JPH09141215A - In-liquid high pressure washing method and device therefor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To effectively generate an impulse wave stream to contribute to washing of an object to be washed by arranging the object to be washed and a nozzle in liquid and intermittently jetting the liquid from the nozzle toward the object to be washed at a high speed and high pressure. SOLUTION: A washing tank 12 stores water 14, and a control bar 16 is arranged freely rotatably around the center line, movably up and down and also movably in biaxial directions vertical to each other in a horizontal plane. A work 18 is freely separatably caught at the lower end and is made freely loadable and unloadable in the washing tank 12, freely movable to an optional position in the washing tank 12 and its direction is made freely shiftable. The nozzle 20 is positioned at a specified depth in water 14 of the washing tank 12, and a guide cylinder 22 surrounding the nozzle 20 from the outside in the radial direction against the center line of the nozzle 20. The nozzle 20 is intermittently supplied with high speed and high pressure water 14 from a high pressure water feed device 24 and jets it forward. The intermittent impulse wave stream 26 is formed in the guide cylinder 22 in accordance with intermittent high speed high pressure jet of the water 14 from the nozzle 20.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a high-pressure in-liquid cleaning method and apparatus for injecting a high-speed, high-pressure jet from a nozzle toward an object to be cleaned, which is immersed in the liquid, and cleaning (including deburring). It is about.

[0002]

2. Description of the Related Art A high-speed, high-pressure jet is jetted from a nozzle toward an object to be cleaned that is immersed in water, and while utilizing cavitation bubbles, the surface film such as an oil film is peeled off or the object to be cleaned is cleaned. An underwater cleaning device for deburring a machined part of a machine is already known (eg, Japanese Patent Publication No. 4-43712).
JP-A-5-212317, etc.). In the conventional underwater cleaning device, the nozzle continuously jets a high-speed, high-pressure jet.

[0003]

The problems of the conventional underwater cleaning apparatus are as follows. (A) A very high-pressure pump is required for high-speed, high-pressure injection from the nozzle. (B) A large capacity pump is required as the consumption of jet water increases significantly. (C) The object to be cleaned is cleaned only by the collision force of the high-speed and high-pressure jet on the object to be cleaned and the bursting force of the cavitation bubbles.

An object of the present invention is to provide a submerged high pressure cleaning method and apparatus which overcome the above problems. Another object of the present invention is to provide a submerged high-pressure cleaning method and apparatus that can effectively generate a shock wave flow that contributes to cleaning an object to be cleaned. Another object of the present invention is to provide an in-liquid high pressure cleaning device equipped with a liquid supply means capable of appropriately performing intermittent injection from a nozzle.

[0005]

In the submerged high-pressure cleaning method of the present invention, an object to be cleaned (18) and a nozzle (20) are arranged in the liquid (14), and the object to be cleaned (18) is discharged from the nozzle (20). Liquid towards ()
Is injected intermittently at high speed and high pressure.

In the present invention, as a concept of high speed and high pressure of the liquid (14) ejected from the nozzle (20), high speed means that the ejection speed at the nozzle (20) is at least 400 to 500 m.
High speed in the range including / s and high pressure means that the injection pressure at the nozzle (20) is at least 350 to 500 kgf / cm ^ 2.
(^ 2 means square. "Cm ^ 2" means square cm).

In this high-pressure in-liquid washing method, intermittent high-speed and high-pressure injection of the liquid (14) from the nozzle (20) is performed by the nozzle (20).
Shears the liquid (14) in front of the cavities to create cavitation bubbles (74) and intermittent shock wave flow (26)
Are generated in front of the nozzle (20). Cavitation bubbles
(74) and the shock wave flow (26) reach the object to be cleaned (18), and the object (18) to be cleaned is washed by the collision of the shock wave flow (26) and the bursting force of the cavitation bubbles (74) (burrs). Including tori.)
Is done. The shock wave flow (26) is also simply the item to be cleaned (18).
Not only it collides with, but also has a flapping force due to the intermittentness, and hits the object to be cleaned (18) to effectively clean the object to be cleaned (18).

In another method of high pressure cleaning in liquid of the present invention, the outer side in the radial direction of the nozzle (20) is in the range including the nozzle (20) inside in the jet direction from the nozzle (20) to the object to be cleaned (18). The surrounding tubular body (22) is provided, and the shock wave flow (26) is guided by the tapered portion (58) of the tubular body (22) whose diameter gradually increases in the distal direction.

In this high-pressure in-liquid washing method, the shock wave flow (26) generated by the high-speed and high-pressure injection of the liquid (14) from the nozzle (20) is directed to the tapered portion (58) of the tubular body (22). While being guided,
Head to the item to be cleaned (18). The shock wave flow (26) is appropriately prevented from diffusing by the tapered portion (58) of the cylindrical body (22), and is given a large impact force to hit the article to be cleaned (18). Cylindrical body
The base end side of (22), that is, the end opposite to the object to be cleaned (18), is open without being blocked, and the liquid behind the tubular body (22) in the flow direction of the jet ( 14) can freely flow into the tubular body (22), and contributes to appropriate generation of the shock wave flow (26) in the tubular body (22).

The submerged high pressure washing apparatus (10) of the present invention has the following elements (a) and (b). (A) Liquid supply means for intermittently discharging high-pressure liquid (14)
(24) (b) The liquid (14) is moved toward the object to be cleaned (18) at high speed according to the intermittent supply of the high-pressure liquid (14) from the liquid supply means (24).
Nozzle for intermittent injection at high pressure (20)

In this submerged high-pressure cleaning apparatus (10), the liquid supply means (24) intermittently sends the high-pressure liquid (14) to the nozzle (20), and the nozzle (20) intermittently supplies the liquid (14). High speed and high pressure injection. The intermittent high-speed and high-pressure injection of the liquid (14) from the nozzle (20) causes a very large velocity gradient at the boundary surface between the jet (72) at the outlet of the nozzle (20) and the surrounding liquid (14), The cavitation bubble (74) is generated and the shock wave flow (26) is generated in front of the nozzle (20). Cavitation bubbles
(74) and the shock wave flow (26) reach the object to be cleaned (18), and the object (18) to be cleaned is washed by the collision of the shock wave flow (26) and the bursting force of the cavitation bubbles (74) (burrs). Including tori.)
Is done. The shock wave flow (26) is also simply the item to be cleaned (18).
Not only it collides with, but also has a flapping force due to the intermittentness, and hits the object to be cleaned (18) to effectively clean the object to be cleaned (18).

Another submerged high pressure washing apparatus (10) of the present invention further has the following element (c). (C) A range including the inside of the nozzle (20) in the jet direction from the nozzle (20) to the object to be cleaned (18), which is provided with a taper portion (58) on the tip side from the nozzle (20) to gradually increase the diameter in the tip direction. A cylindrical body (22) that surrounds the nozzle (20) in the radial direction outside.

In this submerged high pressure cleaning device (10), the nozzle (2
The shock wave flow (26) generated by the high-speed and high-pressure injection of the liquid (14) from the liquid (0) is guided to the object to be cleaned (18) while being guided by the tapered portion (58) of the cylindrical body (22). The shock wave flow (26) is appropriately prevented from diffusing by the tapered portion (58) of the cylindrical body (22),
A large impact force is applied to the object to be cleaned (18). The base end side of the tubular body (22), that is, the end opposite to the object to be cleaned (18), is open without being blocked, and is located behind the tubular body (22) in the jet flow direction. The liquid (14) can freely flow into the tubular body (22), and contributes to appropriate generation of the shock wave flow (26) in the tubular body (22).

In another submerged high-pressure cleaning device (10) of the present invention, the cylindrical body (22) has a taper portion with its diameter gradually decreasing in the direction of its tip.
An inverse taper portion (56) connected to the (58) is provided on the base end side of the taper portion (58).

In this submerged high-pressure cleaning device (10), the cylindrical body (22)
Liquid (14) flowing into the tubular body (22) from the proximal end side of the tubular body (22)
Through the reverse taper portion (56) to the taper portion (58). Tapered part
The base end side of (58) is set to a position and diameter desirable for generating the optimum shock wave flow (26), and the diameter is different from the base end side diameter of the tubular body (22). . The reverse taper part (56) is a cylinder
Smooths the flow of the object to be cleaned (18) from the base end side of (22) toward the tapered portion (58), and the shock wave flow (26) in the tapered portion (58)
Contribute to the proper generation of.

In another submerged high-pressure cleaning device (10) of the present invention, the liquid supply means (24) reciprocally pumps (14) intermittently supplies the liquid (14) to the nozzle (20) by an intermittent discharge stroke. 204)
including.

In this submerged high pressure cleaning device (10), the nozzle (2
0) is the liquid (14) due to the suction and discharge cycle of the reciprocating pump (204)
The intermittent discharge is directly received, and thereby the liquid (14) intermittently supplied from the reciprocating pump (204) is intermittently ejected. In order to intermittently supply the liquid (14) to the nozzle (20), an intermittent valve that periodically opens and closes is provided.However, in the submerged high-pressure cleaning device (10), such an intermittent valve is omitted. Therefore, the structure of the liquid supply means (24) can be simplified.

In another submersible high-pressure washing apparatus (10) of the present invention, the liquid supply means (24) includes a drive shaft (21) of the reciprocating pump (204).
2) so that the reciprocating pump (204) rotates at a low speed and a high speed during the suction stroke and the discharge stroke, respectively.
The drive-side non-circular gear (230) and the driven-side non-circular gear (232), which are engaged with each other and which convert the constant-speed rotation of 6) into non-constant-speed rotation and transmit the non-constant-speed rotation to the drive shaft (212).

In this submerged high pressure cleaning device (10), the input shaft (2
The constant speed rotation of (26) is converted to non-constant speed rotation through the drive-side non-circular gear (230) and the driven-side non-circular gear (232), and is converted to the drive shaft (212) of the reciprocating pump (204). Driven and transmitted (212)
Rotates at high speed and low speed in the discharge stroke and the suction stroke, respectively. This causes the reciprocating pump (204) to move to the nozzle (2
The discharge speed of the liquid (14) toward (0) increases and the reciprocating pump (2
The liquid (14) is discharged from 04) in a short time. In this way, the injection pressure of the liquid (14) from the nozzle (20) can be made steep and the peak thereof can be raised to obtain an appropriate intermittent injection.

[0020]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the drawings. FIG. 1 is an overall configuration diagram of an underwater high-pressure cleaning device 10. The cleaning tank 12 stores water 14 up to the level of an overflow port (not shown). The control rod 16 is rotatable about its center line, vertically movable, and movable in two axial directions at right angles to each other in the horizontal plane. The 18 can be freely taken in and out of the cleaning tank 12, can be moved to any position in the cleaning tank 12, and the orientation of the work 18 can be freely changed. Nozzle 20 is a cleaning tank
Located at a predetermined depth in the water 14 of 12, the guide cylinder 22 surrounds the nozzle 20 from the radial outer side with respect to the center line of the nozzle 20.
The nozzle 20 and the guide cylinder 22 form a nozzle device 52. The nozzle 20 is intermittently supplied with high-speed, high-pressure water 14 from the high-pressure water supply device 24 and jets it forward. Intermittent shock wave flow 26
Are generated in the guide cylinder 22 with the intermittent high-speed and high-pressure injection of the water 14 from the nozzle 20.

In the high-pressure water supply device 24, a motor starting board
The AC 28 is supplied with AC power from the AC power supply 30, and controls the operation of the motor 32. The rotation of the motor 32 is controlled by the power transmission belt 34.
It is transmitted to the plunger pump device 36 via the and drives the plunger pump device 36. The water supply tank 38 stores a predetermined amount of water 14, and the plunger pump device 36 controls the water 14 in the water supply tank 38.
Are inhaled through the strainer 40 and the suction pipe line 42. The discharge pipe line 44 guides the water 14 discharged from the plunger pump device 36 to the nozzle 20. The return pipe line 46 branches from the discharge pipe line 44 in the vicinity of the discharge port of the plunger pump device 36, and the lower end faces the water supply tank 38. The relief valve 48 is
When the water pressure in the discharge conduit 44 is arranged in the return conduit 46 and becomes too large, it opens to return the water 14 in the discharge conduit 44 to the water tank 38, and the water pressure in the discharge conduit 44 becomes excessive. To avoid becoming. The pressure gauge 50 is provided at the discharge port of the plunger pump device 36 and measures the discharge pressure of the plunger pump device 36.

FIG. 2 is a detailed view of the work 18 and the nozzle device 52 shown in FIG. The guide tube 22 is disposed coaxially with the center line of the nozzle 20 on the outer side in the radial direction of the nozzle 20 and with a predetermined gap in the radial direction from the nozzle 20, and the nozzle 20 is placed in the center line direction of the nozzle 20. It extends in a range that includes the inside. The guide cylinder 22 is provided with a cylindrical portion 54 from the base end side, an inverted frustoconical portion 56 that is recessed toward the tip end side, and a frustoconical portion 58 that widens the diameter toward the tip end side in sequence. The work 18 is a truncated cone during cleaning work.
A plurality of drill holes 60 are provided so as to face each other at the tip of 58, and a flash 62 is present at a position within the drill holes 60.

FIG. 3 illustrates preferred numerical ratios or numerical values for the dimensions and angles of each part of the nozzle device 52. Nozzle 20
Is a cylindrical portion 64 along the center line from the base end side, an inverted frustoconical portion 66 that swells in the distal direction, a nozzle hole portion 68 as the smallest inner diameter portion, and a truncated cone portion 70 that expands the diameter in the distal direction in order. We have in a row. The dimensions and angles of each part are as shown in FIG. Regarding the dimensions, the diameter of the injection hole portion 68 and the truncated cone portion
The maximum diameter of 70 is shown as the standard dimension of d and e, respectively.

4 and 5 show states of the shock wave flow 26 and the like in the nozzle device 52 and the work 18, respectively.
With reference to FIG. 4 and FIG.
The operation of will be described. Plunger pump device 36
Driven by the rotational power from the motor 32, the water 14 in the water supply tank 38 is sucked and the high-pressure water 14 is intermittently discharged. High-pressure water intermittently discharged from the plunger pump device 36
14 is intermittently supplied as it is to the nozzle 20 of the nozzle device 52 via the discharge pipe line 44. The nozzle 20 jets the water 14 at high speed and high pressure in accordance with the supply of the water 14 from the high-pressure water supply device 24, and as a result, the jet stream 72 is jetted intermittently from the nozzle 20. In addition,
The jet speed and the jet pressure of the water 14 at the nozzle 20 are 400 to 500 m / s and 350 to 500 kgf / cm, respectively.
It is ^ 2. The jet 72 has a very large velocity gradient at the boundary surface between the jet 72 at the outlet of the nozzle 20 and the surrounding water 14 to generate cavitation bubbles 74. Also the nozzle
Intermittent injection of jet 72 from 20 causes intermittent shock wave
26 is generated in front of the nozzle 20. The guide cylinder 22 is open at the base end side, and the water 14 behind the guide cylinder 22 flows into the guide cylinder 22 through the rear end opening of the cylindrical portion 54, and the nozzle
On the outer side in the radial direction of 20, the flow flows along the inner surfaces of the cylindrical portion 54 and the inverted truncated cone portion 56 like F1 (FIG. 4), and the truncated cone portion 70
In, like F2 (FIG. 4), it goes from the outer side to the inner side in the radial direction along the surface of the truncated cone part 70. The truncated cone portion 58 appropriately narrows the radial range of the shock wave flow 26 to reduce the shock wave flow 26.
Is prevented from weakening due to diffusion, and is guided to the distal end side while maintaining high strength. The base end position and the base end side diameter of the truncated cone part 58 are defined so as to generate an appropriate shock wave flow 26, and therefore the base end side diameter of the truncated cone part 58 is the optimum diameter of the cylindrical part 54. Will be different from. Despite this difference, the inverted frusto-conical portion 56 ensures that the water 14 flows smoothly from the cylindrical portion 54 to the frusto-conical portion 58 and does not interfere with the generation of an appropriate shock wave flow 26.

The work 18 is impinged by the intermittent shock wave flow 26 to clean the surface. Also, the cavitation bubbles 74 that have reached the work 18 explode, and the burst force causes the work to move.
Wash 18. The intermittent shock wave flow 26 collides with the outer surface of the work 18 and enters into the drill hole 60 that opens in the collision surface of the work 18. The shock wave flow 26 has a function of rising by an intermittent flow in addition to the impact force at the time of collision. In this way, the impact force and the swaying force are synergistic, and the work
Effective stripping of 18 surfaces and effective removal of flash 62 are provided.

FIGS. 6 and 7 are structural views showing the plunger pump device 36 in cross sections as seen from above and from the side, respectively. The plunger pump device 36 includes a rotation speed conversion unit 202 and a plunger pump unit 204. Plunger pump part 2
The drive shaft 212 of 04 has a circular crank pin portion 214 whose center is offset from the center line of the drive shaft 212.
Is rotatably supported on the case body 218 of the crankcase 216 via bearings 220 on both sides of the. The case main body 218 has openings closed by lids 222 and 224 on both axial sides of the drive shaft 212. In the rotation speed conversion unit 202, the input shaft 226 is connected to the plunger pump unit 204.
And extends parallel to the drive shaft 212 and is rotatably supported by the lid 222 and the case main body 218 at bearings 228 at two axial positions. Drive side non-circular gear 2
The driven-side non-circular gear 232 has a non-circular pitch curve, is integrally fitted in the input shaft 226 and the drive shaft 212 in the rotational direction, and meshes with each other.

The plunger 234 has a crosshead 236 on the base end side which is fitted in the guide 238 of the crankcase 216 and is guided in the axial direction of the guide 238. The connecting rod 239 has a large end portion fitted in a circular crank pin portion 214 so as to be relatively rotatable in the circumferential direction, and a small end portion thereof is connected to a cross head 236 via a cross pin 237.

The manifold 240 is joined to the crankcase 216, has a suction port 242 on the lower surface side, and has a discharge port 244 on the upper end surface. Pump chamber 246 is a manifold
It is formed in 240 and communicates with the suction port 242 and the discharge port 244. The suction valve 248 is incorporated between the suction port 242 and the pump chamber 246, is prevented from coming out of the manifold 240 by the plug 250, and prevents the reverse flow of the liquid from the pump chamber 246 to the suction port 242. The discharge valve 252 includes a pump chamber 246 and a discharge port 244.
Installed between the manifold 240 and the plug 254
It prevents the liquid from flowing back from the discharge port 244 to the pump chamber 246. The seal retainers 255 and 256 are fitted and inserted into the joint portion between the crankcase 216 and the manifold 240, and the collars 257 are provided on the inner peripheral sides on both axial sides to hold the oil seals 258 and 260, respectively. It prevents the lubricating oil therein from leaking out through the periphery of the plunger 234. The V-packing 262 is pressed by the seal retainer 256 against the stepped portion of the manifold 240, swells in the radial direction, and comes into sliding contact with the peripheral portion of the plunger 234 on the inner peripheral side,
Holds the seal of the pump chamber 246.

FIG. 8 is a drive mechanism diagram of the plunger 234. The plunger 234 is connected to the drive shaft 21 via the connecting rod 239.
It is connected to the second crank pin portion 214, and with the rotation of the drive shaft 212, one half rotation of the drive shaft 212 causes an intake stroke, which reduces the volume of the pump chamber 246 and reduces the volume of the drive shaft 212. On the other half-turn, a discharge stroke occurs, increasing the volume of the pump chamber 246, which is similar to a conventional plunger pump. In this plunger pump device 36, rotation from a prime mover such as an engine is input to the input shaft 226, and the drive shaft 21 is driven via the drive-side non-circular gear 230 and the driven-side non-circular gear 232.
It is transmitted to 2. The design and manufacture of the pitch curves of the driving-side non-circular gear 230 and the driven-side non-circular gear 232 are described, for example, in Mechanical Design Vol. 29, No. 11 (September 1985), pp. 13-18. Design and production of and its application (Author:
Nagaoka Gear Mfg. Co., Ltd. Takashi Yamazaki) ”. In this plunger pump device 36, the input shaft 22
With respect to the constant speed rotation of 6, the drive shaft 212 drives the drive-side non-circular gear 230 and the driven-side non-circular so that the rotation speed in the half stroke of the discharge stroke can be made higher than the rotation speed in the half rotation of the suction stroke. The pitch curve of the gear 232 is set.

FIG. 9 is a characteristic graph in which the horizontal axis represents the rotation angle of the input shaft 226 and the vertical axis represents the displacement and speed ratio of the plunger 234. Drive-side non-circular gear 230 and driven-side non-circular gear 232
As a result of the pitch curve of FIG. 8 being set as shown in FIG. 8, the rotation angle range of the input shaft 226 corresponding to the discharge stroke and the suction stroke is 1
Greatly changed from 80 °, eg 90 ° each
And 270 °. As a result, the drive shaft 212
The rotation speed in the discharge stroke is significantly higher than the rotation speed in the suction stroke, the moving speed of the plunger 234 in the discharge stroke is significantly increased, and the decrease rate of the volume of the pump chamber 246 in the discharge stroke is increased. The discharge pressure of the liquid intermittently discharged from the discharge port 244 increases.

As described above, the input shaft 226 of the plunger pump device 36 is rotated at a constant speed by the rotational power from the motor 32, and this constant speed rotation is driven by the drive side non-circular gear 230 and the driven side of the rotation speed conversion unit 202. The non-circular gears 232 are converted into non-uniform speed rotation by mutual meshing, and the plunger pump unit 204
The drive shaft 212 is rotated at non-constant speeds such that the plunger pump 204 has a low speed and a high speed in the suction stroke and the discharge stroke, respectively. As a result, the water 14 is discharged from the discharge port 244 in a short time, and the peak of the water pressure of the water 14 sent from the plunger pump device 36 to the nozzle 20 increases.

FIG. 10 shows a comparison of the case where the velocity of the jet 72 from the nozzle 20 is an intermittent flow and a continuous flow. The intermittent velocity of the jet flow 72 (solid line) is when the plunger pump device 36 is connected to the nozzle 20 as in the embodiment of the invention. The speed of the continuous jet 72 (broken line) is determined by the reciprocating pump having a cycle of the intake stroke and the exhaust stroke of 1: 1 by the motor 32.
Driven by the same as that of the plunger pump device 36, and further, the discharge pressure of the reciprocating pump is made a smooth constant value by the pressure regulating valve, and then the nozzle 20
When sent to. In the case of intermittent jetting of the jet 72, the ratio of the jetting time and the jetting stop time is set to 1: (3 to 5) to make cleaning effective.

The impact force F of the jet 72 is expressed by the following equation. In addition, ^ n (n is an arbitrary number) means the n-th power. In addition,
F: impact force [kgf], ρ: fluid density [kgf · se
c ^ 2 / m ^ 4], Q: Flow rate of the jet 72 [m ^ 3 / se]
c], V: average velocity [m / sec] of the jet 72. F = ρ ・ Q ・ V

From FIG. 10, in the embodiment of the invention, the peak of the velocity of the jet flow 72 is significantly increased for the same constant-speed rotation input, and the consumption amount of the water 14 required for generating the jet flow 72 is greatly reduced. I understand what I can do. Further, it can be understood from the above F = P.Q.V that the impact force F of each intermittent jet flow 72 is significantly increased.

[Brief description of the drawings]

FIG. 1 is an overall configuration diagram of an underwater high-pressure cleaning device.

FIG. 2 is a detailed view of the work and nozzle device of FIG.

FIG. 3 is a diagram exemplifying a preferable numerical value ratio or numerical value for the size and angle of each part of the nozzle device.

FIG. 4 is a diagram showing a state such as a shock wave flow in the nozzle device.

FIG. 5 is a diagram showing a state such as a shock wave flow in a work.

FIG. 6 is a structural diagram showing a cross section of the plunger pump device as seen from above.

FIG. 7 is a structural diagram showing a cross section of the plunger pump device as viewed from the side.

FIG. 8 is a drive mechanism diagram of a plunger.

FIG. 9 is a characteristic graph in which the horizontal axis represents the rotation angle of the input shaft and the vertical axis represents the displacement and speed ratio of the plunger.

FIG. 10 is a diagram showing a comparison between cases where the velocity of the jet flow from the nozzle is an intermittent flow and a continuous flow.

[Explanation of reference numerals] 10 high-pressure underwater cleaning device (high-pressure in-liquid cleaning device) 14 water (liquid) 18 work (object to be cleaned) 20 nozzle 22 guide cylinder (cylindrical body) 24 high-pressure water supply device (liquid supply means) 26 impact Wave flow 56 Reverse truncated cone part (reverse tapered part) 58 Cone truncated part (tapered part) 74 Cavitation bubble 204 Plunger pump part (reciprocating pump) 212 Drive shaft 226 Input shaft 230 Drive side non-circular gear 232 Driven side non-circular gear

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[Procedure amendment]

[Submission date] January 11, 1996

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] Full text

[Correction method] Change

[Correction contents]

[Document Name] Statement

Title: In-liquid high pressure cleaning method and apparatus

[Claims]

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a high-pressure in-liquid cleaning method and apparatus for injecting a high-speed, high-pressure jet from a nozzle toward an object to be cleaned, which is immersed in the liquid, and cleaning (including deburring). It is about.

[0002]

2. Description of the Related Art A high-speed, high-pressure jet is jetted from a nozzle toward an object to be cleaned that is immersed in water, and while utilizing cavitation bubbles, the surface film such as an oil film is peeled off or the object to be cleaned is cleaned. An underwater cleaning device for deburring a machined part of a machine is already known (eg, Japanese Patent Publication No. 4-43712).
JP-A-5-212317, etc.). In the conventional underwater cleaning device, the nozzle continuously jets a high-speed, high-pressure jet.

[0003]

The problems of the conventional underwater cleaning apparatus are as follows. (A) A very high-pressure pump is required for high-speed, high-pressure injection from the nozzle. (B) A large capacity pump is required as the consumption of jet water increases significantly. (C) The object to be cleaned is cleaned only by the collision force of the high-speed and high-pressure jet on the object to be cleaned and the bursting force of the cavitation bubbles.

An object of the present invention is to provide a submerged high pressure cleaning method and apparatus which overcome the above problems. Another object of the present invention is to provide a submerged high-pressure cleaning method and apparatus that can effectively generate a shock wave flow that contributes to cleaning an object to be cleaned. Another object of the present invention is to provide an in-liquid high pressure cleaning device equipped with a liquid supply means capable of appropriately performing intermittent injection from a nozzle.

[0005]

In the submerged high-pressure cleaning method of the present invention, an object to be cleaned (18) and a nozzle (20) are arranged in the liquid (14), and the object to be cleaned (18) is discharged from the nozzle (20). Liquid towards ()
Is injected intermittently at high speed and high pressure.

In the present invention, as a concept of high speed and high pressure of the liquid (14) ejected from the nozzle (20), high speed means that the ejection speed at the nozzle (20) is at least 400 to 500 m.
High speed in the range including / s and high pressure means that the injection pressure at the nozzle (20) is at least 350 to 500 kgf / cm ^ 2.
(^ 2 means square. "Cm ^ 2" means square cm).

In this high-pressure in-liquid washing method, intermittent high-speed and high-pressure injection of the liquid (14) from the nozzle (20) is performed by the nozzle (20).
Shears the liquid (14) in front of the cavities to create cavitation bubbles (74) and intermittent shock wave flow (26)
Are generated in front of the nozzle (20). Cavitation bubbles
(74) and the shock wave flow (26) reach the object to be cleaned (18), and the object (18) to be cleaned is washed by the collision of the shock wave flow (26) and the bursting force of the cavitation bubbles (74) (burrs). Including tori.)
Is done. The shock wave flow (26) is also simply the item to be cleaned (18).
Not only it collides with, but also has a flapping force due to the intermittentness, and hits the object to be cleaned (18) to effectively clean the object to be cleaned (18).

In another method of high pressure cleaning in liquid of the present invention, the outer side in the radial direction of the nozzle (20) is in the range including the nozzle (20) inside in the jet direction from the nozzle (20) to the object to be cleaned (18). The surrounding tubular body (22) is provided, and the shock wave flow (26) is guided by the tapered portion (58) of the tubular body (22) whose diameter gradually increases in the distal direction.

In this high-pressure in-liquid washing method, the shock wave flow (26) generated by the high-speed and high-pressure injection of the liquid (14) from the nozzle (20) is directed to the tapered portion (58) of the tubular body (22). While being guided,
Head to the item to be cleaned (18). The shock wave flow (26) is appropriately prevented from diffusing by the tapered portion (58) of the cylindrical body (22), and is given a large impact force to hit the article to be cleaned (18). Cylindrical body
The base end side of (22), that is, the end opposite to the object to be cleaned (18), is open without being blocked, and the liquid behind the tubular body (22) in the flow direction of the jet ( 14) can freely flow into the tubular body (22), and contributes to appropriate generation of the shock wave flow (26) in the tubular body (22).

The submerged high pressure washing apparatus (10) of the present invention has the following elements (a) and (b). (A) Liquid supply means for intermittently discharging high-pressure liquid (14)
(24) (b) The liquid (14) is moved toward the object to be cleaned (18) at high speed according to the intermittent supply of the high-pressure liquid (14) from the liquid supply means (24).
Nozzle for intermittent injection at high pressure (20)

In this submerged high-pressure cleaning apparatus (10), the liquid supply means (24) intermittently sends the high-pressure liquid (14) to the nozzle (20), and the nozzle (20) intermittently supplies the liquid (14). High speed and high pressure injection. The intermittent high-speed and high-pressure injection of the liquid (14) from the nozzle (20) causes a very large velocity gradient at the boundary surface between the jet (72) at the outlet of the nozzle (20) and the surrounding liquid (14), The cavitation bubble (74) is generated and the shock wave flow (26) is generated in front of the nozzle (20). Cavitation bubbles
(74) and the shock wave flow (26) reach the object to be cleaned (18), and the object (18) to be cleaned is washed by the collision of the shock wave flow (26) and the bursting force of the cavitation bubbles (74) (burrs). Including tori.)
Is done. The shock wave flow (26) is also simply the item to be cleaned (18).
Not only it collides with, but also has a flapping force due to the intermittentness, and hits the object to be cleaned (18) to effectively clean the object to be cleaned (18).

Another submerged high pressure washing apparatus (10) of the present invention further has the following element (c). (C) A range including the inside of the nozzle (20) in the jet direction from the nozzle (20) to the object to be cleaned (18), which is provided with a taper portion (58) on the tip side from the nozzle (20) to gradually increase the diameter in the tip direction. A cylindrical body (22) that surrounds the nozzle (20) in the radial direction outside.

In this submerged high pressure cleaning device (10), the nozzle (2
The shock wave flow (26) generated by the high-speed and high-pressure injection of the liquid (14) from the liquid (0) is guided to the object to be cleaned (18) while being guided by the tapered portion (58) of the cylindrical body (22). The shock wave flow (26) is appropriately prevented from diffusing by the tapered portion (58) of the cylindrical body (22),
A large impact force is applied to the object to be cleaned (18). The base end side of the tubular body (22), that is, the end opposite to the object to be cleaned (18), is open without being blocked, and is located behind the tubular body (22) in the jet flow direction. The liquid (14) can freely flow into the tubular body (22), and contributes to appropriate generation of the shock wave flow (26) in the tubular body (22).

In another submerged high-pressure cleaning device (10) of the present invention, the cylindrical body (22) has a taper portion with its diameter gradually decreasing in the direction of its tip.
An inverse taper portion (56) connected to the (58) is provided on the base end side of the taper portion (58).

In this submerged high-pressure cleaning device (10), the cylindrical body (22)
Liquid (14) flowing into the tubular body (22) from the proximal end side of the tubular body (22)
Through the reverse taper portion (56) to the taper portion (58). Tapered part
The base end side of (58) is set to a position and diameter desirable for generating the optimum shock wave flow (26), and the diameter is different from the base end side diameter of the tubular body (22). . The reverse taper part (56) is a cylinder
Smooths the flow of the object to be cleaned (18) from the base end side of (22) toward the tapered portion (58), and the shock wave flow (26) in the tapered portion (58)
Contribute to the proper generation of.

In another submerged high-pressure cleaning device (10) of the present invention, the liquid supply means (24) reciprocally pumps (14) intermittently supplies the liquid (14) to the nozzle (20) by an intermittent discharge stroke. 204)
including.

In this submerged high pressure cleaning device (10), the nozzle (2
0) is the liquid (14) due to the suction and discharge cycle of the reciprocating pump (204)
The intermittent discharge is directly received, and thereby the liquid (14) intermittently supplied from the reciprocating pump (204) is intermittently ejected. In order to intermittently supply the liquid (14) to the nozzle (20), an intermittent valve that periodically opens and closes is provided.However, in the submerged high-pressure cleaning device (10), such an intermittent valve is omitted. Therefore, the structure of the liquid supply means (24) can be simplified.

In another submersible high-pressure washing apparatus (10) of the present invention, the liquid supply means (24) includes a drive shaft (21) of the reciprocating pump (204).
2) so that the reciprocating pump (204) rotates at a low speed and a high speed during the suction stroke and the discharge stroke, respectively.
The drive-side non-circular gear (230) and the driven-side non-circular gear (232), which are engaged with each other and which convert the constant-speed rotation of 6) into non-constant-speed rotation and transmit the non-constant-speed rotation to the drive shaft (212).

In this submerged high pressure cleaning device (10), the input shaft (2
The constant speed rotation of (26) is converted to non-constant speed rotation through the drive-side non-circular gear (230) and the driven-side non-circular gear (232), and is converted to the drive shaft (212) of the reciprocating pump (204). Driven and transmitted (212)
Rotates at high speed and low speed in the discharge stroke and the suction stroke, respectively. This causes the reciprocating pump (204) to move to the nozzle (2
The discharge speed of the liquid (14) toward (0) increases and the reciprocating pump (2
The liquid (14) is discharged from 04) in a short time. In this way, the injection pressure of the liquid (14) from the nozzle (20) can be made steep and the peak thereof can be raised to obtain an appropriate intermittent injection.

[0020]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the drawings. FIG. 1 is an overall configuration diagram of an underwater high-pressure cleaning device 10. The cleaning tank 12 stores water 14 up to the level of an overflow port (not shown). The control rod 16 is rotatable about its center line, vertically movable, and movable in two axial directions at right angles to each other in the horizontal plane. The 18 can be freely taken in and out of the cleaning tank 12, can be moved to any position in the cleaning tank 12, and the orientation of the work 18 can be freely changed. Nozzle 20 is a cleaning tank
Located at a predetermined depth in the water 14 of 12, the guide cylinder 22 surrounds the nozzle 20 from the radial outer side with respect to the center line of the nozzle 20.
The nozzle 20 and the guide cylinder 22 form a nozzle device 52. The nozzle 20 is intermittently supplied with high-speed, high-pressure water 14 from the high-pressure water supply device 24 and jets it forward. Intermittent shock wave flow 26
Are generated in the guide cylinder 22 with the intermittent high-speed and high-pressure injection of the water 14 from the nozzle 20.

In the high-pressure water supply device 24, a motor starting board
The AC 28 is supplied with AC power from the AC power supply 30, and controls the operation of the motor 32. The rotation of the motor 32 is controlled by the power transmission belt 34.
It is transmitted to the plunger pump device 36 via the and drives the plunger pump device 36. The water supply tank 38 stores a predetermined amount of water 14, and the plunger pump device 36 controls the water 14 in the water supply tank 38.
Are inhaled through the strainer 40 and the suction pipe line 42. The discharge pipe line 44 guides the water 14 discharged from the plunger pump device 36 to the nozzle 20. The return pipe line 46 branches from the discharge pipe line 44 in the vicinity of the discharge port of the plunger pump device 36, and the lower end faces the water supply tank 38. The relief valve 48 is
When the water pressure in the discharge conduit 44 is arranged in the return conduit 46 and becomes too large, it opens to return the water 14 in the discharge conduit 44 to the water tank 38, and the water pressure in the discharge conduit 44 becomes excessive. To avoid becoming. The pressure gauge 50 is provided at the discharge port of the plunger pump device 36 and measures the discharge pressure of the plunger pump device 36.

FIG. 2 is a detailed view of the work 18 and the nozzle device 52 shown in FIG. Guide cylinder 22 is arranged with a predetermined gap in radial direction between the coaxially and nozzle 20 to the center line of the nozzle 20 in the radial direction outside of the nozzle 20, Nozzle 20 to the center line direction of the nozzle 20 Extends in a range including inside. The guide cylinder 22 is an inverted cone that bulges from the base end side to the cylindrical portion 54 and the tip end side.
Bei Eteiru and lined cylindrical portion 56, and a tapered tubular portion 58 to widen the diameter distally in order. The work 18 is a conical cylinder portion during cleaning work.
A plurality of drill holes 60 are provided so as to face each other at the tip of 58, and a flash 62 is present at a position within the drill holes 60.

FIG. 3 illustrates preferred numerical ratios or numerical values for the dimensions and angles of each part of the nozzle device 52. Nozzle 20
Is a cylindrical portion 64 from the base end side along the center line, an inverted conical cylindrical portion 66 that swells in the distal direction, a nozzle hole portion 68 as the smallest inner diameter portion, and a conical cylindrical portion 70 that expands the diameter in the distal direction in order. We have in a row. The dimensions and angles of each part are as shown in FIG. Regarding the dimensions, the diameter of the injection hole portion 68 and the conical cylinder portion
The maximum diameter of 70 is shown as the standard dimension of d and e, respectively.

4 and 5 show states of the shock wave flow 26 and the like in the nozzle device 52 and the work 18, respectively.
With reference to FIG. 4 and FIG.
The operation of will be described. Plunger pump device 36
Driven by the rotational power from the motor 32, the water 14 in the water supply tank 38 is sucked and the high-pressure water 14 is intermittently discharged. High-pressure water intermittently discharged from the plunger pump device 36
14 is intermittently supplied as it is to the nozzle 20 of the nozzle device 52 via the discharge pipe line 44. The nozzle 20 jets the water 14 at high speed and high pressure in accordance with the supply of the water 14 from the high-pressure water supply device 24, and as a result, the jet stream 72 is jetted intermittently from the nozzle 20. In addition,
The jet speed and the jet pressure of the water 14 at the nozzle 20 are 400 to 500 m / s and 350 to 500 kgf / cm, respectively.
It is ^ 2. The jet 72 has a very large velocity gradient at the boundary surface between the jet 72 at the outlet of the nozzle 20 and the surrounding water 14 to generate cavitation bubbles 74. Also the nozzle
Intermittent injection of jet 72 from 20 causes intermittent shock wave
26 is generated in front of the nozzle 20. The guide cylinder 22 is open at the base end side, and the water 14 behind the guide cylinder 22 flows into the guide cylinder 22 through the rear end opening of the cylindrical portion 54, and the nozzle
On the outer side in the radial direction of 20, the flow flows along the inner surfaces of the cylindrical portion 54 and the inverted conical cylindrical portion 56 as in F1 (FIG. 4), and the conical cylindrical portion 70
In, like F2 (FIG. 4), it goes from the outer side to the inner side in the radial direction along the surface of the conical cylindrical portion 70. The conical cylinder portion 58 appropriately narrows the radial range of the shock wave flow 26 to reduce the shock wave flow 26.
Is prevented from weakening due to diffusion, and is guided to the distal end side while maintaining high strength. Since the base end side position and the base end side diameter of the conical cylinder part 58 are defined so as to generate an appropriate shock wave flow 26, the base end side diameter of the conical cylinder part 58 is the optimum diameter of the cylindrical part 54. Will be different from. In spite of this difference, the inverted conical tube portion 56 ensures that the water 14 smoothly flows from the cylindrical portion 54 to the conical tube portion 58 and does not interfere with the generation of the appropriate shock wave flow 26.

The work 18 is impinged by the intermittent shock wave flow 26 to clean the surface. Also, the cavitation bubbles 74 that have reached the work 18 explode, and the burst force causes the work to move.
Wash 18. The intermittent shock wave flow 26 collides with the outer surface of the work 18 and enters into the drill hole 60 that opens in the collision surface of the work 18. The shock wave flow 26 has a function of rising by an intermittent flow in addition to the impact force at the time of collision. In this way, the impact force and the swaying force are synergistic, and the work
Effective stripping of 18 surfaces and effective removal of flash 62 are provided.

FIGS. 6 and 7 are structural views showing the plunger pump device 36 in cross sections as seen from above and from the side, respectively. The plunger pump device 36 includes a rotation speed conversion unit 202 and a plunger pump unit 204. Plunger pump part 2
The drive shaft 212 of 04 has a circular crank pin portion 214 whose center is offset from the center line of the drive shaft 212.
Is rotatably supported on the case body 218 of the crankcase 216 via bearings 220 on both sides of the. The case main body 218 has openings closed by lids 222 and 224 on both axial sides of the drive shaft 212. In the rotation speed conversion unit 202, the input shaft 226 is connected to the plunger pump unit 204.
And extends parallel to the drive shaft 212 and is rotatably supported by the lid 222 and the case main body 218 at bearings 228 at two axial positions. Drive side non-circular gear 2
The driven-side non-circular gear 232 has a non-circular pitch curve, is integrally fitted in the input shaft 226 and the drive shaft 212 in the rotational direction, and meshes with each other.

The plunger 234 has a crosshead 236 on the base end side which is fitted in the guide 238 of the crankcase 216 and is guided in the axial direction of the guide 238. The connecting rod 239 has a large end portion fitted in a circular crank pin portion 214 so as to be relatively rotatable in the circumferential direction, and a small end portion thereof is connected to a cross head 236 via a cross pin 237.

The manifold 240 is joined to the crankcase 216, has a suction port 242 on the lower surface side, and has a discharge port 244 on the upper end surface. Pump chamber 246 is a manifold
It is formed in 240 and communicates with the suction port 242 and the discharge port 244. The suction valve 248 is incorporated between the suction port 242 and the pump chamber 246, is prevented from coming out of the manifold 240 by the plug 250, and prevents the reverse flow of the liquid from the pump chamber 246 to the suction port 242. The discharge valve 252 includes a pump chamber 246 and a discharge port 244.
Installed between the manifold 240 and the plug 254
It prevents the liquid from flowing back from the discharge port 244 to the pump chamber 246. The seal retainers 255 and 256 are fitted and inserted into the joint portion between the crankcase 216 and the manifold 240, and the collars 257 are provided on the inner peripheral sides on both axial sides to hold the oil seals 258 and 260, respectively. It prevents the lubricating oil therein from leaking out through the periphery of the plunger 234. The V-packing 262 is pressed by the seal retainer 256 against the stepped portion of the manifold 240, swells in the radial direction, and comes into sliding contact with the peripheral portion of the plunger 234 on the inner peripheral side,
Holds the seal of the pump chamber 246.

FIG. 8 is a drive mechanism diagram of the plunger 234. The plunger 234 is connected to the drive shaft 21 via the connecting rod 239.
It is connected to the second crank pin portion 214, and with the rotation of the drive shaft 212, one half rotation of the drive shaft 212 causes an intake stroke, which reduces the volume of the pump chamber 246 and reduces the volume of the drive shaft 212. On the other half-turn, a discharge stroke occurs, increasing the volume of the pump chamber 246, which is similar to a conventional plunger pump. In this plunger pump device 36, rotation from a prime mover such as an engine is input to the input shaft 226, and the drive shaft 21 is driven via the drive-side non-circular gear 230 and the driven-side non-circular gear 232.
It is transmitted to 2. The design and manufacture of the pitch curves of the driving-side non-circular gear 230 and the driven-side non-circular gear 232 are described, for example, in Mechanical Design Vol. 29, No. 11 (September 1985), pp. 13-18. Design and production of and its application (Author:
Nagaoka Gear Mfg. Co., Ltd. Takashi Yamazaki) ”. In this plunger pump device 36, the input shaft 22
With respect to the constant speed rotation of 6, the drive shaft 212 drives the drive-side non-circular gear 230 and the driven-side non-circular so that the rotation speed in the half stroke of the discharge stroke can be made higher than the rotation speed in the half rotation of the suction stroke. The pitch curve of the gear 232 is set.

FIG. 9 is a characteristic graph in which the horizontal axis represents the rotation angle of the input shaft 226 and the vertical axis represents the displacement and speed ratio of the plunger 234. Drive-side non-circular gear 230 and driven-side non-circular gear 232
As a result of the pitch curve of FIG. 8 being set as shown in FIG. 8, the rotation angle range of the input shaft 226 corresponding to the discharge stroke and the suction stroke is 1
Greatly changed from 80 °, eg 90 ° each
And 270 °. As a result, the drive shaft 212
The rotation speed in the discharge stroke is significantly higher than the rotation speed in the suction stroke, the moving speed of the plunger 234 in the discharge stroke is significantly increased, and the decrease rate of the volume of the pump chamber 246 in the discharge stroke is increased. The discharge pressure of the liquid intermittently discharged from the discharge port 244 increases.

As described above, the input shaft 226 of the plunger pump device 36 is rotated at a constant speed by the rotational power from the motor 32, and this constant speed rotation is driven by the drive side non-circular gear 230 and the driven side of the rotation speed conversion unit 202. The non-circular gears 232 are converted into non-uniform speed rotation by mutual meshing, and the plunger pump unit 204
The drive shaft 212 is rotated at non-constant speeds such that the plunger pump 204 has a low speed and a high speed in the suction stroke and the discharge stroke, respectively. As a result, the water 14 is discharged from the discharge port 244 in a short time, and the peak of the water pressure of the water 14 sent from the plunger pump device 36 to the nozzle 20 increases.

FIG. 10 shows a comparison of the case where the velocity of the jet 72 from the nozzle 20 is an intermittent flow and a continuous flow. The intermittent velocity of the jet flow 72 (solid line) is when the plunger pump device 36 is connected to the nozzle 20 as in the embodiment of the invention. The speed of the continuous jet 72 (broken line) is determined by the reciprocating pump having a cycle of the intake stroke and the exhaust stroke of 1: 1 by the motor 32.
Driven by the same as that of the plunger pump device 36, and further, the discharge pressure of the reciprocating pump is made a smooth constant value by the pressure regulating valve, and then the nozzle 20
When sent to. In the case of intermittent jetting of the jet 72, the ratio of the jetting time and the jetting stop time is set to 1: (3 to 5) to make cleaning effective.

The impact force F of the jet 72 is expressed by the following equation. In addition, ^ n (n is an arbitrary number) means the n-th power. In addition,
F: impact force [kgf], ρ: fluid density [kgf · se
c ^ 2 / m ^ 4], Q: Flow rate of the jet 72 [m ^ 3 / se]
c], V: average velocity [m / sec] of the jet 72. F = ρ ・ Q ・ V

From FIG. 10, in the embodiment of the invention, the peak of the velocity of the jet flow 72 is significantly increased for the same constant-speed rotation input, and the consumption amount of the water 14 required for generating the jet flow 72 is greatly reduced. I understand what I can do. Further, it can be understood from the above-mentioned F = ρ · Q · V that the impact force F of each intermittent jet flow 72 greatly increases.

[Brief description of the drawings]

FIG. 1 is an overall configuration diagram of an underwater high-pressure cleaning device.

FIG. 2 is a detailed view of the work and nozzle device of FIG.

FIG. 3 is a diagram exemplifying a preferable numerical value ratio or numerical value for the size and angle of each part of the nozzle device.

FIG. 4 is a diagram showing a state such as a shock wave flow in the nozzle device.

FIG. 5 is a diagram showing a state such as a shock wave flow in a work.

FIG. 6 is a structural diagram showing a cross section of the plunger pump device as seen from above.

FIG. 7 is a structural diagram showing a cross section of the plunger pump device as viewed from the side.

FIG. 8 is a drive mechanism diagram of a plunger.

FIG. 9 is a characteristic graph in which the horizontal axis represents the rotation angle of the input shaft and the vertical axis represents the displacement and speed ratio of the plunger.

FIG. 10 is a diagram showing a comparison between cases where the velocity of the jet flow from the nozzle is an intermittent flow and a continuous flow.

[Explanation of reference numerals] 10 high-pressure underwater cleaning device (high-pressure in-liquid cleaning device) 14 water (liquid) 18 work (object to be cleaned) 20 nozzle 22 guide cylinder (cylindrical body) 24 high-pressure water supply device (liquid supply means) 26 impact Wave flow 56 Reverse conical cylinder part (reverse taper part) 58 Conical cylinder part (taper part) 74 Cavitation bubble 204 Plunger pump part (reciprocating pump) 212 Drive shaft 226 Input shaft 230 Drive side non-circular gear 232 Driven side non-circular gear

Claims (7)

[Claims] 1. An article to be cleaned (18) and a nozzle (2) in a liquid (14).
0) is arranged, and the liquid (14) is intermittently jetted from the nozzle (20) toward the object (18) to be cleaned at high speed and high pressure, which is a high-pressure in-liquid cleaning method. 2. A tubular body (22) surrounding the radially outer side of the nozzle (20) in a range including the nozzle (20) inside in the jet direction from the nozzle (20) to the object to be cleaned (18). ) Is provided, and the shock wave flow (26) is guided by the taper portion (58) of the cylindrical body (22) whose diameter gradually increases in the distal direction.
The high-pressure in-liquid washing method described. 3. A liquid supply means (24) for intermittently discharging a high-pressure liquid (14), and (b) a liquid supply means (24).
To be cleaned according to the intermittent supply of high pressure liquid (14) from
A high-pressure in-liquid washing device having a nozzle (20) for intermittently jetting the liquid (14) toward (18) at high speed and high pressure. 4. The nozzle (20), comprising: (c) a taper portion (58) having a diameter gradually increasing toward the tip from the nozzle (20).
To the object to be cleaned (18) in the direction of the jet flow, the tubular body (22) surrounding the radially outer side of the nozzle (20) in a range including the nozzle (20) inside, Claim 1
The in-liquid high pressure cleaning device described. 5. The cylindrical body (22) is provided with a reverse taper portion (56) on the base end side of the taper portion (58), the reverse taper portion (56) connecting to the taper portion (58) with a diameter gradually decreasing in the distal direction. The high-pressure in-liquid washing device according to claim 4, wherein 6. The liquid supply means (24) includes a reciprocating pump (204) for intermittently supplying the liquid (14) to the nozzle (20) by an intermittent discharge process. 3-
The submerged high-pressure cleaning device according to any one of 5 above. 7. The liquid supply means (24) is configured so that a drive shaft (212) of the reciprocating pump (204) rotates at a low speed and a high speed during a suction stroke and a discharge stroke of the reciprocating pump (204), respectively. Converting the input shaft (226) from non-constant speed rotation to non-constant speed rotation, the driving side non-circular gear (230) and the driven side non-circular gear (232) that mesh with each other are transmitted to the drive shaft (212). The submerged high-pressure cleaning device according to claim 6, which is provided.