JPH11324905A - High-pressure reciprocating pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To simplify the manufacture, assembling and disassembling, and to pressurize the slurry for pressure-feeding without generating the leak. SOLUTION: This pump reciprocates a plunger connected to a driving unit, and opens and closes a suction flow passage and a discharge flow passage in response to the reciprocation so as to pressure-feed the fluid with high- pressure. In this case, a device is formed with plural plunger cases 5 for axial insertion of plural plungers 3, a seal part 6 for sealing a clearance between the inner wall of the plunger case 5 and the plunger 3, a support frame 9 for supporting the plural plunger cases 5 in parallel with each other freely to be removed, and a tip surface of each plunger case 5 is closed freely to be removed so as to form a pump chamber 5c, in which the plunger 3 is reciprocated, Further, the device is provided with a head plate 10 having passages 10b, one of which communicates with the pump chamber 5c, therein and a direction control valve 14 connected to the head plate while communicating with the other passage 10b.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a high-pressure reciprocating pump for generating a high pressure and an ultra-high pressure in a liquid phase, and more particularly to a high-pressure reciprocating pump suitable for pressurizing and feeding a slurry.

[0002]

2. Description of the Related Art Conventionally, a high-pressure reciprocating pump reciprocates a plunger in a cylinder, and correspondingly opens and closes a flow path to a suction pipe or a discharge pipe through a valve to reduce the volume of fluid in the pump chamber. By changing, the fluid is sent to the high pressure side.

[0003] This type of high-pressure reciprocating pump is used for cleaning drains, ships and the like in chemical plants, food processing factories and buildings, or for maintenance and cleaning of civil engineering and construction machinery. It is used by being incorporated in water jet processing machines and electronic component cleaning equipment.

As shown in FIG. 8, a general configuration of a high-pressure reciprocating pump is a crankshaft 61 provided in a crankshaft case 60 and a connecting rod having one end connected to the crankshaft 61. A plunger 64 connected to the other end of the connecting rod 62 and reciprocating in a cylinder 63;
And a valve case 65 which is attached to the distal end portion so as to close the opening portion.

[0005] In the suction stroke, the plunger 64 moves to the left in the suction stroke, the volume in the valve case 65 increases by the moved volume, and the pressure is reduced. Fluid is sucked from the water supply port 66 by the force of the air pressure, and the valve case 65 is
Fluid is taken in. In the discharge stroke,
As shown in b), the plunger 64 moves rightward, and the fluid in front of the plunger 64 pushes the discharge side valve 68 open and is discharged from the discharge port 69.

In the configuration in which the plunger 64 reciprocates, the pressure and the flow rate fluctuate in the discharge flow. Therefore, in general, an accumulator for absorbing pressure pulsation is provided in the discharge pipe to reduce pulsation. By increasing the number of cylinders, the number of discharges during one rotation of the crankshaft is increased and the flow is averaged by using a so-called multiple type.

A plunger 64 and a piston 64a
Are connected and integrated by screwing the male screw portion and the female screw portion.

[0008]

However, the valve case of the conventional high-pressure reciprocating pump is usually made of a block-shaped heavy object integrally formed by casting or forging. By doing so, the pressurizing chamber 65a, the suction passage 65b, and the discharge passage 65c are formed in a complicated manner therein. Therefore, it is not easy to manufacture the pressurizing chamber and the valve section, and when assembling or disassembling and performing repair, even if the reciprocating pump has a relatively small shape, a multiple pressurizing chamber is used. And the valves are all one-piece heavy objects, so multiple workers must handle them using a crane, and they must handle them carefully so as not to damage or damage the plunger or packing. However, there is a problem that workability is poor. Further, there is also a disadvantage that the entire valve case must be removed from the crankshaft case every time the repair is performed.

In the conventional valve case, the pressure chamber 6
5a, when the suction passage 65b and the discharge passage 65c are cut, the suction passage 65b or the discharge passage 65c is orthogonal to the pressurizing chamber 65a in the valve case 65, and the portion where the pressurizing chamber and the passage intersect Will be formed with corners. If the corner of the high-pressure reciprocating pump is exposed to a high-pressure or ultra-high-pressure pulsating flow, low-cycle fatigue failure is likely to occur from the corner, and the valve case 65 may be broken.

In order to prevent breakage, it is conceivable to use a more expensive high-strength material or to select a hard member which has been subjected to a treatment such as quenching. Lightening will be hindered,
Processing becomes difficult and handling becomes more difficult.

Further, since the driving piston 64a and the plunger 64 are integrated, the pressure chamber is extremely high when the pressurizing chamber is formed by combining the crankshaft case and the valve case to secure the seal of the plunger 64. Assembly accuracy is required.

[0012] However, in order to obtain such an assembly precision for a high-pressure reciprocating pump, which is a heavy material, artisan skills were required. In particular, a metal plunger does not pose a problem, but a plunger coated with a brittle material such as ceramics has a problem that if the positioning accuracy is low and the centering is poor, the plunger breaks. . Further, if the centering is poor, uneven wear occurs in the seal portion, and as a result, the life of the seal portion is shortened, so that the reliability of the high-pressure reciprocating pump is reduced.

Further, in this type of high-pressure reciprocating pump, when a slurry, particularly a slurry containing an inorganic substance, is pressurized and fed, there is a problem that a leak is generated from a seal of a sliding portion in the high-pressure reciprocating pump.

The present invention has been made in consideration of the problems of the conventional high-pressure reciprocating pump described above, and a first object is to manufacture, assemble, and manufacture a pump head of the high-pressure reciprocating pump.
The second object is to realize a leak-free seal structure so that the slurry can be directly pressurized and fed,
A third object is to eliminate a failure caused by misalignment of a plunger or the like in a high-pressure reciprocating pump.

[0015]

A high-pressure reciprocating pump according to the present invention reciprocates a plunger connected to a driving unit,
A high-pressure reciprocating pump that opens and closes a suction flow path or a discharge flow path by a valve in response to the pressure and feeds the fluid at a high pressure. And a directional control valve that is detachably provided to supply and discharge fluid to and from the pump chamber.

The high-pressure reciprocating pump according to the present invention reciprocates a plunger connected to a driving unit, and opens and closes a suction flow passage or a discharge flow passage by a valve corresponding to the reciprocating movement, thereby pumping fluid at a high pressure. , A plurality of plunger cases that allow a plurality of plungers to pass through each other, a seal portion that seals a gap between the plunger case inner wall and the plunger, and a plurality of plunger cases that are arranged parallel to each other and can be removed. A support frame for supporting, and a head in which a distal end face of each plunger case is removably closed to form a pump chamber in which the plunger reciprocates, and one of passages provided therein communicates with the pump chamber. A plate, and a directional control valve connected to the head plate in a state of communicating with the other of the passages. The gist of the door.

In the present invention, each plunger case comprises a cylinder having a small-diameter portion and a large-diameter portion, and a through-hole in which the small-diameter portion of the cylinder is fitted is arranged in the support frame. It is preferable that the plunger case is positioned by inserting the plunger into the support frame until the stepped surface of the plunger contacts the peripheral edge of the through hole.

It is preferable that the mounting portion of the support frame and the head plate are configured to be fixed to the case and the support portion of the driving portion using bolts.

Further, the head plate can be constituted by a plurality of lid-like members which are fastened and fixed to the support frame for each plunger case, and an integral structure having a lid common to each plunger case. It can also be composed of a lid-shaped member.

In the present invention, it is preferable that the plunger is connected to the piston of the driving unit via an automatic alignment mechanism. In this case, the configuration of the self-centering mechanism includes a sliding plate provided at a plunger side end of the piston or a piston side end of the plunger in a direction orthogonal to the axis of the plunger or the piston, and a piston and the plunger. It is preferable that the sliding plate is constructed so that the piston end or the plunger end can slide on the plate surface.

In the present invention, the connecting portion includes a connection fitting loosely fitted to the plunger end of the piston or the piston end of the plunger, the piston end of the plunger or the plunger end of the piston. And a connected fitting screwed to the connecting fitting. Further, it is preferable that a protrusion is provided at the end of the piston or the end of the plunger so as to slide in a state of being partially in contact with the sliding plate.

The connecting portion includes a fitting fixed to the plunger-side end of the piston or the piston-side end of the plunger and having a locking portion, and a piston-side end of the plunger or a plunger-side end of the piston. And a connected metal fitting having a groove that can be engaged with the locking part attached to the part.

In the present invention, the seal portion is disposed between the laminated seal material inserted into the annular groove formed between the inner wall of the plunger case and the plunger, and between the laminated seal material and the bottom surface of the annular groove. Preferably, the coil spring includes a coil spring and a tightening portion that is disposed on the side opposite to the side where the coil spring is disposed in the seal member and presses the seal member against the urging force. Also, the combination sealing material
It is preferable that the plunger is formed by alternately stacking a large number of ramie seals and resin backup rings in the axial direction of the plunger.

As the fluid that can be pumped by the high-pressure reciprocating pump of the present invention, a slurry containing an organic or inorganic substance in a liquid such as water, an organic solvent, or a chemical solution is shown. Of course, a liquid containing no slurry is also pressurized. Can be pumped.

[0025]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the present invention will be described in detail based on preferred embodiments shown in the drawings. Fig. 1 (a)
(C) shows the appearance of the high-pressure reciprocating pump of the present invention. In the description, the pump head side of the high-pressure reciprocating pump will be described as the front, and the crankshaft case side will be described as the rear.

[0026] In the figure, the high-pressure reciprocating pump P, the input shaft crank shaft case portion for driving the driving force is given by S (drive portion) P _1, the piston arrangement side of the driving crank shaft case portion P ₁ securing the support frame portion P ₂ provided, each plunger casing portion P ₃ by the supporting frame portion P ₂ arranged in triplicate 3
It is mainly composed of head plate portions P ₄ and check valve portions CV as directional control valves connected to the respective head plate portions P ₄ . Incidentally, the plunger case P ₃ and the head plate portion P ₄ can be regarded as a pressure casing. In the drawing, 1 is a piston, 2 is an automatic alignment mechanism, and 3 is a plunger. P ₂ ′ is a support frame cover. Hereinafter, the configuration of each unit will be described in detail.

[0027] In FIG. 2, the rear end of the piston 1 is connected to a crank shaft of the crank shaft case P ₁ via a connecting rod (not shown), the distal end portion of the piston 1, the automatic aligning mechanism Plunger with cylindrical sleeve or cylindrical plunger 3 through 2
Is connected. As the material of the latter plunger 3, it is preferable to use a hard material such as SUS440C, alumina, zirconia, cemented carbide (WC or the like), silicon carbide, silicon nitride or the like. FIG. 2 shows a state where the piston 1 is located at the top dead center.

The plunger 3 is inserted into a cylindrical plunger case 5 via a spring receiver 4 formed of a sleeve. The plunger 3 is connected to the inner surface of the plunger case 5 formed by the insertion of the spring receiver 4. A seal portion 6 is provided in an annular groove with the outer peripheral surface of the jar 3. The seal portion 6 is urged in the direction of arrow A by a compression coil spring 7 supporting the spring receiver 4.

As shown in detail in FIG. 3, the seal portion 6 alternately includes a ramie seal 6a as a gland packing and a resin ring 6b as a packing spacer arranged so that the plunger 3 passes through the shaft. It is configured by laminating a plurality of sheets. The ramie seal 6a is a packing in which hemp is impregnated with a Teflon resin or a silicone resin, and is formed by connecting a band-shaped material into a ring shape. The connection portion is shifted by 90 ° for each ramie seal (in the cross section in the diameter direction of the plunger) so that the connection positions are not aligned in the axial direction of the plunger 3 when the plunger 3 is passed through the shaft. Shall be arranged in

On the other hand, the resin ring 6b is made of, for example, polyetheretherketone, polyethylene, high-density polyethylene, ultra-high-molecular-weight polyethylene, polyamide, polyacetal, polycarbonate, polyphenylene oxide, polybutylene having excellent solvent resistance, toughness and moldability. It is formed in a ring shape by using one or more of terephthalate, polysulfone, polyphenylene sulfide, polyamide imide, fluorine-based resin, silicon-based resin and the like. Note that these exemplified resins are properly used depending on the processing fluid.

A spring seat 8 is inserted between the spring 7 and the resin ring 6b. According to the configuration in which the ramie seal 6a and the resin ring 6b are alternately combined in this manner, a slurry containing an inorganic substance such as alumina or calcium carbonate can be pumped while a liquid-tight state is reliably maintained. In FIG. 3, reference numeral B ₁ represents indicates the position of the tip of the plunger 3 when the piston 1 is positioned at the top dead center position of the tip of the plunger 3 when located at the reference numeral B ₂ is also the bottom dead center Is shown.

At the rear end of the plunger case 5, a screw hole 5d having a depth "d" is formed. The screw hole 5d is provided with a through hole as a tightening portion. The bolt 15 is screwed. In the figure, d indicates the depth of the screw hole 5d, and the gap between the bottom surface of the screw hole 5d and the tightening bolt 15 screwed becomes an additional tightening allowance.

The tightening bolt 15 has the screw hole 5d
A male screw part 15a is formed at the tip of the male screw part 15a, and a cylindrical part 15b that can be inserted into the annular groove part into which the seal part 6 is inserted is formed. This cylindrical portion 15b
Abuts on the rear end of the seal portion 6 to press the seal portion 6 in the direction of arrow B.

A hexagonal head 15c to which a hexagon wrench can be attached is formed at the rear end of the tightening bolt 15 for tightening the tightening bolt 15. Hex head 1
5c is not limited to this, and a hook groove for a hook spanner may be formed at six or more locations in the circumferential direction. A locking nut 16 is screwed into the male screw portion 15a so as to come into contact with the rear end face of the plunger case 5. The deep hole 1 is formed at the rear end of the tightening bolt 15 so as to avoid the rear end of the reciprocating plunger.
5d is formed.

In FIG. 4 showing a state in which the support frame cover P ₂ ′ is removed, the plunger case 5 is fixed to a crankshaft case portion P _{1 (} not shown) via a window frame-like support frame 9. Case 5
The support frame 9 can be combined with the support frame 9 by fitting the plunger case 5 into a through hole 9b formed in the support portion 9a of the support frame 9.

More specifically, as shown in FIG. 2, the plunger case 5 has a large-diameter portion and a small-diameter portion whose outer diameter gradually decreases in the mounting direction (the direction of arrow A). The portion 5a is fitted into the through-hole 9b, and the stepped step surface, which is the boundary between the small-diameter portion 5a and the large-diameter portion 5b, is locked to the opening periphery of the through-hole 9b. Insertion depth, that is, positioning can be performed.

The plunger case 5 positioned on the support frame 9 has a plunger case 5
The head plate 10 is arranged so as to close the distal end side of the head frame, and the head plate 10 is fastened and fixed to the support portion 9a of the support frame by using four mounting bolts 11.

More specifically, the head plate 10 is formed with four through holes 10a for allowing the mounting bolts 11 to pass therethrough (see FIG. 1B). , The head plate 10 is brought into contact with the front end face of the plunger case 5, and the nut 11 a is screwed into the mounting bolt 11 to be tightened. Are integrated with each other. In addition, a pressurizing chamber is formed in the plunger case 5.

A passage 10b is formed in the head plate 10 at a position corresponding to the tip of the plunger 3, and an inlet of one of the passages 10b is provided in the pump chamber 5c.
The other end of the passage 10b is connected to a joint 10c for connecting a valve case 14 described later.
Is in communication with

A valve case 14 is connected to the joint portion 10c via a connection pipe 13. The plunger 3 moves in the direction of arrow A to move the check valve 14b from the suction port 14a.
Is discharged from the discharge port 14d through the check valve 14c when the plunger 3 moves in the direction of arrow B.

The head plate 10 can be removed from the plunger case 5 by removing the nut 11a, and then the plunger 3 appears when the plunger case 5 is removed from the support 9a. Further, by removing the nut 12a that is screwed to the bolt 12 has been planted crankshaft case P _1, it is possible to remove the supporting frame 9 from the crankshaft case.

Next, the automatic alignment mechanism 2 will be described. At the tip of the piston 1 as a drive shaft, the piston 1
The connection receiving bolt 20 is connected coaxially. More specifically, the connection receiving bolt 20 has a disk portion 20a as a sliding plate at its tip and a male screw portion 20b at its rear end. By tightening into the female screw part 1a formed at the tip,
It is configured to be fixed to the piston 1.

Also, the shaft of the connection receiving bolt 20 has
A cylindrical connection cap nut 21 as a connection fitting having a through hole 21a is loosely fitted with the cap 21. The diameter of the through-hole 21a is, for example, 3 mm larger than the outer diameter of the connection receiving bolt 20.
It is formed about mm larger. Also, connection cap nut 2
The inner surface of the first flange portion 21b comes into contact with the rear surface of the disk portion 20a of the connection receiving bolt 20.

On the other hand, at the rear end of the plunger 3, a cylindrical plunger holding fitting 22 as a connected fitting is fixed coaxially with the plunger 3 by shrink fitting. A male screw part 22 is provided on the body of the plunger holding bracket 22.
a is formed, and by screwing the male screw portion 22a to the female screw portion of the connection cap nut 21 described above,
The connection cap nut 21 and the plunger holding bracket 22 are combined, whereby the drive unit piston 1 and the plunger 3 are connected. The connection cap nut 21 and the plunger holding bracket 22 can be regarded as a connecting portion.

A protruding portion 22 b is formed on the piston-side end surface (hereinafter, simply referred to as a rear end surface) of the plunger holding bracket 22 on the axis of the plunger 3.
2b is in surface contact with the front surface of the disk portion 20a of the receiving bolt 20 for connection.

FIG. 6 shows a second embodiment of the automatic alignment mechanism. In the following description, the same components as those in FIG. 5 are denoted by the same reference numerals, and description thereof will be omitted.

In the self-aligning mechanism shown in FIG. 6, a recess 22c is formed in the rear end face of the plunger holding bracket 22, and a steel ball 22d is stored and held in the recess 22c. However,
A part (projection) of the steel ball 22d is projected from the opening edge of the recess 22c. The protruding steel ball 22d is brought into contact with the front surface of the disk portion 20a of the connection receiving bolt 20. According to this configuration, the plunger holding fitting 22 and the connection receiving bolt 20 come into contact with each other with a smaller contact area, specifically, a point contact as compared with the configuration of FIG.

FIG. 7 shows a third embodiment of the self-aligning mechanism, which can be applied to a piston 1 having a male screw portion 1a formed at the tip. 7A shows a vertical cross-sectional view, and FIG. 7B shows a cross-sectional view taken along the line CC of FIG. 7A.

In the configuration shown in FIG. 7, the female screw portion 24f of the box-shaped connection fitting 24 is screwed to the male screw portion 1a. The connection fitting 24 is composed of an upper part 24a and a lower part 24b which are divided into two parts. A pair of through holes 24c through which the bolt 25 is inserted are formed in the upper part 24a, and a female screw part 24 for screwing the bolt 25 into a position corresponding to the through hole 24c is formed in the lower part 24b.
d is formed. When the components 24a and 24b are combined, the female screw portion 24f engages with the male screw portion 1a of the piston 1.

An engaging portion 24e which is bent in an L-shape toward the axis of the piston and forms a circular opening is formed on the front side of the connection fitting 24.

On the other hand, an annular groove 26a is formed at the rear end of the plunger holding metal member 26 as a connected metal member. The jar 3 and the piston 1 are connected with play. The play means, for example, the connection fitting 24
A gap of about 3 mm is provided between the plunger holding bracket 26 and the plunger holding fitting 26. Further, when a 10mm width t ₁ of the annular groove, the thickness t ₂ of the engaging portion 24e is 9.7～9.8Mm, clearance t ₃ of the locking portion 24e and the annular groove 26a is 0 .2
0.3 mm. Also, the gap t ₄ the plunger holding metal fitting 26 and the piston 1 tip is preferably secured about 1 mm. That is, in this self-centering mechanism, play is provided in both the axial direction and the diametrical direction of the piston 1.

Thus, the plunger 3 and the piston 1
Since the edge is completely cut off, the assembling becomes easier as compared with the configuration shown in FIGS. 5 and 6, and there is no need to perform operations such as temporary assembling, running-in operation, and final fastening. Also,
Since there is no need to worry about manufacturing errors and assembly errors (coaxiality and straightness errors), anyone, not only skilled personnel, can easily and surely assemble the automatic alignment mechanism. A flange 26b as a sliding plate is formed in a circular shape on the rear side of the annular groove 26a, and the locking portion 24e slides on the surface of the flange 26b.

In each of the embodiments described above, the connecting fitting is provided on the piston side and the connected fitting is provided on the plunger side. Next, the operation of the high-pressure reciprocating pump having the above configuration will be described.

In FIG. 2, in the suction stroke, the plunger 3 moves in the direction of arrow A to expand the volume of the pump chamber 5c, the check valve 14b opens to suck fluid from the suction port 14a, and the pump chamber 5c A fluid is introduced into the interior. At this time, the check valve 14c is in a closed state.

Next, in the compression stroke, the plunger 3 moves in the direction of arrow B and the volume of the pump chamber 5c is reduced, so that the pressure in the pump chamber 5c increases, and the check valve 14
c is opened and the fluid is pumped from the discharge port 14d. At this time, the check valve 14b is in a closed state.

In the conventional reciprocating pump, since the plunger case 5 and the valve case 14 constituting the pressurizing chamber are integrally formed, when disassembling at the time of failure or inspection and maintenance, First, the valve part is disassembled to disassemble the plunger part. To disassemble the valve part, remove the blind plug of the valve part using a socket wrench and remove the valve assembly from the manifold using pliers, etc.When removing the valve case, use the nut on the manifold. Are all removed from the crankshaft case, thereby disengaging the valve case from the crankshaft case. At this time, sufficient care must be taken not to damage or break the plunger and the packing with the manifold.

Also, when assembling the valve case thus removed, the positioning is carefully performed so that each plunger projecting from the crankshaft case is correctly inserted into the plunger guide cylinder of the valve case. After assembly, the plunger and packing must be assembled without damaging them.

On the other hand, in the high-pressure reciprocating pump according to the present embodiment, since the pressurizing chamber and the valve case are formed independently for each plunger, for example, the pressure in the discharge passage is reduced and the reciprocating pump is used. When it is necessary to disassemble and inspect, the valve case can be first removed from the plunger pump for inspection, and if necessary, the pressurizing chamber can be removed from the crankshaft case and disassembled. As described above, in the present embodiment, it is not necessary to always remove the entire valve portion from the crankshaft case as in the conventional configuration, and the appropriate engagement between the plunger and the plunger case is automatically and individually determined for each plunger. Since adjustment can be performed by the centering mechanism, assembly and disassembly can be performed easily in a short time.

The operation of the automatic alignment mechanism will be described. First, the assembling of the plunger case 5 to the support frame 9 will be described. The plunger holding bracket 22 at the rear end of the plunger is opposed to the connection cap nut 21 loosely fitted to the connection receiving bolt 20. Then, the plunger holding fitting 22 is screwed into the connection cap nut 21 to combine them together. However, at this stage, both are not completely tightened and fixed.

Next, the small diameter portion 5a of the plunger case 5
Is fitted into the through hole 9b of the support frame 9 and the plunger 3 is made to pass through the shaft. Next, the seal part 6, the compression coil spring 7, and the spring receiver 4 are inserted in this order to form a seal structure.

In this state, the piston 1 is reciprocated several times to make the plunger 3 and the seal portion 6 fit together, and the connection cap nut 21 and the plunger holding bracket 22 are tightened.

In the high-pressure reciprocating pump assembled in this manner, the axis of the piston 1 and the axis of the plunger 3 do not always coincide with the theoretical axis due to the presence of a machining error, an assembly error, and the like. That is, coaxiality cannot be obtained. Specifically, the reason why coaxiality cannot be obtained is as follows.
As shown in FIG. 5, the axis L ₁ of the piston 1 and the axis L _{2 of the} plunger 3 are displaced in parallel with each other and have coaxiality errors, and each axis L ₁ , L ₂ has a certain angle. And a straightness error occurs due to the intersection at the points. Therefore, it is necessary to provide a coaxiality tolerance so that these two errors can be absorbed. What is coaxiality tolerance?
The area inside the cylinder of diameter d having an axis coincident with the desired theoretical axis is shown, in this embodiment d = 3 mm. However, the axial length of the cylinder is the stroke of the piston 1.

According to the configuration shown in FIG. 5, the plunger holding bracket 22 is in contact with the disk portion 20a of the connection receiving bolt 20 via the convex portion 22b having a small contact area. Cap nut 21 and connection receiving bolt 2
Since a gap is provided between the piston 1 and the plunger 3, the axial misalignment between the piston 1 and the plunger 3 can be kept within the above-described coaxiality tolerance.

Next, the operation of the seal portion 6 will be described. In the seal portion structure of the present invention, when the plunger 3 is incorporated in the plunger case 5, the retightening portion receives the seal portion 6 with a minimum interference that does not leak. Gradually increase the pressing force until there is no leakage.

That is, by performing retightening,
The life of the seal portion 6 can be greatly extended. Further, since the pressing force applied to the seal portion 6 can be gradually increased in accordance with the decrease in the sealing function, the sealing effect between the inner wall of the plunger case 5 and the plunger 3 can be stabilized.

The operation of the above tightening portion will be described more specifically. The plunger 3 is axially inserted into the plunger case 5, and the tightening bolt 15 is screwed to the plunger case 5 in a state where the seal portion 6 is formed. When the tightening bolt 15 is tightened, the seal portion 6 is compressed by the urging force of the spring 7. At this time, the additional tightening bolt 15 presses the seal portion 6 with the minimum interference that does not cause leakage.

If a leak occurs in the seal portion 6 due to the continuous operation of the high-pressure reciprocating pump, a hexagon wrench is attached to the hexagonal head 15c of the tightening bolt 15 and tightened. Gradually increase.

Conventionally, for example, in a seal structure using a V-packing or the like, if leakage occurs, retightening is performed.
A method is used to stop leaks. However, in the conventional sealing structure, since one of the sealing members is fixed by the wall surface, there is a problem that when the tightening force in the retightening is increased, the frictional resistance of the plunger 3 increases rapidly. That is, in the conventional seal structure, since the interference is small, it is difficult to finely adjust the additional tightening.

On the other hand, in the present embodiment, the coil spring 7 is gradually contracted as the retightening is performed, so that the tightening force by the retightening can be gradually increased within the range of the retightening allowance. . That is, since the tightening margin is large, the additional tightening can be easily finely adjusted.

[Examples] The following fluids were introduced into the high-pressure reciprocating pump of this embodiment and the conventional high-pressure reciprocating pump, and the results of pressurization and pressure feeding are shown below. The pressure of the pump was set at 140 MPa, the discharge rate of the pump was set at 500 l / h, and the rotation speed of the crankshaft was set at 150 rpm. However, the characteristics of the high-pressure reciprocating pump of this embodiment are as follows:
500 MPa, discharge rate of the pump: 10 to 2000 l / h. Slurry type: water + alumina powder Solid content concentration: 50 wt% Solid content hardness: 1500 Hv Solid particle size: 100 μm Slurry viscosity: 5000 cp

In the conventional high-pressure reciprocating pump, after operation,
Leakage occurred in the seal part of the sliding part of the high-pressure reciprocating pump within a few minutes, making it unusable. On the other hand, the high-pressure reciprocating pump according to the present invention was able to perform the pressure feeding operation stably for several hundred hours.

Further, in the high-pressure reciprocating pump of the present invention, the valve for supplying and discharging the fluid and the pressurizing chamber for pressurizing the fluid are formed separately, and the plunger reciprocates in the cylinder for the pump head. Since only a simple pressurizing function that moves is used, it can be manufactured easily, and a sufficient strength can be ensured in a portion of the pump head that is exposed to a high-pressure or ultra-high-pressure pulsating flow.

Further, since the pump head is provided independently for each plunger and a joint is formed so that a valve can be connected to each head plate, the pump head can be easily attached to and detached from the crankshaft case. In addition, the valve can be easily attached to and detached from the pump head, thereby simplifying the manufacture, assembly and disassembly and repair work of the high-pressure reciprocating pump.

In the self-aligning mechanism, for example, when the crankshaft case and the pump head are assembled integrally, the axial misalignment generated between the piston and the plunger connected to the piston is absorbed. Therefore, the assembling work is greatly reduced. In addition, by eliminating the centering defect, uneven wear of the seal portion is eliminated, and as a result, the life of the reciprocating pump can be extended.

The seal portion of the high-pressure reciprocating pump has the shortest service life among the constituent elements of the pump and requires maintenance. Therefore, if the maintenance cycle can be extended by extending the life of the seal portion, the reliability of the high-pressure reciprocating pump will be further enhanced.

Although the support frame 9 of the present invention is constituted by a frame-like frame in the above embodiment, the present invention is not limited to this.
Any frame can be used as long as it can be fixed to _one .

In the above embodiment, the head plate 10 is provided independently for each plunger case 5 and the valve case 14 is connected to each head plate 10. However, the present invention is not limited to this configuration. The plunger case may be formed as an integral structure that covers the plunger case in common. Further, a valve case having an integral structure in which a suction part and a discharge part are built in corresponding to each plunger 3 can be connected to the head plate.

In the above embodiment, the rear edge of the large-diameter portion 5b of the plunger case 5 is positioned by contacting the peripheral edge of the through hole 9b of the support portion 9a.
However, the position can be determined by subjecting the support portion 9a to counterbore processing and inserting the cylindrical plunger case into contact with the counterbore-processed bottom surface.

In the above embodiment, the head plate 1
0 is fixed to the support portion 9a of the support frame by the mounting bolt 11, but when the discharge amount is small, for example, 100 l / Hr or less, the head plate is directly fixed to the plunger case with bolts. Is also good.

The high-pressure reciprocating pump of the present invention is suitable for the pressure-feeding of the slurry containing the inorganic substance shown in the above embodiment, but is not limited to this and can be used for the pressure-feeding of any fluid.

[0081]

As is apparent from the above description,
According to the present invention, it is possible to provide a light and highly reliable pump head which is easy to manufacture and assemble, and a high-pressure reciprocating pump using the same. In addition, since the pump section is divided into a pressurizing section and a valve section to have a separate configuration, the structure of the pump head can be simplified, and
Only the portion exposed to high pressure may be made of a high-strength member, and even if worn, there is no need to replace the entire pump, so that the cost of the high-pressure reciprocating pump can be reduced.

Conventionally, in a multiple pump, the entire pump is disassembled even when the seal material for one cylinder is replaced. However, in the present invention, the seal material is individually provided for each plunger case. Can be replaced, so that there is an advantage that the pump repair work, which mostly involves the replacement of the sealing material, is simplified.

According to the seal portion of the present invention, the sealing effect can be stabilized in the high-pressure pump. Therefore, even if the fluid to be treated is slurry, the slurry can be stably pressurized and fed without causing leakage. Can be. Further, even in the case where leakage occurs, by performing the retightening, the sealing effect can be enhanced and the life of the sealing material can be extended.

According to the present invention having the self-centering mechanism, since the misalignment between the piston shaft and the plunger shaft can be absorbed, anybody can easily assemble the pump without requiring any craftsmanship skills. Repair work can be performed. Further, there is an advantage that even if a plunger made of an expensive and brittle material such as ceramics is used, there is no possibility that the plunger is broken. Further, since uneven wear in the seal portion can be eliminated, the life of the seal portion can be extended, and as a result, the reliability of the pump can be improved.

[Brief description of the drawings]

FIG. 1 is an explanatory diagram showing a configuration of a high-pressure reciprocating pump of the present invention.

FIG. 2 is a longitudinal sectional view showing a structure of a pump head part of FIG.

FIG. 3 is a longitudinal sectional view showing a configuration of a seal unit in FIG. 1;

FIG. 4 is a plan view of FIG. 2;

FIG. 5 is a vertical sectional view showing a configuration of the self-centering mechanism of FIG. 2;

FIG. 6 is a view corresponding to FIG. 5, showing a second embodiment of the automatic alignment mechanism.

FIG. 7 is a view corresponding to FIG. 5, showing a third embodiment of the automatic alignment mechanism.

FIG. 8 is an explanatory view showing a configuration of a conventional reciprocating pump.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Drive part piston 2 Self-centering mechanism 3 Plunger 4 Spring receiver 5 Plunger case 6 Seal part 7 Coil spring 8 Spring receiving seat 9 Support frame 10 Head plate 11 Mounting bolt 14 Valve case

Claims (12)

[Claims] 1. A high-pressure reciprocating pump for reciprocating a plunger connected to a drive unit, opening and closing a suction flow path or a discharge flow path by a valve corresponding to the plunger, and forcing a fluid to be supplied at a high pressure. A pressurizing case having the plunger therein, and a directional control valve detachably provided to the pressurizing case and supplying and discharging the fluid to and from the pump chamber. High pressure reciprocating pump. 2. A high-pressure reciprocating pump for reciprocating a plunger connected to a driving unit, opening and closing a corresponding suction flow passage or discharge flow passage by a valve, and pumping a fluid at a high pressure. A plurality of plunger cases through which the jars are respectively axially passed; a seal portion for sealing a gap between the inner wall of the plunger case and the plunger; and a plurality of the plunger cases arranged in parallel with each other and detachably supported. A support frame, and a head in which one end of each of the plunger cases is removably closed to form a pump chamber in which the plunger reciprocates, and one of the passages provided therein communicates with the pump chamber. A directional control valve connected to the head plate in a state of communicating with the other of the passages. High-pressure reciprocating pump. 3. The plunger case includes a cylinder having a small-diameter portion and a large-diameter portion, and a through-hole in which the small-diameter portion of the cylinder is fitted is arranged in the support frame. The high-pressure reciprocating pump according to claim 2, wherein the plunger case is positioned by inserting the plunger into the support frame until a step surface of the portion contacts the peripheral edge of the through hole. 4. The high-pressure reciprocating pump according to claim 2, wherein the support frame and the head plate are fixed to the case of the drive unit and the support frame, respectively, using bolts. 5. The high-pressure reciprocating pump according to claim 2, wherein said head plate comprises a plurality of lid-like members which are fixedly fastened to said support frame for each of said plunger cases. 6. The high-pressure reciprocating pump according to claim 2, wherein the head plate is formed of a lid member having an integral structure and covering the plunger cases in common. 7. The plunger is connected to a piston of the driving unit via an automatic centering mechanism, and the self-centering mechanism includes a plunger-side end of the piston or a piston-side end of the plunger. A sliding plate provided in a direction orthogonal to the axis of the plunger or the piston, and a connecting portion bridged with play between the piston and the plunger, wherein the sliding plate is 3. A high-pressure reciprocating pump according to claim 2, wherein said piston end or said plunger end is slidable on its plate surface. 8. A connection fitting in which the connecting portion is loosely fitted to a plunger side end of the piston or the piston side end of the plunger, and a piston side end of the plunger or a plunger of the piston. The high-pressure reciprocating pump according to claim 7, further comprising a connected metal fitting attached to a side end and screwed to said connecting metal fitting. 9. The high-pressure reciprocating device according to claim 7, wherein a convex portion is provided at the end of the piston or the end of the plunger so as to slide in a state of being partially in contact with the sliding plate. pump. 10. A connection fitting, wherein the connecting portion is fixed to a plunger side end of the piston or the piston side end of the plunger and has a locking portion, and a piston side end of the plunger or the piston. 8. A high-pressure reciprocating pump according to claim 7, further comprising: a fitting which is attached to a plunger side end of said fitting and has a groove which can be engaged with said locking portion. 11. The laminated seal member, wherein the seal portion is inserted into an annular groove formed between the inner wall of the plunger case and the plunger, and between the laminated seal member and the bottom surface of the annular groove. A coil spring arranged on the
The high-pressure reciprocating pump according to claim 2, further comprising: a re-tightening portion that is disposed on a side of the laminated sealing material opposite to the side where the coil spring is disposed, and that presses the laminated sealing material against the urging force. 12. The high-pressure reciprocating pump according to claim 11, wherein the laminated sealing material is formed by alternately laminating a plurality of ramie seals and resin backup rings in the axial direction of the plunger.