CN117108511B - Self-adaptive centrifugal pressure test pump set and pump system capable of avoiding overpressure - Google Patents
Self-adaptive centrifugal pressure test pump set and pump system capable of avoiding overpressure Download PDFInfo
- Publication number
- CN117108511B CN117108511B CN202311351843.1A CN202311351843A CN117108511B CN 117108511 B CN117108511 B CN 117108511B CN 202311351843 A CN202311351843 A CN 202311351843A CN 117108511 B CN117108511 B CN 117108511B
- Authority
- CN
- China
- Prior art keywords
- pump body
- pressure
- centrifugal
- outlet
- pressure test
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000012360 testing method Methods 0.000 title claims abstract description 115
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 109
- 239000007788 liquid Substances 0.000 claims abstract description 71
- 238000002347 injection Methods 0.000 claims abstract description 45
- 239000007924 injection Substances 0.000 claims abstract description 45
- 230000005540 biological transmission Effects 0.000 claims description 22
- 230000007246 mechanism Effects 0.000 claims description 6
- 238000011144 upstream manufacturing Methods 0.000 claims description 5
- 238000004891 communication Methods 0.000 claims description 4
- 230000003044 adaptive effect Effects 0.000 claims description 3
- 238000007789 sealing Methods 0.000 claims description 3
- 239000012530 fluid Substances 0.000 abstract description 11
- 230000000694 effects Effects 0.000 abstract description 9
- 238000013461 design Methods 0.000 abstract description 4
- 230000007423 decrease Effects 0.000 description 19
- 238000000034 method Methods 0.000 description 12
- 230000008569 process Effects 0.000 description 11
- 230000008859 change Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 6
- 230000002706 hydrostatic effect Effects 0.000 description 6
- 239000003638 chemical reducing agent Substances 0.000 description 3
- 238000005381 potential energy Methods 0.000 description 3
- 230000003068 static effect Effects 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 230000033228 biological regulation Effects 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 238000010992 reflux Methods 0.000 description 2
- 239000000243 solution Substances 0.000 description 2
- 238000012549 training Methods 0.000 description 2
- 238000013022 venting Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000004146 energy storage Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 239000007858 starting material Substances 0.000 description 1
- 238000010998 test method Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
-
- 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
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
-
- 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
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/14—Combinations of two or more pumps the pumps being of different types at least one pump being of the non-positive-displacement type
-
- 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
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
- F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
- F04D15/0011—Control, e.g. regulation, of pumps, pumping installations or systems by using valves by-pass valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0066—Control, e.g. regulation, of pumps, pumping installations or systems by changing the speed, e.g. of the driving engine
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E30/00—Energy generation of nuclear origin
- Y02E30/30—Nuclear fission reactors
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention belongs to the technical field of fluid delivery, and particularly discloses a self-adaptive centrifugal pressure test pump set capable of avoiding overpressure and a pump system. In the water injection stage, rivers are through the direct output of water injection export, make full use of centrifugal pump body's large-traffic characteristic carries out quick water injection, then divide partial rivers drive liquid drive force device and high-pressure pump to pressurize another part rivers in the pressurization stage to realize changing the effect of pressure with the flow, compare in traditional design can save a set of electric drive system, and only need switch centrifugal pump body's export flow direction can when switching the mode moreover, easy operation. And severe accidents caused by excessive overpressure can be avoided, and the phenomenon of pump holding can not occur, so that the pump, the motor and the test system are protected.
Description
Technical Field
The invention belongs to the technical field of fluid conveying, and particularly relates to a self-adaptive centrifugal pressure test pump set and a pump system for avoiding overpressure.
Background
In order to ensure the safety and reliability of the hydraulic equipment, various pipelines, pressure vessels, valve bodies, connecting pieces and fluid systems are required to be subjected to pressure-resistant tests, and the hydraulic equipment can be used after being tested to be qualified according to the test standard.
Conventional large system tubing pumping is divided into two stages: a water injection stage and a pressurization stage. The traditional centrifugal pump can provide larger flow in the water injection stage, but cannot meet the pressurizing requirement due to insufficient output in the pressurizing stage. The plunger pump can stably provide high pressure required in the pressurizing stage, but the plunger pump is small in flow in the water injection stage, water injection is slow, and the working period is prolonged. In the prior art, a high-pressure centrifugal pump is also used for increasing the output pressure in a high-rotation speed or multistage centrifugal mode, but the high-pressure centrifugal pump is unstable in pressurization, is extremely easy to generate serious abnormal phenomena such as cavitation and reflux, has high requirements on the stability of medium flow and pressure, and has low flow. In order to solve the above problems, the conventional operation is to fill water with a centrifugal pump at first in the water filling stage, close the centrifugal pump pipeline after completing water filling, and start a plunger pump for pressurization. However, the following problems occur:
the cost is high: the centrifugal pump and the plunger pump respectively need a set of electric drive system, and the cost is increased.
Risk of overpressure: the traditional plunger pump can continuously apply pressure in the pressurizing process, if the operation is improper, the risk of overpressure of the system is easy to cause, if the intervention is not timely, or the output of the plunger pump is insufficient and stops, so that a motor is burnt out, or the system is continuously boosted, and finally serious accidents are caused. The safety valve is a common means for preventing the system from being overpressured, but the pressure test system usually has different test pressures due to different pressure test objects, so that the pressure relief pressure of the safety valve needs to be readjusted before each pressure test is carried out, and the calibration and the test are carried out, but the site often does not have the test condition of the safety valve, and whether the safety valve is reliable or not only can depend on the quality of a product. In addition, the pressure regulation of the safety valve is omitted before pressure test, and in reality, the system pressure mainly depends on manual regulation.
The operation is complex: the centrifugal pump is used for filling water and the plunger pump is used for pressurizing respectively, corresponding pipelines and valves are guaranteed to be ready and in a correct state in the switching process of the working pump, the operation complexity is increased, the overpressure risk exists, and professional personnel are often required to operate to guarantee effective and safe pressure test, so that the labor cost and the training requirements are increased.
In summary, it is clear that the prior art has inconvenience and defects in practical use, so that improvement is needed.
Disclosure of Invention
In view of the above-mentioned drawbacks, an object of the present invention is to provide an adaptive centrifugal pressure test pump set and pump system capable of avoiding overpressure, which can utilize part of water flow output by a centrifugal pump body to drive a liquid driving device by arranging the liquid driving device at the downstream of the centrifugal pump body, the liquid driving device drives a high-pressure pump again, and the high-pressure pump pressurizes another part of water output by the centrifugal pump body. In the water injection stage, rivers are through the direct output of water injection export, make full use of centrifugal pump body's large-traffic characteristic carries out quick water injection, then partial rivers drive liquid drive force device and high-pressure pump are pressed to another part rivers in the pressurization stage to realize the effect with flow pressure changing, compare in traditional design can save a set of electric drive system, reduce cost, only need switch centrifugal pump body's export flow direction can when switching the mode moreover, easy operation. More importantly, when the high-pressure pump body is a plunger type pump body, the plunger type pump body is driven by the liquid driving force device, so long as the output power of the centrifugal pump body is set, once the system pressure rises to a certain degree, the liquid driving force device and the plunger type pump body can be stopped when the system pressure fails to drive the plunger type pump body to run continuously, serious accidents caused by excessive overpressure are avoided, and water flow output by the centrifugal pump body can still flow through the liquid driving force device without pump blocking phenomenon, so that the pump, the motor and the test system are protected.
In order to achieve the above purpose, the invention provides an adaptive centrifugal pressure test pump set for avoiding overpressure, which comprises a centrifugal pump body, a driving device for driving the centrifugal pump body, a liquid driving force device, a high-pressure pump body, a water injection outlet and a pressurizing outlet; the outlet of the centrifugal pump body is respectively communicated with the inlet of the liquid driving force device, the inlet of the high-pressure pump body and the water injection outlet, and the output end of the liquid driving force device drives the high-pressure pump body to operate, and the outlet of the high-pressure pump body is a pressurizing outlet.
The centrifugal pump further comprises a three-way reversing valve, an outlet of the centrifugal pump body is communicated with an inlet of the three-way reversing valve, a first outlet of the three-way reversing valve is a water injection outlet, and a second outlet of the three-way reversing valve is communicated with an inlet of the high-pressure pump body and an inlet of the liquid driving force device.
Further, the high-pressure pump body is a plunger type pump body.
Further, the output end of the liquid driving force device is connected with an eccentric wheel, and the eccentric wheel is in transmission connection with the plunger pump body through a plunger rod; the second outlet of the three-way reversing valve is provided with a reducing pipe, the thick end of the reducing pipe is connected with the second outlet of the three-way reversing valve, the thin end of the reducing pipe is connected with the inlet of the plunger type pump body, the side surface of the reducing pipe extends outwards to form a side pipe, and the side pipe is connected with the inlet of the liquid driving force device.
Further, the axis of the centrifugal pump body, the inlet of the centrifugal pump body, the axis of the liquid driving force device, the first outlet of the three-way reversing valve, the inlet axis of the plunger type pump body and the outlet axis are parallel to each other, the outlet of the centrifugal pump body is opposite to the inlet of the liquid driving force device, and the outlet of the plunger type pump body is communicated with the front end of the first outlet of the three-way reversing valve.
Further, the device also comprises a speed changing device, wherein the speed changing device comprises a gear set and an auxiliary driver, and the gear set comprises a driving shaft, a planet carrier, a planetary gear, a middle gear, an outer gear ring, an output shaft and a transmission gear; the planetary gear mechanism is composed of at least two planetary gears, an intermediate gear, a planetary gear and an outer gear ring, wherein a driving shaft is connected with the planetary gears through a planet carrier and synchronously rotates, an output shaft is fixedly connected with the intermediate gear coaxially and synchronously rotates, and a transmission gear is meshed with the outer wall of the outer gear ring; the auxiliary driver comprises a cylinder body and a piston, the piston is in sealing sliding contact with the inner wall of the cylinder body, gas is stored between the piston and the cylinder body, and the piston is connected with the crankshaft through a connecting rod; the outer gear ring is connected with the crankshaft in a transmission way.
Further, the drive shaft is connected with the output end of the driving device, and the output shaft is connected with the centrifugal pump body.
Further, the drive shaft is connected with the output end of the hydraulic driving force device, and the output shaft is connected with the high-pressure pump body.
The centrifugal pressure test pump system comprises the self-adaptive centrifugal pressure test pump set capable of avoiding overpressure, a water injection bypass and a three-way reversing valve, wherein the downstream of the centrifugal pump body is connected with an inlet of the three-way reversing valve, one outlet of the three-way reversing valve is connected with the water injection bypass, and the other outlet of the three-way reversing valve is connected with a liquid driving force device and a high-pressure pump body.
Further, the downstream of the water injection bypass and the high-pressure pump body are converged and connected with a one-way valve, the downstream of the one-way valve is connected with an energy accumulator, and the downstream of the energy accumulator is connected with pressure testing equipment or a system.
Further, the device also comprises a first shutoff valve which is arranged at the downstream of the water injection bypass and the high-pressure pump body and at the upstream of the energy accumulator, wherein the liquid side of the energy accumulator is communicated with the pressure test pipeline, and the gas side of the energy accumulator is communicated with the air compressor.
Further, a second shut-off valve is provided between the accumulator and the pressure test device or system.
Compared with the prior art, the invention has the following beneficial effects:
the invention uses partial water flow output by the centrifugal pump body to drive the liquid driving device, which drives the high-pressure pump body, and the high-pressure pump body pressurizes the other part of water output by the centrifugal pump body. In the water injection stage, rivers pass through the water injection export and directly export, make full use of centrifugal pump body's large-traffic characteristic carries out quick water injection, then partial rivers drive liquid drive force device and high-pressure pump body are pressed to another part rivers in the pressurization stage to realize changing the effect of pressure with the flow, compare in traditional design can save a set of electric drive system, reduce cost, only need switch centrifugal pump body's export flow direction can when switching the mode moreover, easy operation reduces human cost and training demand. More importantly, when the high-pressure pump body is a plunger type pump body, the plunger type pump body is driven by the liquid driving force device, along with the gradual rise of the pressure in the pressure test equipment or the system, the pressure at the rear end of the plunger type pump body gradually increases, the driving force required by the conveying medium of the plunger type pump body gradually increases, so that the flow of the plunger type pump body gradually decreases, the water passing through the plunger type pump body decreases, the water passing through the liquid driving force device increases, namely the water participating in driving the liquid driving force device and the plunger type pump body increases, the pressurizing capacity of the plunger type pump body increases, the flow decreases, and the liquid driving force device and the plunger type pump body stop at the moment until all water can not drive the plunger type pump body to run continuously, and the water flow output by the centrifugal pump body can still flow through the liquid driving force device without generating a pump phenomenon, thereby playing a role in protecting the pump, the motor and the test equipment or the system. The larger the output power of the centrifugal pump body is, the larger the water quantity and the water pressure which can flow through the liquid driving force device are, and the larger the maximum pressurizing pressure of the plunger type pump body is. Therefore, as long as the output power of the centrifugal pump body is set in the pressurization stage, the maximum pressurization pressure is set, and even if the operation is wrong, the pressure in the pressure test device or system does not rise in an uncontrolled manner.
In the pressurizing process, along with the gradual rise of the pressure in the pressure test equipment or the system, the pressure at the rear end of the plunger pump body gradually increases, the driving force required by the plunger pump body for conveying the medium gradually increases, so that the flow rate of the plunger pump body gradually decreases, the water passing through the plunger pump body decreases, and the water passing through the liquid driving force device increases, namely, the water participating in driving the liquid driving force device and the plunger pump body increases, and the pressurizing capacity of the plunger pump body increases and the flow rate decreases.
According to the invention, the speed change device is arranged, along with the gradual increase of the pressure at the rear end of the centrifugal pump body, the load of the output shaft is gradually increased, the rotation speed is reduced, the rotation speed of the outer gear ring is increased along with the increase, more work input by the driving shaft acts on the auxiliary driver, the auxiliary driver absorbs the work from the driving shaft when compressing gas, and the auxiliary driver transfers the work to the output end together with the driving shaft when the gas rebounds, and the auxiliary driver absorbs the work from the driving shaft and does work on the output shaft, so that the effect that the rotation speed of the output shaft is greatly reduced, and the rotation speed of the driving shaft is only slightly reduced or not reduced is achieved, thereby ensuring that the driving device does not deviate from the range of rated working conditions. Similarly, the invention can reduce the influence of the pressure rise at the rear end of the plunger pump body on the rotating speed of the water wheel by arranging the speed changing device, and ensure that the flow field in the water wheel is in a proper state.
The invention can change according to different types of pressure tests, thereby forming different pressure test pump systems and meeting the requirements of different pressure tests on fluidity and pressure maintaining property. Meanwhile, through the use of the air compressor and the energy accumulator, the highest pressure of the system for static pressure test is improved.
Drawings
FIG. 1 is a perspective view of a centrifugal pressure test pump unit of the present invention;
FIG. 2 is a further perspective view of a centrifugal pressure test pump unit of the present invention;
FIG. 3 is a perspective exploded view of the centrifugal pressure test pump unit of the present invention;
FIG. 4 is a diagram of a centrifugal test pump system according to a second and third embodiment of the present invention;
FIG. 5 is an enlarged view of FIG. 4 at A;
FIG. 6 is a diagram of a centrifugal test pump system according to a fourth embodiment of the invention;
FIG. 7 is a diagram of a centrifugal test pump system according to a fifth embodiment of the invention;
FIG. 8 is a diagram of a centrifugal test pump system according to a sixth embodiment of the invention;
FIG. 9 is a perspective view of a seventh centrifugal pressure test pump unit according to the embodiment of the present invention;
FIG. 10 is a schematic diagram of a seventh gear set according to an embodiment of the present invention;
fig. 11 is a schematic diagram of a seventh auxiliary driver according to an embodiment of the invention.
In the figure: 110-centrifugal pump body, 120-driving device, 130-liquid driving device, 131-eccentric wheel, 132-transmission cavity, 133-bent pipe, 140-plunger pump body, 210-water source, 220-pressure sensor, 230-three-way reversing valve, 240-reducing pipe, 250-side pipe, 260-water injection bypass, 270-one-way valve, 280-accumulator, 281-air compressor, 282-third shutoff valve, 291-first shutoff valve, 292-second shutoff valve, 310-liquid driving device water return pipeline, 320-pressure test water return pipeline, 330-throttle valve, 400-speed change device, 410-gear set, 411-driving shaft, 412-planet carrier, 413-planet gear, 414-intermediate gear, 415-external gear ring, 416-output shaft, 417-transmission gear, 420-auxiliary drive, 421-cylinder, 422-piston, 423-connecting rod, 424-crankshaft, 430-connecting shaft.
Detailed Description
In the description of the present embodiment, it should be noted that the azimuth or positional relationship indicated by the terms "upper", "lower", "inner", "bottom", etc. are based on the azimuth or positional relationship shown in the drawings, or the azimuth or positional relationship in which the inventive product is conventionally put in use, are merely for convenience of describing the present invention and simplifying the description, and are not indicative or implying that the apparatus or element to be referred to must have a specific azimuth, be configured and operated in a specific azimuth, and therefore should not be construed as limiting the present invention.
In the description of the present embodiment, it should also be noted that the terms "disposed," "connected," and "connected" are to be construed broadly, unless explicitly stated or limited otherwise.
For the purpose of making the objects, technical solutions and advantages of the present invention more apparent, embodiments of the present invention will be described in further detail below with reference to the accompanying drawings.
Example 1
Referring to fig. 1 to 3, the present embodiment discloses a centrifugal pressure test pump set including a centrifugal pump body 110 and a driving device 120, such as a motor, driving the centrifugal pump body 110, and further including a liquid driving device 130, a high-pressure pump body, a water injection outlet, and a pressurizing outlet; the hydraulic driving force device 130 is preferably a water wheel device, i.e. a device for driving the impeller to rotate by utilizing potential energy and kinetic energy of water, generally comprises a housing and an impeller rotating inside, and is a simple prior art and will not be described in detail. The outlet of the centrifugal pump body 110 is respectively communicated with the inlet of the liquid driving force device 130, the inlet of the high-pressure pump body and the water injection outlet, and the output end of the liquid driving force device 130 drives the high-pressure pump body to operate, and the outlet of the high-pressure pump body is a pressurizing outlet. The present embodiment controls the flow direction of two fluids at the output end of the centrifugal pump body 110 through a valve: one is that fluid is directly output through a water injection outlet after leaving the outlet of the centrifugal pump body 110 and is injected into pressure test equipment or a system, the other is that the fluid is divided into two paths after leaving the outlet of the centrifugal pump body 110, one path of fluid flows through the liquid driving force device 130, the liquid driving force device 130 is driven to rotate, the liquid driving force device 130 drives the high-pressure pump body to operate again, and the other path of fluid flows through the high-pressure pump body, and the fluid is output from a pressurizing outlet after being further increased in pressure by the high-pressure pump body. The valve may be disposed on each branch to control the opening and closing of each branch, and more preferably, a three-way reversing valve 230 is disposed, the outlet of the centrifugal pump body 110 is communicated with the inlet of the three-way reversing valve 230, the first outlet of the three-way reversing valve 230 is a water injection outlet, and the second outlet of the three-way reversing valve 230 is communicated with the inlet of the high-pressure pump body and the inlet of the liquid driving device 130. Further, the high-pressure pump body is preferably a plunger pump body 140, and the plunger pump body 140 can stably supply high pressure required in the pressurizing stage, has low requirements for stability of fluid, and does not cause serious abnormal phenomena such as cavitation and reflux.
In this embodiment, by providing the liquid driving device 130 downstream of the centrifugal pump body 110, the liquid driving device 130 is driven by a part of the water flow output from the centrifugal pump body 110, and the liquid driving device 130 drives the high-pressure pump body again, so that the high-pressure pump body pressurizes another part of the water output from the centrifugal pump body 110. In the water injection stage, water flow is directly output through a water injection outlet, the high-flow characteristic of the centrifugal pump body 110 is fully utilized to carry out quick water injection, and in the pressurization stage, part of water flow is separated to drive the liquid driving force device 130 and the high-pressure pump body to pressurize the other part of water flow, so that the effect of changing pressure with flow is realized, one set of electric drive system can be saved compared with the traditional design, the cost is reduced, and in addition, only the outlet flow direction of the centrifugal pump body 110 needs to be switched when the mode is switched, so that the operation is simple. More importantly, when the high-pressure pump body is the plunger pump body 140, the plunger pump body 140 is driven by the liquid driving force device 130, along with the gradual increase of the pressure in the pressure test equipment or the system, the pressure at the rear end of the plunger pump body 140 gradually increases, the driving force required by the plunger pump body 140 for conveying media gradually increases, so that the flow rate of the plunger pump body 140 gradually decreases, the water passing through the plunger pump body 140 decreases, the water passing through the liquid driving force device 130 increases, namely the water participating in driving the liquid driving force device 130 and the plunger pump body 140 increases, the pressurizing capacity of the plunger pump body 140 increases, the flow rate decreases until all the water passes through the liquid driving force device 130 and can not drive the plunger pump body 140 to continue to operate, at this moment, the liquid driving force device 130 and the plunger pump body 140 stop, serious accidents caused by excessive overpressure are avoided, the water flow output by the centrifugal pump body 110 can still pass through the liquid driving force device 130, no occurrence of a pump blocking phenomenon, and the protection effect on the pump, the motor and the test equipment or the system is achieved. The larger the output of the centrifugal pump body 110, the larger the amount of water and the water pressure that can flow through the hydraulic driving force device 130, and the larger the maximum pressurizing pressure of the plunger pump body 140. Therefore, as long as the output power of the centrifugal pump body 110 is set in the pressurization stage, the maximum pressurization pressure is set, and even if the operation is erroneous, the pressure in the pressure test device or system does not rise in an uncontrolled manner.
As a further scheme of this embodiment: the output end of the hydraulic driving force device 130 is connected with an eccentric wheel 131, the eccentric wheel 131 is in transmission connection with a plunger pump body 140 through a plunger rod, and the plunger rod is arranged in the transmission cavity 132. The eccentric 131 and the plunger rod are the basic components that make up the plunger pump, and are all well known in the art. The second outlet of the three-way reversing valve 230 is provided with a reducer pipe 240, the thick end of the reducer pipe 240 is connected with the second outlet of the three-way reversing valve 230, the thin end is connected with the inlet of the plunger pump 140, the side surface of the reducer pipe 240 extends outwards to form a side pipe 250, and the side pipe 250 is connected with the inlet of the liquid driving device 130.
As a further scheme of this embodiment: spatially, the high pressure pump body is a plunger pump body 140; the axis of the centrifugal pump body 110, the inlet of the centrifugal pump body 110, the axis of the liquid driving force device 130, the first outlet of the three-way directional valve 230, the inlet axis and the outlet axis of the plunger pump body 140 are parallel to each other, the outlet of the centrifugal pump body 110 faces the inlet of the liquid driving force device 130, and the outlet of the plunger pump body 140 communicates with the front end of the first outlet of the three-way directional valve 230. Further, an elbow pipe 133 may be provided at the outlet of the hydraulic power unit 130, and the outlet direction of the elbow pipe 133 may be the same as the first outlet direction of the three-way directional valve 230. By adopting the layout mode, the water coming out of the centrifugal pump body 110 is directly fed into the liquid driving force device 130 without steering, the liquid driving force device 130 can be driven to rotate by utilizing the kinetic energy of the water better, and the water inlet, the water injection outlet, the pressurizing outlet of the centrifugal pump body 110 and the water return port of the liquid driving force device 130 can be all integrated in one direction by the layout mode, so that the operation and the observation of operators are facilitated. Specifically, the front and rear sections of the plunger pump body 140 are respectively provided with a check valve 270 for matching with the water inlet and outlet of the plunger pump body 140, and the arrangement of the check valve 270 in the plunger pump body 140 is common knowledge in the art, and will not be described herein.
Example two
Referring to fig. 4 and 5, the present embodiment provides a centrifugal pressure test pump system, which includes a centrifugal pump body 110, the centrifugal pump body 110 is driven to operate by a driving device 120, and further includes a liquid driving device 130, a high pressure pump body and a water injection bypass 260, wherein the downstream of the centrifugal pump body 110 is respectively connected with the liquid driving device 130, the high pressure pump body and the water injection bypass 260, and the output end of the liquid driving device 130 drives the high pressure pump body to operate. The pressure test pump system controls the downstream of the centrifugal pump body 110 through a valve to open only the water injection bypass 260 or simultaneously open the hydraulic driving force device 130 and the high-pressure pump body. Preferably, the downstream of the centrifugal pump body 110 is connected to the inlet of the three-way directional valve 230, one outlet of the three-way directional valve 230 is connected to the water injection bypass 260, and the other outlet is connected to the hydraulic driving force device 130 and the high-pressure pump body, and the water injection bypass 260 is controlled to be opened or the hydraulic driving force device 130 and the high-pressure pump body are simultaneously opened by the three-way directional valve 230.
It should be understood by the skilled person that, even if the centrifugal pressure test pump set disclosed in the first embodiment is not adopted, the centrifugal pump body 110, the high-pressure pump body and the hydraulic driving force device 130 which are independent of each other are used and are mutually communicated through the pipeline and the valve, so as to form the centrifugal pressure test pump system disclosed in the first embodiment, and the centrifugal pressure test pump system also belongs to the protection scope of the present invention. The principle and the application method of the present embodiment are the same as those of the first embodiment, and are not described here again.
Example III
The hydrostatic test is divided into a dynamic hydrostatic test and a static hydrostatic test, and the static hydrostatic test is divided into a pressure decay test and a pressure withstanding test, and different pressure test pump systems are required to be matched according to different test requirements.
The dynamic hydrostatic test, namely that water continuously flows in the equipment, is further improved in the pressure test pump system according to the dynamic hydrostatic test on the basis of the second embodiment.
Referring to fig. 4, in the present embodiment, a water injection bypass 260 and a downstream of the high pressure pump body are merged and connected with a check valve 270 to prevent the backflow of high pressure liquid in the pressure test device or system. An accumulator 280 is connected downstream of the check valve 270 to stabilize the water pressure in the pressure test device or system. A pressure test device or system is connected downstream of the accumulator 280. Further, a pressure sensor 220 is provided between the check valve 270 and the pressure test device or system for monitoring the test pressure. A water source 210, such as a water tank, is connected upstream of the centrifugal pump body 110. The pressure test pump system also includes a hydraulic drive force device return line 310 and a pressure test return line 320 of the pressure test apparatus or system. If the water source 210 is a water tank, the hydraulic driving force apparatus return line 310 and the pressure test return line 320 are connected to the water tank. Further, in order to maintain the pressure in the pressure test device or system to be satisfactory, it may be necessary to limit the flow rate of the water flow, and a throttle valve 330 may be provided on the pressure test return line 320.
The present embodiment continues to deliver high pressure fluid to a pressure test device or system through the centrifugal pump body 110 and the high pressure pump body.
Example IV
In a pressure decay test, a device or system is gradually pressurized to a specified pressure and held for a period of time, and then the pressure drop is observed. If the pressure drops very rapidly, this indicates that there is a leak in the device or system. The test does not require constant supply of steady water pressure nor does it require the accumulator 280 to store energy. In the second embodiment, the pressure test pump system is further improved for the pressure decay test.
Referring to fig. 6, in the present embodiment, the downstream of the water injection bypass 260 and the high pressure pump body is merged and connected with the check valve 270 and the first shut-off valve 291, and the sequential positions of the check valve 270 and the first shut-off valve 291 are not particularly limited. Downstream of the check valve 270 and the first shut-off valve 291 is connected a pressure test device or system. Further, a pressure sensor 220 should be provided between the check valve 270 and the first shut-off valve 291 and the pressure test device or system. A water source 210 is connected to the upstream of the centrifugal pump body 110, and a liquid driving force device return water line 310 is provided to the downstream of the liquid driving force device 130. Of course, the pressure release pipeline and the pressure release valve should also be provided, the arrangement modes of the pressure release pipeline and the pressure release valve are various, technicians can set according to actual conditions, the pressure release pipeline and the pressure release valve belong to common knowledge in the field, and the embodiment mainly relates to a pump system, so that the pressure release pipeline and the pressure release valve are not specifically unfolded.
In the specific operation process of this embodiment, after the pressure test device or the system pressure reaches the requirement, the pressure decay test can be performed by closing the first shut-off valve 291. The pressure relief valve should of course also be closed during the entire pressurization and pressure maintaining process (except in the case of venting with a pressure relief line).
Example five
Referring to fig. 7, this embodiment is further optimized based on the fourth embodiment, when the test pressure is higher than the maximum pressure that can be provided by the high-pressure pump body, an accumulator 280 may be disposed downstream of the check valve 270 and the first shut-off valve 291 and upstream of the pressure test device or system, where the liquid side of the accumulator 280 is in communication with the pressure test line, and the gas side is in communication with the air compressor 281. A second shut-off valve 292 is provided between the accumulator 280 and the pressure test device or system. Further, a third shut-off valve 282 should be further disposed between the air compressor 281 and the accumulator 280, and the third shut-off valve 282 is closed in an initial state, so that the accumulator 280 can perform an energy storage function without air leakage.
In the specific operation process of the embodiment, after the high-pressure pump body is used to pressurize the pressure test equipment or system to a certain pressure, the first shut-off valve 291 is closed, then the air compressor 281 and the third shut-off valve 282 are opened, the air compressor 281 is used to pressurize the energy accumulator 280, so that the pressure in the pressure test equipment or system is further increased, and after the pressure meets the experimental requirement, the second shut-off valve 292 is closed to perform the pressure attenuation test.
Example six
In a pressure test, a device or system is pressurized to a specified pressure and held for a period of time to see if the device or system is able to withstand the pressure. This process is mainly tested for the pressure resistance and durability of the device or system. The liquid does not need to flow in the pressure test, but often requires a higher test pressure and needs to be maintained for a period of time, and the pressure should be maintained within a preset range with only a few leaks.
Referring to fig. 8, in the present embodiment, the second shutoff valve 292 may be deleted on the basis of the fifth embodiment.
In the specific operation process of this embodiment, after the high-pressure pump body is used to pressurize the pressure test device or system to a certain pressure, the first shut-off valve 291 is closed, then the air compressor 281 and the third shut-off valve 282 are opened, and the air compressor 281 is used to pressurize the accumulator 280, so that the pressure in the pressure test device or system is further increased until the pressure meets the test requirement, and then the pressure is preferably higher than the lower limit of the test requirement pressure, and then the third shut-off valve 282 is closed. In the present embodiment, during the pressure maintaining process, the capacity change caused by a small amount of leakage can be absorbed by the accumulator 280, so that the pressure in the pressure test device or system is still maintained within the preset range.
Example seven
Because the flow output by the centrifugal pump body 110 is large, the water injection efficiency into the pressure test system is high directly through the centrifugal pump body 110, and in the actual use process, the duration of the water injection stage can be prolonged as much as possible, and the duration of the pressurization stage is shortened. At the end of the water filling phase, the pressure in the pressure test system has increased to a certain extent, and the high pressure has an influence on the rotation of the centrifugal pump body 110, so that the rotational speed of the centrifugal pump body 110 is reduced, the efficiency is reduced, and even the driving device 120 may be damaged. To solve this problem, the present embodiment adds the transmission 400 on the basis of the first embodiment.
Referring to fig. 9 to 11, the transmission 400 includes a gear set 410 and an auxiliary drive 420, and the gear set 410 includes a drive shaft 411, a carrier 412, a planetary gear 413, an intermediate gear 414, an outer gear 415, an output shaft 416, and a transmission gear 417. At least two planetary gears 413 are arranged, an intermediate gear 414, the planetary gears 413 and an outer gear ring 415 form a planetary gear mechanism together, a driving shaft 411 is connected with the planetary gears 413 through a planet carrier 412 and synchronously rotates, an output shaft 416 is fixedly connected with the intermediate gear 414 coaxially and synchronously rotates, and a transmission gear 417 is meshed with the outer wall of the outer gear ring 415. The auxiliary driver 420 comprises a cylinder 421 and a piston 422, the piston 422 is in sealing sliding contact with the inner wall of the cylinder 421, gas is sealed between the piston 422 and the cylinder 421, and the piston 422 is connected with a crankshaft 424 through a connecting rod 423. The outer gear ring 415 is in driving connection with the crankshaft 424, and the driving connection manner is not particularly limited, wherein the simplest manner is to use a connecting shaft 430, one end of the connecting shaft 430 is fixedly connected with the driving gear 417 coaxially, and the other end is fixedly connected with the crankshaft 424 coaxially. The drive shaft 411 is connected to an output end of the drive device 120, and the output shaft 416 is connected to the centrifugal pump body 110.
The operating principle of the transmission 400 is as follows:
the planetary gear mechanism is a classical transmission mechanism, and the specific principle is not described in detail, and the characteristic is that the faster the rotation speed of the outer gear ring 415, the smaller the rotation speed ratio of the output shaft 416 and the driving shaft 411, that is, the smaller the transmission ratio. The outer gear ring 415 drives the crankshaft 424 to rotate through transmission, the crankshaft 424 rotates to drive the piston 422 to reciprocate, when gas is compressed, the piston 422 overcomes the pressure of the gas to do work, and meanwhile the elastic potential energy of the compressed gas is increased; when the compressed gas rebounds, the elastic potential energy of the gas is released, and the released energy is conducted to the crankshaft 424. When the above-described transmission 400 is applied to the first embodiment, as the pressure at the rear end of the centrifugal pump body 110 gradually increases, the load of the output shaft 416 gradually increases and the rotational speed decreases. If the external gear ring 415 does not rotate or the rotation speed is unchanged, the rotation speed of the driving shaft 411 is reduced, so that the rotation speed of the driving device 120 is reduced, the rated working condition is deviated, and the output is reduced. While the outer gear ring 415 of the present embodiment is in driving connection with the auxiliary driver 420, when the rotation speed of the output shaft 416 decreases, the rotation speed of the outer gear ring 415 increases along with the decrease, and more work input by the driving shaft 411 acts on the auxiliary driver 420, so that the auxiliary driver 420 absorbs work from the driving shaft 411 when compressing gas, and together with the driving shaft 411, transfers work to the output end when the gas rebounds. It can be seen that the auxiliary driver 420 itself is ideally energy-free, and is operative to absorb work from the driving shaft 411 and apply work to the output shaft 416, so as to achieve the effect that the rotation speed of the output shaft 416 is greatly reduced, and the rotation speed of the driving shaft 411 is only slightly reduced or not reduced, so as to ensure that the driving device 120 does not deviate from the range of the rated working condition.
As a further solution of this embodiment, a person skilled in the art may set an air inlet and an air outlet to control the pressure of the air in the auxiliary driver 420, so as to change the difficulty of compressing the air, and further change the influence degree of the auxiliary starter on the gear ratio of the gear set 410 according to actual needs.
Example eight
In the actual use process, along with the gradual rise of the pressure at the rear end of the plunger pump body 140, the running speed of the plunger pump body 140 gradually decreases, so that the rotation speed of the water wheel decreases along with the gradual rise, and if the rotation speed of the water wheel decreases too much, the water flow field can be changed, and the driving effect on the water wheel decreases. To solve this problem, the transmission 400 of the seventh embodiment may be added between the water wheel and the plunger pump 140 in the first embodiment. The drive shaft 411 is connected to the output of the water wheel, and the output shaft 416 is connected to the eccentric wheel 131.
When the transmission 400 is applied between the water wheel and the plunger pump 140, the load of the output shaft 416 gradually increases and the rotation speed decreases as the pressure at the rear end of the plunger pump 140 gradually increases. If the outer gear ring 415 does not rotate or the rotation speed is unchanged, the rotation speed of the driving shaft 411 is reduced, so that the rotation speed of the water wheel is reduced, and the flow field is damaged. While the outer gear ring 415 of the present embodiment is in driving connection with the auxiliary driver 420, when the rotation speed of the output shaft 416 decreases, the rotation speed of the outer gear ring 415 increases along with the decrease, and more work input by the driving shaft 411 acts on the auxiliary driver 420, so that the auxiliary driver 420 absorbs work from the driving shaft 411 when compressing gas, and together with the driving shaft 411, transfers work to the output end when the gas rebounds. It can be seen that the auxiliary driver 420 itself is not energy consuming in an ideal situation, and is effective in absorbing the work from the driving shaft 411 and acting on the output shaft 416, so as to achieve the effect that the rotation speed of the output shaft 416 is greatly reduced, but the rotation speed of the driving shaft 411 is only slightly reduced, so as to ensure that the flow field in the water wheel is in a proper state.
The above embodiments only illustrate the operation directly related to the pump system during the pressure test, and do not represent the only operation of the pressure test, and the actual operation should be performed by conventional venting, pressure relief, etc. steps according to the actual situation, and those operations not illustrated in detail are well known to those skilled in the art, and should be performed according to the relevant specifications of the test procedure.
The foregoing description of the preferred embodiments of the present invention should not be taken as limiting the invention, but rather should be understood to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the invention.
Claims (11)
1. An adaptive centrifugal pressure test pump set capable of avoiding overpressure comprises a centrifugal pump body (110) and a driving device (120) for driving the centrifugal pump body (110), and is characterized by further comprising a liquid driving force device (130), a high-pressure pump body, a water injection outlet and a pressurizing outlet; the outlet of the centrifugal pump body (110) is respectively communicated with the inlet of the liquid driving force device (130), the inlet of the high-pressure pump body and the water injection outlet, the output end of the liquid driving force device (130) drives the high-pressure pump body to operate, and the outlet of the high-pressure pump body is the pressurizing outlet;
the centrifugal pump further comprises a three-way reversing valve (230), wherein an outlet of the centrifugal pump body (110) is communicated with an inlet of the three-way reversing valve (230), a first outlet of the three-way reversing valve (230) is the water injection outlet, and a second outlet of the three-way reversing valve (230) is communicated with an inlet of the high-pressure pump body and an inlet of the liquid driving force device (130).
2. The centrifugal pressure test pump assembly according to claim 1, wherein the high pressure pump body is a plunger pump body (140).
3. The centrifugal pressure test pump set according to claim 2, wherein an output end of the liquid driving force device (130) is connected with an eccentric wheel (131), and the eccentric wheel (131) is in transmission connection with the plunger pump body (140) through a plunger rod; the second outlet of the three-way reversing valve (230) is provided with a reducing pipe (240), the thick end of the reducing pipe (240) is connected with the second outlet of the three-way reversing valve (230), the thin end of the reducing pipe is connected with the inlet of the plunger type pump body (140), the side surface of the reducing pipe (240) extends outwards to form a side pipe (250), and the side pipe (250) is connected with the inlet of the liquid driving force device (130).
4. A centrifugal pressure test pump assembly according to claim 3, wherein the axis of the centrifugal pump body (110), the inlet of the centrifugal pump body (110), the axis of the liquid driving force device (130), the first outlet of the three-way reversing valve (230), the inlet axis of the plunger pump body (140) and the outlet axis are parallel to each other, the outlet of the centrifugal pump body (110) is opposite to the inlet of the liquid driving force device (130), and the outlet of the plunger pump body (140) communicates with the front end of the first outlet of the three-way reversing valve (230).
5. The centrifugal pressure test pump set according to any one of claims 1-4, further comprising a transmission (400), the transmission (400) comprising a gear set (410) and an auxiliary drive (420), the gear set (410) comprising a drive shaft (411), a planet carrier (412), a planet gear (413), an intermediate gear (414), an outer gear ring (415), an output shaft (416), a transmission gear (417); the planetary gear mechanism comprises at least two planetary gears (413), wherein the intermediate gears (414), the planetary gears (413) and the outer gear ring (415) jointly form a planetary gear mechanism, the driving shaft (411) is connected with the planetary gears (413) through the planet carrier (412) and synchronously rotates, the output shaft (416) is fixedly connected with the intermediate gears (414) coaxially and synchronously rotates, and the transmission gear (417) is meshed with the outer wall of the outer gear ring (415); the auxiliary driver (420) comprises a cylinder body (421) and a piston (422), wherein the piston (422) is in sealing sliding contact with the inner wall of the cylinder body (421), gas is sealed between the piston and the cylinder body, and the piston (422) is connected with a crankshaft (424) through a connecting rod (423); the outer gear ring (415) is in driving connection with the crankshaft (424).
6. Centrifugal pressure test pump unit according to claim 5, characterized in that the drive shaft (411) is connected to the output of the drive means (120), and the output shaft (416) is connected to the centrifugal pump body (110).
7. Centrifugal pressure test pump unit according to claim 5, characterized in that the drive shaft (411) is connected to the output of the hydraulic drive device (130), and the output shaft (416) is connected to the high pressure pump body.
8. A centrifugal pressure test pump system, characterized by comprising the self-adaptive centrifugal pressure test pump set for avoiding overpressure according to claim 1, further comprising a water injection bypass (260) and a three-way reversing valve (230), wherein the downstream of the centrifugal pump body (110) is connected with the inlet of the three-way reversing valve (230), one outlet of the three-way reversing valve (230) is connected with the water injection bypass (260), and the other outlet is connected with the liquid driving force device (130) and the high-pressure pump body.
9. The centrifugal pressure test pump system according to claim 8, wherein the water injection bypass (260) and the downstream of the high pressure pump body are converged and connected with a one-way valve (270), an accumulator (280) is connected downstream of the one-way valve (270), and a pressure test device or system is connected downstream of the accumulator (280).
10. The centrifugal pressure test pump system of claim 9, further comprising a first shut-off valve (291) disposed downstream of the water injection bypass (260) and the high pressure pump body and upstream of the accumulator (280), a liquid side of the accumulator (280) being in communication with a pressure test line and a gas side being in communication with an air compressor (281).
11. Centrifugal pressure test pump system according to claim 10, characterized in that a second shut-off valve (292) is arranged between the accumulator (280) and the pressure test device or system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311351843.1A CN117108511B (en) | 2023-10-19 | 2023-10-19 | Self-adaptive centrifugal pressure test pump set and pump system capable of avoiding overpressure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311351843.1A CN117108511B (en) | 2023-10-19 | 2023-10-19 | Self-adaptive centrifugal pressure test pump set and pump system capable of avoiding overpressure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN117108511A CN117108511A (en) | 2023-11-24 |
| CN117108511B true CN117108511B (en) | 2023-12-22 |
Family
ID=88796820
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202311351843.1A Active CN117108511B (en) | 2023-10-19 | 2023-10-19 | Self-adaptive centrifugal pressure test pump set and pump system capable of avoiding overpressure |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN117108511B (en) |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101397970A (en) * | 2007-09-24 | 2009-04-01 | 付兵远 | Distribution-type tri-functional water wheel vacuum pump |
| CN202811382U (en) * | 2012-10-22 | 2013-03-20 | 石家庄国融安能分布能源技术有限公司 | Device used for replacing self-priming pump to work |
| CN103758722A (en) * | 2014-01-06 | 2014-04-30 | 西安昆仑液压传动机械厂 | Hydraulic drive type water injection pump |
| CN105240240A (en) * | 2015-10-17 | 2016-01-13 | 李德生 | Two-level pressure dividing and boosting energy-saving system for circulating water |
| CN108915970A (en) * | 2018-07-09 | 2018-11-30 | 北京中岩大地科技股份有限公司 | A kind of multi-cylinder liquid plunger locellus pump |
| CN210343745U (en) * | 2019-07-04 | 2020-04-17 | 江苏情意实业有限公司 | Remote strong self-suction device of duplex water supply pump |
| DE102019131129A1 (en) * | 2019-11-19 | 2021-05-20 | Voith Patent Gmbh | Hydraulic fracturing pumping apparatus and method of propelling the same |
| CN214698379U (en) * | 2020-12-01 | 2021-11-12 | 华能澜沧江水电股份有限公司 | Device for switching water supply of water pump under low water level |
| CN218439598U (en) * | 2022-11-15 | 2023-02-03 | 北京亿德龙石油天然气技术开发有限公司 | High-efficient power generation facility of pipeline residual pressure |
-
2023
- 2023-10-19 CN CN202311351843.1A patent/CN117108511B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101397970A (en) * | 2007-09-24 | 2009-04-01 | 付兵远 | Distribution-type tri-functional water wheel vacuum pump |
| CN202811382U (en) * | 2012-10-22 | 2013-03-20 | 石家庄国融安能分布能源技术有限公司 | Device used for replacing self-priming pump to work |
| CN103758722A (en) * | 2014-01-06 | 2014-04-30 | 西安昆仑液压传动机械厂 | Hydraulic drive type water injection pump |
| CN105240240A (en) * | 2015-10-17 | 2016-01-13 | 李德生 | Two-level pressure dividing and boosting energy-saving system for circulating water |
| CN108915970A (en) * | 2018-07-09 | 2018-11-30 | 北京中岩大地科技股份有限公司 | A kind of multi-cylinder liquid plunger locellus pump |
| CN210343745U (en) * | 2019-07-04 | 2020-04-17 | 江苏情意实业有限公司 | Remote strong self-suction device of duplex water supply pump |
| DE102019131129A1 (en) * | 2019-11-19 | 2021-05-20 | Voith Patent Gmbh | Hydraulic fracturing pumping apparatus and method of propelling the same |
| CN214698379U (en) * | 2020-12-01 | 2021-11-12 | 华能澜沧江水电股份有限公司 | Device for switching water supply of water pump under low water level |
| CN218439598U (en) * | 2022-11-15 | 2023-02-03 | 北京亿德龙石油天然气技术开发有限公司 | High-efficient power generation facility of pipeline residual pressure |
Also Published As
| Publication number | Publication date |
|---|---|
| CN117108511A (en) | 2023-11-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN109736953B (en) | Multi-start liquid oxygen kerosene engine of gas-driven pre-compressed turbine and starting method | |
| BRPI0620369A2 (en) | hydrostatic motor | |
| CN101907106A (en) | Active electric accumulator | |
| WO2013097399A1 (en) | Gas delivery system and gas delivery method | |
| JPWO2019021958A1 (en) | Pump and seal system | |
| CN111272404A (en) | Fire engine fire-fighting pipeline test system | |
| CN110985367A (en) | High-speed hydraulic pump performance test device | |
| CN101532515B (en) | High-voltage energy-storage hydraulic work device | |
| US3570244A (en) | Power piston drive for armatures | |
| CN117108511B (en) | Self-adaptive centrifugal pressure test pump set and pump system capable of avoiding overpressure | |
| CN110131073B (en) | Space propulsion system suitable for filling of large-capacity storage tank | |
| CN102213342A (en) | Non-dynamic shuttle-type cut-off valve driving control device | |
| US9360025B2 (en) | Hydraulic soft start system | |
| US9976576B2 (en) | Hydraulic distribution system employing a dual pump | |
| US8578713B2 (en) | Hydraulic soft start system | |
| CN219605691U (en) | Hydraulic control system of arm-pulling hook equipment | |
| CN115013210B (en) | Explosion-proof diesel engine start control system | |
| US4373866A (en) | Process to control the delivery of a single screw compressor | |
| CN213394642U (en) | Emergency cutting device for oil circuit | |
| CN212931823U (en) | Rotating wheel pressing device of axial-flow propeller turbine | |
| CN103518058B (en) | Fluid system and internal-combustion engine | |
| CN211652045U (en) | Fire engine fire-fighting pipeline test system | |
| CN108457934A (en) | A kind of hydraulic slip ring integrated experimental device and its application method | |
| CN113776737B (en) | Gas tightness pumping pressure equipment and gas tightness inspection method for DF (double fuel) series double fuel host | |
| CN220791623U (en) | A no electric emergency device for radial gate opens and close |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |