US20160084241A1 - Ultra-high pressure generator - Google Patents
Ultra-high pressure generator Download PDFInfo
- Publication number
- US20160084241A1 US20160084241A1 US14/842,987 US201514842987A US2016084241A1 US 20160084241 A1 US20160084241 A1 US 20160084241A1 US 201514842987 A US201514842987 A US 201514842987A US 2016084241 A1 US2016084241 A1 US 2016084241A1
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- Prior art keywords
- working medium
- high pressure
- ultra
- pressurized fluid
- pressure generator
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- 239000000498 cooling water Substances 0.000 description 7
- 239000010720 hydraulic oil Substances 0.000 description 7
- 230000015556 catabolic process Effects 0.000 description 4
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- 230000002159 abnormal effect Effects 0.000 description 3
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- 230000006872 improvement Effects 0.000 description 1
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- 239000002918 waste heat Substances 0.000 description 1
Images
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B26—HAND CUTTING TOOLS; CUTTING; SEVERING
- B26F—PERFORATING; PUNCHING; CUTTING-OUT; STAMPING-OUT; SEVERING BY MEANS OTHER THAN CUTTING
- B26F3/00—Severing by means other than cutting; Apparatus therefor
- B26F3/004—Severing by means other than cutting; Apparatus therefor by means of a fluid jet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2078—Swash plates
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/28—Control of machines or pumps with stationary cylinders
- F04B1/29—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B1/295—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/30—Control of machines or pumps with rotary cylinder blocks
- F04B1/306—Control of machines or pumps with rotary cylinder blocks by turning the swash plate, e.g. with fixed inclination
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/30—Control of machines or pumps with rotary cylinder blocks
- F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
- F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
- F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
- F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
- F04B9/115—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by two single-acting liquid motors, each acting in one direction
Definitions
- the present invention relates to an ultra-high pressure generator obtaining ultra-high pressure output by plungers which are reciprocatively driven by hydraulic pressure or the like.
- An ultra-high pressure pump that discharges a jet of high pressure fluid has been known to have the following configuration (see FIG. 1 in Japanese Patent Application Publication number S63-39799).
- An open-circuit hydraulic pump (working medium pump) 1 is connected, at a discharging side, to low pressure cylinder chambers C1 and C2 in an intensifier 2 via a two-way control valve (directional control valve) 3.
- directional control valve 3 When the directional control valve 3 is at the position V1, hydraulic oil (working medium) boosted by the hydraulic pump 1 is supplied to the cylinder chamber C1 and the working medium in the cylinder chamber C2 is returned to a tank 25. At this time, the piston P in the intensifier 2 is moved toward the right direction in FIG. 1 .
- the directional control valve 3 When the piston P in the intensifier 2 reaches the right end, the directional control valve 3 is switched to the position V2. The pressurized working medium is supplied to the cylinder chamber C2 and the working medium in the cylinder chamber C1 is returned to the tank 25. At this time, the piston P in the intensifier 2 is moved toward the left direction in FIG. 1 . When the piston P in the intensifier 2 reaches the left end, the directional control valve 3 is switched to the position V1. The pressure of the pressurized fluid is pressurized by a factor of intensify ratio in the pressure of the working medium. The pressure of the pressurized fluid is controlled by the relief valve 27 controlling the pressure of the working medium.
- the aforementioned high pressure generator with the open-circuit hydraulic pump and the directional control valve has the following problem.
- the high pressure generator discharges the pressurized fluid continuously.
- the hydraulic pressure generator is driven to have high pressure loss in the directional control valve.
- a double-acting drive cylinder is stopped, which makes the pressure loss of the hydraulic oil as the fluid under low pressure become zero.
- the amount of the pressure loss in the directional control valve appears as temporary abnormal rise of hydraulic pressure of the hydraulic oil.
- the temporary abnormal rise of hydraulic pressure of the hydraulic oil affects the discharge pressure of the fluid under high pressure according to the intensify ratio of the intensifier.
- the intensify ratio is a pressure ratio between the pressure of the pressurized fluid under high pressure and the pressure of the hydraulic oil under low pressure, and is normally set as several tens of times. That is, when the continuous discharge of the fluid under high pressure is stopped, the pressure rises temporarily by the pressure amount of several tens of times of the pressure loss in the directional control valve. Therefore, when the continuous discharge is stopped, the pressure rises excessively.
- the directional control valve for the hydraulic pressure generator is mandatory.
- the pressure loss in the directional control valve causes mechanical efficiency to drop.
- the present invention is intended to provide an ultra-high pressure generator that reduces fluctuations in a pressure waveform of pressurized fluid and enhances mechanical efficiency.
- an ultra-high pressure generator including: an intensifier that discharges pressurized fluid and includes a double-acting drive cylinder formed to have a first chamber and a second chamber which are delimited by a piston that is driven by a working medium, a high pressure cylinder that discharges the pressurized fluid, and a plunger that reciprocates with the piston in the high pressure cylinder; a closed-circuit working medium pump that has a first port and a second port as suction/discharge ports for the working medium, and sucks/discharges the working medium from/to the first chamber and the second chamber respectively via the first port and the second port to drive the intensifier; a drive source that drives the closed-circuit working medium pump; a first working medium channel that communicates the first chamber with the first port; and a second working medium channel that communicates the second chamber with the second port.
- the closed-circuit working medium pump is used to suck the working medium from a pressurized side in the intensifier, pressurize it, and to return it to a pressing side in the intensifier, which does not require a directional control valve that controls flow directions of the working medium to be supplied to the first or second chamber. Therefore, the problem can be resolved such that pressure of the high pressure fluid or the pressurized fluid increases abnormally at the time of stopping discharge due to the pressure loss in the directional control valve.
- the pressure in either one of the first and second chambers becomes approximately 0 MPa, and the other one is pressurized immediately. Further, since the pressure of the working medium becomes zero temporarily when the travel direction of the piston in the double-acting drive cylinder is switched, the pressure does not increase abnormally at the time of switching the travel direction. With these effects, astable pressure waveform can be obtained which has little pressure fluctuations of the high pressure fluid.
- the ultra-high pressure generator having the configuration above, since the working medium filled in the double-acting drive cylinder of the intensifier is directly driven by the closed-circuit working medium pump, high response speed of the intensifier can be achieved. Thus, the pressure waveform of the pressurized fluid can be stable.
- the working medium is filled in the first or second chamber of the double-acting drive cylinder.
- the direction of the intensifier is switched, either one of the first and second chambers which has been pressurized is changed to a supply side, and the other one that has been a supply side is pressurized.
- a bidirectionally rotatable drive source is reversely rotated against inertial force of the closed-circuit pressurizing device to suck the working fluid from a supplying chamber.
- the pressurized fluid that has been pressurized in the high pressure cylinder is expanded based on compression rate of the pressurized fluid to push back the piston, a load on the drive system can be reduced.
- the closed-circuit working medium pump is preferably a fixed-displacement swash plate axial pump and the drive source is preferably a bidirectionally rotatable drive source.
- the closed-circuit working medium pump may be a variable-displacement swash plate axial pump that can reverse a tilt angle between positive and negative directions.
- a unidirectionally rotatable drive source can be applied as a drive source.
- the drive source can preferably be a servo motor
- the ultra-high pressure generator can comprise a pressure detector that detects pressure of the pressurized fluid discharged from the intensifier and a controller that controls the number of rotations of the servo motor in response to the pressure detected by the pressure detector.
- the flow rate and the pressure of the closed-circuit working medium pump is controlled in response to the pressure of the pressurized fluid detected by the pressure detector. Since proper pressure of the working medium can be generated by the closed-circuit working medium pump when the ultra-high pressure generator is driven, the pressure waveform of the pressurized fluid is stabilized.
- the ultra-high pressure generator of the present invention since the ultra-high pressure generator of the present invention does not need to include a relief circuit for regulating the pressure of the working medium, the thermal loss of the relief circuit does not exist, thereby increasing the mechanical efficiency. Further, since the thermal loss of the relief circuit does not need to be recovered, the amount of cooling water can be significantly reduced.
- the ultra-high pressure generator of the present invention when the discharge of the pressurized fluid is stopped, the servo motor continues to rotate so that the closed-circuit working medium pump keeps the pressure.
- the ultra-high pressure generator of the present invention preferably includes a storage tank in which the pressurized fluid is stored, a supply port through which the pressurized fluid is supplied to the storage tank, and a heat exchanger that cools the working medium, wherein the pressurized fluid supplied through the supply port is supplied to the storage tank via the heat exchanger.
- the ultra-high pressure generator according to the present invention can reduce the fluctuations in the pressure waveform of the pressurized fluid and can improve the mechanical efficiency.
- FIG. 1 is a diagram showing a hydraulic pressure circuit of an ultra-high pressure generator according to an embodiment of the present invention.
- FIG. 2 is a chart showing a pressure waveform of fluid under high pressure in the ultra-high pressure generator according to the embodiment of the present invention.
- a working medium F 1 is hydraulic oil and pressurized fluid F 2 is water, in the ultra-high pressure generator 70 .
- the ultra-high pressure generator 70 is preferably used for water jet cutting in which ultra-high pressure water is discharged continuously.
- the ultra-high pressure generator 70 of the present embodiment is a device that continuously discharges the pressurized fluid F 2 under ultra-high pressure.
- the ultra-high pressure generator 70 includes: an intensifier 40 having a double-acting drive cylinder 44 formed to have a first chamber 41 and a second chamber 42 which are delimited by a piston 43 driven by the working medium F 1 , and plungers 461 , 462 which reciprocate with the piston 43 in high pressure cylinders 451 , 452 respectively; a closed-circuit working medium pump 11 having a first port 111 and a second port 112 as suction/discharge ports; a bidirectionally rotatable drive source 12 that drives the closed-circuit working medium pump 11 ; a first working medium channel 32 that communicates the first chamber 41 with the first port 111 ; and a second working medium channel 33 that communicates the second chamber 42 with the second port 112 .
- the closed-circuit working medium pump 11 is a fixed-displacement swash plate axial pump and a drive source thereof is constituted with a servo motor as a bidirectionally rotatable drive source 12 .
- the ultra-high pressure generator 70 further includes a pressure detector 53 that measures the pressure of the pressurized fluid F 2 discharged from the intensifier 40 and a controller 15 that controls the number of rotations of the bidirectionally rotatable drive source 12 in response to the pressure detected by the pressure detector 53 .
- the ultra-high pressure generator 70 includes a supply port 68 through which the pressurized fluid F 2 is supplied, a heat exchanger 30 that cools the working medium F 1 and a storage tank 69 in which the pressurized fluid F 2 is stored.
- the pressurized fluid F 2 supplied from the supply port 68 flows through the heat exchanger 30 into the storage tank 69 .
- the intensify ratio is determined to be ratio of the cross-sectional area of the piston 43 to cross-sectional areas of the high pressure cylinders 451 , 452 .
- the pressure of the pressurized fluid F 2 is pressurized by a factor of the intensify ratio based on the pressure of the working medium F 1 .
- the boost pressure is set to be several tens of times.
- the plungers 461 , 462 in the intensifier 40 are caused to reciprocate from side to side by the double-acting drive cylinder 44 in the high pressure cylinders 451 , 452 .
- a pair of suction valve 48 and discharge valve 47 is arranged at the ends of the high pressure cylinders 451 , 452 , respectively.
- the piston 43 in the double-acting drive cylinder 44 moves toward the right direction in FIG. 1 .
- the pressurized fluid F 2 flows into the high pressure cylinder 451 through the suction valve 48 .
- the pressurized fluid F 2 is discharged from the high pressure cylinder 452 through the discharge valve 47 .
- a right end detector 492 detects the piston 43 to switch a travel direction of the piston 43 toward the left direction in FIG. 1 .
- the double-acting drive cylinder 44 acts reversely as described above.
- a left end detector 491 detects that the piston 43 has reached around the left end. The reciprocation of the double-acting drive cylinder 44 allows the pressurized fluid F 2 to be discharged continuously.
- detectors such as proximity switches, limit switches may be used as the left end detector 491 and right end detector 492 .
- proximity switches When the proximity switches are used, respective detectors 491 , 492 can be installed in the intensifier 40 , resulting in a simple structure.
- suction valves 48 and discharge valves 47 are check valves, but a directional flow regulation valve may be used in place of the pair of check valves.
- the discharge valves 47 is unnecessary.
- the closed-circuit working medium pump 11 is a fixed-displacement swash plate axial pump.
- the first port 111 is directly connected to the first chamber 41 via the first working medium channel 32
- the second port 112 is directly connected to the second chamber 42 via the second working medium channel 33 . That is, when the piston 43 in the intensifier 40 moves toward the right side, the closed-circuit working medium pump 11 pressurizes the working medium F 1 in the second chamber 42 to predetermined pressure to feed to the first chamber 41 .
- the closed-circuit working medium pump 11 feeds the working medium F 1 in the first chamber 41 to the second chamber reversely.
- the closed-circuit working medium pump 11 controls the pressure and the flow rate of the working medium F 1 by controlling the number of rotations thereof.
- the bidirectionally rotatable drive source 12 as a servo motor can control the number of rotations as desired to maintain a rotation angle such that the output shaft thereof does not rotate.
- the closed-circuit working medium pump 11 can control the pressure and the flow rate of the working medium F 1 by the use of combination of the fixed-displacement swash plate axial pump and the bidirectionally rotatable servo motor, and can set the flowing rate of the working medium F 1 to zero while maintaining the pressure of the working medium F 1 . Still further, reliability of the ultra-high pressure generator is enhanced by the use of the fixed-displacement swash plate axial pump.
- variable-displacement axial plunger pump that can reverse a tilt angle from positive to negative or vice versa and a unidirectionally rotatable drive source can be used in place of the combination of the closed-circuit working medium pump 11 and the bidirectionally rotatable drive source 12 .
- the variable-displacement axial plunger pump capable of reversing a tilt angle can switch a suction side and a discharge side of two ports by reversing the tilt angle, and can be used as the closed-circuit working medium pump.
- a circuit for the working medium F 1 is arranged in a valve block 20 as shown below.
- the valve block 20 is connected to the intensifier 40 and is connected to the closed-circuit working medium pump 11 with rubber hoses 321 , 321 , 331 , 331 as pipes, respectively. Connecting respective components with the rubber hoses 321 , 321 , 331 , 331 allows for absorbing vibrations that may occur at respective components to improve assemblability and maintainability as well as durability of the ultra-high pressure generator 70 .
- the valve block 20 includes a temperature detector 28 that detects temperature of the working medium. When the temperature of the working medium F 1 increases abnormally, the temperature detector 28 gives a warning. The temperature detector 28 is attached to the valve block 20 not to contact the working medium F 1 directly, and then the temperature detector 28 is hard to suffer damage due to the pressure fluctuations of the working medium F 1 or the like.
- the temperature detector 28 can be connected to a supply circuit 21 or a selection circuit 26 when a problem such as breakdown does not need to be considered.
- the first working medium channel 32 is connected to the second working medium channel 33 with the selection circuit 26 inclusive of a pair of check valves 26 a , 26 b .
- the check valves 26 a , 26 b are installed to have the working medium channels 32 , 33 as upstream sides.
- a pressure detector 27 that detects the pressure of the working medium F 1 is arranged in the selection circuit 26 .
- the selection circuit 26 allows the pressure detector 27 to detect the pressure of either one of the first working medium channel 32 and the second working medium channel 33 which has higher pressure.
- the pressure detector 27 can inform abnormality when the pressure of the working medium F 1 is out of a normal range.
- the first working medium channel 32 is connected to the second working medium channel 33 with the supply circuit 21 that includes a pair of check valves 21 a , 21 b having the working medium channels 32 , 33 as downstream sides.
- the supply circuit 21 communicates the check valves 21 a , 21 b with a working medium tank 31 .
- the working medium tank 31 is applied with internal pressure.
- the working medium F 1 as hydraulic oil is incompressible fluid, but is slightly compressed by pressurization.
- One of the first chamber 41 and second chamber 42 in the intensifier 40 which is at a supply side, is set to have pressure around zero MPa normally, and the other is set to have setting pressure.
- the total amount of the working medium F 1 accumulated in the system is changed depending on the volume of the working medium F 1 presented in either one of the first chamber 41 and second chamber 42 , which is at a compression cycle side, and the pipes.
- the supply circuit 21 functions to regulate the total amount of the working medium F 1 .
- the working medium tank 31 only needs to have the function to regulate the total amount of the working medium F 1 , and therefore can be reduced in size.
- the working medium tank 31 is equivalent to a thin-walled gas accumulator to have a radiation function for the working medium F 1 .
- a pressure equalization circuit 22 including an electromagnetic valve 22 a and a throttle valve 22 b for driving the intensifier 40 connects the first working medium channel 32 with the second working medium channel 33 .
- the electromagnetic valve 22 a shuts off the pressure equalization circuit 22 before the closed-circuit working medium pump 11 starts operation, and opens the pressure equalization circuit 22 when the closed-circuit working medium pump 11 stops operation.
- the pressure equalization circuit 22 is open, the pressure of the first working medium channel 32 and the pressure of the second working medium channel 33 become identical and the intensifier stops operation. Since the electromagnetic valve 22 a is normally open, the electromagnetic valve 22 a opens the pressure equalization circuit 22 to function as a safety circuit when the power supply is stopped at emergency.
- the throttle valve 22 b prevents the hydraulic device from receiving impact pressure to be damaged due to abrupt pressure change when the pressure equalization circuit 22 opens. Further, if the total amount of the working medium F 1 in the system is large, the pressure of the working medium F 1 may fluctuate due to switching of the electromagnetic valve 22 a . However, since the total amount of the working medium F 1 in the present embodiment is small, large pressure fluctuations do not occur, and then the throttle valve 22 b is not necessarily required.
- the pressure equalization circuit 22 is not necessarily required.
- a recovery circuit 34 communicates the selection circuit 26 with the working medium tank 31 .
- a safety valve 25 is connected in parallel with a flow regulation valve 24 , and a filter 29 and a heat exchanger 30 are connected with these elements in series. If control in the servo system of the closed-circuit working medium pump 11 runs away, the safety valve 25 functions to maintain the pressure of the working medium F 1 less than or equal to a setting value. This function of the safety valve 25 prevents the pressure of the ultra-high pressure generator 70 from increasing abruptly.
- the flow regulation valve 24 controls the amount of the highly pressurized working medium F 1 that is recovered from the selection circuit 26 to the working medium tank 31 via the recovery circuit 34 .
- the working medium tank 31 regulates the amount of the working medium F 1 in the system according to the reciprocation of the piston 43 in the intensifier 40 .
- the recovery circuit 34 functions to supply the necessary working medium F 1 to the working medium tank 31 .
- the working medium F 1 is filtered by the filter 29 and cooled by the heat exchanger 30 .
- the working medium F 1 is supplied from the working medium tank 31 via the supply circuit 21 and is returned from the selection circuit 26 to the working medium tank 31 .
- a constant amount of the working medium F 1 flows in the circuits via the working medium tank 31 according to the operation of the intensifier 40 . Therefore, the working medium F 1 is always cooled by the heat exchanger 30 and the temperature thereof is kept constant.
- the working medium F 1 recovered via the recovery circuit 34 is a leak of the working medium F 1 boosted by the closed-circuit working medium pump 11 . Since the flow regulation valve 24 is arranged in the recovery circuit 34 for the leak that deteriorates the mechanical efficiency, the leak amount can be regulated properly to prevent the mechanical efficiency from being deteriorated excessively.
- the flow regulation valve 24 is arranged in the recovery circuit 34 , allowing for setting the flow rate of the working medium F 1 flowing into the heat exchanger 30 to a predetermined amount.
- a cooling medium of the heat exchanger 30 is the pressurized fluid F 2 . Since all the pressurized fluid F 2 is flown through the heat exchanger 30 , heat quantity recovered by the heat exchanger 30 may become too large. However, by throttling the flow rate of the working medium F 1 having higher temperature which is flown through the heat exchanger 30 , the recovered heat quantity can be controlled.
- the safety valve 25 may be eliminated.
- the heat exchanger 30 is unnecessary.
- the flow regulation valve 24 and the pipe connecting the flow regulation valve 24 can be eliminated. If the safety valve 25 and the flow regulation valve 24 can be eliminated, the recovery circuit 34 is unnecessary. In this case, all the working medium to be supplied can be offset by the leak from the working medium pump 11 .
- the pressurized fluid F 2 is supplied from the supply port 68 for the pressurized fluid F 2 , passes through the heat exchanger 30 , is filtered by the filter 67 , and then, is stored in the storage tank 69 .
- the pressurized fluid F 2 is supplied into the storage tank 69 by the use of a ball tap 66 , and when the liquid surface in the storage tank 69 reaches an upper limit, the supply of the pressurized fluid F 2 is stopped.
- positions of the filter 67 and the heat exchanger 30 are exchangeable.
- a vortex pump 65 sucks the pressurized fluid F 2 from the bottom of the storage tank 69 to supply the pressurized fluid F 2 to suction valves 48 , 48 in the intensifier 40 through a supply channel 60 .
- a safety valve 63 is arranged in the supply channel 60 .
- the safety valve 63 has advantageous effects of deterring the discharge port of the vortex pump 65 from being closed completely when discharging of the pressurized fluid F 2 is stopped to prevent breakdown of the vortex pump 65 . Further, if the suction valve 48 is leaked, the pressurized fluid F 2 under ultra-high pressure flows into the supply channel 60 .
- the safety valve 63 has functions to prevent the breakdown of the device at the time of this kind of emergency.
- an electromagnetic valve 61 is arranged to supply cooling water for packing.
- the cooling water for packing flows through the throttle valve 62 to packing members (not shown) that seal between the high pressure cylinders 451 , 452 and the plungers 461 , 462 to cool the packing members.
- a pressure switch 64 for detecting supply pressure is arranged in the supply channel 60 . The pressure switch 64 monitors whether the supply pressure of the pressurized fluid F 2 exceeds cracking pressure of the suction valves 48 , 48 so that the pressurized fluid F 2 is supplied to the intensifier 40 .
- pressure switch 64 can be replaced by a pressure detector.
- the discharge valves 47 , 47 are in communication with a discharge port 55 via an accumulator 51 through a discharge pipe 56 .
- a filter 52 is arranged in the accumulator 51 . Since the filter 52 is arranged in the accumulator 51 , the filter 52 receives ultra-high pressure from inside and outside thereof. A filter for a normal pressure level can be used as the filter 52 .
- the pressurized fluid F 2 under ultra-high pressure discharged from the discharge port 55 is ejected from a nozzle 59 via an on-off valve 58 .
- the pressure detector 53 that detects the pressure of the pressurized fluid F 2 under ultra-high pressure is connected to the discharge pipe 56 .
- the controller 15 controls the pressure and the flow rate of the closed-circuit working medium pump 11 , and the travel direction in the intensifier 40 according to the position of the piston 43 in the intensifier 40 and the pressure of the pressurized fluid F 2 that is detected by the pressure detector 53 .
- Pressure feedback is calculated based on the degree of pressure increase.
- the modern control having high robustness such as the adaptive control can be properly used for the pressure control.
- FIG. 2 shows a pressure waveform W 1 of the pressurized fluid F 2 generated by the ultra-high pressure generator 70 configured as described above.
- the horizontal axis indicates elapsed time and the vertical axis indicates pressure.
- the pressure and the flow rate of the closed-circuit working medium pump 11 is regulated based on actual discharge pressure to determine the speed of the plungers 461 , 462 properly, which forms the pressure waveform W 1 of the pressurized fluid F 2 as an approximately straight line at a setting pressure P.
- the pressure is temporarily decreased at constant time intervals in synchronization with switching the travel directions of the piston 43 .
- the closed-circuit working medium pump 11 stops rotating, and this rotation status is maintained by the bidirectionally rotatable drive source 12 .
- the working medium F 1 in the closed-circuit working medium pump 11 does not flow at the pressuring side. Since the working medium F 1 does not flow, the pressure loss in the first and second working medium channels 32 , 33 disappears and the pressure of working medium. F 1 slightly increases. Since the pressure of the pressurized fluid F 2 that is pressurized under ultra-high pressure becomes larger than the pressure of the working medium F 1 by the factor of intensify ratio, the pressure of the pressurized fluid F 2 increases ( ⁇ P) by the factor of intensify ratio relative to pressure increase of the working medium F 1 . The number of rotations of the closed-circuit working medium pump 11 is controlled by the pressure feedback, thereby minimizing the ⁇ P. When the continuous discharge is resumed, the pressure of the pressurized fluid F 2 turns back to stable pressure again at around the setting pressure.
- the pipe fittings such as pipes, valves, hoses, joints and the like used in the ultra-high pressure pipes receive excessive internal stress.
- the ultra-high pressure generator 70 of the present embodiment the pressure vibration is reduced greatly, allowing for longer service life of the pipe fittings. Therefore, the ultra-high pressure generator 70 is suitably adapted to an ultra-high pressure generator that generates especially high pressure.
- the ultra-high pressure generator 70 of the present embodiment controls the closed-circuit working medium pump 11 according to the pressure detected by the pressure detector 53 , thereby keeping the discharge pressure stably at around the setting pressure P.
- the discharge pressure is stable at a constant value, which stabilizes the flow rate and the flow volume of the jet of the pressurized fluid F 2 ejected from the nozzle 59 . Further, the pressure waveform is stabilized, allowing the volume of the accumulator 51 to be reduced.
- the accumulator 51 is a pressure vessel to have high internal stress generated inside thereof. The internal stress increases in proportion to the square of the internal diameter of the accumulator. In addition, energy accumulated in the accumulator is in proportion to the internal volume.
- the ultra-high pressure generator 70 has a stable pressure waveform, allowing the accumulator volume to be reduced, and can suitably be adapted to an ultra-high pressure generator that generates especially high pressure.
- the ultra-high pressure generator 70 includes the plungers 461 , 462 and the high pressure cylinders 451 , 452 on both sides of the double-acting drive cylinder 44 , the pressure of the pressurized fluid F 2 acts upon the piston 43 via the plungers 461 , 462 when the travel direction of the piston 43 is switched, where the pressure of the pressurized fluid F 2 is ultra-high pressure in the high pressure cylinders 451 , 452 which has been in a compression cycle until right before the switching. At this time, the pressurized fluid F 2 in the high pressure cylinders 451 , 452 is expanded based on the expansion rate thereof. Further, since the working medium. F 1 is slightly compressed, the compressed working medium F 1 is expanded at the time of switching.
- the ultra-high pressure generator 70 does not include the relief valve 27 and the directional control valve 3 (see FIG. 1 in Japanese Patent Application Publication number S63-39799) in the related art, the mechanical efficiency thereof is improved.
- the improvement of the mechanical efficiency reduces waste heat generated from the ultra-high pressure generator 70 . Therefore, the amount of cooling water for cooling the working medium F 1 can be reduced greatly. Since the necessary amount of cooling water is small, the ultra-high pressure generator 70 can match the discharge amount of the pressurized fluid F 2 with the amount of cooling water and can temporarily use the supplied pressurized fluid F 2 as the cooling water. Still further, since the flow rate of the necessary pressurized fluid F 2 is small, the storage tank 69 can be reduced in size.
- the mechanical efficiency of the ultra-high pressure generator 70 is substantially improved, which allows the mechanical components constituting the device to be reduced in size as well as the configuration to be simplified. Thus, the machine can be downsized as a whole.
- the ultra-high pressure generator 70 according to the embodiment of the present invention is described above, but the configuration of the present invention is not limited to the one described above.
- the bidirectionally rotatable drive source 12 is not limited to a servo motor, but may be a source that can control torque and the number of rotations, and can keep the rotation.
- an electromagnetic pressure relief valve can be arranged in the recovery circuit 34 in place of the pressure equalization circuit 22 , the electromagnetic valve 22 a , the throttle valve 22 b , the flow regulation valve 24 and the safety valve 25 .
- the electromagnetic pressure relief valve is opened to reduce the pressure in the working medium channels 32 , 33 .
- the electromagnetic pressure relief valve is closed.
- the ultra-high pressure generator 70 can be applied to a pressure/fatigue breakdown testing device, a hydroforming device, not limited to a water jet application.
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- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
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Abstract
An ultra-high pressure generator includes: an intensifier that discharges pressurized fluid and has a double-acting drive cylinder formed to have a first chamber and a second chamber which are delimited by a piston driven by a working medium, high pressure cylinders which discharge the pressurized fluid, and plungers which reciprocate with the piston in the high pressure cylinders; a closed-circuit working medium pump having a first and second ports as suction/discharge ports for the working medium; a drive source that drives the closed-circuit working medium pump; a first working medium channel that communicates the first chamber with the first port; and a second working medium channel that communicates the second chamber with the second port, wherein the closed-circuit working medium pump sucks/discharges the working medium from/to the first and second chambers respectively via the first and second ports to drive the intensifier.
Description
- This application claims the benefit of priority to Japanese Patent Application No. 2014-190725, filed on Sep. 19, 2014, the disclosures of all of which are hereby incorporated by reference in their entities.
- 1. Field of the Invention
- The present invention relates to an ultra-high pressure generator obtaining ultra-high pressure output by plungers which are reciprocatively driven by hydraulic pressure or the like.
- 2. Description of the Related Arts
- An ultra-high pressure pump that discharges a jet of high pressure fluid has been known to have the following configuration (see FIG. 1 in Japanese Patent Application Publication number S63-39799). An open-circuit hydraulic pump (working medium pump) 1 is connected, at a discharging side, to low pressure cylinder chambers C1 and C2 in an intensifier 2 via a two-way control valve (directional control valve) 3. When the directional control valve 3 is at the position V1, hydraulic oil (working medium) boosted by the hydraulic pump 1 is supplied to the cylinder chamber C1 and the working medium in the cylinder chamber C2 is returned to a
tank 25. At this time, the piston P in the intensifier 2 is moved toward the right direction inFIG. 1 . When the piston P in the intensifier 2 reaches the right end, the directional control valve 3 is switched to the position V2. The pressurized working medium is supplied to the cylinder chamber C2 and the working medium in the cylinder chamber C1 is returned to thetank 25. At this time, the piston P in the intensifier 2 is moved toward the left direction inFIG. 1 . When the piston P in the intensifier 2 reaches the left end, the directional control valve 3 is switched to the position V1. The pressure of the pressurized fluid is pressurized by a factor of intensify ratio in the pressure of the working medium. The pressure of the pressurized fluid is controlled by therelief valve 27 controlling the pressure of the working medium. - The aforementioned high pressure generator with the open-circuit hydraulic pump and the directional control valve has the following problem.
- In a cutting application by water jet, the high pressure generator discharges the pressurized fluid continuously. At the time of discharging the jet from the high pressure generator, the hydraulic pressure generator is driven to have high pressure loss in the directional control valve. When the discharge of the fluid under high pressure is stopped, a double-acting drive cylinder is stopped, which makes the pressure loss of the hydraulic oil as the fluid under low pressure become zero. The amount of the pressure loss in the directional control valve appears as temporary abnormal rise of hydraulic pressure of the hydraulic oil. The temporary abnormal rise of hydraulic pressure of the hydraulic oil affects the discharge pressure of the fluid under high pressure according to the intensify ratio of the intensifier. Here, the intensify ratio is a pressure ratio between the pressure of the pressurized fluid under high pressure and the pressure of the hydraulic oil under low pressure, and is normally set as several tens of times. That is, when the continuous discharge of the fluid under high pressure is stopped, the pressure rises temporarily by the pressure amount of several tens of times of the pressure loss in the directional control valve. Therefore, when the continuous discharge is stopped, the pressure rises excessively.
- In the cutting application by water jet, pulsation in a high pressure circuit occurs when the double-acting intensifier switches directions. If the directional control valve is increased in size with the aim of reducing the pressure loss thereof, responsiveness of the directional control valve deteriorates. At the stroke ends of the intensifier, the pressurized fluid is not supplied from a pressure process in the cylinder to a downstream of a check valve. Then, the pressurized fluid is not supplied till a travel direction in the intensifier is switched, causing the pressure to drop. This pressure drop is determined by the switching time of the travel direction in the intensifier, the volume of an accumulator and the discharge amount. If the responsiveness of the working fluid deteriorates, a pressure waveform of the pressurized fluid is disturbed. The jet of the pressurized fluid, that is, the flow rate of the water jet depends on the pressure. Therefore, the deterioration of responsiveness in the working fluid circuit causes quality of the jet water to degrade.
- In the high pressure generator including a double-acting intensifier driven by the open-circuit hydraulic pump, the directional control valve for the hydraulic pressure generator is mandatory. However, the pressure loss in the directional control valve causes mechanical efficiency to drop.
- The present invention is intended to provide an ultra-high pressure generator that reduces fluctuations in a pressure waveform of pressurized fluid and enhances mechanical efficiency.
- In view of the problem above, the invention provides an ultra-high pressure generator including: an intensifier that discharges pressurized fluid and includes a double-acting drive cylinder formed to have a first chamber and a second chamber which are delimited by a piston that is driven by a working medium, a high pressure cylinder that discharges the pressurized fluid, and a plunger that reciprocates with the piston in the high pressure cylinder; a closed-circuit working medium pump that has a first port and a second port as suction/discharge ports for the working medium, and sucks/discharges the working medium from/to the first chamber and the second chamber respectively via the first port and the second port to drive the intensifier; a drive source that drives the closed-circuit working medium pump; a first working medium channel that communicates the first chamber with the first port; and a second working medium channel that communicates the second chamber with the second port.
- According to the configuration of the ultra-high pressure generator, the closed-circuit working medium pump is used to suck the working medium from a pressurized side in the intensifier, pressurize it, and to return it to a pressing side in the intensifier, which does not require a directional control valve that controls flow directions of the working medium to be supplied to the first or second chamber. Therefore, the problem can be resolved such that pressure of the high pressure fluid or the pressurized fluid increases abnormally at the time of stopping discharge due to the pressure loss in the directional control valve.
- That is, according to the present invention, in a case where the pressurized fluid is discharged continuously, when the flow direction of the closed-circuit working medium pump is reversed, the pressure in either one of the first and second chambers becomes approximately 0 MPa, and the other one is pressurized immediately. Further, since the pressure of the working medium becomes zero temporarily when the travel direction of the piston in the double-acting drive cylinder is switched, the pressure does not increase abnormally at the time of switching the travel direction. With these effects, astable pressure waveform can be obtained which has little pressure fluctuations of the high pressure fluid.
- Still further, according to the ultra-high pressure generator having the configuration above, since the working medium filled in the double-acting drive cylinder of the intensifier is directly driven by the closed-circuit working medium pump, high response speed of the intensifier can be achieved. Thus, the pressure waveform of the pressurized fluid can be stable.
- Therefore, a stable jet can be obtained when the water jet is discharged by the ultra-high pressure generator of the present invention.
- The working medium is filled in the first or second chamber of the double-acting drive cylinder. When the direction of the intensifier is switched, either one of the first and second chambers which has been pressurized is changed to a supply side, and the other one that has been a supply side is pressurized. At the time of switching the directions of the intensifier, a bidirectionally rotatable drive source is reversely rotated against inertial force of the closed-circuit pressurizing device to suck the working fluid from a supplying chamber. At this time, since the pressurized fluid that has been pressurized in the high pressure cylinder is expanded based on compression rate of the pressurized fluid to push back the piston, a load on the drive system can be reduced.
- In the present invention, the closed-circuit working medium pump is preferably a fixed-displacement swash plate axial pump and the drive source is preferably a bidirectionally rotatable drive source.
- According to the ultra-high pressure generator having the configuration above, reliability of the closed-circuit working medium pump is improved.
- In the present invention, the closed-circuit working medium pump may be a variable-displacement swash plate axial pump that can reverse a tilt angle between positive and negative directions. With such a configuration, a unidirectionally rotatable drive source can be applied as a drive source.
- In the present invention, the drive source can preferably be a servo motor, and the ultra-high pressure generator can comprise a pressure detector that detects pressure of the pressurized fluid discharged from the intensifier and a controller that controls the number of rotations of the servo motor in response to the pressure detected by the pressure detector.
- According to the ultra-high pressure generator having the configuration above, the flow rate and the pressure of the closed-circuit working medium pump is controlled in response to the pressure of the pressurized fluid detected by the pressure detector. Since proper pressure of the working medium can be generated by the closed-circuit working medium pump when the ultra-high pressure generator is driven, the pressure waveform of the pressurized fluid is stabilized.
- According to the configuration above, since the ultra-high pressure generator of the present invention does not need to include a relief circuit for regulating the pressure of the working medium, the thermal loss of the relief circuit does not exist, thereby increasing the mechanical efficiency. Further, since the thermal loss of the relief circuit does not need to be recovered, the amount of cooling water can be significantly reduced.
- In a case where the ultra-high pressure generator of the present invention is used as a continuous discharge high pressure generator, when the discharge of the pressurized fluid is stopped, the servo motor continues to rotate so that the closed-circuit working medium pump keeps the pressure.
- The ultra-high pressure generator of the present invention preferably includes a storage tank in which the pressurized fluid is stored, a supply port through which the pressurized fluid is supplied to the storage tank, and a heat exchanger that cools the working medium, wherein the pressurized fluid supplied through the supply port is supplied to the storage tank via the heat exchanger.
- According to the configuration as described above, since a cooling medium that cools the working medium is reused as the pressurized fluid, the amount of the pressurized fluid needed for the ultra-high pressure generator can be reduced.
- Thus, the ultra-high pressure generator according to the present invention can reduce the fluctuations in the pressure waveform of the pressurized fluid and can improve the mechanical efficiency.
-
FIG. 1 is a diagram showing a hydraulic pressure circuit of an ultra-high pressure generator according to an embodiment of the present invention; and -
FIG. 2 is a chart showing a pressure waveform of fluid under high pressure in the ultra-high pressure generator according to the embodiment of the present invention. - Referring to
FIG. 1 , anultra-high pressure generator 70 in an embodiment of the present invention will be described. A working medium F1 is hydraulic oil and pressurized fluid F2 is water, in theultra-high pressure generator 70. Theultra-high pressure generator 70 is preferably used for water jet cutting in which ultra-high pressure water is discharged continuously. - The
ultra-high pressure generator 70 of the present embodiment is a device that continuously discharges the pressurized fluid F2 under ultra-high pressure. Theultra-high pressure generator 70 includes: anintensifier 40 having a double-actingdrive cylinder 44 formed to have afirst chamber 41 and asecond chamber 42 which are delimited by apiston 43 driven by the working medium F1, andplungers piston 43 inhigh pressure cylinders medium pump 11 having afirst port 111 and asecond port 112 as suction/discharge ports; a bidirectionallyrotatable drive source 12 that drives the closed-circuit workingmedium pump 11; a first workingmedium channel 32 that communicates thefirst chamber 41 with thefirst port 111; and a second workingmedium channel 33 that communicates thesecond chamber 42 with thesecond port 112. - The closed-circuit working
medium pump 11 is a fixed-displacement swash plate axial pump and a drive source thereof is constituted with a servo motor as a bidirectionallyrotatable drive source 12. - The
ultra-high pressure generator 70 further includes apressure detector 53 that measures the pressure of the pressurized fluid F2 discharged from theintensifier 40 and acontroller 15 that controls the number of rotations of the bidirectionallyrotatable drive source 12 in response to the pressure detected by thepressure detector 53. - The
ultra-high pressure generator 70 includes asupply port 68 through which the pressurized fluid F2 is supplied, aheat exchanger 30 that cools the working medium F1 and astorage tank 69 in which the pressurized fluid F2 is stored. The pressurized fluid F2 supplied from thesupply port 68 flows through theheat exchanger 30 into thestorage tank 69. - The intensify ratio is determined to be ratio of the cross-sectional area of the
piston 43 to cross-sectional areas of thehigh pressure cylinders plungers intensifier 40 are caused to reciprocate from side to side by the double-actingdrive cylinder 44 in thehigh pressure cylinders suction valve 48 anddischarge valve 47 is arranged at the ends of thehigh pressure cylinders first chamber 41, thepiston 43 in the double-actingdrive cylinder 44 moves toward the right direction inFIG. 1 . At this time, the pressurized fluid F2 flows into thehigh pressure cylinder 451 through thesuction valve 48. Besides, the pressurized fluid F2 is discharged from thehigh pressure cylinder 452 through thedischarge valve 47. When thepiston 43 moves toward the right direction (right side) inFIG. 1 to reach around the right end, aright end detector 492 detects thepiston 43 to switch a travel direction of thepiston 43 toward the left direction inFIG. 1 . When thepiston 43 is moved toward the left direction (left side) inFIG. 1 , the double-actingdrive cylinder 44 acts reversely as described above. Likewise, aleft end detector 491 detects that thepiston 43 has reached around the left end. The reciprocation of the double-actingdrive cylinder 44 allows the pressurized fluid F2 to be discharged continuously. - It is noted that detectors such as proximity switches, limit switches may be used as the
left end detector 491 andright end detector 492. When the proximity switches are used,respective detectors intensifier 40, resulting in a simple structure. - It is also noted that the
suction valves 48 anddischarge valves 47 are check valves, but a directional flow regulation valve may be used in place of the pair of check valves. In addition, if a one-shot ultra-high pressure generator is used which is not the continuous discharge type, thedischarge valves 47 is unnecessary. - The closed-circuit working
medium pump 11 is a fixed-displacement swash plate axial pump. Thefirst port 111 is directly connected to thefirst chamber 41 via the first workingmedium channel 32, and thesecond port 112 is directly connected to thesecond chamber 42 via the second workingmedium channel 33. That is, when thepiston 43 in theintensifier 40 moves toward the right side, the closed-circuit workingmedium pump 11 pressurizes the working medium F1 in thesecond chamber 42 to predetermined pressure to feed to thefirst chamber 41. When thepiston 43 in theintensifier 40 moves toward the left side, the closed-circuit workingmedium pump 11 feeds the working medium F1 in thefirst chamber 41 to the second chamber reversely. The closed-circuit workingmedium pump 11 controls the pressure and the flow rate of the working medium F1 by controlling the number of rotations thereof. The bidirectionallyrotatable drive source 12 as a servo motor can control the number of rotations as desired to maintain a rotation angle such that the output shaft thereof does not rotate. Further, the closed-circuit workingmedium pump 11 can control the pressure and the flow rate of the working medium F1 by the use of combination of the fixed-displacement swash plate axial pump and the bidirectionally rotatable servo motor, and can set the flowing rate of the working medium F1 to zero while maintaining the pressure of the working medium F1. Still further, reliability of the ultra-high pressure generator is enhanced by the use of the fixed-displacement swash plate axial pump. - It is noted that a variable-displacement axial plunger pump that can reverse a tilt angle from positive to negative or vice versa and a unidirectionally rotatable drive source can be used in place of the combination of the closed-circuit working
medium pump 11 and the bidirectionallyrotatable drive source 12. The variable-displacement axial plunger pump capable of reversing a tilt angle can switch a suction side and a discharge side of two ports by reversing the tilt angle, and can be used as the closed-circuit working medium pump. - A circuit for the working medium F1 is arranged in a
valve block 20 as shown below. Thevalve block 20 is connected to theintensifier 40 and is connected to the closed-circuit workingmedium pump 11 withrubber hoses rubber hoses ultra-high pressure generator 70. - The
valve block 20 includes atemperature detector 28 that detects temperature of the working medium. When the temperature of the working medium F1 increases abnormally, thetemperature detector 28 gives a warning. Thetemperature detector 28 is attached to thevalve block 20 not to contact the working medium F1 directly, and then thetemperature detector 28 is hard to suffer damage due to the pressure fluctuations of the working medium F1 or the like. - It is noted that the
temperature detector 28 can be connected to asupply circuit 21 or aselection circuit 26 when a problem such as breakdown does not need to be considered. - The first working
medium channel 32 is connected to the second workingmedium channel 33 with theselection circuit 26 inclusive of a pair ofcheck valves check valves medium channels pressure detector 27 that detects the pressure of the working medium F1 is arranged in theselection circuit 26. Theselection circuit 26 allows thepressure detector 27 to detect the pressure of either one of the first workingmedium channel 32 and the second workingmedium channel 33 which has higher pressure. Thus, the structure for detecting the pressure can be formed simply. Thepressure detector 27 can inform abnormality when the pressure of the working medium F1 is out of a normal range. - The first working
medium channel 32 is connected to the second workingmedium channel 33 with thesupply circuit 21 that includes a pair ofcheck valves medium channels supply circuit 21 communicates thecheck valves medium tank 31. The workingmedium tank 31 is applied with internal pressure. The working medium F1 as hydraulic oil is incompressible fluid, but is slightly compressed by pressurization. One of thefirst chamber 41 andsecond chamber 42 in theintensifier 40, which is at a supply side, is set to have pressure around zero MPa normally, and the other is set to have setting pressure. The total amount of the working medium F1 accumulated in the system is changed depending on the volume of the working medium F1 presented in either one of thefirst chamber 41 andsecond chamber 42, which is at a compression cycle side, and the pipes. Thesupply circuit 21 functions to regulate the total amount of the working medium F1. The workingmedium tank 31 only needs to have the function to regulate the total amount of the working medium F1, and therefore can be reduced in size. The workingmedium tank 31 is equivalent to a thin-walled gas accumulator to have a radiation function for the working medium F1. - A
pressure equalization circuit 22 including anelectromagnetic valve 22 a and athrottle valve 22 b for driving theintensifier 40 connects the first workingmedium channel 32 with the second workingmedium channel 33. Theelectromagnetic valve 22 a shuts off thepressure equalization circuit 22 before the closed-circuit workingmedium pump 11 starts operation, and opens thepressure equalization circuit 22 when the closed-circuit workingmedium pump 11 stops operation. When thepressure equalization circuit 22 is open, the pressure of the first workingmedium channel 32 and the pressure of the second workingmedium channel 33 become identical and the intensifier stops operation. Since theelectromagnetic valve 22 a is normally open, theelectromagnetic valve 22 a opens thepressure equalization circuit 22 to function as a safety circuit when the power supply is stopped at emergency. Thethrottle valve 22 b prevents the hydraulic device from receiving impact pressure to be damaged due to abrupt pressure change when thepressure equalization circuit 22 opens. Further, if the total amount of the working medium F1 in the system is large, the pressure of the working medium F1 may fluctuate due to switching of theelectromagnetic valve 22 a. However, since the total amount of the working medium F1 in the present embodiment is small, large pressure fluctuations do not occur, and then thethrottle valve 22 b is not necessarily required. - It is noted that, if some other device is arranged to secure safety, the
pressure equalization circuit 22 is not necessarily required. - A
recovery circuit 34 communicates theselection circuit 26 with the workingmedium tank 31. In therecovery circuit 34, asafety valve 25 is connected in parallel with aflow regulation valve 24, and afilter 29 and aheat exchanger 30 are connected with these elements in series. If control in the servo system of the closed-circuit workingmedium pump 11 runs away, thesafety valve 25 functions to maintain the pressure of the working medium F1 less than or equal to a setting value. This function of thesafety valve 25 prevents the pressure of theultra-high pressure generator 70 from increasing abruptly. Theflow regulation valve 24 controls the amount of the highly pressurized working medium F1 that is recovered from theselection circuit 26 to the workingmedium tank 31 via therecovery circuit 34. As mentioned above, the workingmedium tank 31 regulates the amount of the working medium F1 in the system according to the reciprocation of thepiston 43 in theintensifier 40. Therecovery circuit 34 functions to supply the necessary working medium F1 to the workingmedium tank 31. When recovered into the workingmedium tank 31, the working medium F1 is filtered by thefilter 29 and cooled by theheat exchanger 30. As mentioned above, according to the switching of the travel directions of thepiston 43 in theintensifier 40, the working medium F1 is supplied from the workingmedium tank 31 via thesupply circuit 21 and is returned from theselection circuit 26 to the workingmedium tank 31. Thus, a constant amount of the working medium F1 flows in the circuits via the workingmedium tank 31 according to the operation of theintensifier 40. Therefore, the working medium F1 is always cooled by theheat exchanger 30 and the temperature thereof is kept constant. - The working medium F1 recovered via the
recovery circuit 34 is a leak of the working medium F1 boosted by the closed-circuit workingmedium pump 11. Since theflow regulation valve 24 is arranged in therecovery circuit 34 for the leak that deteriorates the mechanical efficiency, the leak amount can be regulated properly to prevent the mechanical efficiency from being deteriorated excessively. - In addition, the
flow regulation valve 24 is arranged in therecovery circuit 34, allowing for setting the flow rate of the working medium F1 flowing into theheat exchanger 30 to a predetermined amount. In theultra-high pressure generator 70, a cooling medium of theheat exchanger 30 is the pressurized fluid F2. Since all the pressurized fluid F2 is flown through theheat exchanger 30, heat quantity recovered by theheat exchanger 30 may become too large. However, by throttling the flow rate of the working medium F1 having higher temperature which is flown through theheat exchanger 30, the recovered heat quantity can be controlled. - It is noted, in a case where some other safety measure is taken against the abnormal pressure increase, the
safety valve 25 may be eliminated. In a case where the heat quantity generated in the system is small and the working medium F1 can be cooled sufficiently by outside air, theheat exchanger 30 is unnecessary. - In a case where the leak amount from the working
medium pump 11 can offset the supply amount of the working medium from the workingmedium tank 31, theflow regulation valve 24 and the pipe connecting theflow regulation valve 24 can be eliminated. If thesafety valve 25 and theflow regulation valve 24 can be eliminated, therecovery circuit 34 is unnecessary. In this case, all the working medium to be supplied can be offset by the leak from the workingmedium pump 11. - The pressurized fluid F2 is supplied from the
supply port 68 for the pressurized fluid F2, passes through theheat exchanger 30, is filtered by thefilter 67, and then, is stored in thestorage tank 69. The pressurized fluid F2 is supplied into thestorage tank 69 by the use of aball tap 66, and when the liquid surface in thestorage tank 69 reaches an upper limit, the supply of the pressurized fluid F2 is stopped. - It is noted that positions of the
filter 67 and theheat exchanger 30 are exchangeable. - A
vortex pump 65 sucks the pressurized fluid F2 from the bottom of thestorage tank 69 to supply the pressurized fluid F2 to suctionvalves intensifier 40 through asupply channel 60. - A
safety valve 63 is arranged in thesupply channel 60. Thesafety valve 63 has advantageous effects of deterring the discharge port of thevortex pump 65 from being closed completely when discharging of the pressurized fluid F2 is stopped to prevent breakdown of thevortex pump 65. Further, if thesuction valve 48 is leaked, the pressurized fluid F2 under ultra-high pressure flows into thesupply channel 60. Thesafety valve 63 has functions to prevent the breakdown of the device at the time of this kind of emergency. - In the
supply channel 60, anelectromagnetic valve 61 is arranged to supply cooling water for packing. When theelectromagnetic valve 61 is opened, the cooling water for packing flows through thethrottle valve 62 to packing members (not shown) that seal between thehigh pressure cylinders plungers pressure switch 64 for detecting supply pressure is arranged in thesupply channel 60. Thepressure switch 64 monitors whether the supply pressure of the pressurized fluid F2 exceeds cracking pressure of thesuction valves intensifier 40. - It is noted that the
pressure switch 64 can be replaced by a pressure detector. - The
discharge valves discharge port 55 via anaccumulator 51 through adischarge pipe 56. Afilter 52 is arranged in theaccumulator 51. Since thefilter 52 is arranged in theaccumulator 51, thefilter 52 receives ultra-high pressure from inside and outside thereof. A filter for a normal pressure level can be used as thefilter 52. - The pressurized fluid F2 under ultra-high pressure discharged from the
discharge port 55 is ejected from anozzle 59 via an on-offvalve 58. Thepressure detector 53 that detects the pressure of the pressurized fluid F2 under ultra-high pressure is connected to thedischarge pipe 56. - The
controller 15 controls the pressure and the flow rate of the closed-circuit workingmedium pump 11, and the travel direction in theintensifier 40 according to the position of thepiston 43 in theintensifier 40 and the pressure of the pressurized fluid F2 that is detected by thepressure detector 53. Pressure feedback is calculated based on the degree of pressure increase. The modern control having high robustness such as the adaptive control can be properly used for the pressure control. -
FIG. 2 shows a pressure waveform W1 of the pressurized fluid F2 generated by theultra-high pressure generator 70 configured as described above. InFIG. 2 , the horizontal axis indicates elapsed time and the vertical axis indicates pressure. The pressure and the flow rate of the closed-circuit workingmedium pump 11 is regulated based on actual discharge pressure to determine the speed of theplungers piston 43. - During the continuous discharge being stopped, the closed-circuit working
medium pump 11 stops rotating, and this rotation status is maintained by the bidirectionallyrotatable drive source 12. Thus, the working medium F1 in the closed-circuit workingmedium pump 11 does not flow at the pressuring side. Since the working medium F1 does not flow, the pressure loss in the first and second workingmedium channels medium pump 11 is controlled by the pressure feedback, thereby minimizing the ΔP. When the continuous discharge is resumed, the pressure of the pressurized fluid F2 turns back to stable pressure again at around the setting pressure. - In an ultra-high pressure generator that generates pressure level of 600 MPa, intensify ratio of around 30 times is necessary. The higher the pressure becomes, the greater the intensify ratio is necessary, and, the greater the intensify ratio becomes, the greater the rate of the pressure increase becomes when the discharge is stopped. Further, in a case where the pressure is extremely high, the ultra-high pressure fluid generates high internal stress in the pressure pipes. The pressure causes vibration, which greatly limits a material, thickness and inner surface finishing of the pressure pipes. The pressure increase and pressure vibration of the ultra-high pressure fluid give excessive stress on the ultra-high pressure generator and the pressure pipe system.
- The pipe fittings such as pipes, valves, hoses, joints and the like used in the ultra-high pressure pipes receive excessive internal stress. According to the
ultra-high pressure generator 70 of the present embodiment, the pressure vibration is reduced greatly, allowing for longer service life of the pipe fittings. Therefore, theultra-high pressure generator 70 is suitably adapted to an ultra-high pressure generator that generates especially high pressure. - The
ultra-high pressure generator 70 of the present embodiment controls the closed-circuit workingmedium pump 11 according to the pressure detected by thepressure detector 53, thereby keeping the discharge pressure stably at around the setting pressure P. The discharge pressure is stable at a constant value, which stabilizes the flow rate and the flow volume of the jet of the pressurized fluid F2 ejected from thenozzle 59. Further, the pressure waveform is stabilized, allowing the volume of theaccumulator 51 to be reduced. Theaccumulator 51 is a pressure vessel to have high internal stress generated inside thereof. The internal stress increases in proportion to the square of the internal diameter of the accumulator. In addition, energy accumulated in the accumulator is in proportion to the internal volume. - Therefore, the ultra-high pressure generator that generates ultra high pressure over 600 MPa has a very difficult technical problem in producing an accumulator with large volume. The
ultra-high pressure generator 70 has a stable pressure waveform, allowing the accumulator volume to be reduced, and can suitably be adapted to an ultra-high pressure generator that generates especially high pressure. - Since the
ultra-high pressure generator 70 includes theplungers high pressure cylinders drive cylinder 44, the pressure of the pressurized fluid F2 acts upon thepiston 43 via theplungers piston 43 is switched, where the pressure of the pressurized fluid F2 is ultra-high pressure in thehigh pressure cylinders high pressure cylinders piston 43 in theintensifier 40 is switched, the working medium F1 that has been pressurized until right before the switching flows into the closed-circuit workingmedium pump 11. Although a large stress is applied to the closed-circuit workingmedium pump 11 and the bidirectionallyrotatable drive source 12 when the rotational direction is switched, the stress applied to the closed-circuit workingmedium pump 11 at this time can be reduced by the actions described above. - Since the
ultra-high pressure generator 70 does not include therelief valve 27 and the directional control valve 3 (see FIG. 1 in Japanese Patent Application Publication number S63-39799) in the related art, the mechanical efficiency thereof is improved. The improvement of the mechanical efficiency reduces waste heat generated from theultra-high pressure generator 70. Therefore, the amount of cooling water for cooling the working medium F1 can be reduced greatly. Since the necessary amount of cooling water is small, theultra-high pressure generator 70 can match the discharge amount of the pressurized fluid F2 with the amount of cooling water and can temporarily use the supplied pressurized fluid F2 as the cooling water. Still further, since the flow rate of the necessary pressurized fluid F2 is small, thestorage tank 69 can be reduced in size. - The mechanical efficiency of the
ultra-high pressure generator 70 is substantially improved, which allows the mechanical components constituting the device to be reduced in size as well as the configuration to be simplified. Thus, the machine can be downsized as a whole. - The
ultra-high pressure generator 70 according to the embodiment of the present invention is described above, but the configuration of the present invention is not limited to the one described above. For example, the bidirectionallyrotatable drive source 12 is not limited to a servo motor, but may be a source that can control torque and the number of rotations, and can keep the rotation. - Further, an electromagnetic pressure relief valve can be arranged in the
recovery circuit 34 in place of thepressure equalization circuit 22, theelectromagnetic valve 22 a, thethrottle valve 22 b, theflow regulation valve 24 and thesafety valve 25. In this case, when theintensifier 40 is stopped operation, the electromagnetic pressure relief valve is opened to reduce the pressure in the workingmedium channels intensifier 40 resumes operation, the electromagnetic pressure relief valve is closed. - The
ultra-high pressure generator 70 according to the embodiment of the present invention can be applied to a pressure/fatigue breakdown testing device, a hydroforming device, not limited to a water jet application.
Claims (12)
1. An ultra-high pressure generator comprising:
an intensifier that discharges pressurized fluid and includes a double-acting drive cylinder formed to have a first chamber and a second chamber which are delimited by a piston driven by a working medium, a high pressure cylinder that discharges the pressurized fluid, and a plunger that reciprocates with the piston in the high pressure cylinder;
a closed-circuit working medium pump that has a first port and a second port as suction/discharge ports for the working medium, and sucks/discharges the working medium from/to the first chamber and the second chamber respectively via the first port and the second port to drive the intensifier;
a drive source that drives the closed-circuit working medium pump;
a first working medium channel that communicates the first chamber with the first port; and
a second working medium channel that communicates the second chamber with the second port.
2. The ultra-high pressure generator according to claim 1 , wherein the closed-circuit working medium pump is a fixed-displacement swash plate axial pump and the drive source is a bidirectionally rotatable drive source.
3. The ultra-high pressure generator according to claim 1 , wherein the closed-circuit working medium pump is a variable-displacement swash plate axial pump that can reverse a tilt angle between positive and negative directions.
4. The ultra-high pressure generator according to claim 1 , wherein the drive source is a servo motor, and the ultra-high pressure generator further comprises: a pressure detector that detects pressure of the pressurized fluid discharged from the intensifier; and a controller that controls the number of rotations of the servo motor in response to the pressure detected by the pressure detector.
5. The ultra-high pressure generator according to claim 2 , wherein the drive source is a servo motor, and the ultra-high pressure generator further comprises: a pressure detector that detects pressure of the pressurized fluid discharged from the intensifier; and a controller that controls the number of rotations of the servomotor in response to the pressure detected by the pressure detector.
6. The ultra-high pressure generator according to claim 3 , wherein the drive source is a servo motor, and the ultra-high pressure generator further comprises: a pressure detector that detects pressure of the pressurized fluid discharged from the intensifier; and a controller that controls the number of rotations of the servomotor in response to the pressure detected by the pressure detector.
7. The ultra-high pressure generator according to claim 1 , wherein the ultra-high pressure generator further comprises: a storage tank in which the pressurized fluid is stored; a supply port through which the pressurized fluid is supplied to the storage tank; and a heat exchanger that cools the working medium, and wherein the pressurized fluid supplied through the supply port is supplied to the storage tank via the heat exchanger.
8. The ultra-high pressure generator according to claim 2 , wherein the ultra-high pressure generator further comprises: a storage tank in which the pressurized fluid is stored; a supply port through which the pressurized fluid is supplied to the storage tank; and a heat exchanger that cools the working medium, and wherein the pressurized fluid supplied through the supply port is supplied to the storage tank via the heat exchanger.
9. The ultra-high pressure generator according to claim 3 , wherein the ultra-high pressure generator further comprises: a storage tank in which the pressurized fluid is stored; a supply port through which the pressurized fluid is supplied to the storage tank; and a heat exchanger that cools the working medium, and wherein the pressurized fluid supplied through the supply port is supplied to the storage tank via the heat exchanger.
10. The ultra-high pressure generator according to claim 4 , wherein the ultra-high pressure generator further comprises: a storage tank in which the pressurized fluid is stored; a supply port through which the pressurized fluid is supplied to the storage tank; and a heat exchanger that cools the working medium, and wherein the pressurized fluid supplied through the supply port is supplied to the storage tank via the heat exchanger.
11. The ultra-high pressure generator according to claim 5 , wherein the ultra-high pressure generator further comprises: a storage tank in which the pressurized fluid is stored; a supply port through which the pressurized fluid is supplied to the storage tank; and a heat exchanger that cools the working medium, and wherein the pressurized fluid supplied through the supply port is supplied to the storage tank via the heat exchanger.
12. The ultra-high pressure generator according to claim 6 , wherein the ultra-high pressure generator further comprises: a storage tank in which the pressurized fluid is stored; a supply port through which the pressurized fluid is supplied to the storage tank; and a heat exchanger that cools the working medium, and wherein the pressurized fluid supplied through the supply port is supplied to the storage tank via the heat exchanger.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014190725A JP6371653B2 (en) | 2014-09-19 | 2014-09-19 | Ultra high pressure generator |
JP2014-190725 | 2014-09-19 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20160084241A1 true US20160084241A1 (en) | 2016-03-24 |
Family
ID=54062685
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/842,987 Abandoned US20160084241A1 (en) | 2014-09-19 | 2015-09-02 | Ultra-high pressure generator |
Country Status (3)
Country | Link |
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US (1) | US20160084241A1 (en) |
EP (1) | EP2998579B1 (en) |
JP (1) | JP6371653B2 (en) |
Cited By (8)
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US20160108939A1 (en) * | 2014-10-20 | 2016-04-21 | Bhdt Gmbh | Hydraulic drive for a pressure booster |
US20170089328A1 (en) * | 2015-09-25 | 2017-03-30 | Sugino Machine Limited | Fluid pressure producing method and fluid pressure producing device |
US10422326B2 (en) | 2016-11-30 | 2019-09-24 | Sugino Machine Limited | High pressure generator with bidirectional check valves controlling overpressure |
US20190376535A1 (en) * | 2017-02-01 | 2019-12-12 | Kawasaki Jukogyo Kabushiki Kaisha | Liquid-pressure driving system |
US20220127921A1 (en) * | 2020-10-27 | 2022-04-28 | Sean Mccool | Subterranean well pipe and casing cutter water jet system |
US11401925B2 (en) * | 2018-01-23 | 2022-08-02 | Maximator Gmbh | Device and method for compressing a working medium |
US11428217B2 (en) * | 2019-12-09 | 2022-08-30 | Maximator Gmbh | Compressor comprising a first drive part, a second drive part, and a high-pressure part configured to move in a coupled manner by a piston rod arrangement wherein a first control unit and a second control unit are configured to control a drive fluid to the first and second drive parts |
US12012817B2 (en) * | 2021-10-27 | 2024-06-18 | Sean Mccool | Subterranean well pipe and casing cutter water jet system |
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JP6920801B2 (en) * | 2016-09-29 | 2021-08-18 | 株式会社佐藤渡辺 | Concrete fishing machine and concrete fishing method |
JP7386146B2 (en) | 2020-11-04 | 2023-11-24 | 株式会社スギノマシン | High pressure water processing machine and its failure diagnosis method |
CN113389764B (en) * | 2021-06-30 | 2022-11-15 | 四川航天烽火伺服控制技术有限公司 | Hydraulic equipment and turbo pump outlet pressure control system thereof |
DE102022209608A1 (en) | 2022-09-14 | 2024-03-14 | Robert Bosch Gesellschaft mit beschränkter Haftung | Hydraulic drive for a hydraulic consumer that is pressurized alternately in opposite directions during operation |
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Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
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US20160108939A1 (en) * | 2014-10-20 | 2016-04-21 | Bhdt Gmbh | Hydraulic drive for a pressure booster |
US20170089328A1 (en) * | 2015-09-25 | 2017-03-30 | Sugino Machine Limited | Fluid pressure producing method and fluid pressure producing device |
US10352309B2 (en) * | 2015-09-25 | 2019-07-16 | Sugino Machine Limited | Fluid pressure producing method and fluid pressure producing device |
US10422326B2 (en) | 2016-11-30 | 2019-09-24 | Sugino Machine Limited | High pressure generator with bidirectional check valves controlling overpressure |
US20190376535A1 (en) * | 2017-02-01 | 2019-12-12 | Kawasaki Jukogyo Kabushiki Kaisha | Liquid-pressure driving system |
US10982761B2 (en) * | 2017-02-01 | 2021-04-20 | Kawasaki Jukogyo Kabushiki Kaisha | Liquid-pressure driving system |
US11401925B2 (en) * | 2018-01-23 | 2022-08-02 | Maximator Gmbh | Device and method for compressing a working medium |
US11428217B2 (en) * | 2019-12-09 | 2022-08-30 | Maximator Gmbh | Compressor comprising a first drive part, a second drive part, and a high-pressure part configured to move in a coupled manner by a piston rod arrangement wherein a first control unit and a second control unit are configured to control a drive fluid to the first and second drive parts |
US20220127921A1 (en) * | 2020-10-27 | 2022-04-28 | Sean Mccool | Subterranean well pipe and casing cutter water jet system |
US12012817B2 (en) * | 2021-10-27 | 2024-06-18 | Sean Mccool | Subterranean well pipe and casing cutter water jet system |
Also Published As
Publication number | Publication date |
---|---|
JP6371653B2 (en) | 2018-08-08 |
EP2998579A2 (en) | 2016-03-23 |
EP2998579B1 (en) | 2020-05-06 |
EP2998579A3 (en) | 2016-03-30 |
JP2016061249A (en) | 2016-04-25 |
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