• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Hydraulic drive system and control method. Hydraulic drive system comprising two cylinders and control method of said hydraulic drive system. The invention is based on the tank connection of the chambers of the cylinders passing through the dead zones. This putting into tank occurs through the opening of the braking valves of the cylinder that passes through the dead zone and the connection to the tank of its two chambers by means of its solenoid valve. In the tank, the pressure is zero and therefore no unwanted loads are exerted on the mechanism when passing through said dead zones, thus avoiding the problem of overpressures that are generated in the hydraulic drive system when a piston passes through the dead center . (Machine-translation by Google Translate, not legally binding)
    公开号:ES2544502A1
    申请号:ES201400064
    申请日:2014-01-24
    公开日:2015-08-31
    发明作者:Justo ALBARRRÁN LIGERO；Esteve CODINA MACIÁ；Juan José PÉREZ CARDO
    申请人:Abengoa Solar New Technologies SA；
    IPC主号:
    专利说明:

    production with the consequent loss of power generation of the plant. So far and to withstand the external wind loads, which are the most common, there are braking valves that control the irreversibility of the cylinders. These valves must be tared at a high pressure so as not to let the cylinders move in front of these external loads and lose the solar pointing. EP2535663 discloses a solar tracker that has an electrohydraulic adjustment device with a pressure source, a tank and an electronic controller, where the adjustment device has two double-sided pressurized hydraulic cylinders, where each hydraulic cylinder has a group of valves. In the valve groups there is a brake control valve consisting of a throttle valve with adjustable flow. The four-position solenoid valve groups also present where one of the positions is with the four tracks closed - a position that is not necessary in the invention. In EP2535663 there is no interaction between the cylinders to obtain a line with pilot pressure. Additionally, the block detailed in fig. 3 of EP2535663 indicates that the invention of EP2535663 is focused on providing extra hydraulic rigidity in the cylinder but does not solve the problem of passing through the neutral. EP2226592 shows a typical configuration for parabolic trough solar trackers, in addition to a basic hydraulic circuit, where there is no line with pilot pressure or any relationship between the cylinders. EP2226592 shows a device that has hydraulic cylinders, whose operating lines are connected to pressure sources, ie pumps and / or a tank during a cycle. The operating valves of the hydraulic circuit, for example slide valves, have actuating magnets. The lines are connected to the valves and the chambers on each side of the piston of one of the cylinders and the chambers on each side of the piston of the other cylinder are connected to the pressure sources by means of the actuating magnets. The magnet of one of the valves is supplied with current, during the cycle. In this way, the invention poses a solution to the problem of the overpressures that are generated in the hydraulic circuit when a piston passes through the neutral. Description of the invention
    The present invention proposes a solution to the problem posed above by a hydraulic drive system and its control method.
    Within the scope of the present invention, the dead center is defined as the theoretical point of change of movement of the cylinder, at which time the rod passes from going out to entering, or from entering to leaving, of the cylinder liner. Because this theoretical point is impossible to establish physically in practice, the dead zone is defined as the zone in which the cylinder that goes through the neutral point is connected to the tank. The dead zone is therefore established as the operating range of the cylinder in the scope of the invention. The hydraulic drive system comprises two cylinders (homologous cylinder and cylinder), a series of maximum pressure valves (brake valves and safety valves) and a series of flow dividers. Within the scope of the invention, the maximum pressure valves are set at their corresponding set pressure, pressures at which said valves open. The flow dividers are elements with two inlets and one outlet that connects the outlet to the higher pressure inlet. Maximum pressure valves and flow dividers are used to direct the fluid through the circuit according to different operating modes. The brake valves are connected to each chamber of each cylinder, so that when a cylinder is going through the dead zone, the brake valves allow the movement of the cylinder without exceeding the maximum setting pressure of the brake valves , pressure at which the mechanism would be affected. In the position near the neutral, that is, in an area of uncertainty called the dead zone, a cylinder must change its movement to the opposite. This zone of uncertainty is considered as the dead zone in which the cylinder is connected to the tank by means of its solenoid valve. Because its homologous cylinder is currently providing the mechanism to operate, the homologous cylinder must drag the cylinder through the dead zone. To be able to drag it, it is necessary that the hydraulic fluid circulates through the chambers of the cylinder that passes through the dead zone. Each cylinder has two chambers, and each chamber has a brake valve connected. Due to the high setting pressure of the brake valves to withstand the maximum possible external load, the cylinder that is dragged by the actuator would not move unless this set pressure was exceeded, generating forces that could break the parts. system mechanics without an apparent large outside force. If this pressure is reached, unwanted and dangerous damage to the azimuthal mechanism could occur. The invention is based on the tank connection of the chambers of the cylinders that pass through the dead zones. In the tank, the pressure is zero, and therefore unwanted loads are not exerted on the mechanism when passing through the dead zones. This tank set-up occurs through the opening of the brake valves of the cylinder that passes through the dead zone, and the tank connection of its two chambers by means of its solenoid valve. The opening of the braking valves is provided by the greater of the two pressures that come from the chambers of the cylinder homologous to the cylinder that will pass through the dead zone. The homologous cylinder, which works normally, brings the pressure of its chamber at higher pressure to the brake valves of the cylinder that passes through the dead zone through a pilot. This pilot pressure is achieved by means of an auxiliary circuit that has connections fed with the pressures of the cylinder chambers. The auxiliary circuit also comprises three flow dividers, configured in such a way that the highest pressure of the auxiliary circuit arrives through the pilot line to open the brake valve of the cylinder that is passing through the dead zone. In other words, the highest pressure in the circuit is what governs the auxiliary circuit. The pilot pressure that comes through the pilot line is multiplied by the pilot ratio of the brake valves, thus opening the brake valves long before reaching their set pressure. The pilot ratio in braking valves is achieved by a section ratio. This sectional relationship allows the effective pressure acting on the pilot of the brake valve to be the result of multiplying the pressure that arrives on the pilot line by the pilot ratio. With this configuration, a passage through the soft dead zone is achieved without providing the system with unnecessary dangerous overload. In addition, this configuration of the auxiliary circuit with the flow dividers, allows to obtain a pilot signal from the cylinder that is not passing through the dead zone, without the need to add a new solenoid valve to generate a pilot signal. The hydraulic actuation system also includes safety valves that control the passage of hydraulic fluid into each cylinder chamber. There is a safety valve per chamber. These safety valves always let hydraulic fluid pass into the cylinder chambers, but never let hydraulic chambers flow out of the cylinder: if so, any external force (for example wind, snow, the follower's own weight and , in general, any force
    or pressure exerted on the mechanism or follower that may produce an unwanted movement in the follower and that opposes the movement orders given to the system) could move the cylinder and blur the solar tracker when it is being monitored. The set pressure of the safety valves is defined as the pressure that must be overcome by the external force to move the cylinder. If the follower is very large, the force exerted by the wind is greater, because the follower, having a large surface, receives as a result of the pressure exerted by the wind on its entire surface a high force, and therefore its setting I must be older. That is, the larger the tracker, the more surface on which the wind can act and, consequently, the greater force exerted by the wind on the tracker, then the set pressure must also be greater if the size of the follower is. Another way to withstand more load is to increase the section of the cylinder without changing the set pressure. Brief description of the drawings
    Figure 1 shows a diagram of the hydraulic drive system before theCritical position or neutral. It can be seen that both cylinders are far from thedead zones, represented as scratched sectors.Figure 2 shows a diagram of the hydraulic drive system in theCritical position or neutral. It can be seen that one of the cylinders is in the zonedead.Figure 3 shows a diagram of the hydraulic drive system afterthe critical position or neutral. It can be seen that the cylinder that was in the areadead has already passed it.Figure 4 shows a detail of the scheme of the hydraulic drive system.Figure 5 shows the hydraulic drive system with the two cylindersconnected to tank.The components of the invention are included below:homologous drive cylinders (1000, 1000H);tank (T)First Camera (1010)second chamber (1010 ')piston (1011)first homologous chamber (101 OH)second homologous chamber (101 O'H)homologous piston (1011 H)first brake valve (2000)
    first set pressure of the brake valve (PF1)
    first pilot pressure (PP1)
    first pilot ratio (RP1)
    first duct (1)
    second duct (2)
    second brake valve (2000 ')
    second set pressure of the brake valve (PF2)
    second pilot pressure (PP2)
    second pilot ratio (RP2)
    third duct (3 ')
    fourth conduit (4 ')
    First homologous brake valve (2000H)
    First set pressure of the homologous brake valve (PF1 H)
    First homologous pilot pressure (PP1 H)
    first homologous pilot ratio (RP1 H)
    first homologous duct (1 H)
    second homologous duct (2H)
    second homologous brake valve (2000'H)
    second set pressure of the homologous brake valve (PF2H)
    second homologous pilot pressure (PP2H)
    second homologous pilot ratio (RP2H)
    third homologous duct (3'H)fourth homologous duct (4'H)
    pilot line (1 OOLP)flow divider (100)output (103)First Entry (101)second entry (102)homologous flow divider (100H)homologous output (1 03H)first homologous input (101 H)second homologous input (102H)symmetry flow divider (1 OOS)first symmetry input (101 S)second symmetry input (1 02S)
    symmetry output (1038)
    first safety valve (3000)
    first set pressure of the safety valve (P81)
    fifth duct (5)
    sixth conduit (6)
    second safety valve (3000 ')
    second set pressure of the safety valve (P82)
    seventh conduit (7 ')
    eighth duct (8 ')
    First homologous safety valve (3000H)
    First setting pressure of the homologous safety valve (P81 H)
    fifth homologous duct (5H)
    sixth homologous duct (6H)
    second homologous safety valve (3000'H)
    second setting pressure of the homologous safety valve (P82H)
    seventh homologous duct (7'H)
    eighth homologous duct (8'H)
    pump (7000)
    solenoid valve (4000)
    ninth conduit (9)
    tenth conduit (10)
    eleventh conduit (11)twelfth conduit (12)direct position (41)reverse position (42)tank position (43)actuator (5000)homologous solenoid valve (4000H)ninth homologous duct (9H)10th homologous duct (10H)eleventh homologous duct (11 H)twelfth homologous duct (12H)direct homologous position (41 H)homologous inverse position (42H)homologous tank position (43H)
    homologous actuator (5000H)sensor (6000)means of action (56). Description of a preferred embodiment
    An embodiment of the invention illustrated in Figures 1, 2 and 3 refers to a systemHydraulic drive The critical pressure is reached when the pistonof a cylinder will pass through the neutral or critical position. In Figures 1-5 it isillustrates the dead zone for each of the cylinders as the striped sectors in thecircle representing the turn in azimuth. The hydraulic drive systemcomprises: two homologous drive cylinders (1000, 1000H); a tank (T)that has hydraulic fluid; a pump (7000) configured to aspirate fluidhydraulic tank (T) and pump the hydraulic fluid to the two cylinders ofdrive (1000, 1000H) during a working movement of the systemhydraulic drive The hydraulic drive system comprises meansConnection (2000, 2000 ', 2000H, 2000'H, 100LP, 100, 100H, 1008, 4000, 4000H, 2,4 ', 2H, 4'H) between the drive cylinders (1000, 1000H) and the tank (T)configured for, during the working movement of the drive systemHydraulic: allow a first cylinder connection of the cylindersdrive (1000, 1000H) to tank (T); and to allow the first cylinder of thedrive cylinders (1000, 1000H) be dragged by a second cylinder ofthe drive cylinders (1000, 1000H).According to other features of the invention, the drive cylinders(1000, 1000H) may comprise chambers (1010, 1010 ', 1010H, 1010'H); theconnection means (2000, 2000 ', 2000H, 2000'H, 100LP, 100, 100H, 1008, 4000,4000H, 2, 4 ', 2H, 4'H) may comprise: a braking valve (2000, 2000',2000H, 2000'H) connected to each chamber (1010, 1010 ', 1010H, 1010'H); a circuitauxiliary (100LP, 100, 100H, 1008,2,4 ', 2H, 4'H) configured to open a valvebraking (2000, 2000 ', 2000H, 2000'H).Additionally, the auxiliary circuit (100LP, 100, 100H, 1008, 2, 4 ', 2H, 4'H) cancomprise a pilot line (100LP) connected to the brake valves
    (2000, 2000 ', 2000H, 2000'H) configured to deliver a pilot pressure to
    the braking valves (2000, 2000 ', 2000H, 2000'H).Additionally, the auxiliary circuit (100LP, 100, 100H, 1008, 2, 4 ', 2H, 4'H) can
    comprise: ducts (2, 4 ', 2H, 4'H) fed with chamber pressures
    (1010, 1010 ', 1010H, 1010'H); flow dividers (100, 100H, 1008) configured to obtain a pilot pressure from the chamber pressures (1010, 1010 ', 1010H, 1010'H). Additionally, the connection means (2000, 2000 ', 2000H, 2000'H, 100LP, 100, 100H, 1008.4000, 4000H, 2.4', 2H, 4'H) may comprise: solenoid valves (4000, 4000H) configured to allow hydraulic fluid flows between the chambers (1010, 1010 ', 101 OH, 101 O'H) and an element selected between the tank (T) and the pump (7000). According to other features of the invention: A double acting drive cylinder (1000) may comprise: a first chamber (1010) configured to be filled / emptied of hydraulic fluid; a second chamber (1010 ') configured to be filled / emptied of hydraulic fluid; a piston (1011) configured to be displaced along the cylinder (1000) when the first chamber (1010) is filled / emptied and the second chamber (1010 ') is emptied. A double acting homologous drive cylinder (1000H) may comprise: a first homologous chamber (101 OH) configured to be filled / emptied of hydraulic fluid; a second homologous chamber (101 O'H) configured to be filled / emptied of hydraulic fluid; a homologous piston (1011 H) configured to be displaced along the homologous cylinder (1000H) when the first homologous chamber (101 OH) is filled / emptied and the second homologous chamber (101 O'H) is emptied / filled. The hydraulic actuation system can optionally also comprise: - A first brake valve (2000) set at a first brake valve set pressure (PF1); which has a first pilot pressure (PP1) and a first pilot ratio (RP1); configured to: be connected between a first conduit (1) in communication with the first chamber (1010) and a second conduit
    (2) in communication with the tank (T); being in a normally closed position preventing a flow of hydraulic fluid; be opened when the first setting pressure of the braking valve (PF1) is reached as a result of a sum of a pressure in the first chamber (1010) and the first pilot pressure (PP1) multiplied by the first pilot ratio (RP1). -A second brake valve (2000 ') set at a second set pressure of the brake valve (PF2); having a second pilot pressure (PP2) and a second pilot ratio (RP2); configured to: be connected between a third conduit (3 ') in communication with the second chamber (1010') and a fourth conduit (4 ') in communication with the tank (T); being in a normally closed position preventing a flow of hydraulic fluid; be opened when the second set pressure of the brake valve (PF2) is reached as a result of a sum of a pressure in the second chamber (1010 ') and the second pilot pressure (PP2) multiplied by the second ratio of piloting (RP2). -A first homologous brake valve (2000H): set at a first set pressure of the homologous brake valve (PF1 H); having a first homologous pilot pressure (PP1 H) and a first homologous pilot ratio (RP1 H); configured to: be connected between: a first homologous conduit (1 H) in communication with the first homologous chamber (101 OH) and a second homologous conduit (2H) in communication with the tank (T); being in a normally closed position preventing a flow of hydraulic fluid; be opened when the first set pressure of the homologous brake valve (PF1 H) is reached as a result of a sum of a pressure in the first homologous chamber (101 OH) and the first homologous pilot pressure (PP1 H) multiplied for the first homologous pilot relationship (RP1 H). -A second homologous brake valve (2000'H): set at a second set pressure of the homologous brake valve (PF2H); having a second homologous pilot pressure (PP2H) and a second homologous pilot ratio (RP2H); configured to: be connected between: a third homologous conduit (3'H) in communication with the second homologous chamber (101 O'H) and a fourth homologous conduit (4'H) in communication with the tank (T); being in a normally closed position preventing a flow of hydraulic fluid; be opened when the second set pressure of the homologous brake valve (PF2H) is reached as a result of a sum of a pressure in the second homologous chamber (1010'H) and of the second homologous pilot pressure (PP2H) multiplied by the second homologous pilot relationship (RP2H). -A pilot line (100LP) connected to the first brake valve (2000), the
    second brake valve (2000 '), the first homologous brake valve (2000H) and the second homologous brake valve (2000'H).
    - A flow divider (100) that has two inputs (101, 102) and one output (103):
    configured to: be connected by a first input (101) to the second
    duct (2); by a second inlet (102) to the fourth conduit (4 '); allow a
    passage of hydraulic fluid to the outlet (103) from the inlet (101, 102) at higher pressure, selected from the first inlet (101) and the second inlet (102). -A homologous flow divider (100H) that has two homologous inputs (101H, 102H) and a homologous output (103H) configured to: be connected via a first homologous input (101 H) to the second homologous conduit (2H); by a second homologous input (102H) to the fourth homologous conduit (4'H); allow a passage of hydraulic fluid to the homologous outlet (103H) from the homologous inlet (101 H, 102H) at higher pressure, selected from the first homologous inlet (101H) and the second homologous inlet (102H). -A symmetry flow divider (100S) that has two symmetry inputs (101S, 102S) and a symmetry output (1 03S) configured to: be connected via a first symmetry input (101S) to the output (103) ; by a second symmetry input (102S) to the homologous output (103H); through a symmetry output (103S) to the pilot line (100LP); allow a passage of hydraulic fluid to the symmetry outlet (103S) from the symmetry inlet (101 S, 102S) at higher pressure, selected from the first symmetry inlet (101 S) and the second inlet of symmetry (102S).
    According to other features of the invention:
    The hydraulic drive system can optionally also comprise:
    a) A first safety valve (3000): set to a first set pressure of the safety valve (PS1); configured to: be connected between: a fifth conduit (5) in communication with the first chamber (1010) and a sixth conduit (6) in communication with the tank (T); being in a normally closed position preventing a flow of hydraulic fluid; be opened when the first set pressure of the safety valve (PS1) is reached in the first chamber (1010).
    b) A second safety valve (3000 '): set to a second set pressure of the safety valve (PS2); configured to: be connected between: a seventh conduit (7 ') in communication with the second chamber (1010') and an eighth conduit (8 ') in communication with a tank (T); being in a normally closed position preventing a flow of hydraulic fluid; be opened when the second set pressure of the safety valve (PS2) is reached in the second chamber (1010 ').
    c) A first homologous safety valve (3000H): set at a first set pressure of the homologous safety valve (PS1H); configured to: be connected between: a fifth homologous duct (5H) in communication with the first homologous chamber (101 OH) and a sixth homologous duct (6H) in communication with the tank (T); being in a normally closed position preventing a flow of hydraulic fluid; be opened when the first set pressure of the homologous safety valve (PS1 H) is reached in the first homologous chamber (1010H).
    d) A second homologous safety valve (3000'H): set to a second set pressure of the homologous safety valve (PS2H); configured to: be connected between: a seventh homologous conduit (7'H) in communication with the second homologous chamber (101 O'H) and an eighth homologous conduit (8'H) in communication with a tank (T); being in a normally closed position preventing a flow of hydraulic fluid; be opened when the second setting pressure of the homologous safety valve (PS2H) is reached in the second homologous chamber (101 O'H).
    According to other features of the invention, the second braking valve setting pressure (PF2) is the same as the first braking valve setting pressure (PF1).
    In one embodiment of the invention, a pilot ratio selected from the first pilot ratio (RP1); the first homologous pilot ratio (RP1 H); the second pilot ratio (RP2); the second homologous pilot ratio (RP2H); and combinations thereof are between 4 and 5. That is, it may be the case since a pilot relationship (RP1, RP1 H, RP2, RP2H) is between 4 and 5, until the four pilot relationships (RP1, RP1 H, RP2, RP2H) are between 4 and 5, through intermediate combinations where two or three pilot ratios are between 4 and 5.
    In a preferred embodiment the pilot ratio is 4.25.
    According to other optional features of the invention:
    The first set pressure of the brake valve (PF1) may be greater than the first set pressure of the safety valve (PS1). The second set pressure of the brake valve (PF2) may be greater than the second set pressure of the safety valve (PS2). The second set pressure of the safety valve (PS2) can be the same as the first set pressure of the safety valve (PS1).
    The hydraulic drive system may optionally also comprise: b) An electrovalve (4000) configured to: be connected between a ninth conduit (9) in communication with the first chamber (1010); a tenth conduit (10) in communication with the second chamber (1010 '); an eleventh conduit (11) in communication with the tank (T); a twelfth conduit (12) in communication with the pump (7000); be moved between a direct position (41) where a flow of hydraulic fluid is allowed: from the pump (7000) to the second chamber (1010 '); from the first chamber (1010) to the tank (T); an inverse position (42) where a flow of hydraulic fluid is allowed: from the pump (7000) to the first chamber (1010); from the second chamber (1010 ') to the tank (T); a tank position (43) where a flow of hydraulic fluid is allowed: from the first chamber (1010) to the tank (T); from the second chamber (1010 ') to the tank (T); c) An actuator (5000) configured to move the solenoid valve (4000) between selected positions between the direct position (41), the inverse position (42) and tank position (43); d) A homologous solenoid valve (4000H) configured to: be connected between: a ninth homologous conduit (9H) in communication with the first homologous chamber (1010H); a tenth homologous duct (10H) in communication with the second homologous chamber (1010'H); an eleventh homologous duct (11 H) in communication with the tank (T); a twelfth homologous duct (12H) in communication with the pump (7000); be displaced between: a direct homologous position (41 H) where a flow of hydraulic fluid is allowed: from the pump (7000) to the second homologous chamber (101 O'H); from the first homologous chamber (1010H) to the tank (T); a homologous inverse position (42H) where a hydraulic fluid flow is allowed: from the pump (7000) to the first homologous chamber (1010H); from the second homologous chamber (1010'H) to the tank (T); a homologous tank position (43H) where a flow of hydraulic fluid is allowed: from the first homologous chamber (101 OH) to the tank (T); from the second homologous chamber (101 O'H) to the tank (T); e) A homologous actuator (5000H) configured to move the homologous solenoid valve (4000H) between selected positions between the homologous direct position (41 H), the homologous inverse position (42H) and
    homologous tank position (43H).That is, the hydraulic drive system comprises solenoid valves.
    (4000, 4000H) that can be arranged in three positions:
    to) parallel tracks;
    b) cross roads;
    C) return to tank.
    The hydraulic drive system is configured to drive an azimuth motion of a solar tracker.
    The hydraulic drive system can optionally also comprise: a sensor (6000) configured to detect an orientation position in azimuth; actuation means (56) configured to generate a position change signal of the solenoid valve (4000, 4000H) from the orientation position in azimuth. The position change signal of the solenoid valve (4000, 4000H) from the azimuth orientation position is generated when the cylinder (1000, 1000H) is in a position close to a critical position or neutral, that is, when it approaches the dead zone, where an increase in pressure in a chamber (1010, 1010 ', 1010H, 1010'H) does not translate into a turning movement of the azimuth drive.
    Preferably, the sensor (6000) is an encoder configured to count an azimuth turn of the solar tracker. The sensor (6000) can also be a magnetic tape or any other device that allows counting the azimuth turn of the solar tracker.
    A third aspect of the invention relates to a control method of the hydraulic drive system. The method comprises the following steps: a) move a solenoid valve (4000) to a first position to: a1) move a piston (1011) in a first direction, within a cylinder (1000); and for a2) turn the cylinder (1000) in a first direction;
    b) move a homologous solenoid valve (4000H) to a first homologous position to: b1) move a homologous piston (1011H) in a first direction
    homologous, within a homologous cylinder (1000H); and for b2) rotate the homologous cylinder (1000H) in a first homologous direction; c) move the homologous solenoid valve (4000H) to a tank position, to
    connect to the tank (T) the homologous cylinder (1 OOOH) that will pass through a critical position; d) open a second homologous brake valve (2000'H) connected to the homologous cylinder (1 OOOH) that will pass through the critical position;
    e) move the homologous solenoid valve (4000H) to a second homologous position to: e1) move the homologous piston (1011 H) in a second direction
    homologous, within the homologous cylinder (1 OOOH); And for e2) turn the homologous cylinder (1000H) in a second homologous direction; f) close a first homologous brake valve (2000H) connected to the cylinder
    counterpart (1 OOOH) that has exceeded the critical position. Figures 1-3 show an operating sequence according to the method of the invention. Although the positions of the drive system components for a clockwise rotation are illustrated in this sequence, it is clear that the invention works both ways. A counterclockwise rotation takes place analogously to that illustrated in Figures 1-3. It also follows immediately that the invention contemplates the passage of any of the cylinders (1000, 1000H) through dead zones or critical points in both directions of rotation, as shown in the figures in the shaded sectors. The status of the system is shown in Figures 1-3 showing the positions of the valves at different stages of the method of the invention.
    Figure 1 shows the solenoid valve (4000) in a first position of parallel tracks where a piston (1011) is extended from the cylinder (1000). Figure 1 also shows the homologous solenoid valve (4000H) in a first parallel track position where a homologous piston (1011 H) is retracted into the homologous cylinder (1 OOOH). Figure 2 shows the homologous solenoid valve (4000H) in a tank position, where a homologous cylinder (1000H) that will pass through a critical position is connected to a tank (T). Figure 3 shows the homologous solenoid valve (4000H) in a second cross-track position, where a homologous piston (1011 H) is extended from the homologous cylinder (1000H).
    权利要求:
    Claims (19)
    [1]
    1. A hydraulic drive system comprising:1a) two homologous drive cylinders (1000, 1000H);1b) a tank (T) that has hydraulic fluid;1c) a pump (7000) configured to aspirate hydraulic fluid from the tank (T) and
    pump the hydraulic fluid to the drive cylinders (1000, 1000H)
    during a working movement of the hydraulic drive system; characterized in that it comprises: 1d) connection means (2000, 2000 ', 2000H, 2000'H, 100LP, 100, 100H, 100S,
    4000, 4000H, 2.4 ', 2H, 4'H) between the drive cylinders (1000, 1000H) and the tank (T) configured to, during the working movement of the hydraulic drive system: 1d1) allow a connection of a first cylinder of cylinders of
    drive (1000, 1000H) to tank (T); and to
    1 d2) allow the first cylinder of the drive cylinders (1000, 1000H) to be dragged by a second cylinder of the drive cylinders (1000, 1000H).
    [2]
    2. The hydraulic drive system according to claim 1 characterized in that:
    2a) the drive cylinders (1000, 1000H) comprise chambers (1010, 1010 ', 1010H, 1010'H);
    2b) the connection means (2000, 2000 ', 2000H, 2000'H, 100LP, 100, 100H, 100S, 4000, 4000H, 2, 4', 2H, 4'H) comprise: 2b1) a braking valve ( 2000, 2000 ', 2000H, 2000'H) connected to each
    chamber (1010, 1010 ', 1010H, 1010'H); 2b2) an auxiliary circuit (100LP, 100, 100H, 100S, 2, 4 ', 2H, 4'H) configured to open a brake valve (2000,2000', 2000H, 2000'H).
    [3]
    3. The hydraulic drive system according to claim 2 characterized in that the auxiliary circuit (100LP, 100, 100H, 100S, 2, 4 ', 2H, 4'H) comprises: 3a) a pilot line (100LP) connected to the braking valves (2000, 2000 ',
    2000H, 2000'H) configured to deliver a pilot pressure to the braking valves (2000, 2000 ', 2000H, 2000'H).
    [4]
    4. The hydraulic drive system according to claim 3 characterized in that the auxiliary circuit (1 OOLP, 100, 100H, 100S, 2, 4 ', 2H, 4'H) comprises: 4a) conduits (2, 4', 2H , 4'H) fed with chamber pressures (1010,
    1010 ', 1010H, 1010'H); 4b) flow dividers (100, 100H, 100S) configured to obtain a pilot pressure from the chamber pressures (1010, 1010 ', 101 OH, 101 O'H).
    [5]
    5. The hydraulic drive system according to claim 2 characterized bythat the connection means (2000, 2000 ', 2000H, 2000'H, 100LP, 100, 100H, 100S,4000, 4000H, 2, 4 ', 2H, 4'H) comprise:5a) solenoid valves (4000, 4000H) configured to allow hydraulic fluid flows
    between the chambers (1010, 1010 ', 1010H, 1010'H) and an element selected between the tank (T) and the pump (7000).
    [6]
    6. The hydraulic drive system according to claim 4 characterized bythat:6a) a double acting drive cylinder (1000) comprises:
    6a1) a first chamber (1010) configured to be filled / emptied of hydraulic fluid;
    6a2) a second chamber (1010 ') configured to be filled / emptied of hydraulic fluid;
    6a1) a piston (1011) configured to be moved along the cylinder (1000) when the first chamber (1010) is filled / emptied and the second chamber (1010 ') is emptied / filled;
    6b) a double acting homologous drive cylinder (1000H) comprises:
    6b1) afirstcamerahomologous(101 OH)configuredforbe
    lining / emptying of hydraulic fluid;
    6b2) asecondcamerahomologous(101 O'H)configuredforbe
    filling / emptying of hydraulic fluid;
    6b3) a homologous piston (11 H) configured to be displaced along the homologous cylinder (1000H) when the first homologous chamber (1010H) is filled / emptied and the second homologous chamber (101 O'H) is emptied / filled;
    6c) the first braking valve (2000): 6c1) is tared at a first braking valve setting pressure (PF1); 6c2) has a first pilot pressure (PP1) and a first ratio of
    piloting (RP1);It is configured to:6c3) be connected between:
    6c3a) a first conduit (1) in communication with the first chamber (1010) and 6c3b) a second conduit (2) in communication with an element selected between the tank (T) and the pump (7000); 6c4) being in a normally closed position preventing a flow of hydraulic fluid;
    6c5) be opened when the first braking valve set pressure (PF1) is reached as a result of a sum of a pressure in the first chamber (1010) and the first pilot pressure (PP1) multiplied by the first ratio piloting (RP1);
    6d) the second brake valve (2000 '): 6d 1) is set to a second brake valve set pressure (PF2); 6d2) has a second pilot pressure (PP2) and a second ratio of
    piloting (RP2);It is configured to:6d3) be connected between:
    6d3a) a third conduit (3 ') in communication with the second chamber (1010') and 6d3b) a fourth conduit (4 ') in communication with an element selected between the tank (T) and the pump (7000); 6d4) being in a normally closed position preventing a flow of hydraulic fluid;
    6d5) be opened when the second brake valve setting pressure (PF2) is reached as a result of a sum of a pressure in the second chamber (1010 ') and the second pilot pressure (PP2) multiplied by the second pilot ratio (RP2);
    6e) the first homologous brake valve (2000H):
    6e1) is tared at a first set pressure of the brake valve
    homologous (PF1 H); 6e2) has a first homologous pilot pressure (PP1 H) and a first
    homologous pilot ratio (RP1 H); It is configured to: 6e3) be connected between:
    6e3a) a first homologous conduit (1 H) in communication with the first homologous chamber (1010H) and 6e3b) a second homologous conduit (2H) in communication with an element selected between the tank (T) and the pump (7000); 6e4) being in a normally closed position preventing a flow of hydraulic fluid;
    6e5) be opened when the first set pressure of the homologous brake valve (PF1 H) is reached as a result of a sum of a pressure in the first homologous chamber (101 OH) and the first homologous pilot pressure (PP1 H) multiplied by the first homologous pilot ratio (RP1 H);
    6f) the second homologous brake valve (2000'H): 6f1) is set to a second set pressure of the homologous brake valve (PF2H); 6f2) has a second homologous pilot pressure (PP2H) and a second homologous pilot ratio (RP2H); It is configured to:
    6f3) be connected between:
    6f3a) a third homologous duct (3'H) in communication with the second
    homologous chamber (1010'H) and
    6f3b) afourthconduitcounterpart(4'H)incommunicationwitha
    element selected between the tank (T) and the pump (7000);
    6f4) being in a normally closed position preventing afluid passage
    hydraulic;
    6f5) be opened when the second set pressure of the brake valve
    homologous (PF2H) isreachedhowOutcomefromasumfroma
    pressure in the second homologous chamber (1010'H) and the second pressure
    from homologous piloting (PP2H)multipliedbythesecondrelationship from
    homologous piloting (RP2H);
    6g) the flow divider (100) has two inputs (101, 102) and one output (103):
    It is configured to:
    6g 1) be connected: 6g1 a) through a first inlet (101) to the second conduit (2); 6g1b) by a second inlet (102) to the fourth conduit (4 ');
    6g2) allow a fluid passage to the outlet (103) from the inlet (101, 102) at higher pressure, selected from the first inlet (101) and the second inlet (102);
    6h) the homologous flow divider (1 OOH) has two homologous inputs (101 H, 102H) and a homologous output (103H); It is configured to: 6h1) be connected:
    6h1 a) through a first homologous input (101 H) to the second homologous duct (2H); 6h1b) by a second homologous input (102H) to the fourth homologous conduit (4'H);
    6h2) allow a fluid passage to the homologous outlet (103H) from the homologous inlet (101H, 102H) at higher pressure, selected from the first homologous inlet (10 1H) and the second homologous inlet (1 02H);
    6i) the symmetry flow divider (100S) has two symmetry inputs (101 S, 102S) and one symmetry output (103S); It is configured to:
    6i1) be connected:
    6i1a) through a first symmetry input (101S) to the salida (103);
    6i1 b) throughasecondentryfromsymmetry(102S)totheexit
    homologous (103H);
    6i1 c) throughaexitfromsymmetry(103S)tothelinefrompilotage
    (100LP);
    6i2) allowafluid passagetowards the output of symmetry(1 03S) from the
    symmetry inlet (101 S, 102S) at higher pressure, selection ada between the
    first entryfromsymmetry(101 S)And thesecondentryfromsymmetry
    (102S).
    [7]
    7. The hydraulic drive system according to claim 6 characterized in that it comprises:
    7a) a first safety valve (3000): 7 to 1) set at a first set pressure of the safety valve (PS 1); configured to: 7a2) be connected between:
    7a2a) a fifth conduit (5) in communication with the first chamber (1010) and 7a2b) a sixth conduit (6) in communication with the tank (T); 7a3) being in a normally closed position preventing a flow of hydraulic fluid; 7a4) be opened when the first set pressure of the safety valve (PS1) is reached in the first chamber (1010);
    7b) a second safety valve (3000 '): 7b1) tared at a second safety valve setting pressure (PS2); configured to: 7b2) be connected between:
    7b2a) a seventh conduit (7 ') in communication with the second chamber (1010') and 7b2b) an eighth conduit (8 ') in communication with a tank (T); 7b3) being in a normally closed position preventing a flow of hydraulic fluid; 7b4) be opened when the second set pressure of the safety valve (PS2) is reached in the second chamber (1010 '); 7c) a first homologous safety valve (3000H): 7c1) tared at a first set pressure of the safety valve
    homologous (PS1 H);configured for:7c2) be connected between:
    7c2a) a fifth homologous duct (5H) in communication with the first homologous chamber (1010H) and 7c2b) a sixth homologous duct (6H) in communication with the tank (T); 7c3) being in a normally closed position preventing a flow of hydraulic fluid; 7c4) be opened when the first set pressure of the homologous safety valve (PS1 H) is reached in the first homologous chamber (101 OH);
    7d) a second homologous safety valve (3000'H):
    7d1) setting at a second setting pressure of the safety valve
    homologous (PS2H);
    configured for:
    7 d2) be connected between:
    7d2a) a seventh homologous duct (7'H) in communication with the second homologous chamber (1010'H) and 7d2b) an eighth homologous duct (8'H) in communication with a tank (T); 7d3) being in a normally closed position preventing a flow of hydraulic fluid; 7d4) be opened when the second set pressure of the homologous safety valve (PS2H) is reached in the second homologous chamber (101 O'H).
    [8]
    8. The hydraulic drive system according to claim 6 characterizedbecause the second braking valve setting pressure (PF2) is the same as thefirst set pressure of the brake valve (PF1).
    [9]
    9. The hydraulic drive system according to claim 6 characterizedwhy a selected pilot relationship between:the first pilot relationship (RP1);the first homologous pilot ratio (RP1 H);the second pilot ratio (RP2);the second homologous pilot ratio (RP2H);And combinations thereof are selected between 4 and 5.
    [10]
    10. The hydraulic drive system according to claim 9 characterizedbecause the pilot ratio is 4.25.
    [11]
    eleven. The hydraulic drive system according to claim 7 characterizedbecause the first set pressure of the brake valve (PF1) is greater than theFirst set pressure of the safety valve (PS1).
    [12]
    12. The hydraulic drive system according to claim 7 characterizedbecause the second braking valve setting pressure (PF2) is greater than the
    second setting pressure of the safety valve (PS2).
    [13]
    13. The hydraulic drive system according to claim 7 characterizedbecause the second set pressure of the safety valve (PS2) is the same as theFirst set pressure of the safety valve (PS1).
    [14]
    14. The hydraulic drive system according to claim 7 characterizedbecause it includes:14a) a solenoid valve (4000) configured for:
    14a 1) be connected between: 14a1a) a ninth conduit (9) in communication with the first chamber (1010); 14a1 b) a tenth conduit (10) in communication with the second
    chamber (1010 '); 14a1 c) an eleventh conduit (11) in communication with the tank (T); 14a1d) a twelfth conduit (12) in communication with the pump
    (7000);14a2) be displaced between:
    14a2a) a direct position (41) where a flow of hydraulic fluid is allowed: from the pump (7000) to the first chamber (1010); from the second chamber (1010 ') to the tank (T);
    14a2b) an inverse position (42) where a flow of hydraulic fluid is allowed: from the pump (7000) to the second chamber (1010 '); from the first chamber (1010) to the tank (T);
    14a2c) a tank position (43) where a flow of hydraulic fluid is allowed: from the first chamber (1010) to the tank (T); from the second chamber (1010 ') to the tank (T);
    14b) an actuator (5000) configured to move the solenoid valve (4000) between selected positions between the direct position (41), the inverse position (42) and tank position (43);
    14c) a homologous solenoid valve (4000H) configured to: 14c1) be connected between:
    14c1 a) a ninth homologous conduit (9H) in communication with the first homologous chamber (101 OH); 14c1 b) a tenth homologous duct (10H) in communication with the second homologous chamber (101 O'H); 14c1c) an eleventh homologous duct (11 H) in communication with the tank (T); 14c1 d) a twelfth homologous duct (12H) in communication with the pump (7000); 14c2) be displaced between:
    14c2a) a direct homologous position (41 H) where a flow of hydraulic fluid is allowed: from the pump (7000) to the second homologous chamber (101 O'H); from the first homologous chamber (101 OH) to the tank (T);
    14c2b) a homologous inverse position (42H) where a flow of hydraulic fluid is allowed: from the pump (7000) to the first homologous chamber (101 OH); from the second homologous chamber (1010'H) to the tank (T);
    14c2c) a homologous tank position (43H) where a flow of hydraulic fluid is allowed: from the first homologous chamber (101 OH) to the tank (T); from the second homologous chamber (101 O'H) to the tank (T);
    14d) a homologous actuator (5000H) configured to move the homologous solenoid valve (4000H) between selected positions between the homologous direct position (41 H), the homologous inverse position (42H) and homologous tank position (43H).
    [15]
    fifteen. The hydraulic drive system according to claim 6 characterized in that it is configured for the hydraulic actuation of a solar tracking system, for example the azimuth movement, and specifically to avoid dead spots in hyperstatic systems with at least two hydraulic actuators on the same movement
    [16]
    16. The hydraulic drive system according to claim 5 or 14 characterized in that it comprises: 16a) a sensor (6000) configured to detect an orientation position in
    azimuth;
    16b) actuation means (56) configured to generate an electrovalve position change signal (4000, 4000H) from the azimuth orientation position.
    [17]
    17. The hydraulic drive system according to claim 16 characterized in that the sensor (6000) is an encoder configured to count an azimuth turn of the solar tracker.
    [18]
    18. A control method of the hydraulic drive system of claim 5 characterized in that it comprises: 18a) moving the solenoid valves (4000, 4000H) to a first position for
    generate a working movement of the hydraulic drive system;
    18b) move the solenoid valve (4000, 4000H) corresponding to the drive cylinder (1000, 1000H) to a tank position to pass through a critical position, to allow a flow of hydraulic fluid to the tank (T) from the cylinder drive (1000, 1000H) that will pass through a critical position;
    18c) open the brake valve (2000, 2000 ', 2000H, 2000'H) corresponding to the drive cylinder (1000, 1000H) that will pass through a critical position, to connect the drive cylinder (1000, 1000H) to the tank (T);
    18d) move the solenoid valve (4000, 4000H) corresponding to the drive cylinder (1000, 1000H) that has passed through the critical position, to a second position to continue the working movement of the hydraulic drive system.
    [19]
    19. A control method of the hydraulic drive system according to claim 18 characterized in that it is configured for the hydraulic actuation of a solar tracking system, for example azimuth movement, and specifically to avoid dead spots in hyperstatic systems with at least two hydraulic actuators on the same movement.
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    同族专利:
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    ES2544502B1|2016-06-09|
    WO2015110688A1|2015-07-30|
    WO2015110688A4|2015-09-17|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US6123067A|1999-03-31|2000-09-26|Amonix, Inc.|Solar collector tracking system|
    ES2415410T3|2010-12-28|2013-07-25|Hawe Hydraulik Se|Solar collector|
    EP2535662B1|2011-06-16|2013-08-21|HAWE Hydraulik SE|Solar reflector with hydraulic adjustment device|
    EP2535663B1|2011-06-16|2013-10-16|HAWE Hydraulik SE|Solar reactor with hydraulic adjustment device|IT201800007167A1|2018-07-13|2020-01-13|BALANCING DEVICE|
    CN113037200A|2021-03-26|2021-06-25|西安理工大学|Hydraulic locking wind-resistant control system for double one-way electromagnetic valves of single-shaft photovoltaic tracker|
    法律状态:
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    优先权:
    申请号 | 申请日 | 专利标题
    ES201400064A|ES2544502B1|2014-01-24|2014-01-24|Hydraulic drive system and control method|ES201400064A| ES2544502B1|2014-01-24|2014-01-24|Hydraulic drive system and control method|
    PCT/ES2015/070045| WO2015110688A1|2014-01-24|2015-01-23|Hydraulic actuating system and control method|
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