Hydraulic actuator with dual pneumatic action for use in hydraulic actuation of hydroelectric power generation equipment

Abstract

This application relates to a hydraulic actuator with dual pneumatic operation, which finds application in hydroelectric power plants, specifically in hydropneumatic units that generate hydraulic pressure for operating the inlet valves of hydroelectric power plants. This form of hydropneumatic actuator (1) comprises a hydropneumatic block (2) with two air pumps (4 and 4a) fixed to a base (32). The block houses a cup assembly (36) that contains a cylinder (37) housing a plunger guide (38). The plunger guide (38) is attached to a shaft end (39), which is fixedly fastened to the cup end (36) using a guide nut (40). The hydraulic actuator (47) can be articulated by fitting a female eyelet (48) into a male eyelet (50), both of which are secured by a pin (51).

Description

[Technical Field]

[0001] The present patent application relates to a hydraulic actuator with dual pneumatic action, hereinafter referred to as a hydropneumatic actuator, the object of which is to be used in hydroelectric power plants, in particular in the field of hydropneumatic units for generating hydraulic pressure for operating the inlet valves of hydroelectric power plants. [Background technology]

[0002] Hydraulic generators are commonly applied as designs for jacks, winches, presses, cylinders, and other hydraulic equipment to increase the internal hydraulic pressure within a pressure vessel.

[0003] These hydraulic generators are widely used in current technology, including actuating inlet valves in hydroelectric power plants.

[0004] Such operations also consist of opening and closing entrance gates and spillways, and regulating and protecting hydroturbines and generators. Summary of the Invention [Problem to be solved by the invention]

[0005] Currently, this function is performed by commercially available hydraulic cylinders, which require a hydraulic unit. This configuration of components results in increased structural complexity, higher power consumption, and increased costs compared to the present application. Additionally, current systems have a significant environmental impact resulting from the manufacturing process and the large amount of oil required for operation.

[0006] Therefore, it is important to analyze each aspect of operation, and the systems currently in use exhibit low efficiency due to the structural arrangements and configurations commonly known in the current technology, which inherently entail high installation, operation and maintenance costs. It is also necessary to mention the complexity of their redundant paths and the robustness of the means of operating the current systems, such as compressors, generators, hydroelectric power plants, etc.

[0007] Another solution that this improvement reveals is that the system can be equipped with a pneumatic lung in case of a power outage, which allows the floodgates to be closed in an emergency situation where there is no power.

[0008] An interesting fact to mention is that the simplicity of the present system reduces the capacity of other components, for example it is possible to use compressors, generators and transformers with lower capacities, resulting in the economic advantages of this improvement.

[0009] The objective of this application is to provide a solution to these problems of the current technology by utilizing a hydropneumatic system as the hydraulic actuation for operating the inlet valves of hydroelectric power plants, thereby providing simplicity, technology, environmental awareness and in particular a better and safer operation of the gates of hydroelectric power plants.

[0010] The present application also aims to provide a technically, economically and environmentally viable alternative with respect to what is known in the prior art.

[0011] The document, Korean Patent No. 101570665, is a current state of the art document. The document cites a system for flood disaster prevention applied to a hydroelectric power plant.

[0012] This application has been developed to operate the inlet valves of hydroelectric power plants, preferably as an improvement over existing methods, where pneumatic actuation is generated by two air pumps mounted in parallel on a hydropneumatic block.

[0013] The actuator, reservoir, and controls are assembled into a hydropneumatic system that is installed at the operating site, requiring only the transport of compressed air hoses and electrical power connections to operate the solenoid valves. [Means for solving the problem]

[0014] The objects of this patent application are to: a. Develop a hydraulic actuator with dual pneumatic action applied to the operation of the inlet valve of a hydroelectric generating unit. b. Reducing and optimizing the elements required to manufacture the drive means of the hydroelectric generating device. c. Reducing the manufacturing costs of the drive means of the hydroelectric generating device. d. Reduced environmental impact due to reduced oil consumption in the drive means of the hydroelectric generating equipment. e. Reducing the energy consumption required for the drive means of the hydroelectric generating unit.

[0015] The accompanying drawings show a hydropneumatic actuator applied as a drive for a hydroelectric generating device, which will be more easily understood in conjunction with the reference numerals described in detail below, although the invention can take many different construction forms and ways of implementing the referenced improvements, which are not described in detail here and not shown in the drawings, and which are always customized to each application. [Brief explanation of the drawings]

[0016] [Figure 1] FIG. [Figure 2] FIG. 1 is a diagram of an assembled hydro-pneumatic actuator. [Figure 3] FIG. 2 is an exploded view of the hydro-pneumatic block. [Figure 4] FIG. 1 is a diagram of an assembled hydro-pneumatic block. [Figure 5] FIG. 1 is a partial cross-sectional view of an assembled hydro-pneumatic block. DETAILED DESCRIPTION OF THE INVENTION

[0017] According to the accompanying drawings, the hydro-pneumatic actuator is generally designated by the reference number (1) and is characterized by a cubic shaped hydro-pneumatic block (2) with several holes on all six sides, these holes being the internal interconnection points between channels with a valve system that opens or blocks the passage of oil.

[0018] A cube-shaped hydropneumatic block (2) houses the control elements and makes the necessary hydraulic connections.

[0019] The hydropneumatic block (2) receives on its underside the fitting and fixing of the outlets (3 and 3a) of two air pumps (4 and 4a) arranged parallel to each other.

[0020] The two air pumps (4 and 4a) operate in synchronism to increase the speed of the hydraulic actuator (47) drive.

[0021] The hydro-pneumatic block (2) receives on its underside a hole (5) for fitting the coil (6) of a two-way, two-position directional hydraulic seat valve (7), the hole (5) being circular and deep enough to connect to the high pressure line, the coil (6) being mounted laterally next to an electrical connector (8) for the electrical connection of the electrical coil (6) which serves to electrically operate the directional hydraulic seat valve (7).

[0022] On the upper side there is also a hole (9h) for receiving a ball (10i) locked by an Allen screw (19a), and a hole (9i) for receiving a ball (10j).

[0023] The hydropneumatic block (2) receives on its front face a through hole (9) for mounting a ball (10), which is mounted on a guide pin (11), which in turn is pressed by a compression spring (12), which is supported by a sealing ring (13) engaged by a screw (14), forming a relief valve assembly (15) which serves to limit the operating pressure of the system.

[0024] The compression spring (12) exerts pressure on the guide pin (11), which transmits the pressure to the ball (10), which 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).

[0025] The pressure of the compression spring (12) is adjusted by a relief valve screw (14) which sets the opening pressure.

[0026] The holes (9a) and (9b) receive ball assemblies (10a) and balls (10b) used for static and dynamic sealing, respectively.

[0027] On the left side, the hydro-pneumatic block (2) receives a ball assembly (10c) housed in a closure retainer (16) which in turn is fitted with a threaded set screw (17) operated by a handle (18).

[0028] The closure retainer (16) serves to seal the set screw (17) which serves to actuate the ball (10c) which closes the hole (9c) for the passage of oil.

[0029] The set screw (17) is manually turned using a handle (18), which opens or closes the oil passage depending on the direction of rotation.

[0030] Further closure occurs due to the clamping pressure exerted on the ball (10d) by the Allen screw (19).

[0031] The ball (10e) is pressed by a fisherman spring (20) which fits onto the fastening screw (21) together with a sealing washer (22).

[0032] On the right side, an adjusting screw (23) is fitted with a sealing ring (24) which fits into the hole (9d) and receives a nut (25) threadedly at its opposite end.

[0033] The nut (25) has the function of fixing the position of the adjusting screw (23) that adjusts the oil flow.

[0034] Continuing on the right side, a ball (10f) is assembled into the hole (9e), and the ball (10f) is pressed by a fisherman spring (26) and fitted and locked by a fastening screw (27).

[0035] Another hole (9f) is intended to receive a ball (10g), and hole (9g) is intended to receive a ball (10h) held by a screw (28).

[0036] The backside has a socket hole (9j) and a ball assembly (10l) fitted and biased by a spiral spring (19b) held in place by an Allen screw (29).

[0037] The ball assembly (10m) is biased by a socket hole (9l) and a spiral spring (19c) fitted and held by a screw (29a).

[0038] The ball assembly (10n) is biased by a socket hole (9m) and a spiral spring (19d) fitted and held by a screw (29b).

[0039] The front face is turned towards the base (32) and is fixed by a large screw (30) passing through a longitudinal tunnel (31) in the hydro-pneumatic block (2).

[0040] An O-ring (52) is disposed between the base assembly (32) and the hydro-pneumatic block (2) to seal the oil passage between the hydro-pneumatic block (2) and the hydraulic actuator (47).

[0041] The hydro-pneumatic block (2) has a number of pipes (33) inside it, which are interconnected with a set of valves to open and close the passage of air and oil.

[0042] The rectangular base (32) has a circular channel (34) that fits a flat ring (35) that seals the cup (36), which houses a guide-receiving cylinder (37) fitted to the axial end (39) of the plunger (38) that transmits the force of the plunger (38) to an external connection.

[0043] The shaft (39) moves inside the cylinder (37) due to the force generated by the pressure.

[0044] The shaft (39) is fixed and locked to the end of the cup (36) by a guide nut (40), which also holds a ring (42) and a scraper (41) that prevents contaminants from entering the hydraulic actuator (47).

[0045] The cup (36) is a reservoir and receives on its side a plug assembly (53) which serves to close the dispensing nozzle.

[0046] A seal ring (43) seals the cylinder (37) to the base (32).

[0047] The fiber ring (44) presses against the guide nut (40) to seal the cup (36).

[0048] A shaft gasket (45) is used to seal the plunger (38).

[0049] The anti-extrusion ring (46) prevents the shaft gasket (45) from being extruded.

[0050] The base (32) is attached to the female eyelet (48) by a screw (49).

[0051] The female eyelet (48) fits into the male eyelet (50), is held by a pin (51), and is hinged.

[0052] The inclined joint that occurs between the female eyelet (48) and the male eyelet (50) allows the entire hydraulic actuator (47) and the hydro-pneumatic block (2) attached thereto to move at an inclined angle during actuation of the shaft (39).

[0053] That is, the inclined connection between the two air pumps (4 and 4a) fixed to the hydraulic actuator (47) and the hydropneumatic block (2) occurs at a pin (51) that connects and articulates the female eyelet (48) to the male eyelet (50). [Explanation of symbols]

[0054] 1 Hydropneumatic Actuator 2 Hydropneumatic Block 3, 3a Air pump outlet 4. 4a air pump 47 Hydraulic Actuator 6 coils 7 Valves 8 Electrical Connectors 9a, 9b, 9c, 9d, 9e, 9f, 9g, 9h, 9i, 9j, 9l, 9m, 9 holes 10a, 10b, 10c, 10d, 10e, 10f, 10g, 10h, 10i, 10j, 10 ball 10c, 10l, 10m, 10n ball assemblies 11 Guide pin 12 compression spring 13 Seal ring 14, 21, 28, 29a, 29b, 30, 49 screws 16 Closure retainer 17 Set screw 18 Handle 19, 19a, 29 Allen screws 19b, 19c, 19d Spiral springs 20, 26 Fisherman Springs 22 Seal washer 23 Adjustment screw 24, 43 Seal ring 25 Nut 31 Tunnel 32 Base 33 tube 35 Ring 36 cups 37 cylinders 38 Plunger 39 Shaft, shaft end 40 Guide nut 41 Scraper 42 Ring 44 Fiber Ring 45 Gasket 48 Female eyelet 50 Male Eyelet 51 pin 52 O-ring

Claims

1. A hydraulic actuator with dual pneumatic action for use in hydraulic actuation of hydroelectric generating equipment, comprising a hydropneumatic actuator generally designated by reference number (1), a. The hydropneumatic block (2) receives the fitting and fixing of the outlets (3 and 3a) of two air pumps (4 and 4a) arranged in parallel with each other; b) said hydro-pneumatic block (2) receives a circular hole (5) for receiving the coil (6) of a two-way, two-position hydraulic seat valve (7), said hole (5) having a depth to connect to a high pressure line and laterally located next to an electrical connector (8); c. The electrical connector (8) is an electrical connection for the electrical coil (6) for electrically operating the directional hydraulic seat valve (7); d. Hole (9H) accommodates ball (10i) which is locked by Allen screw (19a), and hole (9i) accommodates ball (10j); e. said hydro-pneumatic block (1) receives at its front face a through hole (9) for mounting said ball (10), said ball being mounted on a guide pin (11), said pin being in turn pressed by a compression spring (12), said spring being supported by a sealing ring (13) locked by a screw (14), forming a relief valve assembly (15) which serves to limit the operating pressure of the system; f. The pressure of the compression spring (12) is adjusted by the relief valve screw (14); g. The holes (9a) and (9b) receive the ball assemblies (10a) and balls (10b) used for static and dynamic sealing, respectively; h) The left side of the hydro-pneumatic block (2) receives a ball assembly (10c) housed in a closure retainer (16) which is fitted with a threaded set screw (17) operated by a handle (18); i. The closure retainer (16) is the sealing part of the set screw (17) which serves to actuate the ball (10c) that closes the oil passage hole (9c); j. Closure occurs by tightening pressure of the Allen screw (19) against the ball (10d); k. The ball (10e) is pressed by a fisherman spring (20) that fits onto the fastening screw (21) together with a sealing washer (22); l. An adjusting screw (23) fits into the hole (9d) together with a sealing ring (24) and receives a nut threadedly at the opposite end (25) to fix the position of the adjusting screw (23) which adjusts the oil flow; m. The hole (9e) of the ball assembly (10f) is pressed by a fisherman spring (26) which is fitted and locked by a fastening screw (27); n. The hole (9f) in which the ball (10g) is fitted and the hole (9g) in which the ball (10h) is fitted are held by a screw (28); o. The socket hole (9j) and ball assembly (10l) are mated and compressed by a spiral spring (19b) held by an Allen screw (29); p. The socket hole (9l) and ball assembly (10m) are fitted together and pressed by a spiral spring (19c) held by a screw (29a); q. The socket hole (9m) and ball assembly (10n) are fitted together and pressed by a spiral spring (19d) held by a screw (29b); r. An O-ring (52) seals the oil passage between the hydro-pneumatic block (2) and the hydraulic actuator (47); s. The base (32) is fixed by a large screw (30) passing through the longitudinal tunnel (31) of the hydro-pneumatic block (2); The base (32) is for mounting a cup (36), and the cup (36) accommodates a cylinder (37) of a piston guide housing (38) fitted onto a shaft end (39) fixed and locked to the cup end (36) by a guide nut (40). A hydraulic actuator characterized by:

2. The hydraulic actuator (47) a. A rectangular base (32) has a circular channel (34) that fits a flat ring (35) that seals a cup (36), said cup (36) houses inside a plunger (38) a guide-receiving cylinder (37) fitted to an axial end (39) that transmits the force of said plunger (38) to an external connection; b. The shaft (39) moves inside the cylinder (37); c) said shaft (39) is fixed and locked to said cup end (36) by a guide nut (40) which holds the ring (42) and scraper (41) in a fixed position; d. The cup (36) is an oil reservoir having a stopper (53) for closing the oil supply nozzle; e. A sealing ring (43) serves to seal said cylinder (37) to said base (32); f. A fiber ring (44) presses against the guide nut (40) to seal the cup (36); g. The stem gasket (45) is the plunger seal (38); h. An anti-extrusion ring (46) prevents the shaft gasket (45) from being extruded; i. said base (32) is attached to a female eyelet (48) by a screw (49); j) The female eyelet (48) fits into the male eyelet (50), is held by a pin (51), and is hinged.

2. A hydraulic actuator with dual pneumatic action for use in hydraulic actuation of a hydroelectric generating device according to claim 1, characterized in that it is formed by:

3. 3. A hydraulic actuator with dual pneumatic operation for use in hydraulic actuation of a hydroelectric generating device according to claim 1 or 2, characterized in that the air pumps (4 and 4a) are driven and operated synchronously.

4. 4. The hydraulic actuator with dual pneumatic operation used for hydraulic actuation of a hydroelectric power generating device according to claim 1, wherein the hydro-pneumatic block (2) has therein a plurality of pipes (33) which are connected to each other and which, together with a set of valves, open or close air passages.

5. 5. The hydraulic actuator having dual pneumatic operation used for hydraulic actuation of a hydroelectric power generating device according to claim 1, wherein the hydraulic actuator is adapted for use in a hydroelectric power generating device.

6. 6. A hydraulic actuator with dual pneumatic operation for use in hydraulic actuation of a hydroelectric generating device, as claimed in any one of claims 1 to 5, characterized in that the actuator, reservoir and control device are all assembled as a hydropneumatic system.

7. A hydraulic actuator with dual pneumatic operation for use as hydraulic actuation for a hydroelectric generating device, according to any one of claims 1 to 6, characterized in that it preferably requires at least one electrical and air power supply point to operate.

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