HYDRAULIC ACTUATOR WITH DUAL PNEUMATIC OPERATION APPLIED AS HYDRAULIC ACTUATION FOR HYDROELECTRIC POWER PLANTS

Abstract

A hydraulic actuator with dual pneumatic operation, used in hydroelectric power plants, specifically in the field of hydropneumatic units generating hydraulic pressure for the operation of intake valves of hydroelectric power plants. The hydropneumatic actuator (1) comprises a hydropneumatic block (2) featuring two pneumatic pumps (4 and 4a) fixed to the base (32). This block accommodates the cup assembly (36), within which resides a cylinder (37) housing the plunger guide (38). The plunger guide (38) is attached to the shaft end (39), which is securely and firmly fastened to the cup end (36) using a guide nut (40). The hydraulic actuator (47) can be articulated by fitting the female eyelet (48) into the male eyelet (50), both of which being secured by the pin (51).

Claims

1. A hydraulic actuator with dual pneumatic operation for hydroelectric power plants comprising a hydropneumatic actuator (1), comprising a hydropneumatic block (2) receiving a fitting and fixing outlets (3 and 3a) of two pneumatic pumps (4 and 4a) aligned parallel to each other; hydropneumatic block (2) receives a circular hole (5) with a depth until connecting to a high-pressure line, for fitting a coil (6) of a 2-way, 2-position directional hydraulic seat valve (7), side-mounted next to the electrical connector (8); the electrical connector (8) is an electrical connection of the electric coil (6) for an electric actuation of the directional hydraulic seat valve (7); a hole (9H) having is a ball housing (10i) locked by Allen screw (19a) and ball housing (10j) hole (91); a hydropneumatics block (1) receives a passage hole (9) on its front face for mounting a ball (10), such ball being mounted on a guide pin (11), wherein the guide pin is pressured by a compression spring (12), said compression spring being supported on a sealing ring (13) which is locked by a relief valve screw (14) forming a relief valve assembly (15) responsible for limiting the operating pressure of the system; a pressure of the compression spring (12) is regulated by the relief valve screw (14); the hole (9a) and the hole (9b) receive, respectively, the ball assembly (10a) and the ball (10b) used for static and dynamic sealing; a left side of the hydropneumatic block (2) receives the ball assembly (10c) housed in the closure retainer (16), which fits into the threaded closing screw (17) operated by a handle (18); a closure retainer (16) is the seal of the closing screw (17) responsible for activating the ball (10c) that closes the oil passage hole (9c); wherein a closure occurs by means of the tightening pressure of the Allen screw (19) on the ball (10d); the ball (10e) is pressed by a fisherman's spring (20) which fits into a fastening screw (21) with sealing washer (22); a regulator screw (23) with sealing ring (24) fits into the hole (9d) and receives the nut threading at the opposite end (25) to lock the position of the regulator screw (23) that regulates the oil flow; the ball assembly (10f) hole (9e) is pressed by the fisherman's spring (26) fitted and locked by the fastening screw (27); the ball fitting (10g) hole (9f) and the ball fitting (10h) hole (9g) are retained by the screw (28); the socket hole (9j) and ball assembly (101) are fitted and pressed by spiral spring (19b) retained by the Allen screw (29); the socket hole (91) and ball assembly (10m) are fitted and pressed by the spiral spring (19c) retained by the screw (29a); the socket hole (9m) and ball assembly (10n) are fitted and pressed by the spiral spring (19d) retained by the screw (29b); O-rings (52) seal the oil channels between hydropneumatic block (2) and the hydraulic actuator (47); the base (32) is fixed by larger screws (30) that pass through the longitudinal tunnels (31) of the hydropneumatic block (2); the base (32) is for mounting the cup (36) which accommodates the cylinder (37) of the piston guide housing (38) fitted to the shaft end (39) fixed and locked to the cup end (36) by means of a guide nut (40).

2. The hydraulic actuator with dual pneumatic operation for hydroelectric power plants according to claim 1, wherein the hydraulic actuator (47) is formed by: a rectangular base (32) having a circular channel (34) fitting the flat ring (35) sealing the cup (36) that accommodates inside the plunger (38) guide housing cylinder (37) fitted to the shaft end (39) that transfers the force of the plunger (38) to an external connection; a shaft (39) moved on the inside of the cylinder (37); the shaft (39) fixed and locked at the cup end (36) by means of a guide nut (40) that holds the ring (42) and the scraper (41) secured; d. The cup (36) is an oil reservoir with a closing plug (53) closing the oil supply nozzle; a sealing ring (43) serves to seal the cylinder (37) at the base (32); a fiber ring (44) is to seal the cup (36) against the guide nut (40); a shaft gasket (45) is a plunger seal (38); an anti-extrusion ring (46) prevents extrusion of the shaft gasket (45); a base (32) is attached to the female eyelet (48) by means of screws (49); a female eyelet (48) is fitted, retained and hinged in the male eyelet (50) by means of a pin (51).

3. The hydraulic actuator with dual pneumatic operation for hydroelectric power plants according to claim 1, wherein the pneumatic pumps (4 and 4a) operate in drive synchrony.

4. The hydraulic actuator with dual pneumatic operation for hydroelectric power plants according to claim 1, wherein the hydropneumatic block (2) in its inner part has a plurality of tubes (33) that interconnect and that, together with the valve sets, releases or blocks the air passage.

5. The hydraulic actuator with dual pneumatic operation for hydroelectric power plants according to claim 1, wherein the hydraulic actuator is applied to hydroelectric power plants.

6. The hydraulic actuator with dual pneumatic operation for hydroelectric power plants according to claim 1, wherein the actuator, oil reservoir and controls are all assembled as a hydropneumatic system.

7. The hydraulic actuator with dual pneumatic operation for hydroelectric power plants according to claim 1, wherein the hydraulic actuator requires at least one electric and pneumatic power supply point to operate.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The attached drawings show the hydropneumatic actuator applied as a drive for hydroelectric power plants, which together with the numerical references detailed below, is more easily understood, although this invention can vary in many different constructive forms, always customized for each application, not shown in the drawings that will be described here in detail and ways to carry out the referred improvement.

[0021] FIG. 1 shows an exploded perspective view.

[0022] FIG. 2 illustrates a view of the assembled hydropneumatic actuator.

[0023] FIG. 3 shows an exploded view of the hydropneumatic block.

[0024] FIG. 4 shows a view of the assembled hydropneumatic block.

[0025] FIG. 5 shows a view of the assembled hydropneumatic block in partial section.

DESCRIPTION OF THE UTILITY MODEL

[0026] According to the attached figures, the hydropneumatic actuator is generally indicated by the number reference (1), being characterized by a cube-shaped hydropneumatic block (2) that has several holes on all six faces, these holes being internal interconnection points between the channels with valve systems that release or prevent the passage of oil.

[0027] The cube-shaped hydropneumatic block (2) houses the control elements and makes the necessary hydraulic connections.

[0028] The hydropneumatic block (2) receives on its lower surface the fitting and fixing of the outlets (3 and 3a) of the two pneumatic pumps (4 and 4a) aligned parallel to each other.

[0029] The two pneumatic pumps (4 and 4a) operate in drive synchrony, increasing the speed of the hydraulic actuator drive (47).

[0030] The hydropneumatic block (2) receives a hole (5) on its lower face, circular with a depth until it connects to the high-pressure line, for fitting the coil (6) of the 2-way, 2-position directional hydraulic seat valve (7), laterally mounted next to the electrical connector (8) of the electrical connection of the electric coil (6) responsible for the electric actuation of the directional hydraulic seat valve (7).

[0031] On the upper side, there is also a hole (9h) to house the ball (10i) locked by an Allen screw (19a), and a hole (9i) for housing the ball (10j).

[0032] The hydropneumatic block (1) receives a passage hole (9) on its front face for mounting the ball (10), such ball being mounted on the guide pin (11), the pin, by its turn, being pressured by the compression spring (12), the spring being supported on the sealing ring (13) which is locked by the screw (14) forming the relief valve assembly (15) responsible for limiting the operating pressure of the system.

[0033] The compression spring (12) exerts pressure on the guide pin (11) which transfers it to the ball (10), this condition that seals the passage of oil through the hole and opens when the force resulting from the oil pressure overcomes the force of the spring (12).

[0034] The pressure of the compression spring (12) is regulated by the relief valve screw (14) which sets the opening pressure.

[0035] The hole (9a) and the hole (9b) receive, respectively, the ball assembly (10a) and the ball (10b) used for static and dynamic sealing.

[0036] On the left side, the hydropneumatic block (2) receives the ball assembly (10c) housed in the closure retainer (16), which fits into the threaded closing screw (17) operated by a handle (18).

[0037] The closure retainer (16) works to seal the closing screw (17) responsible for activating the ball (10c) that closes the hole (9c) for the oil passage.

[0038] The closing screw (17) is turned manually by means of a handle (18) which, depending on the direction of rotation, opens or closes the oil passage.

[0039] Further closure occurs by means of the tightening pressure exerted by the Allen screw (19) on the ball (10d).

[0040] The ball (10e) is pressed by the fisherman's spring (20) which fits into the fastening screw (21) with sealing washer (22).

[0041] On the right side, the regulator screw (23) is mounted with a sealing ring (24), which fits into the hole (9d), receiving the nut threading (25) at the opposite end.

[0042] The nut (25) has the function of locking the position of the regulator screw (23) that regulates the oil flow.

[0043] Still on the right side, in the hole (9e), the ball (10f) is assembled, pressed by the fisherman's spring (26), fitted and locked by the fastening screw (27).

[0044] Another hole (9f) is for ball fitting (10g) and the hole (9g) is for fitting the ball (10h) retained by the screw (28).

[0045] The back face features a socket hole (9j) and ball assembly (101) fitted and pressed by spiral spring (19b) retained by the Allen screw (29).

[0046] The socket hole (91) and ball assembly (10m) fitted and pressed by the spiral spring (19c) retained by the screw (29a).

[0047] The socket hole (9m) and ball assembly (10n) fitted and pressed by the spiral spring (19d) retained by the screw (29b).

[0048] The front face is oriented towards the base (32) to be fixed by larger screws (30) that pass through the longitudinal tunnels (31) of the hydropneumatic block (2).

[0049] Between the base assembly (32) and the hydropneumatic block (2) the o-rings (52) are placed to seal the oil channels between the hydropneumatic block (2) and the hydraulic actuator (47).

[0050] The hydropneumatic block (2) in its inner part is endowed with a plurality of tubes (33), these tubes interconnecting together with the valve sets, releasing or blocking the passage of air and oil.

[0051] The rectangular base (32) features a circular channel (34) fitting the flat ring (35) sealing the cup (36) that accommodates inside the plunger (38) guide housing cylinder (37) fitted to the shaft end (39) that transfers the force of the plunger (38) to an external connection.

[0052] The shaft (39) travels on the inside of the cylinder (37) due to pressure creating a resultant force.

[0053] The shaft (39) is fixed and locked at the end of the cup (36) by means of a guide nut (40) that also holds the ring (42) and the scraper (41) that prevents contaminants from entering the hydraulic actuator (47).

[0054] The cup (36) is an oil reservoir and receives on its side the plug assembly (53) responsible for closing the oil supply nozzle.

[0055] The sealing ring (43) seals the cylinder (37) at the base (32).

[0056] The fiber ring (44) seals the cup (36) against the guide nut (40).

[0057] The shaft gasket (45) is used to seal the plunger (38).

[0058] The anti-extrusion ring (46) prevents extrusion of the shaft gasket (45).

[0059] The base (32) is attached to the female eyelet (48) by means of screws (49).

[0060] The female eyelet (48) is fitted, retained and hinged in the male eyelet (50) by means of a pin (51).

[0061] The tilt joint that occurs between the female eyelet (48) and the male eyelet (50) allows the entire hydraulic actuator (47) and the hydropneumatic block (2), which is attached to it, to move at tilt angles during the shaft drive (39).

[0062] That is, the tilt joint of the hydropneumatic block (2) with two pneumatic pumps (4 and 4a) fixed to the hydraulic actuator (47) occurs at the pin (51) that joins and articulates the female eyelet (48) in the male eyelet (50).