Ultra High Pressure Pump With An Alternating Rotation To Linear Displacement Drive Mechanism

Abstract

A high pressure pump including a linear actuator having a servo motor to axially rotate a hollow rotor shaft in alternating directions, the servo motor having a stator positioned co-axially around the hollow rotor shaft with an interior of the rotor shaft being co-axially coupled to a drive member to convert axial rotation into reciprocal displacement, the drive member being constrained against linear movement and supporting a shaft. At least one piston is coupled to the shaft and the piston is arranged within a cylinder to define a pumping chamber, whereby alternating rotation of the rotor shaft causes reciprocal linear displacement of the piston to pressurize fluid in the pumping chamber. A drive mechanism includes a controller coupled to a servomotor and an encoder to measure movement of the hollow rotor or output shaft and send a feedback signal proportional to the movement to the controller.

Claims

1-18. (canceled)

19. An ultra high pressure pump, comprising: a servo motor; a hollow rotor shaft; drive means; at least one piston; at least one cylinder; at least one pumping chamber; and a screw; the servo motor being adapted to axially rotate the hollow rotor shaft in alternating directions; the servo motor having a stator positioned co-axially around the hollow rotor shaft; the hollow rotor shaft being co-axially coupled to the drive means; the drive means being to convert axial rotation into reciprocal displacement; the servo motor including an encoder to monitor movement of at least one of the hollow rotor shaft and the drive means; the encoder being coupled to the servo motor via a closed feedback loop; the at least one piston having a head arranged within the at least one cylinder to define the at least one pumping chamber between the head and the at least one cylinder; the drive means being coupled to the at least one piston and such that alternating rotation of the hollow rotor shaft causes reciprocal linear displacement of the at least one piston to pressurise fluid in the at least one pumping chamber; the drive means including a nut engaged with the screw and constrained against linear movement; the drive means being coupled to an interior of the hollow rotor shaft; the hollow rotor shaft housing the nut; and the pressurising being to pressures greater than 345 MPa (50,000 psi).

20. The ultra high pressure pump of claim 19, wherein the nut is a roller nut.

21. The ultra high pressure pump according to claim 19, wherein the encoder transmits a velocity feedback signal and/or a position feedback signal.

22. The ultra high pressure pump according to claim 19, wherein the stator is located within a cylindrical housing; and the housing is encased in a water cooled jacket.

23. The ultra high pressure pump according to claim 22, wherein the housing, cooling jacket, stator, hollow rotor shaft, and drive means are all coaxial.

24. The ultra high pressure pump according to claim 19, wherein the nut is in direct engagement with the hollow rotor shaft, the nut threadedly engaging the screw whereby axial rotation of the hollow rotor shaft, and therefore the nut, imparts linear motion to the screw.

25. The ultra high pressure pump according to claim 24, wherein the screw is supported by linear bearings each supported on elongate rails, the linear bearings preventing rotation of the screw whilst facilitating longitudinal movement of the screw.

26. The ultra high pressure according to claim 25, wherein one end of the hollow rotor shaft is supported by an annular bearing and the rails pass through the annular bearing.

27. The ultra high pressure pump according to claim 25, wherein one end of the screw has opposed flats that engage the linear bearings.

28. The ultra high pressure pump according to claim 24, wherein pistons are coupled to opposite ends of the screw, each piston being adapted to complete reciprocal motion within an associated cylinder thus defining two pumping chambers.

29. The ultra high pressure pump according to claim 28, wherein each cylinder has a low pressure water inlet controlled by a low pressure check valve and a high pressure outlet controlled by a high pressure check valve.

30. The ultra high pressure pump according to claim 29, wherein high pressure seals are positioned between the inner ends of the pistons and the cylinders.

31. The ultra high pressure pump according to claim 30, wherein each piston has a stroke of about 175 mm and reciprocates at about 120 strokes per minute to deliver between 2 and 4 litres of fluid per minute.

32. A pump assembly for a waterjet cutting apparatus comprising two pumps according to claim 19 coupled together to produce an ultra-high pressure jet of water, the reciprocation of the pumps being out of phase to reduce pulsing of the water pressure.

33. The pump assembly according to claim 32, wherein the speed of one pump is greater than the speed of the other pump to compensate for the other pump whilst reversing.

Description

DESCRIPTION OF THE DRAWINGS

[0018] An embodiment of the present invention will now be described by way of example only with reference to the accompanying drawings in which:

[0019] FIG. 1 is a side elevational view of an ultra high pressure pump,

[0020] FIG. 2 is an end elevational view of the pump,

[0021] FIG. 3 is a sectional view of the pump taken along the lines A-A of FIG. 2;

[0022] FIG. 4 is a sectional view of the pump taken along the lines B-B of FIG. 1; and

[0023] FIG. 5 is a diagram illustrating the feedback loop for a linear actuator.

DESCRIPTION OF THE PREFERRED EMBODIMENT

[0024] Whilst the preferred embodiment relates to a high pressure pump especially for use in waterjet cutting machinery, it is understood that the invention of the subject application is, in essence, a drive mechanism which can be used in a wide variety of scenarios where close careful control of the drive is necessary. Thus one of the uses of the drive mechanism is a linear actuator that can be used to replace hydraulic cylinders, which are inherently inefficient, noisy, dirty, and not precise, in a wide variety of engineering applications such as presses, robotics, materials handling and other similar uses. It is the use of a servo motor with a closed feedback loop that provides the opportunity to closely and carefully control the drive.

[0025] When the drive mechanism is used in a pump it comprises a servo motor that drives two reciprocating pistons that project from either end of the pump to operate within cylinders to pressurise water introduced into the cylinders to pressures of greater than 50000 psi.

[0026] As shown in FIGS. 1 to 4, the pump 10 comprises a cylindrical housing 11 that is encased within a cylindrical water cooled jacket 12. The housing 11 has end flanges 16, 17 that support a hollow rotor shaft 15 about windings 19 of a servo motor. One end 13 of the rotor shaft 15 is supported by an annular bearing 14 located between the housing 11 and the shaft 15. The other end 18 of the rotor shaft 15 supports a bearing housing 27 that supports a bearing 28.

[0027] The rotor shaft 15 houses a roller nut 30 which is in turn threadedly engaged onto an elongated screw 31. The roller nut 30 is in direct engagement with the interior of the shaft and is constrained against linear movement to rotate with the rotor shaft 15. The screw 31 has a threaded exterior 20 with a flat 21 machined on one end 22. The flat 21 supports linear bearings 23, 24 which run on elongate spaced apart rails 25, 26 (FIG. 4). The rails 25, 26 extend past the end flange 17 of the housing 11. The end 15 of the rotor shaft supporting the bearing 28 supports an externally positioned encoder 80.

[0028] The ends of the screw 31 are coupled to pistons 50 and 51 that are arranged to reciprocate within associated cylinders 54 and 55. The heads 56, 57 of the pistons define with the cylinders 54, 55 compression chambers 58, 59.

[0029] The rotor shaft 15 is located within the casing 11 about the spaced bearings 13 and 28 to facilitate axial rotation of the shaft 15 relative to the casing 11. The end flanges 16, 17 are bolted and secured to the casing 11 to hold the assembly together and the projecting pistons 50, 51 are enclosed within stainless steel mounts 65, 66 that support the cylinders 54, 55.

[0030] The servo motor causes the rotor shaft 15 to rotate which in turn rotates the roller nut 30 which is constrained from axial movement thus meaning that the screw 31 moves linearly within the roller nut 30. By reversing the direction of rotation of the rotor shaft 15, the screw 31 can thus be caused to reciprocate back and forth to give the reciprocating motion to the pistons 50, 51 to in turn pressurise the water that is introduced into the compression chambers 58, 59 via water inlets 60 to effect high pressure delivery of water from the outlets 61 at pressures greater than 50,000 psi.

[0031] Each cylinder 54, 55 has a low pressure water inlet 73 controlled by a check valve 74 communicating with the compression chambers 58, 59 at a 45° angle to axis of the cylinder. A high pressure outlet 75 is positioned co-axial to the end of the cylinder and includes a check valve 76.

[0032] High pressure seals 70, 71 are positioned between the inner ends of the cylinders 54, 55 and the pistons 50, 51 to prevent back pressure.

[0033] The servo motor is controlled by a computer numerical controller (CNC).

[0034] The servo motor which is used in the preferred embodiment is a brushless DC servo motor operating on a DC voltage of about 600 volts. This is a motor which is commonly used in machine tools and has traditionally been very controllable to provide the precision which is required in such machine tool applications. The pistons have a stroke of about 175 mm and reciprocate at approximately 120 strokes per minute. The movement of a piston in one direction lasts about 0.8 seconds. The pump is designed to operate in the most efficient mode with the delivery of water at 2 L per minute but it could operate with a delivery of up to 4 L per minute though this would reduce the life of the pump.

[0035] Because there is a direct drive between the servo motor and the linear motion of the pistons it is possible to achieve extremely accurate diagnostics in the machine. By use of the encoder 80 which reads very fine graduations (typically less than 0.04 mm radially, or some 20,000 counts per revolution in the preferred embodiment), along with the current and voltage information coming back into the CNC from the stator, it is possible to accurately calculate the linear speed and the motor torque to thus very accurately determine the water pressure and flow rate. This level of accuracy is far greater then that of traditional machines. Armed with this information it is therefore possible to determine if there is a problem with the pump. It has been discovered that when high pressure leaks go unattended these leaks very quickly cause fatal damage to the very expensive machine components to the pump. By constant monitoring of the operation of the pump, seal failures can be determined very early so that preventative maintenance can be introduced to prevent serious damage to the componentry.

[0036] An issue which can cause problems with equipment of this kind is the pulsating effect caused by the reciprocation of the pistons. Every time the servo motor reverses direction, there is a delay whilst the piston stops to then reverse direction. This delay can cause as much as a 5000 psi pressure drop which tends to cause the output pressure of the pump to pulsate. The pump of the subject application can overcome this problem by placing two pumps each with two reciprocating piston and cylinder assemblies in tandem and having the pumps running slightly out of phase. By cycling one drive at twice the speed of the other, while the other pump is reversing, it allows the first pump to build up backpressure to balance the drop in pressure which would be caused through reversal of the piston and thus ensure that the output pressure delivered to the waterjet cutter is constant without pulsing. By doing away with the pulsing effect, the main contributor to early fatigue of the components in the waterjet cutting machine is avoided.

[0037] The servo drive pump described above is far more efficient than an intensifier pump while still offering the desired ability to be able to store and hold pressure while not cutting, thus using only minimal power. The rotor shaft is designed to run at about 1500 rpm and the piston is about 180 mm in length running in a bore with a head diameter of 14 mm. This makes the whole assembly small, light and considerably quieter than an intensifier pump. The servo drive system is also very responsive and pressures can be adjusted within milliseconds with infinite control.

[0038] The drive mechanism described above which is used in the embodiment shown in FIGS. 1 to 4 to drive an ultra high pressure pump can also be used in a number of other environments and has particular use as a linear actuator. FIG. 5 is an illustration of a closed loop showing the control of a linear actuator. The computer numerical controller 81 drives a position controller 82 that in turn is coupled to a velocity controller 83 which in turn is coupled to a current controller 84 to drive the servo motor which becomes the linear actuator. The encoder 80 sends two feedback signals, namely a velocity feedback signal that is fed to the velocity controller and a position feedback signal that is fed to the position controller. In this manner the computer controlling operation of the servo motor by monitoring the feedback signals provides an extremely positive and accurate control of the linear displacement of the output shaft which means that the linear actuator can be used to replace the hydraulic cylinders conventionally used in applications such as heavy duty presses, injection moulding machines, lifting tables and platforms or high load cutting or polishing machines. The linear actuator is particularly compact and thus is especially useful where there is a need for increased control of speed, position or force and limited space is available.