CN220869627U - Split liquid inlet and outlet rotary valve of plunger type reciprocating pump - Google Patents

Abstract

The utility model relates to the technical field of rotary valves, and provides a split liquid inlet and outlet rotary valve of a plunger type reciprocating pump; the rotary valve comprises a valve support and a valve body which are sequentially connected, wherein a valve rod is movably inserted in the valve support, a return spring is sleeved between the valve rod and the valve support, a hollow flow passage is arranged on the valve body, a valve core is arranged between the upper end of the hollow flow passage and the valve rod, the valve core is in contact sealing fit with the hollow flow passage, a rotary flow blade is fixedly arranged on the lower end surface of the valve core, and the rotary flow blade is rotationally inserted in the hollow flow passage; according to the utility model, the valve core is driven by liquid flow to rotate while working, so that impurities can be effectively discharged, the retention of the impurities is prevented, the abrasion of a joint surface is reduced, and the service life of the liquid inlet and outlet valve is greatly prolonged.

Description

Split liquid inlet and outlet rotary valve of plunger type reciprocating pump

Technical Field

The utility model relates to the technical field of rotary valves, and provides a split liquid inlet and outlet rotary valve of a plunger type reciprocating pump.

Background

The reciprocating pump includes a piston pump, a metering pump, and a diaphragm pump, which is commonly referred to as a reciprocating pump. The positive displacement pump is one of positive displacement pumps and has wide application. A reciprocating pump is a delivery machine that directly provides energy in the form of pressure energy to a liquid by the reciprocating motion of a piston. Reciprocating pumps are classified into two major types, i.e., motor-driven pumps and direct-driven pumps (vapor, gas, or liquid driven) according to the driving mode.

When the working principle is that the piston of the electric reciprocating pump moves forward, negative pressure is formed in the pump cylinder first, and then liquid in the storage tank enters the pump cylinder through the liquid inlet valve. When the piston moves in return, the liquid in the cylinder is extruded, the pressure is increased, and the liquid is discharged by the liquid discharge valve. The piston reciprocates once, and each of the suction and discharge of a liquid is called a working cycle; such pumps are known as single action pumps. If the piston reciprocates once, each of the two liquids is sucked and discharged, which is called a double-acting pump. The piston moves from one end to the other, referred to as a stroke.

The main characteristics of the reciprocating pump are as follows: ① High efficiency and wide effective area. ② Very high pressures can be achieved and pressure variations hardly affect the flow, thus providing a constant flow. ③ The self-absorption type hydraulic and pneumatic mixture conveyor has self-absorption capability, and can convey slurry, concrete and the like with special design. ④ The flow and pressure have larger pulsations, especially with single action pumps, due to the acceleration of the piston movement and the discontinuities in the fluid discharge. It is often necessary to provide an air chamber on the discharge line (and sometimes also on the suction line) to provide a relatively uniform flow. The use of double-acting pumps and multi-cylinder pumps also significantly improves flow non-uniformity. ⑤ The speed is low, the size is large, the structure is more complex than that of a centrifugal pump, a special pump valve is needed, and the manufacturing cost and the installation cost are high. The piston pump is mainly used for water supply, and the manual piston pump is a household water pump with wider application. The plunger pump is used for providing a high-pressure liquid source, such as high-pressure water supply of a hydraulic press, and the plunger pump can be used as a drilling mud pump and an oil pump of a petroleum mining site. Diaphragm pumps are particularly suited for delivering highly toxic, radioactive, corrosive liquids, valuable liquids, and liquids containing abrasive solids. The diaphragm pump and the plunger pump can also be used as metering pumps.

The plunger type reciprocating pump is mainly used for injecting water, conveying oil, gas and water mixed liquid in the field of oil fields, impurities are contained in the conveyed liquid or are easy to entrain on the joint surface of the valve core of the liquid inlet and outlet valve and the valve body when the valve core is opened and closed after the plunger type reciprocating pump is used for a period of time, the joint surface of the valve core and the valve body is easy to wear, the sealing performance is rapidly reduced, and the service life of the whole liquid inlet and outlet valve is shortened.

Disclosure of Invention

The utility model aims at overcoming the defects in the prior art and provides a split liquid inlet and outlet rotary valve of a plunger type reciprocating pump.

The valve solves the problems that the joint surface of the valve core and the valve body of the liquid inlet and outlet valve is easy to wear and the service life of the liquid inlet and outlet valve is short.

The technical scheme is as follows: the utility model provides a plunger type reciprocating pump components of a whole that can function independently liquid feed and discharge rotary valve, includes valve support and the valve body that connects gradually, and the activity is pegged graft in the valve support has the valve rod, and the cover is equipped with reset spring between valve rod and the valve support, the valve body is equipped with the cavity runner, be equipped with the case between cavity runner upper end and the valve rod, case and cavity runner contact seal fit, swirl vane has set firmly on the terminal surface under the case, swirl vane rotates and pegs graft in the cavity runner.

Further, the swirl vanes include a plurality of axial vanes that are canted in the same direction.

Further, the number of the axial blades is four.

Further, the outer sides of the swirl vanes are in clearance fit with the hollow flow passage.

Further, the centers of the lower end face of the valve rod and the upper end face of the valve core are provided with opposite hemispherical grooves, and grinding balls are embedded in the hemispherical grooves; and a movement gap is reserved between the lower end face of the valve rod and the upper end face of the valve core.

Furthermore, the edge of the lower end face of the valve core and the inner edge of the upper end of the hollow runner are both in an inverted right angle shape.

Further, the reset spring comprises a large spring and a small spring, and the large spring and the small spring are sleeved on the valve rod in a composite mode.

Further, a sealing groove is formed in the outer wall of the valve body.

Further, the lower end of the valve support is a circular base, a plurality of supporting legs extend upwards from the base, the supporting legs extend upwards and then bend to meet on the axis of the base, a shaft hole is formed in the meeting position, and the upper end of the valve rod is movably inserted into the shaft hole.

Further, the number of the supporting legs is four.

The beneficial effects of the utility model are as follows: according to the utility model, the valve core is driven by liquid flow to rotate while working, so that impurities can be effectively discharged, the retention of the impurities is prevented, the abrasion of a joint surface is reduced, and the service life of the liquid inlet and outlet valve is greatly prolonged.

Drawings

Fig. 1 is a schematic top view of the present utility model.

Fig. 2 is a schematic elevational view of the present utility model.

FIG. 3 is a schematic view of the cross-sectional structure A-A in FIG. 1.

Fig. 4 is a schematic diagram of the front view of the valve core.

Fig. 5 is a schematic view of the valve core in a bottom view.

Fig. 6 is a schematic top view of the valve core.

Fig. 7 is a schematic perspective view of the valve core.

Fig. 8 is a schematic diagram of a second embodiment.

In the figure: 1. valve body, 2, case, 3, valve support, 4, valve rod, 5, grinding ball, 6, reset spring, 101, seal groove, 201, first spacing platform, 202, swirl vane, 203, hemisphere groove, 301, shaft hole, 401, second spacing platform, 402, the body of rod, 601 little spring, 602 big spring.

Detailed Description

The objects, technical solutions and advantages of the present utility model will become more apparent by the following detailed description of the present utility model with reference to the accompanying drawings. It should be understood that the description is only illustrative and is not intended to limit the scope of the utility model. In addition, in the following description, descriptions of well-known structures and techniques are omitted so as not to unnecessarily obscure the present utility model.

Embodiment one: referring to fig. 1-3, a split liquid inlet and outlet rotary valve of a plunger type reciprocating pump comprises a valve body 1, a valve core 2, a valve rod 4, a valve bracket 3 and a return spring 6.

The valve body 1 is cylindrical, an annular sealing groove 101 is formed in the side wall and used for installing a sealing ring, a hollow flow passage is formed in the valve body, external threads are formed in the upper end of the valve body, and the valve support 3 is connected with the threads.

The lower end of the valve bracket 3 is a circular base, is provided with internal threads, and is in threaded connection with the valve body 1; four supporting legs or three or more supporting legs extend upwards from the base, the supporting legs extend upwards and then are bent to meet on the axis of the base, an axle hole 301 is formed in the meeting position, and the upper end of the valve rod 4 is movably inserted into the axle hole 301.

The valve rod 4 consists of a second limiting table 401 and a rod body 402; the rod body 402 is cylindrical, the upper end of the rod body is movably inserted into the shaft hole 301, the lower end of the rod body is fixedly provided with a second limiting table 401, and the second limiting table 401 is flat cylindrical; the return spring 6 is sleeved on the rod body 402.

The upper end of the return spring 6 is propped under the junction, the diameter of the return spring is larger than that of the shaft hole 301, limiting cooperation is formed, the lower end of the return spring is propped above the second limiting table 401, the diameter of the return spring is smaller than that of the second limiting table 401, limiting cooperation is formed, and the second limiting table 401 is pressed above the valve core 2 under the action of elasticity.

Referring to fig. 4 to 7, the valve core 2 is composed of a first limiting table 201 and a swirl vane 202; the first limiting table 201 is in a flat cylindrical shape, and has a diameter larger than that of the hollow runner and smaller than that of the base, so that limiting fit is formed; the swirl vanes 202 are fixedly arranged below the first limiting table 201 and are rotationally inserted into the hollow flow passage; the valve core 2 and the upper end of the hollow runner form contact sealing fit (contact sealing fit: namely, the sealing purpose is achieved through direct contact between parts and the requirement of surface quality).

In this embodiment, the swirl blades 202 are formed by four blades, the blades are plate-shaped bodies extending axially from the bottom surface of the first limiting platform 201, the plate-shaped bodies are all inclined in the same direction, rotational power is generated when the plate-shaped bodies are impacted by liquid flow, the outer sides of the plate-shaped bodies are in clearance fit with the inner walls of the hollow flow channels, the inner sides of the plate-shaped bodies are mutually connected in a crossing manner, a twisted multi-prism body is integrally formed, and two or more blades can be used.

Embodiment two: another embodiment of the utility model is shown in fig. 5 and 8.

The center of the top surfaces of the first limiting table 201 and the second limiting table 401, which are opposite, are respectively provided with a hemispherical groove 203, the hemispherical grooves 203 are embedded with grinding balls 5, the diameters of the grinding balls 5 are determined by a movement gap reserved between the first limiting table 201 and the second limiting table 401, the rotation resistance of the valve core 2 is further reduced, the driving flow required by driving the valve core 2 to rotate is reduced, and the service life extension effect is improved.

The lower edge of the first limiting table 201 and the upper inner edge of the hollow runner are respectively provided with an inverted right angle, so that the sealing performance of the contact seal between the valve core 2 and the valve body 1 is improved.

The return spring 6 is composed of a large spring 602 and a small spring 601 in combination to reduce vibration.

The working principle of the utility model is as follows: when the liquid inlet and outlet valve works, fluid enters the hollow flow channel, and impacts the swirl vane 202 while pushing up the valve core 2 to generate rotary power, so that the valve core 2 and the valve body 1 relatively rotate, and the valve core 2 keeps rotating in the fluid flowing process, so that impurities or dirt can be effectively prevented from being detained in a gap between the valve core 2 and the valve body 1; when the liquid inlet and outlet valve is closed, the valve core 2 can rotate relatively to the valve body 1 for a short time under the action of inertia in the process of stopping the rotation of the valve core 2, impurities are further discharged, friction generated during the relative rotation of the valve core 2 can enable the clearance of a joint surface to be smaller, the joint is tighter and the tightness is better during long-term use.

Although embodiments of the present utility model have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made therein without departing from the spirit and scope of the utility model as defined by the appended claims and their equivalents.

Claims (10)

1. The utility model provides a plunger type reciprocating pump components of a whole that can function independently liquid feed and discharge rotary valve, includes valve support (3) and valve body (1) that connect gradually, and valve support (3) internal activity is pegged graft and is had valve rod (4), and the cover is equipped with reset spring (6) between valve rod (4) and valve support (3), valve body (1) are equipped with the cavity runner, be equipped with case (2) between cavity runner upper end and valve rod (4), case (2) and cavity runner contact seal fit, a serial communication port, swirl vane (202) have been set firmly on the terminal surface under case (2), swirl vane (202) rotate and peg graft in the cavity runner.

2. A split liquid inlet and outlet rotary valve for a reciprocating plunger pump as claimed in claim 1 wherein said swirl vanes (202) comprise a plurality of axial vanes, said axial vanes being inclined in the same direction.

3. The split liquid inlet and outlet rotary valve of a plunger type reciprocating pump of claim 2 wherein said axial vanes are four.

4. A split liquid inlet and outlet rotary valve for a plunger type reciprocating pump according to claim 3, wherein the outer side of the swirl vane (202) is in clearance fit with the hollow flow passage.

5. The split liquid inlet and outlet rotary valve of the plunger type reciprocating pump according to claim 1, wherein the centers of the lower end surface of the valve rod (4) and the upper end surface of the valve core (2) are provided with opposite hemispherical grooves (203), and grinding balls (5) are embedded in the hemispherical grooves (203); a movement gap is reserved between the lower end face of the valve rod (4) and the upper end face of the valve core (2).

6. The split liquid inlet and outlet rotary valve of the plunger type reciprocating pump according to claim 1, wherein the edge of the lower end face of the valve core (2) and the inner edge of the upper end of the hollow runner are both in a reverse right angle shape.

7. The split liquid inlet and outlet rotary valve of the plunger type reciprocating pump according to claim 1, wherein the return spring (6) comprises a large spring (602) and a small spring (601), and the large spring (602) and the small spring (601) are sleeved on the valve rod (4) in a combined mode.

8. The split liquid inlet and outlet rotary valve of the plunger type reciprocating pump according to any one of claims 1 to 7, wherein a sealing groove (101) is formed in the outer wall of the valve body (1).

9. The split liquid inlet and outlet rotary valve of the plunger type reciprocating pump according to any one of claims 1 to 7, wherein the lower end of the valve support (3) is a circular base, a plurality of supporting legs extend upwards from the base, the supporting legs are bent and intersected on the axis of the base after extending upwards, an axle hole (301) is formed at the intersection, and the upper end of the valve rod (4) is movably inserted into the axle hole (301).

10. The split liquid inlet and outlet rotary valve of a plunger type reciprocating pump of claim 9 wherein said legs are four.