CN108468640B - High-speed distributing valve of emulsion pump - Google Patents
High-speed distributing valve of emulsion pump Download PDFInfo
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- CN108468640B CN108468640B CN201810303949.7A CN201810303949A CN108468640B CN 108468640 B CN108468640 B CN 108468640B CN 201810303949 A CN201810303949 A CN 201810303949A CN 108468640 B CN108468640 B CN 108468640B
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- valve
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- guide sleeve
- core
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- 239000000839 emulsion Substances 0.000 title claims abstract description 34
- 239000007788 liquid Substances 0.000 claims abstract description 85
- 239000004696 Poly ether ether ketone Substances 0.000 claims description 2
- JUPQTSLXMOCDHR-UHFFFAOYSA-N benzene-1,4-diol;bis(4-fluorophenyl)methanone Chemical compound OC1=CC=C(O)C=C1.C1=CC(F)=CC=C1C(=O)C1=CC=C(F)C=C1 JUPQTSLXMOCDHR-UHFFFAOYSA-N 0.000 claims description 2
- 239000000463 material Substances 0.000 claims description 2
- 229920002530 polyetherether ketone Polymers 0.000 claims description 2
- 239000011162 core material Substances 0.000 description 76
- 238000005213 imbibition Methods 0.000 description 5
- 230000002035 prolonged effect Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 230000003139 buffering effect Effects 0.000 description 2
- 239000003638 chemical reducing agent Substances 0.000 description 2
- 239000003245 coal Substances 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000005065 mining Methods 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Valves (AREA)
- Lift Valve (AREA)
Abstract
The invention belongs to the technical field of hydraulic valves, and particularly relates to a high-speed distributing valve of an emulsion pump. The emulsion pump comprises a shell, wherein a plunger cavity T is arranged in the shell, two ends of the plunger cavity T are respectively connected with a liquid suction valve I and a liquid discharge valve II, the liquid suction valve I comprises a sleeve, a guide sleeve, a valve core, a valve seat and a spring, the two ends of the sleeve are respectively provided with the guide sleeve and the valve seat, the guide sleeve is internally provided with the valve core, the outer side of the valve core is sleeved with the spring, the outer end part of the valve core is in contact with the valve seat, the outer end part of the valve core is in a streamline structure, the guide sleeve end of the liquid suction valve I is communicated with the plunger cavity T, and the valve seat end of the liquid suction valve I is an oil inlet P; the liquid discharge valve II and the liquid inlet valve I have the same structure, the valve seat end of the liquid discharge valve II is communicated with the plunger cavity T, and the guide sleeve end of the liquid discharge valve II is an oil return port O. The invention adopts a specific streamline shape to reduce hydraulic resistance, cavitation and cavitation, greatly prolongs the service life of the valve, and has the response frequency of 25Hz.
Description
Technical Field
The invention belongs to the technical field of hydraulic valves, and particularly relates to a high-speed distributing valve of an emulsion pump.
Background
At present, most underground coal mine fully-mechanized coal mining equipment takes emulsion as a medium, an emulsion pump is power equipment for conveying pressure liquid for a hydraulic support, the rotation speed of the emulsion pump is 500-600 r/min, and the emulsion pump is driven to operate by a motor with the rotation speed of 1500r/min through a gear reducer; the existing new emulsion pump design is to remove a gear reducer, directly drive a pump to operate by a motor, the rotating speed of the pump can reach 1500r/min, the emulsion pump needs a high-speed valve with the frequency of 25Hz to control, the accurate control of the valve is the key of the normal operation of the pump, and the response frequency of the valve is very high and the medium is emulsion, so that the requirements on the quality requirement of a valve core, the structure of the valve core, the service life of the valve core and the like can be correspondingly improved, and the internal valve core of the valve is a great key problem for overcoming the liquid resistance in the moving process.
The basic structure of the existing valve is shown in fig. 1, the valve core is a cone valve and is in surface contact with the valve seat, the bottom of the valve core is of a tripod structure, and the reasons that the valve cannot be used for an emulsion pump matched with the design are as follows:
(1) The highest response frequency of the check valve is generally 500-600 times per minute, and the rotating speed of the emulsion pump matched with the design is up to 1500r/min, which is the most main reason for carrying out the design;
(2) The valve core structure of the valve is of an inverted cone structure, when the valve is opened, emulsion enters, air pockets and vortexes are easy to form around the valve core, and the valve core opening resistance is increased;
(3) The bottom of the valve is of a tripod structure, the bottoms of other types of cone valves are of flat plates, the valve core is easier to impact when liquid flows in, the instability of liquid flow is caused, and the tripod structure reduces the impact, but influences the liquid flow;
(4) The valve core of the valve is generally made of stainless steel materials, so that the valve core has heavier mass, the movement speed of the valve core is further influenced, and the response frequency of the valve is greatly influenced;
(5) For all hydraulic valves, the service life of the valve is one of the most critical problems, the service life of the valve depends on the service life of a valve core to a great extent, and when the valve is closed, the valve core and a valve seat are contacted by great impact force to cause great damage to the valve core and the valve seat, so that the service life of the valve is influenced.
Therefore, a high-speed distributing valve suitable for an emulsion pump running at high speed is required to be invented, and the invention provides a novel high-speed distributing valve.
Disclosure of Invention
The invention provides a high-speed distributing valve of an emulsion pump, which aims to solve the problem of accurately controlling the emulsion pump running at a high speed.
The invention adopts the following technical scheme: the high-speed flow distribution valve of the emulsion pump comprises a shell, wherein a plunger cavity T is arranged in the shell, two ends of the plunger cavity T are respectively connected with a liquid suction valve I and a liquid discharge valve II, the liquid suction valve I comprises a sleeve, a guide sleeve, a valve core, a valve seat and a spring, the two ends of the sleeve are respectively provided with the guide sleeve and the valve seat, the guide sleeve is internally provided with the valve core, the outer side of the valve core is sleeved with the spring, the outer end part of the valve core is in contact with the valve seat, the outer end part of the valve core is of a streamline structure, the guide sleeve end of the liquid suction valve I is communicated with the plunger cavity T, and the valve seat end of the liquid suction valve I is an oil inlet P; the liquid discharge valve II and the liquid inlet valve I have the same structure, the valve seat end of the liquid discharge valve II is communicated with the plunger cavity T, and the guide sleeve end of the liquid discharge valve II is an oil return port O.
Further, the streamline structure comprises a curve section a, a curve section b and a curve section c, wherein the curve section a comprises O 5 Circular arcs with the center of a circle and the radius of 5mm are respectively represented by O 1 And O 2 Two sections of circular arcs with the radius of 17mm are used as circle centers; curve segment b comprises two segments respectively denoted by O 6 And O 9 An arc section with the center of a circle and the radius of 4 mm; the curve section c comprises two symmetrical curves, one of which comprises the curve represented by O 3 Arc with radius of 25mm as circle center and O 7 Is tangent to an arc with the center and the radius of 5 mm; another curve is represented by O 4 Arc with circle center and radius of 25mm and O 8 Is a circle center and is tangential with an arc with the radius of 5 mm; wherein the centers of the three circular arcs of the curve section a are intersected with a point O, and the centers of the two circular arcs of the curve section b are intersected with OO 5 One point O' on the extension line, the circle centers of the 4 circular arcs of the curve section c are all intersected with the point O 5 And the center of circle O 1 With O 2 、O 3 With O 4 、O 7 With O 8 、O 6 With O 9 Symmetric about line OO 'and its extension, point O, O', O 5 Are all on the central symmetry line of the valve core, and the circle center O 5 5mm from the bottom of the valve core, with O 5 Is the origin of coordinates, i.e. O 5 (0, 0), the remaining center coordinates are: o (0, 10), O' (0, 18), O 1 (-15，-16),O 2 (15，-16),O 3 (35，40),O 4 (-35，-40),O 7 (22，13),O 8 (-22,13)，O 6 (19，6),O 9 (-19, 6), (unit: mm), the hydraulic resistance of the liquid is minimal and cavitation formation is minimal when the three curves meet the above conditions. The specific streamline structure enables the liquid to flow more smoothly, the liquid resistance is reduced, cavitation and cavitation generated are also minimum, and the service life of the valve core is prolonged; the curve section a enables liquid to form a jet shape in advance, so that vibration and noise caused by cavitation caused by sudden thinning of a flow beam when the liquid flows into a valve port are reduced; when the curve section c makes the liquid flow, the friction between the liquid and the valve core wall surface and the friction between the liquid are reduced, so that the on-way resistance of the liquid flow is reduced, the vortex formed around the valve core is also minimized, the opening and closing of the valve are more timely, and the control is more accurate.
Further, a gap with an angle of 13 degrees is arranged between the contact surfaces of the valve core and the valve seat. The function is as follows: when the valve is closed, the liquid flow in the gap plays a certain buffering role on the valve core, so that the speed of the valve core is reduced, the impact load on the valve core is reduced, and the service life of the valve core is prolonged.
Further, one end of the valve core inserted in the guide sleeve is of a long rod structure, and the length of the long rod is 1/2 of the length of the whole valve core.
Further, the natural frequency of the valve core hydraulic pressure is 25Hz.
For the imbibition valve I, before the imbibition valve is opened, the plunger cavity is vacuum, the low-pressure emulsion connected with the imbibition port makes the valve core move upwards against the spring force and self gravity under the action of atmospheric pressure, the valve port is opened, the low-pressure emulsion enters the plunger cavity through the imbibition valve, and imbibition work is completed; after the liquid suction work is finished, the spring is increased due to the compression spring force, and the valve core moves downwards under the action of the spring force, so that the valve port is closed, and in the closing process, the speed of the valve core is reduced to reduce the impact when the valve core is about to be closed due to a certain gap left between the valve core and the valve seat.
For the liquid discharge valve II, when the plunger moves upwards, the volume of a plunger cavity is continuously reduced, the hydraulic pressure in the cavity is continuously increased, when the hydraulic pressure is larger than the spring force of the liquid discharge valve, the valve core moves downwards against the spring force, the valve port is opened, high-pressure emulsion in the working cavity is discharged through the liquid discharge valve, and the high-pressure emulsion is supplied to hydraulic equipment; when the hydraulic pressure of the plunger cavity is smaller than the spring force, the valve core moves upwards under the action of the spring force, so that the valve port is closed, and similarly, the speed of the valve core is reduced when the valve is closed, and the impact is reduced.
For an emulsion pump, a motor drives a crankshaft to rotate, the crankshaft drives a five-star wheel to rotate through an eccentric wheel, the five-star wheel pushes 5 plungers to reciprocate up and down in a plunger cavity, vacuum is arranged in the cavity when the plungers start to move downwards, a liquid suction valve is opened by low-pressure emulsion under the action of atmospheric pressure, liquid suction work is started, meanwhile, the plungers continuously move downwards, when a spring of the liquid suction valve is compressed to a certain degree, a valve core moves downwards under the action of the spring force, the liquid suction valve is closed, the liquid suction work is completed, and at the moment, the plungers reach the lower limit position. When the plunger moves upwards, the volume of the plunger cavity is continuously reduced, the hydraulic pressure in the cavity is continuously increased, when the hydraulic pressure is larger than the spring force of the liquid suction valve, the liquid suction valve is opened, high-pressure emulsion starts to be discharged and supplied to hydraulic equipment, after the high-pressure emulsion is discharged, the plunger reaches an upper limit position and starts to move downwards, when the plunger moves downwards, vacuum is formed in the plunger cavity, the liquid suction valve is closed under the action of the spring force, the liquid suction valve starts to suck liquid again, and a new cycle starts. In this way, the emulsion pump continuously provides high-pressure emulsion outwards under the control of the motor and the valve.
Compared with the prior art, the invention has the beneficial effects that: the valve core material of the valve adopts PEEK to reduce the mass of the valve core, the structure adopts a specific streamline shape to reduce hydraulic resistance, cavitation and cavitation, a specific gap of 13 degrees is reserved between the valve seat and the valve core to reduce the impact load born by the valve core, the service life of the valve is prolonged to a great extent, and the response frequency of the valve reaches 25Hz.
Drawings
FIG. 1 is a schematic diagram of the structure of the present invention;
FIG. 2 is an enlarged view of a portion of the contact area of the valve core with the valve seat;
FIG. 3 is an enlarged view of the valve core structure;
in the figure, the valve comprises a 1-shell, a 2-sleeve, a 3-guide sleeve, a 4-spring, a 5-valve core and a 6-valve seat.
Detailed Description
The high-speed flow distribution valve of the emulsion pump comprises a shell 1, wherein a plunger cavity T is arranged in the shell 1, two ends of the plunger cavity T are respectively connected with a liquid suction valve I and a liquid discharge valve II, the liquid suction valve I comprises a sleeve 2, a guide sleeve 3, a valve core 5, a valve seat 6 and a spring 4, the two ends of the sleeve 2 are respectively provided with the guide sleeve 3 and the valve seat 6, the valve core 5 is arranged in the guide sleeve 3, the spring 4 is sleeved outside the valve core 5, the outer end part of the valve core 5 is in contact with the valve seat 6, the outer end part of the valve core is of a streamline structure, the guide sleeve end of the liquid suction valve I is communicated with the plunger cavity T, and the valve seat end of the liquid suction valve I is an oil inlet P; the liquid discharge valve II and the liquid inlet valve I have the same structure, the valve seat end of the liquid discharge valve II is communicated with the plunger cavity T, and the guide sleeve end of the liquid discharge valve II is an oil return port O.
The streamline structure comprises a curve section a, a curve section b and a curve section c, wherein the curve section a comprises O 5 Circular arcs with the center of a circle and the radius of 5mm are respectively represented by O 1 And O 2 Two sections of circular arcs with the radius of 17mm are used as circle centers; curve segment b comprises two segments respectively denoted by O 6 And O 9 An arc section with the center of a circle and the radius of 4 mm; the curve section c comprises two symmetrical curves, one of which comprises the curve represented by O 3 Arc with radius of 25mm as circle center and O 7 Is tangent to an arc with the center and the radius of 5 mm; another curve is represented by O 4 Arc with circle center and radius of 25mm and O 8 Is a circle center and is tangential with an arc with the radius of 5 mm; wherein the centers of the three circular arcs of the curve section a are intersected with a point O, and the centers of the two circular arcs of the curve section b are intersected with OO 5 One point O' on the extension line, the circle centers of the 4 circular arcs of the curve section c are all intersected with the point O 5 And the center of circle O 1 With O 2 、O 3 With O 4 、O 7 With O 8 、O 6 With O 9 Symmetric about line OO 'and its extension, point O, O', O 5 Are all on the central symmetry line of the valve core, and the circle center O 5 5mm from the bottom of the valve core, with O 5 Is the origin of coordinates, i.e. O 5 (0, 0), the remaining center coordinates are: o (0, 10), O' (0, 18), O 1 (-15，-16),O 2 (15，-16),O 3 (35，40),O 4 (-35，-40),O 7 (22，13),O 8 (-22,13)，O 6 (19，6),O 9 (-19, 6), (unit: mm), the hydraulic resistance of the liquid is minimal and cavitation formation is minimal when the three curves meet the above conditions. The specific streamline structure enables the liquid to flow more smoothly, the liquid resistance is reduced, cavitation and cavitation generated are also minimum, and the service life of the valve core is prolonged; the curve section a enables liquid to form a jet shape in advance, so that vibration and noise caused by cavitation caused by sudden thinning of a flow beam when the liquid flows into a valve port are reduced; when the curve section c makes the liquid flow, the friction between the liquid and the valve core wall surface and the friction between the liquid are reduced, so that the on-way resistance of the liquid flow is reduced, the vortex formed around the valve core is also minimized, the opening and closing of the valve are more timely, and the control is more accurate.
A gap with an angle of 13 degrees is arranged between the contact surfaces of the valve core 5 and the valve seat 6.
One end of the valve core 5 inserted into the guide sleeve 3 is of a long rod structure, and the length of the long rod is 1/2 of the length of the whole valve core 5. The natural frequency of the valve core 5 is 25Hz.
The specific gap between the valve seat and the valve core provided by the invention is shown in fig. 2, and in a contact area between the valve core and the valve seat, the angle between the surface A of the valve core and the surface B of the valve seat is 13 degrees, and the specific gap has the following functions: when the valve is closed, the liquid flow in the gap plays a certain buffering role on the valve core, so that the speed of the valve core is reduced, the impact load on the valve core is reduced, and the service life of the valve core is prolonged.
The structure adopting the slender rod is as shown in fig. 3, the slender rod is adopted by the valve core except the cone part, and the slender rod part accounts for 1/2 of the whole length of the valve core, so that the mass of the valve core can be reduced, the valve has higher hydraulic natural frequency, and the response frequency of 25Hz is achieved. The hydraulic natural frequency is generally the lowest response speed of the system, and in order to allow the valve to reach a response frequency of 25Hz, increasing the hydraulic natural frequency is the most effective approach.
The hydraulic natural frequency calculation formula is as follows:
wherein: a is that p : piston area of hydraulic cylinder
V t : total compression volume
m t : converted to total mass on piston
β e : liquid effective bulk modulus of elasticity
From the above formula: can be obtained by adding A p And beta e Reduce V t And m t The natural frequency of the hydraulic pressure is improved.
Since the flow of the valve is determined, the piston area of the hydraulic cylinder, i.e. the cross-sectional area A of the spool p The number cannot be increased randomly; effective bulk modulus of elasticity beta for liquids e If air is mixed in the liquid, beta e Will be reduced, so in order to increase beta e The mixing amount of air in the liquid is reduced as much as possible; for mass m converted to spool t Comprising the mass m of the valve core itself 1 Mass m of liquid in valve cavity 2 Calculated mass m of liquid in connecting pipeline of valve and plunger cavity 3 The method comprises the steps of carrying out a first treatment on the surface of the Mass m of spool itself 1 By using an elongate rod structure to reduce the mass m of liquid in the valve chamber 2 Since the flow determination cannot be changed, the mass m is calculated for the liquid in the valve and plunger chamber connecting pipe 3 If the flow area of the connecting pipeline between the valve and the plunger cavity is a, the total mass of liquid in the pipeline is m 0 The equivalent mass converted to the valve core isThe diameter of the pipe can be effectively reduced by properly increasing the diameter.
Claims (4)
1. An emulsion pump high-speed distributing valve which is characterized in that: the liquid suction valve comprises a shell (1), wherein a plunger cavity T is arranged in the shell (1), two ends of the plunger cavity T are respectively connected with a liquid suction valve I and a liquid discharge valve II, the liquid suction valve I comprises a sleeve (2), a guide sleeve (3), a valve core (5), a valve seat (6) and a spring (4), the two ends of the sleeve (2) are respectively provided with the guide sleeve (3) and the valve seat (6), the valve core (5) is arranged in the guide sleeve (3), the spring (4) is sleeved outside the valve core (5), the outer end part of the valve core (5) is in contact with the valve seat (6), the outer end part of the valve core is of a streamline structure, the guide sleeve end of the liquid suction valve I is communicated with the plunger cavity T, and the valve seat end of the liquid suction valve I is an oil inlet P; the structure of the liquid discharge valve II is the same as that of the liquid inlet valve I, the valve seat end of the liquid discharge valve II is communicated with the plunger cavity T, and the guide sleeve end of the liquid discharge valve II is an oil return port O;
the streamline structure comprises a curve section a, a curve section b and a curve section c, wherein the curve section a comprises O 5 Circular arcs with the center of a circle and the radius of 5mm are respectively represented by O 1 And O 2 Two sections of circular arcs with the radius of 17mm are used as circle centers; curve segment b comprises two segments respectively denoted by O 6 And O 9 An arc section with the center of a circle and the radius of 4 mm; the curve section c comprises two symmetrical curves, one of which comprises the curve represented by O 3 Arc with radius of 25mm as circle center and O 7 Is tangent to an arc with the center and the radius of 5 mm; another curve is represented by O 4 Arc with circle center and radius of 25mm and O 8 Is a circle center and is tangential with an arc with the radius of 5 mm; wherein the centers of the three circular arcs of the curve section a are intersected with a point O, and the centers of the two circular arcs of the curve section b are intersected with OO 5 One point O' on the extension line, the circle centers of the 4 circular arcs of the curve section c are all intersected with the point O 5 Wherein the center of circle O 1 With O 2 ，O 3 With O 4 ，O 7 With O 8 ，O 6 With O 9 Symmetric about line OO 'and its extension, point O, O', O 5 Are all on the central symmetry line of the valve core, and the circle center O 5 5mm from the bottom of the valve core, with O 5 Is the origin of coordinates, i.e. O 5 (0, 0), the remaining center coordinates are: o (0, 10), O' (0, 18), O 1 (-15，-16),O 2 (15，-16),O 3 (35，40),O 4 (-35，-40),O 7 (22，13),O 8 (-22,13)，O 6 (19，6),O 9 (-19，6)；
PEEK is adopted as the valve core (5) material.
2. The emulsion pump high-speed distribution valve according to claim 1, wherein: a gap with an angle of 13 degrees is arranged between the contact surface of the valve core (5) and the valve seat (6).
3. The emulsion pump high-speed distribution valve according to claim 1 or 2, characterized in that: one end of the valve core (5) inserted into the guide sleeve (3) is of a long rod structure, and the length of the long rod is 1/2 of the length of the whole valve core (5).
4. The emulsion pump high-speed distribution valve according to claim 3, wherein: the natural frequency of the hydraulic pressure of the valve core (5) is 25Hz.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810303949.7A CN108468640B (en) | 2018-04-04 | 2018-04-04 | High-speed distributing valve of emulsion pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810303949.7A CN108468640B (en) | 2018-04-04 | 2018-04-04 | High-speed distributing valve of emulsion pump |
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| Publication Number | Publication Date |
|---|---|
| CN108468640A CN108468640A (en) | 2018-08-31 |
| CN108468640B true CN108468640B (en) | 2024-02-20 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810303949.7A Active CN108468640B (en) | 2018-04-04 | 2018-04-04 | High-speed distributing valve of emulsion pump |
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| CN (1) | CN108468640B (en) |
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| CN108468640A (en) | 2018-08-31 |
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