state and a locking state, respectively.

[0020] When the double crankshaft rotates, when both cranks simultaneously engage with the tooth groove of the double-toothed traction wheel, the double-toothed traction wheel remains stationary, and the rotational force of the photovoltaic array is limited to achieve self-locking, which is the locked state; when the double crankshaft rotates to the point where one crank disengages from the tooth groove and the other crank delves into the tooth groove, it drives the double-toothed traction wheel to rotate and realizes the solar tracking action of the photovoltaic array, which is the transmission state, and the actions of one crank disengaging from the tooth groove and the other crank delves into the tooth groove are performed simultaneously, with alternating engagement;

[0021] In the transmission state, the torsional motion of the photovoltaic array under external force can be transmitted back to the double crankshaft; in the locked state, the two cranks are horizontal and simultaneously engaged. At this time, no matter how much external force passes through the double crankshaft, it cannot continue to push the double crankshaft to rotate. This state is the final dead point state of the photovoltaic array driven by external force, which can realize the passive self-locking of the photovoltaic array.

[0022] Preferably, the mating part of the double-crank crankshaft and the column bushing, as well as the shaft head at the other end, extend outward by a certain length. The shaft head is used to connect to the double-crank crankshaft shaft head of another set of column assemblies via a transmission shaft. The center lines of the two shaft heads of the same double-crank crankshaft are collinear, and the center lines of the two cranks are equidistant from the center lines of the shaft heads, but in opposite directions.

[0023] Preferably, the tooth groove width of the tooth disc is equal to the diameter of the cylindrical portion of the double crankshaft plus an appropriate clearance; the center distance between the two cranks of the double crankshaft is equal to the pitch of the adjacent tooth grooves of the two tooth discs on the pitch circle, and the center line of the tooth groove of any one tooth disc is aligned with the center line of the tooth of the other tooth disc.

[0024] Preferably, it includes several column assemblies, a drive shaft, and a drive motor; the several column assemblies are arranged in a row along the north-south direction, the drive shaft coaxially connects the double-cranked crankshafts of all column assemblies into one unit, and the drive motor is driven to the double-cranked crankshaft of one of the column assemblies, which can drive all the double-cranked crankshafts to rotate synchronously, and drive the photovoltaic array connected to the bracket structure for mounting the photovoltaic array to rotate synchronously for solar tracking through the transmission mechanism of all column assemblies;

[0025] The transmission ratio from the drive shaft of the photovoltaic array mounting bracket structure to the semi-circular swing beam is the product of the number of teeth on the double-toothed traction wheel and the ratio of the semi-circular diameter of the semi-circular swing beam to the diameter of the double-toothed traction wheel's winding wheel. The transmission ratio is not less than 1:100.

[0026] The torsional torque generated by external forces on the photovoltaic array is directly borne and absorbed locally by each column through the passive self-locking function of the locked state. It cannot be transmitted back to the drive motor, but is instead locked by the double crankshaft and then transmitted to the column, realizing the local absorption of external forces on the photovoltaic array, thereby improving the stability of the entire solar photovoltaic tracking support system.

[0027] The beneficial effects of this invention are as follows:

[0028] The overall transmission ratio of this invention is composed of the transmission ratio between the double-crank crankshaft and the double-toothed disc traction wheel, and the transmission ratio between the double-toothed disc traction wheel and the semi-circular swing beam. Both transmission ratios can be designed to be above 1:10, so the overall transmission ratio can reach above 1:100. This enables the motor output torque required for the photovoltaic array tracking action, and the torque that the transmission shaft needs to transmit between adjacent column assemblies is only 1 / 100 of the original. Therefore, a single motor can drive multiple column assemblies to operate simultaneously, and the photovoltaic array can be designed to be longer, effectively reducing the construction cost and subsequent cleaning cost of the equipment, making it highly practical.

[0029] Moreover, the transmission mechanism of this invention can be installed on each column, and each column has a passive self-locking function. In this way, the external force on the photovoltaic array under severe weather conditions such as strong winds can be evenly distributed by each column. After each column is passively self-locked, the photovoltaic array has stronger rigidity, preventing vibration caused by strong winds blowing over the photovoltaic array, thus improving the safety of the single-axis tracking bracket. Furthermore, since each column adopts a unified design, the entire tracking bracket system has a simple structure and a very high cost-performance ratio.

[0030] The above description is merely an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention and to implement it in accordance with the contents of the specification, the preferred embodiments of the present invention are described in detail below with reference to the accompanying drawings. Attached Figure Description

[0031] Figure 1 This is a schematic diagram of the column assembly structure of the present invention;

[0032] Figure 2 This is a schematic diagram of the hyperbolic crankshaft structure of the present invention;

[0033] Figure 3 This is a schematic diagram of the double-toothed disc traction wheel structure of the present invention;

[0034] Figure 4 This is a schematic diagram showing the connection between the double-toothed disc traction wheel and the semi-circular swing beam of the present invention via ropes;

[0035] Figure 5 This is a schematic diagram of the meshing method of the double-crank crankshaft and double-tooth disc traction wheel of the present invention;

[0036] Figure 6 This is a schematic diagram of the flat single-axis photovoltaic tracking bracket structure implemented by the transmission mechanism of the present invention;

[0037] In the diagram: 101-Double crankshaft; 102-Double toothed traction wheel; 103-Transmission rope; 104-Semi-circular swing beam; 105-Main column; 106-Motor; 107-Transmission mechanism; 201-Transmission shaft; 202-Support structure for mounting photovoltaic array; 301-Crankshaft; 302-North-south distance between the two cranks; 303-Distance of the crank from the center; 304-Center distance between the two cranks; 401-Toothed disc; 402-Rope winding wheel; 403-Pitch of the tooth groove on the pitch circle; 404-Toothed disc spacing; 501-Transmission state; 502-Locking state; 601-Rope winding method. Detailed Implementation

[0038] The technical solution of the present invention will now be clearly and completely described with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0039] Example:

[0040] like Figure 1 As shown in the figure, the double-crank crankshaft double-tooth disc rope transmission mechanism for solar trackers described in this embodiment can be applied to the solar tracking action of a flat single-axis photovoltaic tracking bracket. The whole embodiment is based on the column 105, and the double-crank crankshaft 101, double-tooth disc traction wheel 102, and semi-circular swing beam 104 are fixedly or rotatably mounted on the column 105.

[0041] like Figure 2 As shown, the double-toothed traction wheel 102 pulls and holds the two ends of the semi-circular swing beam 104 through a pair of transmission ropes 103. The whole assembly consisting of the double-crankshaft 101, the double-toothed traction wheel 102, the semi-circular swing beam 104 and the column 105 is the column assembly. In actual application, several column assemblies will be arranged in rows along the north-south direction. Then, the bracket structure 202 for installing the photovoltaic array is erected on the semi-circular swing beam 104. The double-crankshaft 101 of each column assembly is coaxially connected through the transmission shaft 201. The synchronous operation of all column assemblies can be achieved by driving a single drive motor 106 through the transmission mechanism 107. The rotation axis of the double-crankshaft 101 always faces due south and due north, and the extension direction of the semi-circular swing beam 104 in the horizontal state always faces due east and due west. This is to ensure that the tracking direction of the photovoltaic array is the same as the trajectory of the sun.

[0042] The double crankshaft 101 is the power input component of the entire transmission mechanism, rotating around its own axis. The double crankshaft 101 includes two cranks 301, which have the same offset distance 303 from the center, face opposite directions, and have an included angle of 180°. The north-south distance 302 between the two cranks is the same as the tooth spacing 404 between the two toothed discs 401 of the double-toothed traction wheel 102. The center distance 304 between the two cranks of the double crankshaft 101 is the same as the pitch 403 of the adjacent tooth grooves of the two toothed discs 401 of the double-toothed traction wheel 102 on the pitch circle. This dimensional matching can ensure the accuracy of the meshing between the cranks 301 and the tooth grooves. The center distance 304 between the two cranks is the vertical distance between the center lines of the two cranks 301, and the pitch 403 of the tooth grooves on the pitch circle is the vertical distance of the straight line perpendicular to the toothed disc 401 drawn through the intersection of the center lines of the adjacent tooth grooves of the two toothed discs and the pitch circle of the toothed disc 401.

[0043] like Figure 3 As shown, the mating part of the double crankshaft 101 and the bushing of the column 105, as well as the shaft head at the other end of the crankshaft, extend outward by a certain length. The extended shaft head is used to connect with the shaft head of the double crankshaft 101 of another set of column assemblies through the transmission shaft 201. The center lines of the two shaft heads of the same double crankshaft 101 are kept collinear, ensuring that when the transmission shaft 201 transmits power, the double crankshafts 101 of all column assemblies can achieve reciprocating rotation at the same speed and angle. The center distance 304 between the two cranks is twice the center deviation distance 303 of one of the cranks.

[0044] The double-toothed traction wheel 102 is an integral structure, consisting of two toothed discs 401 of identical size and a cylindrical rope winding wheel 402. The two toothed discs 401 are fixed at both ends of the rope winding wheel 402. The tooth spacing 404 between the two toothed discs 401 is the same as the north-south spacing 302 between the two cranks of the double crankshaft 101, which ensures engagement with the double crankshaft 101.

[0045] The two gear discs 401 have the same number of teeth and tooth groove specifications. When combined as a whole, the two gear discs 401 deflect each other by the pitch angle 403 of the adjacent tooth grooves on the pitch circle. The value of the pitch angle 403 of the tooth grooves on the pitch circle is 360° divided by the number of teeth of the gear disc 401 and then divided by 2, which allows the center line of any tooth groove of any gear disc 401 to be aligned with the center line of the tooth of the other gear disc 401. The tooth groove width of the gear disc 401 is equal to the sum of the diameter of the cylindrical part of the crank 301 of the double crankshaft 101 and the appropriate clearance. The crank center distance 304 of the double crankshaft 101 is the same as the pitch angle 403 of the adjacent tooth grooves of the two gear discs 401 of the double gear disc traction wheel 102 on the pitch circle. The double gear disc traction wheel 102 is sleeved on the shaft below the double crankshaft 101 and is used to transmit the power of the double crankshaft 101 to the transmission rope 103.

[0046] like Figure 4 As shown, the transmission rope 103 can connect the double-toothed traction wheel 102 and the semi-circular swing beam 104. One end of the pair of transmission ropes 103 is fixed on the winding wheel 402 of the double-toothed traction wheel 102 and wound around it several times. After the other end of the transmission rope 103 is led out upwards in a cross shape, it will be symmetrically pulled upwards along the semi-circular part of the semi-circular swing beam 104 and fixedly connected to the semi-circular swing beam 104. The rope winding method 601 is cross winding, which can keep the transmission rope 103 in a taut state at all times and ensure that the winding and unwinding actions of the two transmission ropes 103 are synchronized and stable when the double-toothed traction wheel 102 rotates.

[0047] The semi-circular swing beam 104 is an integral structure, consisting of a crossbeam, a bearing sleeve, and a semi-circular grooved component. The bearing sleeve is directly located in the middle of the crossbeam. This bearing sleeve is used to support the rotation of the semi-circular swing beam 104 and provides a stable rotation center for the reciprocating rotation of the semi-circular swing beam 104. The semi-circular grooved component is integrally connected to the crossbeam.

[0048] At least three shafts or bushings are arranged vertically from top to bottom on the column 105. The uppermost shaft or bushing is specifically used to locate the rotation center of the semi-circular swing beam 104, the middle shaft or bushing is used to locate the rotation center of the double-crank crankshaft 101, and the lowermost shaft or bushing is used to locate the rotation center of the double-toothed traction wheel 102. The rotation center lines of the three components are all oriented north-south and are parallel to each other.

[0049] The hyperboloid crankshaft 101 can be directly driven by the transmission mechanism 107 via the motor 106 to reciprocate, or it can receive power from the hyperboloid crankshaft 101 of another set of column assemblies via the transmission shaft 201 to achieve reciprocating rotation at the same speed and angle. The two cranks 301 of the hyperboloid crankshaft 101 correspond one-to-one with the two gears 401 of the double-tooth traction wheel 102, and they mesh alternately or simultaneously. Each rotation of the hyperboloid crankshaft 101 will alternately drive each gear 401 of the double-tooth traction wheel 102 to rotate one tooth. When the hyperboloid crankshaft 101 rotates beyond a certain range of the horizontal position, one crank 301 disengages from the tooth groove and the other crank 301 re-enters the tooth groove. At this time, the transmission mechanism is in the transmission state 501. The reciprocating rotation of the crankshaft 101 will drive the double-toothed traction wheel 102 to reciprocate synchronously. When the double-toothed traction wheel 102 rotates, one of the transmission ropes 103 is in a state of being wound up and the other is being released. The lengths of the wound ropes and the released ropes are the same and the directions are opposite. The winding and releasing actions of the transmission ropes 103 will drive the semi-circular swing beam 104 to reciprocate around its own bearing as the rotation center. This will then drive the photovoltaic array on the bracket structure 202 to reciprocate synchronously with the semi-circular swing beam 104, ultimately realizing the solar tracking action of the single-axis photovoltaic array. If the photovoltaic array is subjected to external force and undergoes torsional action in the transmission state 501, this torsional force can be transmitted back to the double-crankshaft 101 through the transmission ropes 103 and the double-toothed traction wheel 102.

[0050] like Figure 5 As shown, when the double-crank crankshaft 101 rotates and the two cranks 301 are in a horizontal position, and when the two cranks 301 simultaneously enter the tooth groove of the double-toothed traction wheel 102, the transmission mechanism enters a locked state 502. The double-toothed traction wheel 102 remains stationary, and the rotational force on the photovoltaic array is limited by the tooth groove to achieve self-locking. In this state, the resultant force of the external forces on the two cranks 301 just passes through the rotation axis of the double-crank crankshaft 101. No matter how much external force the photovoltaic array experiences to generate a torsional torque, it cannot continue to push the double-crank crankshaft 101. The rotation and locked state 502 is the final dead point state of the hyperboloid crankshaft 101 when the photovoltaic array is pushed by an external force. No matter what angle the hyperboloid crankshaft 101 is initially at, the torsional motion of the photovoltaic array caused by the external force will push the double-tooth traction wheel 102, thereby pushing the hyperboloid crankshaft 101 to rotate and reset to the horizontal locked state 502. Even if the motor 106 is de-energized and the hyperboloid crankshaft 101 is in free rotation, the photovoltaic array can still be locked, realizing the passive self-locking of the photovoltaic array and ensuring the safety of the photovoltaic array in harsh environments such as strong winds.

[0051] like Figure 6As shown, several column assemblies, drive shaft 201, and drive motor 106 can form a complete flat single-axis photovoltaic tracking bracket. After several column assemblies are arranged in a row along the north-south direction, the drive shaft 201 coaxially connects the double-cranked crankshafts 101 of all column assemblies into one unit. The drive motor 106 is connected to the double-cranked crankshaft 101 of one of the column assemblies, so that all double-cranked crankshafts 101 can be driven to rotate synchronously. Through the transmission mechanism of all column assemblies, the photovoltaic array connected to the bracket structure 202 on which the photovoltaic array is installed can be driven to rotate synchronously for solar tracking.

[0052] The transmission ratio of the drive shaft 201 to the semi-circular swing beam 104 of this single-axis photovoltaic tracking bracket is the product of the number of teeth on the toothed disc 401 of the double-toothed traction wheel 102 and the ratio of the semi-circular diameter of the semi-circular swing beam 104 to the diameter of the rope wheel 402 of the double-toothed traction wheel 102. The transmission ratio is not less than 1:100. The torque of the drive shaft 201 acting on the photovoltaic array can be amplified by more than 100 times, so the photovoltaic array can be longer. One drive motor 106 can drive more photovoltaic modules, which can effectively reduce the equipment cost and operation and maintenance cost of the photovoltaic tracking bracket. In addition, the passive self-locking function of the locked state 502 is as follows: the torque cannot be transmitted to the drive motor 106 in the reverse direction. Instead, it is blocked by the double crankshaft 101 and then transmitted to the column 105 to realize the local absorption of the external force on the photovoltaic array, thereby improving the stability of the entire solar photovoltaic tracking bracket system.

[0053] The embodiments described above are merely illustrative of implementation methods of the present invention, and while the descriptions are specific and detailed, they should not be construed as limiting the scope of the invention patent. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these all fall within the protection scope of the present invention. Therefore, the protection scope of this invention patent should be determined by the appended claims.

Claims

1. A hyperboloid crankshaft double-tooth disc rope transmission mechanism for a solar tracker, characterized in that, It includes a hyperboloid crankshaft (101), a double-tooth disc traction wheel (102), a transmission rope (103), a semi-circular swing beam (104), and a column (105) for mounting the various components. The hyperboloid crankshaft (101), the double-toothed traction wheel (102), and the semi-circular swing beam (104) are mounted on the column (105) in a fixed or rotatable manner. The double-toothed traction wheel (102) is pulled and held by the two ends of the semi-circular swing beam (104) by a pair of transmission ropes (103). The entire assembly of the hyperboloid crankshaft (101), the double-toothed traction wheel (102), the semi-circular swing beam (104), and the column (105) is the column assembly. When the column assembly is used in a single-axis tracking bracket, it is arranged in a row along the north-south direction. The rotation axis of the double-curved crankshaft (101) is oriented due south and due north. The semi-circular swing beam (104) extends in the horizontal direction towards due east and due west. The double-curved crankshaft (101) is directly driven by the transmission mechanism (107) through the motor (106) to make reciprocating rotation, or the double-curved crankshaft is connected to the double-curved crankshaft (101) of another set of column assemblies through the transmission shaft (201) to achieve reciprocating rotation at the same speed and angle. The double-toothed traction wheel (102) is sleeved on the shaft below the double-crank crankshaft (101). The double-crank crankshaft (101) includes two cranks (301). The two cranks (301) alternately mesh with the adjacent tooth grooves of the two toothed discs (401) of the double-toothed traction wheel (102). One end of the pair of transmission ropes (103) is fixed to the double-toothed traction wheel (102). When the transmission ropes reciprocate, the pair of transmission ropes (103) are in a state where one is retracted and the other is released, and the lengths of the retracted and released ropes are the same but the directions are opposite. The other end of the transmission rope (103) is fixed to both ends of the semi-circular swing beam (104). The winding and unwinding action of the transmission rope (103) drives the semi-circular swing beam (104) to reciprocate around its own bearing as the rotation center. The bracket structure (202) for installing the photovoltaic array is mounted on the semi-circular swing beam (104). With the reciprocating rotation of the semi-circular swing beam (104), the solar tracking action of the flat single-axis photovoltaic array is realized.

2. The hyperboloid crankshaft double-tooth disc rope transmission mechanism for a solar tracker according to claim 1, characterized in that, The two cranks (301) have the same distance (303) from the center, face opposite directions, and have an included angle of 180°. The north-south distance (302) between the two cranks is the same as the distance (404) between the two teeth (401) of the double-tooth traction wheel (102). The center distance (304) between the two cranks is the same as the pitch (403) of the adjacent tooth grooves of the two teeth (401) of the double-tooth traction wheel (102) on the pitch circle. The center distance (304) between the two cranks is the vertical distance between the center lines of the two cranks (301). The pitch (403) of the tooth grooves on the pitch circle is the vertical distance of the straight line perpendicular to the tooth (401) drawn through the intersection of the center lines of the adjacent tooth grooves of the two teeth and the pitch circle of the tooth (401).

3. The hyperboloid crankshaft double-tooth disc rope transmission mechanism for a solar tracker according to claim 2, characterized in that, The double-toothed traction wheel (102) is an integral structure. The double-toothed traction wheel (102) includes two toothed discs (401) with the same specifications and dimensions and a cylindrical rope winding wheel (402). The two toothed discs (401) are respectively fixed at both ends of the rope winding wheel (402). The tooth spacing (404) between the two toothed discs (401) is the same as the north-south spacing (302) between the two cranks of the double crankshaft (101). The two toothed discs (401) have the same number of teeth and tooth groove specifications. When combined into a whole, they deflect each other at the angle corresponding to the pitch (403) of the adjacent tooth grooves on the pitch circle. The pitch (403) angle of the tooth grooves of the double toothed disc (401) on the pitch circle is 360° divided by the number of teeth of the toothed disc (401) and then divided by 2. Furthermore, the center line of any tooth groove of any toothed disc (401) is aligned with the center line of the tooth of the other toothed disc (401).

4. The hyperboloid crankshaft double-tooth disc rope transmission mechanism for a solar tracker according to claim 3, characterized in that, One end of the pair of transmission ropes (103) is fixed on the winding wheel (402) of the double-toothed traction wheel (102) and wound around several times. The other end is led out crosswise and then pulled up symmetrically along the semicircular part of the semicircular swing beam (104) and fixedly connected to the semicircular swing beam (104). The winding method (601) of the transmission ropes (103) is cross-winding.

5. A hyperboloid crankshaft double-tooth disc rope transmission mechanism for a solar tracker according to claim 4, characterized in that, The semi-circular swing beam (104) is an integral structure, including a crossbeam, a bearing sleeve and a semi-circular grooved component. The bearing sleeve is located in the middle of the crossbeam and is a bearing used to support the rotation of the semi-circular swing beam (104). The semi-circular grooved component is connected to the crossbeam, which allows the transmission rope (103) to be tensioned. The bracket structure (202) for installing the photovoltaic array is fixedly connected to the integrated structure of the semi-circular swing beam (104).

6. A hyperboloid crankshaft double-tooth disc rope transmission mechanism for a solar tracker according to claim 5, characterized in that, The column (105) has at least three shafts or bushings arranged vertically from top to bottom. The uppermost shaft or bushing is used to locate the rotation center of the semi-circular swing beam (104), the middle shaft or bushing is used to locate the rotation center of the double-curved crankshaft (101), and the lowermost shaft or bushing is used to locate the rotation center of the double-toothed traction wheel (102). The three rotation center lines are all oriented north-south and are parallel to each other.

7. A hyperboloid crankshaft double-tooth disc rope transmission mechanism for a solar tracker according to claim 6, characterized in that, The two cranks (301) of the hyperboloid crankshaft (101) correspond one-to-one with the two gears (401) of the double-tooth traction wheel (102), and are in an alternating or simultaneous meshing state. Each rotation of the hyperboloid crankshaft (101) drives each gear (401) of the double-tooth traction wheel (102) to rotate one tooth. The hyperboloid crankshaft (101) and the double-tooth traction wheel (102) are in a transmission state (501) and a locking state (502). When the double crankshaft (101) rotates, when both cranks (301) simultaneously engage with the tooth groove of the double-toothed traction wheel (102), the double-toothed traction wheel (102) remains stationary, and the rotational force of the photovoltaic array is limited to achieve self-locking, which is the locked state (502). When the double crankshaft (101) rotates to the point where one crank (301) disengages from the tooth groove and the other crank (301) penetrates into the tooth groove, it drives the double-toothed traction wheel (102) to rotate and realizes the solar tracking action of the photovoltaic array, which is the transmission state (501). The actions of one crank (301) disengaging from the tooth groove and the other crank (301) penetrating into the tooth groove are performed simultaneously and alternately mesh. In the transmission state (501), the torsional motion of the photovoltaic array under external force can be transmitted back to the double crankshaft (101); in the locking state (502), the two cranks (301) are horizontal and simultaneously engaged. At this time, no matter how much external force passes through the double crankshaft (101), it cannot continue to push the double crankshaft (101) to rotate. This state is the final dead point state of the photovoltaic array under external force, which can realize the passive self-locking of the photovoltaic array.

8. A hyperboloid crankshaft double-tooth disc rope transmission mechanism for a solar tracker according to claim 7, characterized in that, The mating part of the double-crank crankshaft (101) and the bushing of the column (105), as well as the shaft head at the other end, extend outward by a certain length. The shaft head is used to connect with the shaft head of the double-crank crankshaft (101) of another set of column assemblies through the transmission shaft (201). The center lines of the two shaft heads of the same double-crank crankshaft (101) are collinear, and the center lines of the two cranks are equidistant from the center lines of the shaft heads, but in opposite directions.

9. A hyperboloid crankshaft double-tooth disc rope transmission mechanism for a solar tracker according to claim 8, characterized in that, The tooth groove width of the tooth disk (401) is equal to the diameter of the cylindrical part of the crank (301) of the double crankshaft (101) plus an appropriate clearance; the center distance (304) between the two cranks of the double crankshaft (101) is the same as the pitch (403) of the adjacent tooth grooves of the two tooth disks (401) of the double tooth disk traction wheel (102) on the pitch circle; the tooth groove center line of any tooth disk (401) of the two tooth disks (401) is aligned with the tooth center line of the other tooth disk (401).

10. A hyperboloid crankshaft double-tooth disc rope transmission mechanism for a solar tracker according to claims 1-9, characterized in that, It includes several column assemblies, a drive shaft (201), and a drive motor (106); the column assemblies are arranged in a row along the north-south direction, the drive shaft (201) connects the double-cranked crankshafts (101) of all column assemblies into one unit, and the drive motor (106) is connected to the double-cranked crankshaft (101) of one of the column assemblies, which can drive all the double-cranked crankshafts (101) to rotate synchronously, and drive the photovoltaic array connected to the bracket structure (202) for mounting the photovoltaic array to rotate synchronously for solar tracking through the transmission mechanism of all column assemblies; The transmission ratio from the drive shaft (201) of the bracket structure (202) for installing the photovoltaic array to the semi-circular swing beam (104) is the product of the number of teeth on the toothed disc (401) of the double-toothed traction wheel (102) and the ratio of the semi-circular diameter of the semi-circular swing beam (104) to the diameter of the rope-winding wheel (402) of the double-toothed traction wheel (102). The transmission ratio is not less than 1:

100. The torsional torque generated by the photovoltaic array under external force is directly borne and absorbed by each column (105) through the passive self-locking function of the locked state (502). It cannot be transmitted to the drive motor (106) in reverse. Instead, it is blocked by the double crankshaft (101) and then transmitted to the column (105), thereby realizing the local absorption of the external force on the photovoltaic array and improving the stability of the entire solar photovoltaic tracking bracket system.

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