CN109458326B - Double-acting hydraulic end of horizontal valve group of reciprocating pump - Google Patents
Double-acting hydraulic end of horizontal valve group of reciprocating pump Download PDFInfo
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- CN109458326B CN109458326B CN201910008398.6A CN201910008398A CN109458326B CN 109458326 B CN109458326 B CN 109458326B CN 201910008398 A CN201910008398 A CN 201910008398A CN 109458326 B CN109458326 B CN 109458326B
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- 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
- F04B53/109—Valves; Arrangement of valves inlet and outlet valve forming one unit
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- Reciprocating Pumps (AREA)
Abstract
The invention relates to a double-acting hydraulic end of a horizontal valve group of a reciprocating pump, which comprises the following components: the pump body is internally provided with a piston channel and two combined valve channels communicated with the piston channel; the piston core of the piston assembly is movably arranged in the piston channel; the two combined valves are respectively arranged in the two combined valve channels, and each combined valve comprises a liquid inlet valve and a liquid outlet valve which share the same valve seat; the two combined valve channels are respectively positioned at two ends of the piston channel and are coaxially arranged with the piston channel; the side wall of the pump body corresponding to each combination valve is provided with a liquid inlet channel communicated with the liquid inlet cavity of the liquid inlet valve and a liquid discharge channel communicated with the liquid discharge cavity of the liquid discharge valve. Because the piston channel and the combined valve channel are positioned on the same axis, the problem of stress concentration caused by vertical intersection of the two channels in the prior art is effectively avoided, the cracking of the pump body is not easy to occur, and the redundant invalid volume caused by cross interference is not generated, so that the gas-liquid mixed fluid can be efficiently conveyed.
Description
Technical Field
The invention relates to the technical field of reciprocating pumps, in particular to a double-acting hydraulic end of a horizontal valve group of a reciprocating pump.
Background
The reciprocating pump may be classified into a single-acting pump, in which a plunger of the reciprocating pump does work during a forward stroke and a double-acting pump, in which a piston (plunger) of the reciprocating pump does not work during a return stroke, and in which the piston (plunger) of the reciprocating pump does work during both the forward stroke and the return stroke. The double-acting reciprocating pump can utilize mechanical energy of a power end which does not do work in return stroke, so that the mechanical energy does work in return stroke, and further, the design volume of the power end with similar matched power can be one step smaller, wherein in the design of the hydraulic end, valve groups of the double-acting reciprocating pump are doubled compared with valve groups of a single-acting reciprocating pump, the valve groups of the reciprocating pump can be in an upper valve structure and a lower valve structure or in a combined valve structure, the valve groups of the hydraulic end of the traditional reciprocating pump are in a vertical structure, and accordingly, the working conditions of the valve groups are all operated vertically, and the Chinese patent application number is CN201710310625.1 discloses such a hydraulic end structure of the reciprocating pump.
However, the hydraulic end of such a reciprocating pump has certain disadvantages: firstly, because the running channel of the piston (plunger) of the reciprocating pump and the valve cavity channel of the valve group are arranged at right angles, a high-pressure alternating region with concentrated stress is easily formed at the intersection position of the two channels, when the reciprocating pump is used for conveying fluid, the pressure level of the reciprocating pump is not more than 25MPa, otherwise, the cracking risk of the pump body can occur; in addition, the reciprocating pump fluid end with the vertical valve group structure has the advantages that the area of the ineffective volume is large when the reciprocating pump fluid end is used for conveying gas-liquid mixed fluid due to the cross interference between the piston channel and the valve cavity channel, so that the operation efficiency of the pump can be reduced due to the occurrence of air lock, the problem of high vibration noise exists, and the efficient conveying of gas-liquid media is difficult to realize.
Disclosure of Invention
Aiming at the current state of the art, the invention provides the double-acting hydraulic end of the horizontal valve group of the reciprocating pump, which is difficult to crack and has small ineffective volume so as to be capable of efficiently conveying gas-liquid mixed fluid.
The technical scheme adopted for solving the technical problems is as follows: a double acting fluid end of a reciprocating pump horizontal valve block comprising: the pump body is internally provided with a piston channel and two combined valve channels communicated with the piston channel; the piston assembly comprises a piston rod and a piston core arranged at the end part of the piston rod, and the piston core is movably arranged in the piston channel; the two combined valves are respectively arranged in the two combined valve channels, and each combined valve comprises a liquid inlet valve and a liquid outlet valve which share the same valve seat; the two combined valve channels are respectively positioned at two ends of the piston channel and are coaxially arranged with the piston channel, and a liquid inlet valve and a liquid outlet valve of the combined valve are respectively positioned at two ends of the valve seat, wherein the liquid inlet valve is positioned at one side facing the piston channel, and the liquid outlet valve is positioned at one side facing away from the piston channel; and the side wall of the pump body corresponding to each combination valve is provided with a liquid inlet channel communicated with the liquid inlet cavity of the liquid inlet valve and a liquid discharge channel communicated with the liquid discharge cavity of the liquid discharge valve.
In order to fix each combination valve at two ends of the pump body so that the action directions of the piston assembly and the two combination valves are consistent, the two combination valves are respectively a main combination valve arranged at the front end of the pump body and a secondary combination valve arranged at the rear end of the pump body; the inner diameters of the two combined valve channels are larger than the inner diameter of the piston channel, so that a first shoulder used for limiting the main combined valve and a second shoulder used for limiting the auxiliary combined valve are formed in the axial direction, the main combined valve is fixed at the front end of the pump body through a first cock and the first shoulder which are covered at the opening position of the combined valve channel, and the auxiliary combined valve is fixed at the rear end of the pump body through a second cock and the second shoulder which are covered at the opening position of the other combined valve channel.
In order to enable the power end of the reciprocating pump to drive the piston assembly more conveniently, the purpose that the piston assembly can do work in both the propelling process and the return process is achieved, and the piston rod penetrates through the auxiliary combination valve and the second cock to be connected with the power end of the reciprocating pump; the valve seat of the auxiliary combination valve is provided with a first pore canal for the piston rod to pass through, and a sealing box body used for being in sealing fit with the piston rod is arranged in the first pore canal. A plurality of different sealing fillers can be arranged in the sealing box body to realize reciprocating sealing between the sealing box body and the sealing box body.
As an improvement, the valve seat of each combination valve is provided with a liquid inlet channel and a liquid outlet channel, the liquid inlet channel is communicated with the liquid inlet channel of the pump body and the liquid inlet cavity of the liquid inlet valve, and the liquid outlet channel is communicated with the liquid inlet cavity of the liquid inlet valve and the liquid outlet cavity of the liquid outlet valve. When the piston assembly is pushed in, the liquid inlet valve is closed, the liquid discharge valve is opened, and fluid medium sucked into the piston channel can enter a liquid discharge cavity of the liquid discharge valve through a liquid discharge hole channel on the valve seat so as to be pressed into a liquid discharge channel of the pump body to be output into an external pipeline; when the piston assembly returns, the liquid discharge valve is closed, the liquid inlet valve is opened, and fluid medium in an external pipeline sequentially enters the liquid inlet cavity of the liquid inlet valve through the liquid inlet channel of the pump body and the liquid inlet hole channel on the valve seat, and is further sucked into the piston channel, so that liquid inlet and outlet circulation is completed.
In order to increase the conveying flow of the reciprocating pump and improve the conveying efficiency, a plurality of liquid inlet channels are formed in the valve seat of each combined valve and are uniformly distributed around the axial lead of the valve seat, a first annular groove is formed in the outer wall of the valve seat, and the first annular groove is communicated with the liquid inlet channel of the pump body and each liquid inlet channel; the liquid discharge holes on the valve seat of each combination valve are multiple and are uniformly distributed around the axial lead of the valve seat.
As an improvement, the liquid inlet valve of each combined valve comprises a first valve core, a first spring and a first spring seat besides a common valve seat, and the two first spring seats are respectively abutted against the first shoulder and the second shoulder; the first spring is arranged between the first valve core and the first spring seat, so that the first valve core is movably matched with the port of the liquid inlet duct.
As an improvement, the liquid discharge valve of each combination valve comprises a second valve core, a second spring and a second spring seat besides a common valve seat, and the two second spring seats are connected to the valve seat through screws; the second spring is arranged between the second valve core and the second spring seat, so that the second valve core is movably matched with the port of the liquid draining duct.
In order to enable opening and closing actions of liquid inlet valves and liquid outlet valves of all the combination valves to be more flexible, two end faces of valve seats of all the combination valves are planes, namely a liquid inlet plane and a liquid outlet plane respectively, a second annular groove is formed in the liquid inlet plane, ports of liquid inlet channels and liquid outlet channels are formed in the bottom face of the second annular groove, a guide part which is axially arranged is further arranged on the inner edge of the second annular groove, a liquid inlet valve plate which is movably sleeved on the guide part is arranged on the first valve core, the liquid inlet valve plate is in sealing fit with the bottom face of the second annular groove, and liquid return holes which correspond to the ports of the liquid outlet channels in the valve seats are further formed in the liquid inlet valve plate; the second valve core is a drain valve plate which is in sealing fit with the drain plane, and the drain valve plate is provided with a guide hole for the screw rod to pass through.
As an improvement, the pump body is also connected with a liquid inlet pipeline for communicating the liquid inlet channel and a liquid discharge pipeline for communicating the liquid discharge channel; the liquid inlet pipeline is positioned at one of the upper and lower positions of the pump body, and the liquid outlet pipeline is positioned at the other position. When in use, the liquid inlet pipeline or the liquid outlet pipeline can be arranged above or below the pump body according to the actual working condition requirement.
As an improvement, the pump body is provided with a plurality of groups of piston channels and combined valve channels in parallel in the horizontal direction, and correspondingly, the liquid inlet pipeline and the liquid outlet pipeline are provided with a plurality of groups; and each group of liquid inlet pipelines are communicated through a total liquid inlet manifold, and each group of liquid outlet pipelines are communicated through a total liquid outlet manifold. That is, the reciprocating pump can be designed into two cylinders or multiple cylinders according to actual needs.
Compared with the prior art, the invention has the advantages that: the hydraulic end of the horizontal valve group of the reciprocating pump is a double-acting hydraulic end, two ends of a piston channel of the hydraulic end are respectively communicated with two combined valve channels, wherein the two combined valve channels and the piston channel are coaxially arranged, and the piston channel and the combined valve channel are positioned on the same axis, so that the problem of stress concentration caused by vertical intersection of the two channels in the prior art is effectively avoided, the cracking of a pump body is difficult to occur, and the high-pressure fluid with the pressure level higher than 25MPa can be conveniently conveyed; on the other hand, because the piston channel and the combined valve channel are positioned on the same axis, the movement direction of the piston component is consistent with the movement direction of each combined valve, and therefore, redundant invalid volume caused by cross interference between the two channels is avoided, the problems of airlock and vibration in the process of conveying the gas-liquid mixed fluid like a reciprocating pump in the prior art are avoided, and the gas-liquid mixed fluid can be conveyed efficiently.
Drawings
Fig. 1 is a schematic diagram of the internal structure of a double-acting hydraulic end of a horizontal valve block of a reciprocating pump according to an embodiment of the present invention;
FIG. 2 is a right side view of a double acting fluid end of a reciprocating pump horizontal valve block of an embodiment of the present invention;
FIG. 3 is a schematic view of a main combined valve according to an embodiment of the present invention;
FIG. 4 is a schematic view of a secondary combination valve according to an embodiment of the present invention;
FIG. 5 is a right side view of the pump body of an embodiment of the present invention;
FIG. 6 is a cross-sectional view taken along A-A of FIG. 5;
FIG. 7 is a top view of a pump body according to an embodiment of the present invention;
fig. 8 is a schematic structural diagram of a connection between a liquid inlet pipeline and a total liquid inlet manifold according to an embodiment of the present invention.
Detailed Description
The invention is described in further detail below with reference to the embodiments of the drawings.
Referring to fig. 1-8, a double-acting hydraulic end of a horizontal valve group of a reciprocating pump includes a pump body 10, a piston assembly 20, a main combination valve 60 disposed at a front end of the pump body 10 and a sub combination valve 70 disposed at a rear end of the pump body, wherein a piston channel 11 and two combination valve channels 12 communicating with the piston channel 11 are disposed in the pump body 10, the two combination valve channels 12 are disposed at two ends of the piston channel 11, the main combination valve 60 and the sub combination valve 70 are disposed in the two combination valve channels 12, respectively, specifically, the piston assembly 20 includes a piston rod 21 and a piston core 22 disposed at an end of the piston rod 21, the piston core 22 is movably disposed in the piston channel 11, the piston channel 11 in this embodiment refers to a working chamber for reciprocating motion of the piston core 22 of the piston assembly 20, and more specifically, the two combined valve channels 12 and the piston channel 11 are coaxially arranged, namely, the axial lead of the piston channel 11 and the axial lead of the two combined valve channels 12 are positioned on the same straight line, each combined valve comprises a liquid inlet valve 40 and a liquid outlet valve 50 which share the same valve seat, wherein the liquid inlet valve 40 and the liquid outlet valve 50 are respectively positioned at two ends of the valve seat, the liquid inlet valve 40 is positioned at one side facing the piston channel 11, the liquid outlet valve 50 is positioned at one side facing away from the piston channel 11, correspondingly, the side wall of the pump body 10 corresponding to each combined valve is provided with a liquid inlet channel 13 communicated with the liquid inlet cavity 400 of the liquid inlet valve 40 and a liquid outlet channel 14 communicated with the liquid outlet cavity 500 of the liquid outlet valve 50, when the piston assembly 20 is pushed in, the liquid inlet valve 40 is closed, the liquid outlet valve 50 is opened, and a fluid medium sucked into the piston channel 11 can be output into an external pipeline through the liquid outlet channel 14 of the pump body 10; when the piston assembly 20 returns, the liquid discharge valve 50 is closed, the liquid inlet valve 40 is opened, the fluid medium in the external pipeline enters the liquid inlet cavity 400 of the liquid inlet valve 40 through the liquid inlet channel 13 of the pump body 10 and is further sucked into the piston channel 11 to complete a liquid inlet and outlet circulation, and as the two ends of the piston channel 11 are provided with the combined valves capable of controlling the fluid medium, the piston assembly 20 can do work in the pushing and returning processes, and high-efficiency conveying of the fluid medium is realized.
Referring to fig. 1, in the present embodiment, the piston core 22 of the piston assembly 20 is fixed at the end of the piston rod 21 by a bolt, correspondingly, the other end of the piston rod 21 is connected to a power end (not shown) of the reciprocating pump, specifically, a cylinder sleeve 23 for accommodating the piston core 22 is disposed in the piston channel 11 of the present embodiment, and a sealing member is disposed on an outer circle of the piston core 22 to realize sealing fit with an inner wall of the cylinder sleeve 23, which naturally, it is conceivable that the cylinder sleeve 23 and the piston assembly 20 in the present embodiment may be replaced by corresponding functional bodies and plunger assemblies, that is, a reciprocating plunger pump is formed.
In order to fix each combination valve at both ends of the pump body 10 so that the piston assembly 20 coincides with the operation direction of the two combination valves, the inner diameters of the two combination valve passages 12 in this embodiment are both larger than the inner diameter of the piston passage 11, so that a first shoulder 15 for restricting the main combination valve 60 and a second shoulder 16 for restricting the sub-combination valve 70 are formed in the axial direction, the main combination valve 60 is fixed at the front end of the pump body 10 by a first tap 81 and a first shoulder 15 which are covered at the opening position of the combination valve passage 12, the sub-combination valve 70 is fixed at the rear end of the pump body 10 by a second tap 82 and a second shoulder 16 which are covered at the opening position of the other combination valve passage 12, wherein the first tap 81 and the second tap 82 are both fixed at the front and rear end walls of the pump body 10 by screw threads, specifically, in order to make each combination valve more firmly set in each combination valve passage 12, the middle part of the valve seat 61 of the main combination valve 60 is provided with a positioning hole 600 which is axially opened, the inner side of the first cock 81 is provided with a positioning column 810 which is matched with the positioning hole 600, and likewise, the piston rod 21 passes through the auxiliary combination valve 70 and the second cock 82 to be connected with the power end of the reciprocating pump, wherein the valve seat 71 of the auxiliary combination valve 70 is provided with a first pore canal 700 for the piston rod 21 to pass through, the first pore canal 700 is internally provided with a sealing box body 701 which is used for being in sealing fit with the piston rod 21, a plurality of different sealing fillers can be arranged in the sealing box body 701 to realize reciprocating sealing between the two, such as V-shaped, U-shaped, rectangular and other filler seals, and in order to conveniently assemble the auxiliary combination valve 70, the piston assembly 20 and the pump body 10, the valve seat 71 of the auxiliary combination valve 70 and the sealing box body 701 can be designed into a whole; in addition, in order to avoid leakage of the medium between the valve seat and the inner wall of each combination valve passage 12, a seal groove (not shown) for placing an O-ring seal is further provided on the outer circumference of the valve seat of each combination valve. The piston rod 21 in this embodiment passes through the auxiliary combination valve 70 and the second cock 82 to connect with the power end of the reciprocating pump, so that the power end of the reciprocating pump can more conveniently drive the piston assembly 20, and the purpose that the piston assembly 20 can do work in both the pushing process and the returning process is achieved.
Referring to fig. 3 and 4, the valve seat of each combination valve is provided with a liquid inlet channel 91 and a liquid outlet channel 92, the liquid inlet channel 91 is communicated with the liquid inlet channel 13 of the pump body 10 and the liquid inlet cavity 400 of the liquid inlet valve 40, and the liquid outlet channel 92 is communicated with the liquid inlet cavity 400 of the liquid inlet valve 40 and the liquid outlet cavity 500 of the liquid outlet valve 50; in order to increase the delivery flow of the reciprocating pump and improve the delivery efficiency, the valve seat of each combination valve has a plurality of liquid inlet channels 91 which are uniformly distributed around the axial line of the valve seat, wherein the outer wall of the valve seat of each combination valve is provided with a first annular groove 93, and the first annular groove 93 is communicated with the liquid inlet channel 13 of the pump body 10 and each liquid inlet channel 91; the liquid discharge holes 92 on the valve seat of each combination valve are multiple and uniformly distributed around the axis of the valve seat to form an annular surface, and more specifically, the number of the liquid inlet holes 91 is equal to that of the liquid discharge holes 92, part of the liquid inlet holes 91 and the liquid discharge holes 92 are positioned on the same annular surface, and the liquid inlet holes 91 and the liquid discharge holes 92 are sequentially arranged at intervals. When the piston assembly 20 is pushed in, the liquid inlet valve 40 is closed, the liquid outlet valve 50 is opened, and the fluid medium sucked into the piston channel 11 can enter the liquid outlet cavity 500 of the liquid outlet valve 50 through the liquid outlet hole 92 on the valve seat so as to be pressed into the liquid outlet channel 14 of the pump body 10 and output to an external pipeline; when the piston assembly 20 returns, the liquid discharge valve 50 is closed, the liquid inlet valve 40 is opened, and the fluid medium in the external pipeline sequentially enters the liquid inlet cavity 400 of the liquid inlet valve 40 through the liquid inlet channel 13 of the pump body 10 and the liquid inlet hole 91 on the valve seat, and is further sucked into the piston channel 11, so that a liquid inlet and discharge cycle is completed.
With continued reference to fig. 3 and 4, the liquid inlet valve 40 of each combination valve further includes a first valve core 41, a first spring 42 and a first spring seat 43, and inner sides of the two first spring seats 43 respectively abut against the first shoulder 15 and the second shoulder 16; the first spring 42 is arranged between the first valve core 41 and the first spring seat 43, so that the first valve core 41 can be axially and movably matched at the port of the liquid inlet duct 91 to realize the opening and closing of the liquid inlet valve 40, specifically, the first spring seat 43 is an annular positioning sleeve with a flow passage hole 430 at the middle part, when the two first spring seats 43 are installed in the combined valve channel 12, the inner edges of the two first spring seats are flush with the inner wall surface of the cylinder sleeve 23 in the piston channel 11, the cylinder sleeve 23 is just pressed in the piston channel 11, and then specifically, the outer side of the first spring seat 43 is provided with a convex positioning part 431, and one end of the first spring 42 is sleeved on the positioning part 431; correspondingly, the drain valve 50 of each combination valve further comprises a second valve core 51, a second spring 52 and a second spring seat 53, and the two second spring seats 53 in the embodiment are connected to the valve seat through a screw 83; the second spring 52 is disposed between the second valve core 51 and the second spring seat 53, so that the second valve core 51 can be axially movably matched at the port of the drain hole 92 to realize opening and closing of the drain valve 50, specifically, the inner end of the screw 83 is screwed on the corresponding valve seat through the first screw thread 832, and the outer end of the screw 83 fixes the second spring seat 53 through the second screw thread 831 and the locknut 833.
In order to make the opening and closing actions of the liquid inlet valve 40 and the liquid outlet valve 50 of each combination valve more flexible, the two end surfaces of the valve seat of each combination valve are respectively a liquid inlet plane and a liquid outlet plane, and correspondingly, the valve cores of the liquid inlet valve 40 and the liquid outlet valve 50 are respectively of valve plate structures, specifically referring to fig. 3 and 4, the liquid inlet plane is provided with a second annular groove 94, ports of the liquid inlet channel 91 and the liquid outlet channel 92 are respectively arranged on the bottom surface of the second annular groove 94, the inner edge of the second annular groove 94 is also provided with a guide part 95 axially arranged, wherein the first valve core 41 is a liquid inlet valve plate movably sleeved on the guide part 95, the liquid inlet valve plate is in sealing fit on the bottom surface of the second annular groove 94, and the liquid inlet valve plate is also provided with a liquid return hole 410 corresponding to the port of the liquid outlet channel 92 on the valve seat; the second valve core 51 is a drain valve plate hermetically matched on a drain plane, and a guide hole 510 for the screw 83 to pass through is formed on the drain valve plate, wherein in this embodiment, the liquid inlet valve plate and the drain valve plate of the main combination valve 60 have the same structure as the liquid inlet valve plate and the drain valve plate of the auxiliary combination valve 70, respectively, and can be used interchangeably.
Referring to fig. 1, the pump body 10 is further connected with a liquid inlet pipeline 84 for communicating with the liquid inlet channel 13 and a liquid outlet pipeline 85 for communicating with the liquid outlet channel 14, wherein the liquid inlet pipeline 84 is located at one of the upper and lower positions of the pump body 10, the liquid outlet pipeline 85 is located at the other position, and when in use, the liquid inlet pipeline 84 or the liquid outlet pipeline 85 can be arranged above or below the pump body 10 according to actual working condition requirements, in this embodiment, two liquid inlet pipelines 84 are respectively connected on the upper plane of the pump body 10 through flanges and are communicated with the two liquid inlet channels 13, and likewise, two liquid outlet pipelines 85 are respectively connected on the lower plane of the pump body 10 through flanges and are communicated with the two liquid outlet channels 14; referring to fig. 5-8, the pump body 10 may be provided with multiple sets of piston channels 11 and combined valve channels 12 in parallel in the horizontal direction (three-cylinder reciprocating pump is illustrated in this embodiment, but the reciprocating pump is not limited to three cylinders, and may be designed into two cylinders or other multi-cylinders according to actual needs), accordingly, the liquid inlet pipeline 84 and the liquid outlet pipeline 85 are provided with multiple sets, each set of liquid inlet pipelines 84 is communicated with each other through a total liquid inlet manifold 840, each set of liquid outlet pipelines 85 of the total liquid inlet manifold 840 is communicated with each other through a total liquid outlet manifold 850, wherein the front end and the rear end of the total liquid inlet manifold 840 and the total liquid outlet manifold 850 are provided with blind flanges 841,851 and through flanges 842,852 for connecting external pipelines, and the blind flanges 842,852 and 841,851 are interchanged according to actual needs, fig. 7 illustrates a schematic upper plane structure of the pump body 10, a lower plane structure of the pump body 10 is the same as that of the liquid inlet pipelines, and fig. 8 illustrates a structure of the total liquid inlet manifold 840 connected with each liquid outlet pipeline 850 is the same as that of the drain pipelines connected with the liquid outlet pipelines.
The piston assembly 20 of the reciprocating pump in this embodiment can do work when driven by the power end to reciprocate, and the specific process is as follows: when the piston assembly 20 is pushed in, the liquid inlet valve 40 of the main combination valve 60 is closed, the liquid outlet valve 50 is opened, wherein the fluid medium in the piston channel 11 can be output to the liquid outlet pipeline 85 through the liquid outlet cavity 500 of the main combination valve 60 and the liquid outlet channel 14 of the pump body 10, meanwhile, the liquid inlet valve 40 of the auxiliary combination valve 70 is opened, the liquid outlet valve 50 is closed, and the fluid medium in the liquid inlet pipeline 84 can be sequentially sucked in through the liquid inlet channel 13 of the pump body 10 and the liquid inlet cavity 400 of the auxiliary combination valve 70, so as to fill the piston channel 11 of the pump body 10; when the piston assembly 20 returns, the pressure of the fluid medium in the piston channel 11 rises, the drain valve 50 of the auxiliary combination valve 70 is opened, the liquid inlet valve 40 is closed, the fluid medium can be output to the drain pipeline 85 through the drain cavity 500 of the auxiliary combination valve 70 and the drain channel 14 of the pump body 10, meanwhile, the drain valve 50 of the main combination valve 60 is closed, the liquid inlet valve 40 is opened, and the fluid medium in the liquid inlet pipeline 84 can be sequentially sucked through the liquid inlet channel 13 of the pump body 10 and the liquid inlet cavity 400 of the main combination valve 60, and the piston channel 11 of the pump body 10 is filled with the fluid medium to complete a liquid inlet and drain cycle. In the process of pushing and returning the piston assembly 20, the piston channel 11 and the combined valve channel 12 are positioned on the same axis, so that the pump body 10 cracking caused by the problem of stress concentration of a cross duct is effectively avoided, and the service life of the reciprocating pump is prolonged; on the other hand, the piston passage 11 and the combination valve passage 12 do not have excessive dead volume due to cross interference, and thus the gas-liquid mixed fluid can be efficiently transported.
The hydraulic end of the horizontal valve group of the reciprocating pump in the embodiment is a double-acting hydraulic end, two ends of a piston channel 11 of the hydraulic end are respectively communicated with two combined valve channels 12, wherein the two combined valve channels 12 and the piston channel 11 are coaxially arranged, and because the piston channel 11 and the combined valve channel 12 are positioned on the same axis, the problem of stress concentration caused by vertical intersection of the two channels in the prior art is effectively avoided, and the pump body 10 is not easy to crack, so that high-pressure fluid with the pressure level higher than 25MPa can be conveniently conveyed; on the other hand, since the piston channel 11 and the combining valve channel 12 are located on the same axis, the movement direction of the piston assembly 20 is consistent with the movement direction of each combining valve, so that the redundant invalid volume caused by cross interference between the two channels is avoided, the problems of air lock and vibration in the prior art are avoided when the gas-liquid mixed fluid is conveyed, and the gas-liquid mixed fluid can be conveyed efficiently.
Claims (7)
1. A double acting fluid end of a reciprocating pump horizontal valve block comprising:
the pump comprises a pump body (10), wherein a piston channel (11) and two combined valve channels (12) communicated with the piston channel (11) are arranged in the pump body (10);
the piston assembly (20) comprises a piston rod (21) and a piston core (22) arranged at the end part of the piston rod (21), and the piston core (22) is movably arranged in the piston channel (11);
the two combined valves are respectively arranged in the two combined valve channels (12), and each combined valve comprises a liquid inlet valve (40) and a liquid outlet valve (50) which share the same valve seat;
the method is characterized in that: the two combined valve channels (12) are respectively positioned at two ends of the piston channel (11) and are coaxially arranged with the piston channel (11), and a liquid inlet valve (40) and a liquid outlet valve (50) of the combined valve are respectively positioned at two ends of the valve seat, wherein the liquid inlet valve (40) is positioned at one side facing the piston channel (11), and the liquid outlet valve (50) is positioned at one side facing away from the piston channel (11);
a liquid inlet channel (13) communicated with a liquid inlet cavity (400) of the liquid inlet valve (40) and a liquid outlet channel (14) communicated with a liquid outlet cavity (500) of the liquid outlet valve (50) are arranged on the side wall of the pump body (10) corresponding to each combination valve;
the two combined valves are a main combined valve (60) arranged at the front end of the pump body (10) and a secondary combined valve (70) arranged at the rear end of the pump body (10);
the inner diameters of the two combined valve channels (12) are larger than the inner diameter of the piston channel (11), so that a first shoulder (15) used for limiting the main combined valve (60) and a second shoulder (16) used for limiting the auxiliary combined valve (70) are formed in the axial direction, the main combined valve (60) is fixed at the front end of the pump body (10) through a first cock (81) and the first shoulder (15) which are covered at the opening position of the combined valve channel (12), and the auxiliary combined valve (70) is fixed at the rear end of the pump body (10) through a second cock (82) and the second shoulder (16) which are covered at the opening position of the other combined valve channel (12);
the piston rod (21) penetrates through the auxiliary combination valve (70) and the second cock (82) to be connected with the power end of the reciprocating pump;
a first pore canal (700) for the piston rod (21) to pass through is arranged on a valve seat of the auxiliary combination valve (70), and a sealing box body (701) for sealing and matching with the piston rod (21) is arranged in the first pore canal (700);
the valve seat of each combination valve is provided with a liquid inlet duct (91) and a liquid outlet duct (92), the liquid inlet duct (91) is communicated with a liquid inlet channel (13) of the pump body (10) and a liquid inlet cavity (400) of the liquid inlet valve (40), and the liquid outlet duct (92) is communicated with the liquid inlet cavity (400) of the liquid inlet valve (40) and a liquid outlet cavity (500) of the liquid outlet valve (50).
2. The dual acting fluid end of a reciprocating pump horizontal valve block of claim 1, wherein: the valve seat of each combined valve is provided with a plurality of liquid inlet channels (91) which are uniformly distributed around the axial lead of the valve seat, the outer wall of the valve seat is provided with a first annular groove (93), and the first annular groove (93) is communicated with the liquid inlet channel (13) of the pump body (10) and each liquid inlet channel (91);
the liquid discharge holes (92) on the valve seat of each combination valve are multiple and are uniformly distributed around the axial lead of the valve seat.
3. The dual acting fluid end of a reciprocating pump horizontal valve block of claim 1, wherein: the liquid inlet valve (40) of each combined valve comprises a first valve core (41), a first spring (42) and a first spring seat (43) besides a common valve seat, and the two first spring seats (43) are respectively abutted against the first shoulder (15) and the second shoulder (16);
the first spring (42) is arranged between the first valve core (41) and the first spring seat (43), so that the first valve core (41) is movably matched with a port of the liquid inlet duct (91).
4. A double acting fluid end of a reciprocating pump horizontal valve block as defined in claim 3, wherein: the liquid discharge valve (50) of each combined valve comprises a second valve core (51), a second spring (52) and a second spring seat (53) besides a common valve seat, and the two second spring seats (53) are connected to the valve seats through screws (83);
the second spring (52) is arranged between the second valve core (51) and the second spring seat (53), so that the second valve core (51) is movably matched with the port of the liquid draining pore canal (92).
5. The dual acting fluid end of a reciprocating pump horizontal valve block of claim 4, wherein: the two end surfaces of the valve seat of each combined valve are planes, namely a liquid inlet plane and a liquid outlet plane, the liquid inlet plane is provided with a second annular groove (94), ports of the liquid inlet pore canal (91) and the liquid outlet pore canal (92) are arranged on the bottom surface of the second annular groove (94), the inner edge of the second annular groove (94) is also provided with a guide part (95) which is axially arranged, the first valve core (41) is a liquid inlet valve plate which is movably sleeved on the guide part (95), the liquid inlet valve plate is in sealing fit with the bottom surface of the second annular groove (94), and the liquid inlet valve plate is also provided with a liquid return hole (410) which corresponds to the port of the liquid outlet pore canal (92) on the valve seat;
the second valve core (51) is a drain valve plate which is in sealing fit with the drain plane, and a guide hole (510) for the screw (83) to pass through is formed in the drain valve plate.
6. A double acting fluid end of a reciprocating pump horizontal valve block as claimed in any one of claims 1 to 5 wherein: the pump body (10) is also connected with a liquid inlet pipeline (84) used for communicating the liquid inlet channel (13) and a liquid outlet pipeline (85) used for communicating the liquid outlet channel (14);
the liquid inlet pipeline (84) is positioned at one of the upper and lower positions of the pump body (10), and the liquid outlet pipeline (85) is positioned at the other position.
7. The dual acting fluid end of a reciprocating pump horizontal valve block of claim 6, wherein: the pump body (10) is provided with a plurality of groups of piston channels (11) and combination valve channels (12) in parallel in the horizontal direction, and correspondingly, the liquid inlet pipeline (84) and the liquid outlet pipeline (85) are provided with a plurality of groups;
the liquid inlet pipelines (84) of each group are communicated through a total liquid inlet manifold (840), and the liquid outlet pipelines (85) of each group are communicated through a total liquid outlet manifold (850).
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| CN201910008398.6A CN109458326B (en) | 2019-01-04 | 2019-01-04 | Double-acting hydraulic end of horizontal valve group of reciprocating pump |
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| CN201910008398.6A CN109458326B (en) | 2019-01-04 | 2019-01-04 | Double-acting hydraulic end of horizontal valve group of reciprocating pump |
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| CN109458326A CN109458326A (en) | 2019-03-12 |
| CN109458326B true CN109458326B (en) | 2023-10-03 |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CA3160190A1 (en) * | 2019-12-23 | 2021-07-01 | Zvonimir Batarilo | Multi-fluid delivery system |
| CN113586383B (en) * | 2021-09-29 | 2021-12-07 | 宁波合力机泵股份有限公司 | Horizontal two-section compression mixed transportation pump hydraulic end |
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| CN102913442A (en) * | 2012-10-29 | 2013-02-06 | 陕西联盟物流有限公司 | Novel water injection pump valve |
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| EP3001036A1 (en) * | 2014-09-20 | 2016-03-30 | Sugino Machine Limited | Fluid coupling |
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| US9382905B2 (en) * | 2013-09-09 | 2016-07-05 | Federal Signal Corporation | High power reciprocating pump manifold and valve cartridges |
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| CN202545162U (en) * | 2012-04-26 | 2012-11-21 | 潍坊胜利石化机械有限公司 | Novel water supply and mixing pump |
| CN102913442A (en) * | 2012-10-29 | 2013-02-06 | 陕西联盟物流有限公司 | Novel water injection pump valve |
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| CN109458326A (en) | 2019-03-12 |
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