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An air-to-hydraulic fluid pressure amplifier comprising an air cylinder having an internal reciprocating air piston; a first hydraulic cylinder having a first valve fitting and a first internal hydraulic ram that is slidably positioned within the first hydraulic cylinder; a second hydraulic cylinder

An air-to-hydraulic fluid pressure amplifier comprising an air cylinder having an internal reciprocating air piston; a first hydraulic cylinder having a first valve fitting and a first internal hydraulic ram that is slidably positioned within the first hydraulic cylinder; a second hydraulic cylinder having a second valve fitting and a second internal hydraulic ram that is slidably positioned within the second hydraulic cylinder; a first flow control valve and a second flow control valve; a first plunger-operated pilot valve and a second plunger-operated pilot valve. Each of the first and second plunger-operated pilot valves comprises an inlet port, an outlet port, a plunger, a barrel, and a compression spring.

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1. An air-to-hydraulic fluid pressure amplifier comprising: (a) an air cylinder having an internal reciprocating air piston;(b) a first hydraulic cylinder having a first valve fitting and a first internal hydraulic ram that is slidably positioned within the first hydraulic cylinder;(c) a second hydr

1. An air-to-hydraulic fluid pressure amplifier comprising: (a) an air cylinder having an internal reciprocating air piston;(b) a first hydraulic cylinder having a first valve fitting and a first internal hydraulic ram that is slidably positioned within the first hydraulic cylinder;(c) a second hydraulic cylinder having a second valve fitting and a second internal hydraulic ram that is slidably positioned within the second hydraulic cylinder;(d) a first flow control valve and a second flow control valve; and(e) a first plunger-operated pilot valve and a second plunger-operated pilot valve;wherein a proximal end of the first hydraulic ram is rigidly attached to a first face of the air piston so that a longitudinal axis of the first internal hydraulic ram is collinear with a longitudinal axis of the air piston, and wherein a proximal end of the second internal hydraulic ram is rigidly attached to a second face of the air piston so that a longitudinal axis of the second hydraulic ram is collinear with the longitudinal axis of the air piston;wherein when a first port of a directional control valve supplies compressed air to a pilot of the first flow control valve, the first control valve supplies air to a first side of the air cylinder via a first air cylinder port, thereby moving the air piston toward a second side of the air cylinder;wherein as the air piston moves to the second side of the air cylinder, air present in the second side of the air cylinder is exhausted through a second air cylinder port and through the second flow control valve to atmosphere;wherein movement of the air piston toward the second side of the air cylinder causes the first hydraulic ram to move toward the second side of the air cylinder, thereby pressurizing hydraulic fluid within the first hydraulic cylinder and forcing pressurized hydraulic fluid within the first hydraulic cylinder to exit the first hydraulic cylinder through a first hydraulic check valve and through a first external hydraulic line into external lift cylinders;wherein movement of the air piston toward the second side of the air cylinder causes the second hydraulic ram to move toward the second side of the air cylinder, thereby drawing hydraulic fluid into the second hydraulic cylinder from a hydraulic reservoir through a second external hydraulic line and through a second hydraulic check valve;wherein the air piston continues to move toward the second side of the air cylinder until it contacts a first plunger-operated pilot valve; andwherein the first plunger-operated pilot valve is an end-of-stroke sensor for the air piston. 2. The air-to-hydraulic fluid pressure amplifier of claim 1, wherein when the air piston comes into contact with the first plunger-operated pilot valve, the first plunger-operated pilot valve supplies compressed air to a first pneumatic pilot tube; wherein the first pneumatic pilot tube is connected to a first pilot of the directional control valve;wherein air pressure on the first pilot of the directional control valve causes the directional control valve to shuttle, thereby causing compressed air to be supplied from a second port of the directional control valve to a second pneumatic pilot tube that is connected to a pilot of the second flow control valve and causing compressed air to flow into the second side of the air cylinder through a first air supply pipe, through the second flow control valve, and through the second air cylinder port;wherein the compressed air moving into the second side of the air cylinder causes the air piston to stop moving toward the second side of the air cylinder and to begin moving toward the first side of the air cylinder;wherein as output of the compressed air shifts from the first port of the directional flow control valve to the second port of the directional control valve, air pressure is removed from the pilot of the first flow control valve, thereby causing internal components within the first flow control valve to shift an internal air flow path within the first flow control valve to a deactivated state; andwherein the shifting of the internal air flow path within the first flow control valve to a deactivated state allows compressed air in the first side of the air cylinder to exit the air cylinder through the first cylinder port and escape to atmosphere through an exhaust port of the first flow control valve. 3. The air-to-hydraulic fluid pressure amplifier of claim 2, wherein as compressed air enters the second side of the air cylinder, the air piston moves toward the first side of the air cylinder and away from the second side of the air cylinder; wherein compressed air flows through second port of the directional control valve to the pilot of the second flow control valve, thereby causing the second control valve to supply compressed air to the second side of the air cylinder via the second air cylinder port;wherein as the air piston moves toward the first side of the air cylinder, air that is in the first side of the air cylinder is exhausted to atmosphere through the first flow control valve via the first air cylinder port;wherein movement of the air piston toward the first side of the air cylinder causes the second hydraulic ram to move toward the first side of the air cylinder, thereby pressurizing hydraulic fluid within the second hydraulic cylinder and forcing the pressurized hydraulic fluid to exit the second hydraulic cylinder through a third hydraulic check valve, through a third external hydraulic line, and into the external lift cylinders; andwherein movement of the air piston toward the first side of the air cylinder causes the first hydraulic ram to move toward the first side of the first hydraulic cylinder, thereby drawing hydraulic fluid into the first hydraulic cylinder from the hydraulic reservoir via a fourth external hydraulic line and through a fourth hydraulic check valve. 4. The air-to-hydraulic fluid pressure amplifier of claim 3, wherein movement of the air piston toward the first side of the air cylinder causes it to contact the second plunger-operated pilot valve, thereby causing the second plunger-activated pilot valve to supply compressed air to a third pneumatic pilot tube that is connected to a second pilot of the directional control valve; wherein air pressure on the second pilot of the directional control valve causes the directional control valve to shuttle, thereby causing compressed air to be supplied from the first port of the directional control valve to a fourth pneumatic pilot tube that is connected to the pilot of the first flow control valve and causing compressed air to flow into the first side of the air cylinder through a second air supply pipe, through the first flow control valve, and through the first air cylinder port;wherein the compressed air moving into the first side of the air cylinder causes the air piston to stop moving toward the first side of the air cylinder and begin moving toward the second side of the air cylinder;wherein as output of the compressed air shifts from the second port of the directional flow control valve to the first port of the directional control valve, air pressure is removed from the pilot of the second flow control valve, thereby causing the second flow control valve to shift to a deactivated state; andwherein the shifting of the second flow control valve to a deactivated state allows compressed air in the second side of the air cylinder to exit the air cylinder via the second air cylinder port and escape to atmosphere through an exhaust port of the second flow control valve. 5. The air-to-hydraulic fluid pressure amplifier of claim 4, wherein an outlet of the first plunger-operated pilot valve is connected to the first pilot of the directional control valve by the first pneumatic pilot tube, and wherein an outlet of the second plunger-operated pilot valve is connected to the second pilot of the directional control valve by the third pneumatic pilot tube; and wherein the second port of the directional control valve is connected to the second flow control valve with the third pneumatic pilot tube, and the first port of the directional control valve is connected to the first flow control valve with the fourth pneumatic pilot tube. 6. The air-to-hydraulic fluid pressure amplifier of claim 3, wherein the first hydraulic check valve and the fourth hydraulic check valve are attached to a distal end of the first hydraulic cylinder with a first dual-port threaded valve fitting so that the first hydraulic check valve is connected parallel to a radial axis of the first hydraulic cylinder and the fourth hydraulic check valve is connected parallel to a longitudinal axis of the first hydraulic cylinder. 7. The air-to-hydraulic fluid pressure amplifier of claim 6, wherein the second hydraulic check valve and the third hydraulic check valve are connected to a distal end of the second hydraulic cylinder with a second dual-port valve fitting so that the second hydraulic check valve is connected parallel to a longitudinal axis of the second hydraulic cylinder and the third hydraulic check valve is connected parallel to a radial axis of the second hydraulic cylinder. 8. The air-to-hydraulic fluid pressure amplifier of claim 1, further comprising a first seal keeper and a second seal keeper, wherein the first seal keeper maintains a fluid-tight pressure seal between the air cylinder and the first and second hydraulic cylinders, and the second seal keeper maintains a fluid-tight pressure seal between the air cylinder and the first and second hydraulic rams. 9. The air-to-hydraulic fluid pressure amplifier of claim 8, wherein both of the first and second seal keepers are in the form of a cylinder with a hollow core. 10. The air-to-hydraulic fluid pressure amplifier of claim 1, further comprising a first end block that attaches the air cylinder to the first hydraulic cylinder and a second end block that attaches the air cylinder to the second hydraulic cylinder; wherein the first plunger-operated pilot valve is installed into the first end block, and the second plunger-operated pilot valve is installed into the second end block. 11. The air-to-hydraulic fluid pressure amplifier of claim 1, further comprising a first drip leg and a second drip leg, both of which are mounted on a bottom side of the air cylinder, and both of which are moisture drain valves to drain fluids that accumulate on a bottom inside surface of the air cylinder. 12. The air-to-hydraulic fluid pressure amplifier of claim 1, wherein each of the first and second hydraulic rams has an outer diameter, and wherein the outer diameters of the first and second hydraulic rams are selected to provide a certain value of pressure amplification. 13. The air-to-hydraulic pressure amplifier of claim 1, wherein the first plunger-operated pilot valve comprise an inlet port, an outlet port, a plunger, a barrel, and a compression spring with a force; wherein the plunger comprises a push rod and an annular flow channel;wherein the barrel has four flow channels;wherein the first plunger-operated pilot valve is activated when the push rod of the plunger is contacted by the air piston, thereby causing the plunger to overcome the force of the compression spring and to move; andwherein movement of the plunger causes the flow channel of the plunger to connect to the four flow channels of the barrel, thereby allowing compressed air to enter the inlet port, pass through the flow, channels of the plunger and the barrel, and exit through the outlet port. 14. The air-to-hydraulic pressure amplifier of claim 13, wherein the second plunger-operated pilot valve comprises an inlet port, an outlet port, a plunger, a barrel, and a compression spring with a force; wherein the plunger comprises a push rod and an annular flow channel;wherein the barrel has four flow channels;wherein the second plunger-operated pilot valve is activated when the push rod of the plunger is contacted by the air piston, thereby causing the plunger to overcome the force of the compression spring and to move; andwherein movement of the plunger causes the flow channel of the plunger to connect to the four flow channels of the barrel, thereby allowing compressed air to enter the inlet port, pass through the flow channels of the plunger and the barrel, and exit through the outlet port.