Hydraulically powered compressor and hydraulic control and power system therefor

• US 4,653,986 A
• Filed: 04/16/1986
• Issued: 03/31/1987
• Est. Priority Date: 07/28/1983
• Status: Expired due to Term

• Current Assignee: Robert Ashton
• Original Assignee: Tidewater Compression Service, Inc.
• Inventors: Ashton, Robert
• Primary Examiner(s): Smith, Leonard E.
• Application Number:
  US06/854,714
• Time in Patent Office: 349 Days
• Field of Search: 417/264, 417/267, 417/268, 417/274, 417/275, 417/276, 417/390, 417/397, 417/403, 417/404, 60/456, 91/305, 91/306, 91/313, 91/308, 91/291, 91/293, 91/301
• US Class Current: 417/243
• CPC Class Codes: F04B 49/002 Hydraulic systems to change the pump delivery
• CPC Class Codes: F04B 9/113 reciprocating movement of the pumping members being obtained by a double-acting liquid motor

Abstract

A hydraulically powered compressor has infinitely variable capacity control through use of a variable displacement hydraulic pump, and a hydraulic control and power system provides the infinitely variable capacity control with a proportionate change in required power. Components may be mounted in an air duct.

Claims

1. A hydraulically powered compressor for elevating the pressure of gaseous substances, comprising;

a first double-acting piston and compression cylinder for initially compressing the gaseous substance;

a second double-acting piston and compression cylinder for additional compression of the gaseous substance;

a hydraulic power piston and cylinder disposed between the first and second double-acting pistons and cylinders;

the first and second double acting pistons and the hydraulic power piston each being disposed on a common elongate piston rod;

first piping for transferring the compressed gaseous substance from the first piston and compression cylinder to the second piston and compression cylinder;

second piping for transferring the compressed gaseous substance from the second piston and compression cylinder to an exit orifice;

first and second coils respectively associated with the first and second piping for cooling the compressed gaseous substance;

means for forcing air to flow over the first and second cooling coils;

the first and second pistons and compression cylinders, power piston and cylinder, first and second piping, first and second cooling coils, and air forcing means are all disposed within an air-cooling duct to provide cooling thereto; and

means for providing infinitely variable capacity control with a proportionately variable power requirement for the first and second pistons and compression cylinders, such means including a variable displacement hydraulic pump means for actuating the hydraulic power piston and cylinder so that the first and second pistons and compression cylinders may be operated over a range of from 0 to 100% of their capacity, with a proportionately variable power requirement.

2. The compressor of claim 1, wherein the first and second pistons and compression cylinders and hydraulic power piston and cylinder are disposed on a mounting plate by means of two mounting bolts, whereby transmission of stress forces to the compression cylinders and power cylinder from the mounting plate is greatly minimized.

3. The compressor of claim 1, wherein the first and second pistons are threadedly affixed in a first direction to the piston rod and are secured to the piston rod by a locking member which is threaded into the piston rod in a second opposite direction.

4. The compressor of claim 1, wherein the means for forcing air includes a fan and hydraulic motor therefor, and the motor has a pressure compensated flow control valve associated therewith operatively connected between the variable displacement hydraulic pump and the motor, so that the fan motor is powered by the variable displacement hydraulic pump, and operates at a constant speed to provide cooling to the first and second cooling coils, first and second pistons and cylinders, and hydraulic power piston and cylinder and to blow out of the air cooling duct any accumulated gaseous substance.

5. The compressor of claim 1, wherein the piston rod is provided with a plurality of rod packings and the variable displacement hydraulic pump is associated therewith to automatically provide lubricating hydraulic oil thereto.

6. The compressor of claim 1, wherein the first and second cylinders are provided with lubrication connections associated with the first and second pistons and the variable displacement hydraulic pump, whereby lubricating hydraulic oil is automatically provided to the interface between the first and second pistons and first and second compression cylinders.

7. The compressor of claim 1, wherein each of the first and second cylinders and the hydraulic power cylinder each engage a header member at the first and second ends of each cylinder, and a seal means is provided on each header member which seal means contacts the internal surface of each cylinder.

8. The compressor of claim 1, wherein a pressure relief valve means associated with the hydraulic variable displacement pump and first and second compression cylinders, for preventing excessive pressure build-up from occuring in the first or second compression cylinders due to liquid, rather than a gaseous substance, entering either cylinder, so that the liquid may pass therethrough at a safe operating pressure level.

9. The compressor of claim 1, wherein a cooling chamber is provided between the hydraulic power piston and cylinder, and each of the first and second pistons and cylinders, each cooling chamber surrounding a portion of the piston rod and including means for directing air flow from the means for forcing air over the piston rod.

10. The compressor of claim 1, wherein at least one of the compression cylinders is provided with a pipe tapped opening and a clearance bottle is attached thereto, whereby the volume of said cylinder is variable to provide balancing of compression ratios between the first and second compression cylinders.

11. A system as recited in claim 1 wherein said variable displacement hydraulic pump provides constant output throughout the reciprocatory cycle of said reciprocating hydraulic power piston.

18. The hydraulic control and power system of claim 11, wherein the pilot valve has a mechanical detent mechanism which holds the pilot valve in position on loss of hydraulic pump flow.

12. A hydraulic control and power system for a compressor for gaseous substances having first and second double-acting pistons and compression cylinders and a reciprocating hydraulic power piston and cylinder for actuating the first and second pistons, comprising:

a variable displacement hydraulic pump for providing hydraulic fluid to the power piston and cylinder to reciprocate the power piston within its cylinder;

a two position shuttle valve for alternating the flow of hydraulic fluid from the pump into and out of the ends of the hydraulic power piston cylinder;

a cam-operated, spring loaded check valve associated with each end of the power piston cylinder, said check valves being actuated by the reciprocating motion of the power piston to discharge hydraulic fluid from the respective end of said power piston cylinder;

a pilot valve for actuating the shuttle valve in response to a pressure differential caused by the discharge of hydraulic fluid through one of the cam-operated, spring loaded check valves;

a hydraulic fluid reservoir; and

hydraulic fluid piping operatively associating the pump, shuttle valve, check valves, pilot valve and reservoir, with one another, so that upon varying the displacement of the pump, the speed of reciprocation of the power piston is varied, said hydraulic piping including means operatively connecting said check valves and pilot valve, said means consisting of conduits operatively extending from each of said check valves directly to said pilot valve for providing an all-hydraulic control of said pilot valve.

13. The hydraulic control and power system of claim 12, wherein a pressure relief valve is operatively associated with the pump, whereby an excessive pressure build-up within the piping of either compression cylinder is safely relieved.

14. The hydraulic control and power system of claim 12, wherein a bladder accumulator is operatively associated with the pump and piping, whereby pressure shocks caused by reciprocation of the shuttle valve are absorbed, and pump energy is stored during the time required to switch the shuttle valve.

15. The hydraulic control and power system of claim 12, wherein a pressure compensated flow control valve and distribution block are operatively associated with the pump and piping to provide lubricating hydraulic fluid to the compression cylinders and piston rod for the double-acting pistons.

16. The hydraulic control and power system of claim 12, wherein a check valve is operatively disposed in the piping between the pump and the shuttle valve, to prevent pressurized hydraulic fluid which exited from the pump from re-entering the exit side of the pump.

17. The hydraulic control and power system of claim 12, wherein an accumulator and relief valve are disposed in vent piping from the shuttle valve to the reservoir to minimize pressure shocks caused by reciprocation of the shuttle valve.

19. A system as recited in claim 12 wherein said variable displacement hydraulic pump provides constant output throughout the reciprocatory cycle of said reciprocating hydraulic power piston.

20. The hydraulic control and power system of claim 12, further comprising, a flow control valve means operatively associated with each end of the shuttle valve to for throttling the hydraulic fluid flowing from the pilot valve to either end of the shuttle valve, so that the response time of the shuttle valve is controlled and hydraulic shocks caused by the shuttle valve moving too quickly are controlled.

21. The hydraulic control and power system of claim 20, wherein the check valves and fluid control valves are each operatively associated with a needle valve for creating a pressure differential to reciprocate the pilot valve.

22. A system as recited in claim 13 wherein said hydraulic fluid piping further comprises:

conduit means operatively connecting said variable displacement hydraulic pump output so that the flow of hydraulic fluid from it is regulated by said pilot valve; and

piping connecting the fluid whose flow is regulated by said pilot valve to said shuttle valve to control said shuttle valve.

23. A hydraulically powered compressor for elevating the pressure of gaseous substances, comprising:

a first double-acting piston and compression cylinder for compressing the gaseous substance;

a second double-acting piston and compression cylinder for compression of the gaseous substance;

a hydraulic power piston and cylinder disposed between the first and second double-acting pistons and cylinders;

the first and second double acting pistons and the hydraulic power piston each being disposed on a common elongated piston rod;

piping for transferring the compressed gaseous substance from the first and second pistons and compression cylinders to an exit orifice;

cooling coils respectively associated with the piping for cooling the compressed gaseous substance;

means for forcing air to flow over the cooling coils;

the first and second pistons and compression cylinders, power piston and cylinder, piping, cooling coils, and air forcing means all being disposed within an air-cooling duct to provide cooling thereto; and

means for providing infinitely variable capacity control for the first and second pistons and compression cylinders, the capacity control means including a variable displacement hydraulic pump for actuating the hydraulic power piston and cylinder, so that the first and second pistons and compression cylinders may be operated over a range of from 0 to 100% of their capacity.

24. The compressor of claim 23, wherein the first and second pistons and compression cylinders and hydraulic power piston and cylinder are disposed on a mounting plate by means of two mounting bolts, whereby transmission of stress forces to the compression cylinders and power cylinder from the mounting plate is greatly minimized.

25. The compressor of claim 23, wherein the first and second pistons are threadedly affixed in a first direction to the piston rod and are secured to the piston rod by a locking member which is threaded into the piston rod in a second opposite direction.

26. The compressor of claim 23, wherein the means for forcing air includes a fan and hydraulic motor therefor, and the motor has a pressure compensated flow control valve associated therewith operatively connected between the variable displacement hydraulic pump and the motor, so that the fan motor is powered by the variable displacement hydraulic pump, and operates at a constant speed to provide cooling to the first and second cooling coils, first and second pistons and cylinders, and hydraulic power piston and cylinder and to blow out of the air cooling duct any accumulated gaseous substance.

27. The compressor of claim 23, wherein the piston rod is provided with a plurality of rod packings and the variable displacement hydraulic pump is associated therewith to automatically provide lubricating hydraulic oil thereto.

28. The compressor of claim 23, wherein the first and second cylinders are provided with lubrication connections associated with the first and second pistons and the variable displacement hydraulic pump, whereby lubricating hydraulic oil is automatically provided to the interface between the first and second pistons and first and second compression cylinders.

29. The compressor of claim 23, wherein each of the first and second cylinders and the hydraulic power cylinder each engage a header member at the first and second ends of each cylinder, and a seal means is provided on each header member which seal means contacts the internal surface of each cylinder.

30. The compressor of claim 23, wherein a pressure relief valve is associated with the hydraulic variable displacement pump and first and second compression cylinders, whereby excessive pressure build-up is prevented from occuring in the first or second compression cylinders due to liquid, rather than a gaseous substance, entering either cylinder, so that the liquid may pass therethrough at a safe operating pressure level.

31. The compressor of claim 23, wherein a cooling chamber is provided between the hydraulic power piston and cylinder, and each of the first and second pistons and cylinders, each cooling chamber surrounding a portion of the piston rod and including means for directing air flow from the means for forcing air over the piston rod.

32. A system as recited in claim 23 wherein said variable displacement hydraulic pump provides constant output throughout the reciprocatory cycle of said reciprocating hydraulic power piston.