KR19990079544A - Plunger pump and its system - Google Patents

Abstract

A small and lightweight plunger pump with high efficiency and durability, and a system thereof.

In the plunger pump, the valve device has a valve body, and the central angle of the arc of the cross section of the spherical portion provided on the inner edge of the cylindrical cross section of the valve seat is set within a predetermined range. A coupling means for connecting the front end surface of the piston and the rear end surface of the plunger sets a clearance between the plunger and the plunger so that they can move with respect to each other in a direction perpendicular to the axis. An opening communicating with each of the valve devices is provided on the side wall of the cylindrical space of the plunger chamber. A lubricating oil outlet is provided on the lower side of the inner wall of the packing case supporting the plunger and on the upper side of the lubricating oil supply port.

Description

Plunger pump and its system

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a plunger pump used for pressurizing a high-pressure fluid and an arrangement of the pump system.

Plunger pumps for high-pressure fluids are often used for high-pressure transfer of slurry containing cement milk and the like at construction sites related to civil engineering construction. As a basic structure, a crank mechanism that converts rotational motion by a motor into reciprocating linear motion of a piston, a plunger rod that is provided in front of the piston and a plunger that performs reciprocating linear motion, and a plunger chamber that is installed on the suction side and the discharge side of the plunger chamber, respectively And a valve device for controlling the flow of the fluid.

There is also a plunger pump in which a plurality of plungers are connected in parallel to increase the discharge capacity to three or four.

Table 1 below shows the performance of a conventional plunger pump and the size of the entire system (including a motor, a transmission, and a control unit) as an example. This conventional example illustrates that the motor power and the diameter and number of the plunger are almost equal to each other in order to compare with the embodiment of the present invention shown in Table 2 to be described later.

[Table 1]

(Conventional example)

Plunger stroke ... 46mm

plunger… Diameter 50mm × 3 pieces (3 stations)

Maximum discharge pressure ... 400kgf / cm2

Maximum discharge rate ... 70 liters / minute

Inhalation ... 2 inches

Discharge aperture ... 3/4 inch

Motor power ... 55KW

Dimensions of the whole pump system ... W1500 mm L2200 mm H1250 mm

The weight of the entire pump system ... 2500kg

The plunger pump for high-pressure fluid has the basic problem of obtaining as high a discharge capacity as possible with a smaller motor power, but also the durability of the component parts due to the sliding heat due to the plunger and the shock caused by the movable part, complete sealing against high pressure, , Compactness of the entire pump system, workability of parts replacement and maintenance, and the like.

Furthermore, when the cement slurry is used for pressurization, the cement particles or solid foreign matter pierce into the gaps between the plunger, the valve device, and the seal part, so that the component parts are damaged in a short period of time and the parts have to be frequently replaced. If the components were cemented by cement, the replacement work was extremely difficult and took a long time.

As a measure for preventing the penetration of the cement slurry in the conventional plunger pump, for example, a partition wall such as a diaphragm or an elastic body is installed in the plunger chamber so that the valve device side and the plunger side are collapsed to prevent the cement particles from entering the plunger side . However, such a partition wall member requires deformation to ensure high pump efficiency, repeated deformation at high speed, and durability to withstand the plunger sliding heat, and in most cases, it will be broken in a short time. It is not preferable to install such a partition member in the plunger room because it largely affects the pressure transmission property and lowers the pump efficiency.

In addition, as a measure for preventing the solid from entering the water, a large number of pores (small pores) are provided in place of the cylindrical shape of the valve seat for the purpose of preventing large diameter particles from passing through the plunger chamber, And that a gap is provided between the intake port and the intake port or that the space between the plunger chamber and the intake port is communicated by a plurality of fine flow paths. In this way, the method of eliminating solid matter by the fine flow path immediately blocks the flow path, and smooth flow is hindered.

In the valve device, normally, the valve body is held in a state of being pressed against the valve seat by the coil spring. In addition, the valve body abuts against the valve seat every time the valve is opened and closed, and the high-pressure fluid is subjected to strong shock as a flow, and is liable to be damaged. In order to realize a durable valve device, a valve body and a valve seat of various shapes have been proposed. The shape of the valve body is plane, spherical, spherical, etc., and the shape of the valve seat is flat, spherical, conical, and the like. Although the surface of the valve body or the valve seat is made of an elastic material in order to improve the hermeticity, the use of an elastic material in the movable portion of the high-pressure pump damages in a short period of time and is frequently required to be replaced. It is inadequate to use an elastic material such as an O-ring in the movable portion or the pressure fluctuation portion of the high-pressure pump in actuality. In addition, in the case of slurry pressure feeding, cement particles are dug and damaged in a short period of time.

The rod-like plunger of the plunger pump performs reciprocating linear motion in the plunger chamber and simultaneously slides against the inner wall of the cylindrical support case. This sliding causes a large frictional heat.

Conventionally, a certain degree of clearance is placed between the plunger and the inner wall of the support case, in consideration of the shaking motion of the reciprocating linear motion of the plunger. Therefore, at least five to six V-packings and U-packings are arranged on the inner wall of the support case to ensure airtightness. A large amount of heat is generated again due to friction between the plurality of packings and the plunger, and these packings themselves are also easily consumed. Since there is a clearance between the plunger and the inner wall of the support case, the cement particles are easily infiltrated into the plunger, and the plunger is damaged by being swept into these particles, and if the cement particles are consolidated, it becomes difficult to disassemble.

The conventional plunger pump tends to complicate and enlarge the structure to solve all the problems. As a result, air is easily infiltrated into the inside of the plunger, and the air plume is liable to be generated. It is needless to say that the air filling in the plunger chamber significantly reduces the pump efficiency.

Also, when looking at the entire plunger pump system, the mechanical parts other than the control part usually consist of three main parts: a motor, a transmission, and a plunger pump. In many cases, these three major components are arranged side by side. As a result, the distance from the motor to the plunger pump becomes longer, so that rotational motion is transmitted through several parts therebetween. If the length of the shaft and the number of joints that transmit the rotation are increased, the shaft may be displaced or bent, causing vibration and noise, and the device may also fail. The efficiency of the motor output also decreases. Also, as the size of the entire device becomes larger, the burden of carrying and installation becomes greater.

Therefore, it is preferable that the entire plunger pump system is made compact and lightweight, that is, compact.

It is an object of the present invention to provide a plunger pump having durability and high efficiency in consideration of the above phenomenon. By doing so, a plunger pump or the like is provided which can reduce frequent parts replacement work and facilitate maintenance work.

It is also an object of the present invention to improve the pump performance of the plunger pump, to realize a compact and lightweight structure and to simplify the structure, and to realize a compact and lightweight overall plunger pump system including a motor and a transmission. By doing so, it improves the transportation and installation of the pump system and realizes low noise and low vibration.

The present invention also aims at improving the reliability, durability and workability of a safety valve mechanism and a pressure gauge mechanism, which are usually used together with a plunger pump.

1 is a schematic sectional view of an example of a plunger pump of the present invention,

FIG. 2 is a view showing the shape of a valve ball and a valve seat of a valve apparatus according to the present invention, wherein FIG. 2 (a) is a longitudinal sectional view of the valve seat,

3 is an enlarged cross-sectional view showing the plunger coupling and the circumference thereof, which connects the piston and the plunger shown in Fig. 1,

4 is a sectional view showing a safety valve unit installed in the plunger pump system according to the present invention,

FIG. 5A is an enlarged cross-sectional view showing the structure of a pressure gauge provided on the plunger pump according to the present invention, FIG.

Fig. 6 is a schematic side cross-sectional view of the plunger pump system of the present invention, and Fig. 6 (b) is a schematic plan view of Fig. 6 (a).

* Explanation of symbols for major parts of the diagram *

2 connecting rod

3 Crankshaft

4 Crank pin

5 Crankcase

6 Crankcase cover

7 Plunger case

8 Piston

9 Piston pin

11 head case

14 Packing case

15 plunger coupling

16 Cylinder sleeve

18 plunger

22 Suction valve device

23 Discharge valve device

24 valve seat

15 fluid passage

26 valve spring

27 valve chamber

28 valve ball

29 plunger chamber

33, 34 packing

36 Lubricating oil well

46 Metal packing

47 Connecting rod bearing

51 inlet

52 Outlet

60 Safety valve unit

61 Safety valve unit housing

62 Spring Clamp

63 room piston

64 valve ball

65 valve seat

66 coil spring

67 Pressure release bolt

68 Pressure release nut

69 Fitting bolts

70 O ring

71 Packing

72 through hole

73 outlet

80 Threaded Pressure Calculation

81 Flanged pressure account

82 column

83 Pressure transfer chamber

84 Packing

85 Hydraulic surface

86 Fluid · Oil contact surface

88 Pressure gauge body

89a Fitting screw hole

89b Fitting screws

100 plunger pump

110 motor

112 Motor shaft

120 transmission

122 transmission shaft

130 device cantilever

140 control unit

150 oil pump

151 Oil tank

200 plunger pump system

The plunger pump according to the present invention includes a plunger driven by a crank mechanism for converting a rotational motion into reciprocating linear motion, a plunger rod connected to the front of the electric piston, a plunger chamber for performing reciprocating linear motion of the electric front, And a valve device provided on the suction side and the discharge side, respectively, and has the following characteristic features.

The valve device according to the present invention has a spherical valve body, a cylindrical valve seat, and means for resiliently pushing the valve body against the valve seat.

And the valve seat surface material to accommodate the installed in the cylindrical section of the valve seat an internal combustion, having part spherical surface of the same curvature as the spherical valve body, one into the spherical portion range of the central angle of the circle ^{50-20 0} of the section will be.

Further, preferably, the conical surface portion is provided on the outer side adjacent to the spherical surface portion of the valve seat.

Preferably, there is provided a coupling means for connecting the front end surface of the piston and the rear end surface of the plunger so that they can not be moved in the axial direction with respect to each other. The piston and the coupling means are fixed so as not to move with respect to each other in a direction perpendicular to the axis, while a clearance gap is provided between the plunger and the coupling means so as to be mutually movable in a direction perpendicular to the axis.

Still more preferably, the plunger chamber is formed into a cylindrical space, and an opening communicating with each of the valve devices is provided on the side wall of the cylindrical space of the plunger chamber.

The plunger main surface is slidable with respect to the inner wall of the packing case during reciprocating linear motion, and the inner surface of the inner surface of the packing case inner wall A lubricant oil supply port is provided on the lower side of the cylinder head, and a lubricant oil outlet is provided on the upper side.

More preferably, the safety valve unit is provided on the passage of the high-pressure fluid. The structure includes a housing fixed on the passage of the high-pressure fluid, a spherical valve body disposed in the valve chamber in the housing, A valve seat having a communication port to the high-pressure fluid passage, an outlet opening outward from the valve chamber to the safety valve unit, a piston body disposed on the valve body and having a seal, A coil spring for resiliently pushing the valve body against the valve seat, and a spring clamp for holding the coil spring in a compressed state.

In addition to the structure of the safety valve unit described above, there is a means for forcibly lifting the piston body against the elastic force of the coil spring so as to release the valve body from the elasticity of the coil spring and to release the pressure of the high- .

More preferably, a pressure gauge is provided on the passage of the high-pressure fluid. The pressure gauge has a columnar pressure transfer chamber filled with sealing oil, a pressure-receiving pressure surface disposed on the ceiling surface of the pressure transfer chamber, And a capillary tube communicating with the passage of the high-pressure fluid from the upper surface of the pressure transmission chamber.

Preferably, the pressure gauge is constituted by a pressure gauge body and a pressure gauge, and the pressure transmission chamber is formed by integrating the circulating blood stuck to each of the pressure gauge body and the pressure account interconnecting portion.

The plunger pump system according to the present invention has a motor as a main component, a transmission for transmitting the power of the solenoid motor, and a plunger pump driven by a crank mechanism connected to the sun gear. The characteristic arrangement is that the motor and the transmission are stacked in the vertical direction and the output side shaft of the motor and the input side shaft of the transmission are connected by the power transmission means so that the transmission and the plunger pump are disposed adjacent to each other, Connect the crankshaft of the crank mechanism directly. Preferably, the plunger pump according to the present invention is used as the plunger pump.

In the valve device of the plunger pump according to the present invention, since the spherical valve body can be rotated, the location of contact with the valve seat is always different, so that the valve body is less damaged and its service life is prolonged. In addition, by suitably setting the width of the spherical valve body and the spherical surface portion of the valve seat to be in contact with each other, good adhesion can be obtained at the time of closing, and smooth opening and closing operation can be achieved because there is no excessive contact. And the conical portion on the outer side of the spherical portion serves as a guide of the spherical valve body.

In addition, the coupling means for contacting and connecting the rear end face of the front end plunger of the piston of the plunger pump is fixed so that it can not move with respect to the piston in the direction perpendicular to the axis, while the plunger is fixed to the plunger in the direction perpendicular to the axis Since the clearance gap is set so as to be movable, an automatic referee function can be given to the reciprocating linear motion of the plunger, and there is no shaking motion of the plunger movement.

Since the plunger chamber has an opening communicating with each of the valve devices on the side wall thereof and directly connected to the respective valve devices, there is no extra pressure transmitting space between the valve devices and there is no loss in pump efficiency.

The lubricating oil provided in the packing case for supporting the plunger discharges the lubricating oil from the downward direction and discharges the lubricating oil from the upper side so that the lubricating oil spreads freely on the main surface of the plunger and discharges the air in the event of air clogging.

When the safety valve unit reaches a predetermined pressure or more, the valve body is automatically opened against the elastic force to discharge the pressure fluid, and then returns to the closed state after the pressure is lowered.

In other words, there is an automatic return function, no parts are consumed every time it is operated. In addition, since the safety valve unit has a simple structure of the pressure release mechanism, the pressure release can be easily performed at any time.

Since the pressure gauge communicates with the high-pressure fluid passage via the capillary tube, the sealing oil of the pressure gauge does not leak into the fluid passage due to the capillary phenomenon, and at the same time, the fluid in the fluid passage does not enter the pressure gauge.

Since the plunger pump system according to the present invention is arranged so that the motor and the transmission are overlapped in the vertical direction and the transmission and the plunger pump are disposed adjacent to each other and the crankshaft of the crank mechanism of the plunger pump is directly connected to the output shaft of the transmission, And the length of the rotary conduction shaft is shortened, so that the shaft vibration is small and the transfer efficiency of the rotary motion is good. In addition, it becomes possible to store the entire pump system in the cube body.

1 is a schematic cross-sectional view of an example of a plunger pump according to the present invention for explaining an embodiment of the present invention. The crankshaft 3 of the plunger pump 100 of Fig. 1 is rotationally driven by a motor and a transmission (not shown). The crank pin 4 rotates about the crankshaft 3 and the crank pin 4 is connected to the piston pin 9 through the connecting rod 2 so that the piston pin 9 and / And the piston 8 connected thereto performs reciprocating linear motion in the piston sleeve 16. [

The plunger 18 is connected to the front end of the piston 8 via a plunger coupling 15.

The plunger coupling 15 is one of the features of the present invention and will be described in detail in Fig.

The plunger 18 is supported by the cylindrical packing case 14 around its periphery and performs reciprocating linear motion in the packing case 14 and the plunger chamber 29 in accordance with reciprocating linear motion of the piston 8 .

In this reciprocating linear motion, the plunger 18 slides against the inner wall of the packing case 14. Practical packings 33, 34 are disposed on the inner wall of the packing case 14.

The plunger chamber 29 is a circumferential space surrounded by the packing case 14, the plunger case 7, and the head case 11. The head case 11 has an opening communicating with the suction valve device 22 on the lower side and an opening communicating with the discharge valve device 23 on the upper side.

In the present invention, it is important to provide an opening in the plunger chamber 29 that directly communicates with each valve device. In the conventional general plunger pump, the space of the pressure fluid passage is provided further forward than the position of the best end of the plunger, and communicates with the respective valve devices from the space.

Installing such a useless pressure transfer space leads to a drop in pump efficiency. The size of the plunger chamber 29 in the present invention is the minimum required for the plunger 18 to reciprocate linearly, and there is no extra space at all.

As a result, extremely high pump efficiency is realized in the present invention.

Next, the configuration of the valve device will be schematically described with reference to Fig.

The discharge valve device 23 includes a spherical valve body 28 (hereinafter referred to as a "belt ball") provided in the valve chamber 27 and a valve seat 24 having a spherical surface corresponding to the valve ball 28 A valve spring 26 on the coil for pushing and supporting the valve ball 28 against the valve seat 24, and a practical packing 46. The valve ball 28 and the valve seat 24 are all made of metal such as stainless steel.

The metal packing 46 is preferably made of a relatively flexible metal such as copper, brass or aluminum.

The suction valve device 22 also has the same configuration as that of the discharge valve device 23 although the installation direction is reversed.

In the present invention, in the valve device part, the elastic material is not included at all. The resilient material is insufficient in durability in the movable portion or the pressure fluctuation portion of the high-pressure pump and is damaged early, so frequent replacement is necessary.

The suction port is denoted by reference numeral 51, and the discharge port is denoted by reference numeral 52. In this example, all of the hoses are connected so as to be perpendicular to the paper surface. The positions of the inlet and outlet are arbitrary

2 is a view showing the shape of a valve ball and a valve seat of a valve device according to the present invention. Fig. 2 (A) is a longitudinal sectional view of the valve seat 24. Fig. The valve seat 24 is substantially cylindrical in shape with a fluid passage 25 provided at its center. Sheet surfaces 24a and 24b are formed on the inner edge of the cylindrical cross section of the valve seat 24. [

In the illustrated example, since the seat surfaces are provided at both ends of the valve seat 24, the valve seat can be reversed.

The seat surface of the city has a spherical surface portion 24a provided on the inner side and a conical surface portion 24b provided on the outer side.

Fig. 2B is an enlarged cross-sectional view of the seat surfaces 24a and 24b of the valve seat 24 in Fig. 2 (A). The dashed line represents the contour of the valve ball 28 of the sphere and the dashed line represents the radius thereof. The radius of curvature of the spherical surface portion 24a of the seat surface coincides with the radius R of the valve ball 28. [ In addition, the width, that is, the length of the cross-section of the arc of the spherical portion (24a) is preferably the central angle of a circular arc is in the range of ^{50-20 0.}

If the width of the spherical portion 24a is smaller than this, the contact with the valve ball 28 is substantially in line contact with the conical valve seat. In the case of line contact, the valve ball and the valve seat are liable to be damaged in a short period of time because they are weak in impact resistance. If they are damaged, the airtightness is lost and the efficiency of the pump is lowered. Therefore, spherical contact is preferable in terms of impact resistance. On the other hand, if the width of the spherical portion 24a is wider than the above-mentioned preferable range, the adhesion between the valve ball and the valve seat becomes excessively strong, so that the phenomenon that the valve ball and the valve seat are attracted to each other does not occur. As a result, the opening and closing operation is not smoothly performed.

Therefore, even if the width of the spherical surface portion 24a is too wide, it is inappropriate.

Conventionally, there is a valve device by spherical contact, but the proper width of the contact surface is not considered. In the present invention, the preferable contact surface range of the spherical contact valve device in the plunger pump for high-pressure fluid is first proposed.

Another advantage of the valve ball is that it does not come into contact with the valve seat on the same plane at all times because the ball is electrically movable, and that the other surface contacts the valve seat every time it is opened or closed.

This prevents damage to the valve ball and significantly extends its service life. In this respect, the valve ball of the present invention is superior to a valve body having a partial spherical surface.

The conical surface portion 24b from the upper end to the open end of the spherical portion 24a serves as a guide for the valve ball 28. [ In other words, when the valve ball 28 slightly deviates from the central axis of the valve seat 24, it acts to return it to the center position.

2 (C) and 2 (D) show another embodiment of the valve seat of the present invention. 2 (C), the spherical portion 24a is located on the outer side and the conical portion 24b is located on the inner side. In this case, since the conical surface portion 24b is present in the fluid passage, the flow of the fluid is more smoothly performed.

2 (D) shows an example in which only the spherical portion 24a is provided.

Of course, the width of the spherical portion of these embodiments is set within the above preferable range.

3 is an enlarged cross-sectional view showing the plunger coupling 15 connecting the piston 8 and the plunger 18 shown in Fig. A contact portion 8a is provided at the distal end of the piston 8 via a constricted portion 8b and the flat front surface of the contact portion 8a serves as the contact surface. The contact portion 18a is provided at the rear end of the plunger 18 via the constricted portion 18b and the flat rear surface of the contact portion 18a is the contact surface. The coupling 15 is a connecting part which is composed of two half halves which divide the approximately cylindrical shape into two halves and faces the halves to face each other to cover and fix the connection object.

When the piston 8 and the plunger 18 are connected to each other, the abutting surfaces of the abutting portions 8a and 18a are brought into contact with each other so as to face each other, And the coupling 15 is fixed with a suitable bolt or the like. As a result, the piston 8 and the plunger 18 are fixed so as not to move with respect to each other in the axial direction.

The important point in Fig. 3 is that the contact portion 18a and the cervical portion 18b of the plunger 18 and the couple 18b of the plunger 18 are fixed to each other while the gap between the neck portion 8b of the piston 8 and the coupling 15 is fixed, And a clearance (indicated by an oblique line) as a clearance is set between the rings 15. That is, the piston 8 and the coupling 15 are fixed so as not to move with respect to each other in a direction perpendicular to the axis, but the plunger 18 and the coupling 15 are movable in a direction perpendicular to the axis, .

By this clearance, the plunger 18 is provided with an automatic cleaner for self-correcting when the axis tends to tilt, thereby ensuring that the reciprocating linear motion without shaking is performed.

In the conventional plunger pump, attention has been paid to securely fix the plunger so that the axis of the plunger coincides with the axis of the plunger to prevent the plunger from shaking. However, even if it is firmly fixed, it is impossible to completely eliminate the shaking motion of the plunger which is exposed to violent vibration at the time of operation.

For this reason, in the conventional plunger pump, it is necessary to set a clearance of a certain degree between the plunger 18 and the packing case 14, taking into consideration that the axis of the plunger is inclined. As a result, in the conventional packing case, at least five to six packings are required in order to ensure airtightness. As a result, the friction of the plunger also increases, and the packing case also becomes larger. In addition, there was a major drawback in cement slurry pressurization that the cement particles were liable to squeeze between the plunger and the packing case.

In the present invention, by completely reversing the configuration, the connection portion of the plunger is not completely fixed, but rather has room for automatic maintenance. Therefore, in the present invention, it is not necessary to set a clearance between the plunger 18 and the packing case 14, and the minimum necessary sliding fit is sufficient. As a result, according to the present invention, when one to three or more packings are arranged in the packing case 14, the packing case can be miniaturized since the sealing property is sufficiently obtained, and also the prevention of the penetration of the cement particles into the gap between the plunger and the packing case It has a great effect. Further, in the present invention, there is no fear that the plunger will be worn out due to the cemented particles introduced therein, so that damage to the plunger can be avoided and the service life is remarkably prolonged. In addition, since there is no damage caused by cement solidification, the decomposition becomes extremely easy.

3 shows a more useful mechanism of the plunger pump of the present invention.

Lubricating oil openings 36a and 36b are provided at upper and lower portions of the packing case 14, respectively. The lubricating oil is supplied from the lower lubricating oil port 36a to wet the entire circumferential surface of the plunger 18 and is discharged from the lubricating oil port 36b. Preferably, the lubricating oil is circulated as indicated by the dotted line to be used without leaving.

The conventional supply of lubricating oil is known from a dropping type or a grease pump type from the upper side. In this way, it can not be guaranteed that the lubricating oil is supplied to the rolling surface of the plunger. Furthermore, where lubrication oil can not be reached, air entrainment is likely to occur.

Poor efficiency of the pump drops when air is introduced into the plunger chamber.

In addition, the plunger main surface of the portion where the lubricant does not reach is liable to be damaged, and when the plunger is damaged, the lubricant may leak into the plunger chamber.

In the method of supplying lubricating oil according to the present invention, since the lubricating oil moves from the bottom to the top, it is difficult for the lubricating oil to be poured into the air, and the piled air can be surely pushed upward.

4 is a cross-sectional view showing a safety valve unit 60 provided in the plunger pump according to the present invention. The safety valve unit 60 is suitably installed, for example, on a high-pressure fluid passage communicating with the discharge port 52 of Fig. The safety valve unit used in the conventional plunger pump is a method in which the pin is broken at a predetermined pressure or more, so that the pin has to be replaced each time the safety valve unit is operated. On the contrary, the present invention realizes a novel safety valve unit capable of automatic return.

Fig. 4 shows that the safety valve unit 60 is fixed to the arbitrary place of the high-pressure fluid passage by the fitting bolt 69 of the approximately cylindrical safety valve unit housing 61. Fig. The housing 61 is provided with a valve seat 65, a spherical valve ball 64, an actual piston 63 disposed on the valve ball 64, and a coil spring 66). A ring 70 is disposed between the seal piston 66 and the inner wall of the housing to prevent fluid leakage. The spring clamp 62, which also serves as a lid of the housing 61, holds the coil spring 66 in a compressed state. The coil spring 66 resiliently presses the valve ball 64 against the valve seat 65 via the seal piston 63.

The valve seat 65 is provided via a fitting packing 71 and communicates with the high-pressure fluid passage of the through hole 72 of the valve seat 65. On the other hand, a discharge port 73 is provided in the valve chamber 74 in which the valve ball 64 is housed. When the pressure of the high-pressure fluid is higher than a predetermined value, the coil spring 66 opposes the valve ball 64 The open high-pressure fluid is discharged from the discharge port 73 and the pressure is lowered.

The safety valve unit 60 according to the present invention is an automatic return type unlike the conventional one, and does not require replacement of parts.

The safety valve unit 60 of the present invention shown in Fig. 4 also has a manual pressure release mechanism. The pressure release balloon 67 is fixed to the screw hole on the upper surface of the thread piston 63 through the through hole of the spring clamp 62. When the pressure is forcibly released, the pressure releasing nut 68 is rotated to move the pressure releasing bolt 67 upward. Then, the thread piston 63 together with the pressure releasing bolt 67 is raised against the coil spring 66.

Thus, the valve ball 64 is released from the elastic force of the coil spring 66, and the pressure in the high-pressure fluid passage opens the valve ball 64 to release the pressure.

5 is a diagram showing a novel pressure gauge structure provided in the plunger pump according to the present invention. 5 (A) shows a method of installing the pressure gauge body 88 using two kinds of pressure accounts. The flange pressure account 81 located on the right side of the opposite side is fixed to the pump body by bolts or the like and the screwed pressure account 80 on the left side is directly fixed to the screw hole of the pump body. The pressure gauge body 88 is screwed on the upper surfaces of the respective pressure accounts 80 and 81. Pressure transfer chambers 83 are formed in all the pressure accounts.

The upper surface side of the pressure transmission type 83 communicates with the fluid passage 54 and the pressure side surface 85 of the detection mechanism of the pressure gauge body 88 is exposed on the ceiling surface side. The pressure in the fluid passage 54 is transmitted to the pressure receiving surface 85 of the pressure gauge via the pressure transfer chamber 83.

5 (B) is an enlarged cross-sectional view showing in detail the structure of the connecting portion of the pressure gauge body 88 and the pressure accounts 80, 81 shown in Fig. 5 (A). The pressure accounts 80 and 81 are provided with a screw hole 89a for body fitting on the upper end surface and a circular blood 83a extending further downward from the bottom center of the screw hole 89a.

Further, a capillary tube 82 is provided on the upper surface of the primary blood 83a so as to pass through the lower end surface of the pressure vessel.

On the other hand, the pressure gauge main body 88 is also provided with a circumferential blood 83b extending upward from the lower end surface of the fitting screw 89b.

A pressure sensing surface 85 for pressure sensing is provided on the top surface of the circular stamen 83b. 5B shows a state in which the fitting thread 89b of the pressure gauge body 88 is inserted or screwed into the fitting thread hole 89a of the pressure accounts 80 and 81. As shown in Fig. At this time, both the circular blood spots 83a and 83b are combined to form a circumferential pressure transmission chamber 83. [ A packing 84 is disposed between the pressure gauge body 88 and the pressure accounts 80, 81.

The pressure transmission chamber 83 is filled with a sealing oil. It is important to fill the sealing oil so that air is not contained in the pressure-transmitting chamber 83 in order to accurately perform the pressure measurement.

The pressure transfer chamber 83 and the fluid passage 54 communicate with each other via the capillary tube 82 when the pressure account is installed on the fluid passage 54. [

The capillary tube 82 is a tube having a narrow inner diameter enough to be recognized as capillary phenomenon (or capillary shape). By installing this capillary tube 82, the sealing oil in the pressure transmission chamber 83 does not leak into the fluid passage 54 due to the capillary phenomenon. At the same time, penetration of the fluid into the pressure gauge is also prevented. Reference numeral 86 denotes a contact surface between the fluid and the sealing oil.

In the conventional pressure gauge, the pressure fluid tends to penetrate into the pressure gauge. Particularly, when the fluid contains cement particles, the pressure gauge breaks down due to the penetration and solidification of the pressure gauge. In the pressure gauge of the present invention, such a problem is solved, and the life of the pressure gauge is prolonged and workability can be improved.

The structure of the safety valve unit shown in Fig. 4 and the pressure gauge shown in Fig. 5 show a great effect by providing a plunger pump or the like when the cement slurry or the like is made of a high-pressure fluid, but it is needless to say that it can be widely used for other uses .

6 is a diagram showing a preferred arrangement of the plunger pump system according to the present invention. 6 (A) is a schematic side cross-sectional view of the plunger pump system 200. Fig. The main components of the plunger pump system are the motor 110, the transmission 120 and the plunger pump 100, and all the components are housed in the housing 130. A transmission 120 is disposed immediately below the motor 100 and a power transmission belt or the like is interposed between the motor shaft 112 and the transmission shaft 122 to transmit power. The transmission 120 and the crankcase of the plunger pump 100 are disposed adjacent to each other and the output shaft of the transmission 120 is directly connected to the crankshaft 3 of the plunger pump 100. [ Reference numeral 6 denotes a crankcase cover. 6 (A), the plunger, the suction port 51 and the discharge port 52 are located immediately in front.

6 (B) is a schematic plan view of the plunger pump system 200 of Fig. 6 (A) viewed from above. The plunger pump 100 shown in FIG. 3 is of a three-stage type and has three plungers 18.

An oil pump 150 for lubricating oil circulation is mounted on the crankcase cover of the plunger pump 100 and a lubricating oil tank 151 is disposed in front of the crankcase.

Since the motor 110 and the transmission 120 are stacked in the vertical direction, only the shaft 122 of the transmission 120 is visible. 6B shows a control unit 140 installed at one corner of the housing 130. As shown in Fig. The control unit 140 controls the operation of the entire plunger pump system 200 and the operation lamp is disposed on the outer surface of the housing 130 corresponding to the control unit 140.

As shown in Fig. 6, in the present invention, by arranging the components of the plunger pump system three-dimensionally, the entire device is compactly stored in the cube-shaped body. As a result, the extra connecting parts interposed between the respective components can be omitted.

Conventionally, it has been common to connect the rotating shafts of a motor, a transmission, and a plunger pump in series, and there are many extra connecting parts. As a result, the rotational transmission shaft becomes long and the loss becomes large, and at the same time, the shaft shrinkage and the failure are likely to occur. Also, vibration, noise, and overall device size

(Example)

Table 2 shows one embodiment of the entire plunger pump and the pump system according to the present invention. Comparing this embodiment with the conventional example shown in Table 1, it is clear that the efficiency of the plunger pump according to the present invention is extremely high and the entire system is also small and lightweight.

[Table 2]

Plunger stroke .... 90mm

Plunger ... diameter 50mm 3 patterns (3 stations)

Maximum discharge pressure ... 400 kgf / cm ²

Maximum discharge rate .... 130 liters / minute

Inhalation aperture ... 2 inches

Discharge aperture .... 3/4 inch

Motor power ... 55kw

Outer dimension of whole pump system. W 1200mm × L 1200mm × H 1500mm

Overall weight of pump system ... 1300kg

Operation example ... Pressure 400 kg / cm ² ... Discharge amount 80 liter / minute

Pressure 350 kg / cm ² ... Discharge amount 90 liters / minute

Pressure 300kg / cm ² ... Discharge amount 105 liters / minute

Pressure 250 kg / cm ² ... Discharge 130 l / min

In the valve device according to the present invention, since the spherical contact with the valve seat is realized by using the specific valve, reliable opening and closing of the valve device is ensured, and durability is improved, . This has relieved frequent part replacement work.

Further, in the plunger pump of the present invention, the plunger having the self-aligning mechanism is realized by a simple structure, and the straightness of the plunger is ensured. As a result, the extra space around the plunger is eliminated and practical parts can be reduced. Furthermore, penetration of the cement particles into the plunger portion is also prevented. The air is also excluded by circulating the lubricant from the bottom up. In addition, the plunger chamber and valve chamber are directly connected. As a result, the pump efficiency of the plunger pump is improved, and the burden on the parts due to the cement particles and the replacement work is reduced. The frequency of replacement of the parts of the plunger pump of the present invention is much smaller than that of the prior art, and the disassembly is extremely easy.

The safety valve mechanism mounted on the plunger pump also has a pressure relief function, which eliminates the need for component replacement. Similarly, in the pressure gauge mechanism, the prevention of the intrusion of the cement particles was realized, and the reliability, durability and workability were improved.

By using them together, the durability and workability of the plunger pump and the entire pump system are further improved.

In the plunger pump system according to the present invention, the main components are arranged in an extremely compact manner, and the rotation transmission shaft between the components is also shortened as much as possible, thereby reducing redundant connection parts. This realizes the small size and light weight of the entire plunger pump system, improving the transportation and installation of the pump system, and achieving low noise and low vibration.

As described above, the present invention provides a plunger pump and pump system that is far superior to the prior art, and provides great benefits in its application.

Claims (11)

A plunger driven by a reciprocating linear motion, a plunger connected to the front of the piston, a plunger chamber for performing reciprocating linear motion, A plunger pump comprising: a valve body provided with a spherical valve body, a cylindrical valve seat, and a valve body provided on both the suction side and the discharge side of the plunger chamber, Wherein a seat surface provided on the inner circumference of the cylindrical end surface of the valve seat has a spherical surface portion having a curvature equivalent to that of the valve element to accommodate the valve element, To 20% by weight of the plunger. The plunger pump according to claim 1, further comprising a conical surface portion adjacent to and outside the spherical surface portion of the valve seat. A piston driven by a crank mechanism for converting a rotary motion into a reciprocating linear motion for feeding the high-pressure fluid; a rod-like plunger connected to the front of the piston; a plunger chamber for reciprocating linear motion of the plunger; A plunger pump comprising a valve device installed on a suction side and a discharge side of a seal, the plunger comprising: a coupling means for connecting the front end surface of the piston and the rear end surface of the plunger so that they can not move in the axial direction, Wherein the piston and the coupling means are fixed such that they can not move relative to each other in a direction perpendicular to the axis, while the plunger and the coupling means are arranged in such a way that the gap And the plunger pump is installed. A piston driven by a crank mechanism for converting a rotational motion into a reciprocating linear motion for pressurizing the high-pressure fluid; a plunger in the form of a rod connected to the front of the piston; a plunger chamber for reciprocating linear motion of the plunger; Wherein the plunger chamber is formed as a cylindrical space, and an opening communicating with each of the electric valve devices is formed in the sidewall of the cylindrical space of the plunger chamber, Wherein the plunger pump is provided with a plunger pump. A piston driven by a crank mechanism for converting a rotary motion into a reciprocating linear motion for feeding the high-pressure fluid; a rod-like plunger connected to the front of the piston; a plunger chamber for reciprocating linear motion of the plunger; A plunger pump comprising a valve device installed on a suction side and a discharge side of a seal, the plunger having a packing case supporting the plunger and having a practical packing, the main surface of the plunger being, when reciprocatingly linear, Wherein a lubricating oil supply port is provided on the lower side of the inner wall of the packing case and a lubricating oil discharge port is provided on the upper side of the packing case so as to slide on the inner wall of the case and to supply lubricating oil to the main surface of the plunger. A piston driven by a crank mechanism for converting a rotary motion into a reciprocating linear motion for feeding the high-pressure fluid; a rod-like plunger connected to the front of the piston; a plunger chamber for reciprocating linear motion of the plunger; And a valve device provided on a suction side and a discharge side of the seal, wherein the safety valve unit is provided on the passage of the high-pressure fluid, and the safety valve unit is fixed on the passage of the high- A valve seat having a spherical valve body provided in the valve chamber in the housing, and a communication hole communicating with the passage of the high-pressure fluid while accommodating the valve body; A piston body disposed on the valve body, the piston body being disposed on the piston body; A coil spring for resiliently pushing the valve body to the valve seat via a piston body, and a spring clamp for holding the coil spring in a compressed state. 7. The valve apparatus according to claim 6, wherein the valve body of the safety valve unit is released from the elastic force of the coil spring to release the pressure of the high-pressure fluid passage, The plunger pump having means for lifting the plunger to the plunger. A piston driven by a crank mechanism that changes its rotational motion into reciprocating linear motion to pressurize the high-pressure fluid, a rod-like plunger connected to the front of the piston, a plunger chamber in which the plunger performs reciprocating linear motion, And a valve device provided on a suction side and a discharge side of the pressure chamber, respectively, wherein the plunger pump has a pressure gauge installed on a passage of the high-pressure fluid, the pressure gauge being filled with sealing oil, A pressure sensing surface for pressure detection disposed on the ceiling surface of the transfer chamber and a capillary tube communicating with the high pressure fluid passage from the upper surface of the pressure transmission chamber. A piston driven by a crank mechanism for converting a rotary motion into reciprocating linear motion for pressurizing the high-pressure fluid, a plunger in the form of a rod connected to the front of the piston, a plunger chamber for reciprocating linear motion of the electric plunger, A plunger pump comprising a valve device provided on a suction side and a discharge side of a plunger chamber, wherein a pressure gauge made up of a pressure gauge body and a pressure gauge is provided on the passage of the high-pressure fluid, A pressure transmission chamber formed in the mutual connection portion of the pressure chambers, the pressure transmission chamber being formed by merging the circumferential cylinders respectively formed in the mutual connection portions of the pressure chambers, the sealing oil filled in the pressure transmission chambers, the pressure receiving surface disposed on the ceiling surface of the pressure transmission chambers, And a capillary tube communicating with the high-pressure fluid passage from an upper surface of the pressure transmission chamber. A plunger pump system comprising a motor, a transmission for transmitting power of a sun gear, and a plunger pump driven by a crank mechanism connected to the sun gear, wherein the motor and the transmission are arranged in a stacked manner in a vertical direction, Wherein the output side shaft and the input side shaft of the transmission are connected by power transmission means so that the transmission and the plunger pump are disposed adjacent to each other so that the output shaft of the transmission and the crankshaft of the crank mechanism are directly connected. Pump system. The plunger pump system according to claim 10, wherein the plunger pump is the plunger pump according to any one of claims 1 to 9.