CN201786595U - Full water-lubrication superhigh pressure plunger-type water pump - Google Patents
Full water-lubrication superhigh pressure plunger-type water pump Download PDFInfo
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- CN201786595U CN201786595U CN2010205389865U CN201020538986U CN201786595U CN 201786595 U CN201786595 U CN 201786595U CN 2010205389865 U CN2010205389865 U CN 2010205389865U CN 201020538986 U CN201020538986 U CN 201020538986U CN 201786595 U CN201786595 U CN 201786595U
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Abstract
The utility model discloses a full water-lubrication superhigh pressure plunger-type water pump essentially comprising a chamber, a rotary main shaft, and a plunger port unit, wherein the plunger port unit contains a port valve component and a plunger sliding shoe component, the chamber being divided into a pressure chamber and a lubricating chamber which are mutually independent by the plunger sliding shoe component. The plunger sliding shoe component is driven by the rotary main shaft to perform reciprocating movement, which enables the port valve component to carry out water charging and water discharging through a water pump inlet and a water pump outlet and simultaneously to introduce water to the lubricating chamber through the water pump inlet so as to provide fluid lubrication to a rotary unit and thus achieve full water lubrication. The port valve component adopts integration design, which enables a quick exchanging of component in maintenance and a reduction in maintenance time. The plunger substantially conforms to a step, a cylindrical surface appearing with pit thereon, the bottom of the sliding shoe being provided with a step-like supporting chamber. The utility model solves the problem of friction and wearing of plunger, plunger sleeve kinematic pair and sliding shoe, and tilting tray pair under high speed and heavy duty, thus prolonging service time of water pump.
Description
Technical field
The utility model relates to water liquid pump technical field, is specifically related to a kind of fully water lubricating ultrahigh pressure plunger type water pump.
Technical background
Because the water hydraulic drive technology has safety, flame retarding, environmental friendliness, use and reliably reaches advantages such as easy to maintenance, satisfy the strong needs of human kind sustainable development, therefore this technology has obtained the attention of countries in the world, has become Fluid Transmission and Control field advanced subject.Power source spare-water hydraulic pump as the water hydraulic transmission has been obtained certain development.
At present, the research of relevant water hydraulic pump both at home and abroad concentrates on the mesohigh scope mostly, and pressure is between 10～21MPa.Abroad, the serial water pump of developing as Denmark Danfoss (Dan Fusi) company of Nessie (Buddhist nun's think of) is present ripe, the most most widely used a kind of plunger type water pump of technology in the world, this pump adopts the thrust plate flow, its flow is from 10L/min to 170L/min, pressure reaches 14～16MPa, and total efficiency is greater than 82%.Japan Kayaba (Xuan Chang) company and French Bronzavia Air-equipment (cloth dragon Martin Zawieja aircraft equipment) company cooperate, developing pressure is 21MPa, discharge capacity 7.05mL/r, volumetric efficiency is more than 85%, mechanical efficiency reaches 90% sea water hydraulic pump, this pump is three plunger swash plate rotational structure patterns, has adopted valve flow mode, and swash plate, plunger all adopt pottery.Domestic, the Central China University of Science and Technology developed valve flow sea water hydraulic plunger pump, rated working pressure 3.5MPa, Maximum operating pressure 6.3MPa in 1996, volumetric efficiency is greater than 86%, total efficiency is greater than 74%, and the sea water pump of flow 100L/min is used for the counterpart skirt draining of deep submergence rescue vehicle.
Pressure can satisfy the needs of most of occasion between 10～21MPa, but can't satisfy the needs of some special occasions.As the modernized manned deep-sea vehicle that uses in sea exploration and the exploitation, because submersible sampling back is because the increase of weight, or cause the variation of density of sea water owing to the characteristic (pressure, temperature) of aqueous medium, or along with the increase of submerged depth, submersible pressure-resistance structure generation resiliently deformable, these factors all can cause the variation of displacement of volume, thereby reserve buoyancy is changed.For guaranteeing that submersible has metastable operation attitude at certain depth, need carry out the buoyancy fine setting to it.Manned deeply along with the increase of manned deep-sea vehicle submerged depth, to the corresponding also increase that requires of sea water hydraulic pump delivery pressure in the buoyancy regulating system, as dive 6500m, the delivery pressure that then requires pump is 65MPa.Therefore at present the mesohigh water pump can not satisfy the needs of the device buoyancy regulating system of diving, and less about the research of ultrahigh pressure water pump, at the hydraulic pamp of manned latent device special requirement just still less.
The model utility content
The purpose of this utility model is to provide fully water lubricating ultrahigh pressure axial piston pump, and all friction pairs have avoided oil-water separation formula oil hydraulic pump owing to the inefficacy that seals and high pressure water infiltration lubricant reservoir causes by water lubrication from structure; Adopt special structural design to reach the antifriction antiwear purpose, solve the fretting wear problem of friction pair under the high-speed overload condition, improve the reliability and the life-span of ultrahigh pressure water pump.
Fully water lubricating ultrahigh pressure plunger type water pump comprises:
The pump main body, described pump main body comprises cavity, pump entrance and exit of pump;
Rotary unit, described rotary unit comprises rotary main shaft, and is located in the described pump main body; And
Piston valving unit, described piston valving unit are located in the described pump main body, and described piston valving unit comprises flow-distributing valve assembly and plunger piston slippery boots assembly;
Wherein, described plunger piston slippery boots assembly is located in the described cavity, and described cavity is divided into separate pressure chamber and lubricating cavity, described flow-distributing valve assembly and described pressure chamber fluid communication, described rotary unit is located in the described lubricating cavity, described lubricating cavity and pump entrance fluid communication;
Described plunger piston slippery boots assembly moves back and forth under the drive of described rotary main shaft, make described flow-distributing valve assembly absorb water and the draining action, provide fluid lubrication to lubricating cavity input water to give described rotary unit by pump entrance simultaneously by pump entrance and exit of pump.
As preferred embodiment, described flow-distributing valve assembly comprises suction valve and the delivery valve that is wholely set, wherein, the inlet of described suction valve is communicated with described pump entrance fluid, the outlet of described delivery valve is communicated with described exit of pump fluid, and the outlet of described suction valve is communicated with the inlet fluid of described delivery valve.
As preferred embodiment, described rotary unit also comprises the Returnning spring of being located at successively on the described rotary main shaft, backhaul dish and swash plate, described plunger piston slippery boots assembly comprises ladder plunger and piston shoes, wherein said ladder plunger can be dynamically connected by typed ball bearing pair and described piston shoes, also be provided with plunger channel in the described cavity, described ladder plunger slidably is arranged in the described plunger channel, wherein, one side of described backhaul dish contacts with described Returnning spring, the opposite side of described backhaul dish contacts with described piston shoes, described backhaul dish makes the bottom of described piston shoes be close to the surface of described swash plate under the effect of described Returnning spring, and then make rotatablely moving of described swash plate be delivered to described ladder plunger through described piston shoes, impel the to-and-fro motion in described plunger channel of described ladder plunger, form described pressure chamber, the cavity between the larger diameter end of described ladder plunger and described plunger channel and described lubricating cavity fluid communication between the smaller diameter end of described ladder plunger and described plunger channel.
As preferred embodiment, described plunger piston slippery boots assembly also comprises the ladder plunger bushing of being located in the described plunger channel, and described ladder plunger is located in the described ladder plunger bushing, and directly slidably contacts with described ladder plunger bushing.
As preferred embodiment, described ladder plunger comprises the damping hole that is communicated with described pressure chamber fluid of being located at its surperficial pit and radially being provided with, and described pit is connected with described damping hole.
As preferred embodiment, described piston shoes bottom is provided with the stepped shaft supporting cavity, and described supporting cavity is communicated with described lubricating cavity fluid.
As preferred embodiment, described rotary unit also comprises rolling bearing and the main shaft disk that cooperates with described rotary main shaft, and main shaft disk acts on described swash plate by rolling bearing, guarantees that described swash plate and described piston shoes are along the circumferential direction relative static.
Technique effect of the present utility model is embodied in:
1, plunger piston slippery boots assembly moves back and forth under the drive of described rotary main shaft, make described flow-distributing valve assembly absorb water and the draining action, provide fluid lubrication to lubricating cavity input water to give described rotary unit by pump entrance simultaneously by pump entrance and exit of pump.As optimization, the plunger design of plunger piston slippery boots assembly is become stairstepping, reduce at a high speed, contact stress between piston shoes and the swash plate under the fully loaded transportation condition; And increase spherical on plunger and piston shoes surface or, reduce fitting surface contact stress, the motion of restriction abrasive particle and form local dynamic pressure support, thereby solve the fretting wear problem of friction pair under the high-speed overload condition, the working life of having improved superpressure pump with spherical pit.
2. lubricating cavity is by the water supply of pump entrance, realize fully water lubricating, on this basis, consider sliding bearing serious fretting wear problem under the water lubrication operating mode, preferred rolling bearing replaces sliding bearing, has solved the fully water lubricating of high-pressure water pump under the high-speed overload condition, makes high-pressure water pump need not use lubricant oil, therefore use environmental protection more, easy to maintenance.Make this ultrahigh pressure water pump use extra large following time simultaneously and need not the boost pressure compensator, simplify the structure, have special advantage.
3. four spherical pits of high voltage terminal that wherein are positioned at plunger also are communicated with hyperbaric chamber by tiny damping hole, make to form two damping effects between plunger and plunger bushing, and the prevention plunger is stuck, and reduces directly to wear and tear between the two.
4. flow-distributing valve is the integrated whole assembly form of suction valve and delivery valve, can quick change assembly when safeguarding, shorten engineering time.The flow-distributing valve seal form is a ball valve, adopts the soft or hard combination simultaneously, and valve seat is PEEK, and spool is a pottery, has the structure letter and gathers, and has not only improved condition of high voltage lower seal reliability, has reduced the Strike note between spool and the valve seat simultaneously, thereby reduces the overall noise of pump.Spool adopts pottery, because ceramic phase to metal, has the hardness height, therefore the characteristics that density is little have improved the ability of anti-cavitation erosion; Help reducing the weight of spool, improve the response characteristic that flow is joined, reduce the lag time of flow-distributing valve, thus volumetric efficiency under improving at a high speed.
Description of drawings
Figure 1 shows that the utility model structure principle chart.
Figure 2 shows that flow-distributing valve modular construction schematic diagram.
Fig. 3 is a ladder plunger piston slippery boots assembly structural drawing, and wherein Fig. 3 a) is depicted as ladder plunger piston slippery boots assembly graphics, Fig. 3 b) be depicted as ladder plunger piston slippery boots assembly two-dimensional structure schematic diagram.
Figure 4 shows that the three-dimensional enlarged view of the anti-stuck damping hole of second order.
Embodiment
Below in conjunction with drawings and Examples the utility model is further described.
Valve flow fully water lubricating axial plunger high pressure sea-fresh water pump shown in Figure 1, comprise pump chamber, pump chamber is linked in sequence by front cover 2, rear end cover 15, cylinder body 14 and housing 4 and constitutes, and rotary main shaft 1 is connected with housing 4 and cylinder body 14 by ceramic bearing 5,6,23.
As shown in figures 1 and 3, near the flow-distributing valve assembly plunger piston slippery boots assembly 24 is installed in the cylinder body 14, plunger piston slippery boots assembly 24 comprises a stepped column plug sleeve 20 of axial placement, lay stepped plunger 37 in the plunger bushing 20, the larger diameter end of plunger 37 connects piston shoes 39 and forms typed ball bearing pair, cavity between smaller diameter end and the plunger bushing 20 forms pressure chamber 19, pressure chamber 19 also is that the delivery valve inlet communicates with the suction valve outlet, the cavity that larger diameter end and plunger bushing 20 forms is connected with lubricating cavity 11 through runner 21, to prevent to form in this cavity the contact stress of 9 of high pressure water increase piston shoes 39 and swash plates.Plunger 37 has sphere or elliposoidal pit 38 with piston shoes 39 surface Machining, is processed with tiny damping hole 38 at the plunger left end, as shown in Figure 4, by tiny damping hole 38 make plunger surface wherein one group of pit be connected with hyperbaric chamber 19.Piston shoes 39 end faces are processed with three grades of step supporting cavities 41, and supporting cavity 41 communicates with the housing inner chamber by runner 40.Stepped plunger has reduced under the ultra-high pressure condition contact stress between the piston shoes 39 and swash plate 9.When three grades of step supporting cavities 41 slide piston shoes 39 on swash plate 9, thereby produce dynamic pressure support by changing water film thickness.Pit 38 can reduce fitting surface contact stress, the motion of restriction abrasive particle, and forms local dynamic pressure support.Tiny damping hole 38 makes one group of pit 37 communicate with hyperbaric chamber 19, make 20 of plunger 37 and plunger bushings form two damping effects, solved to the volumetric efficiency that improves superpressure pump and reduced the stuck problem of plunger that plunger bushing and plunger gap cause, and reduce the probability of direct contact between the two, thereby reduce the wearing and tearing between plunger 37 and the plunger bushing 20.Above-mentioned each structure solves the wear problem of friction pair under the high-speed overload condition targetedly, has improved the working life of superpressure pump.
Rotary main shaft 1 front and back link to each other with housing 4 with cylinder body 14 respectively by annular bearing with rolling contact 23,5, and stretch out being connected of realization and prime mover (as motor, petrol engine etc.) through mechanical seal 3 and front cover 2 from housing 4.Be processed with the main shaft disk that becomes certain inclination angle with rotary main shaft on the rotary main shaft 1, the annular bearing with rolling contact 8 that passes on left of main shaft disk connects thrust bearing 7, and thrust-bearing 7 is connected with swash plate 9 again, and the right side of main shaft disk links to each other with housing 4 by thrust-bearing 6.By being used in combination annular bearing with rolling contact 8 and thrust bearing 7, making piston shoes 39 and swash plate 9 speed of related movement along the circumferential direction is zero in theory, motion between the two has only the relative swash plates 9 of piston shoes 39 to swing and produces less speed of related movement, has reduced between piston shoes 39 and the swash plate 9 wearing and tearing in the water lubrication condition.Being enclosed within Returnning spring 13 on the rotary main shaft 1 makes piston shoes 39 remain with swash plate 9 by ball pivot 12 and backhaul dish 10 to contact.Being fixedly coupled the hole with cylinder body 14 on the housing 4 is tapped hole, is connected and fixed with bolt between cylinder body 14, rear end cover 15 and the housing 4, after bolt is installed on tapped hole on the housing 4, is installed on the bolt housing locking nut 22 bolt is locked again.
The working procedure of this ultrahigh pressure water pump is specially: rotary main shaft 1 up time or rotate counterclockwise under the drive of prime mover drives thrust-bearing 7 rotating rings that are installed on the rotary main shaft swash plate and rotates, thereby promotes swash plate 9 swings that are attached thereto.Returnning spring 13 logical ball pivots 12 and backhaul dish 9 put on active force on each piston shoes 39 equably, piston shoes 39 are close on the swash plate 9 slide.Plunger 37 is subjected to the active force that swash plate 9 is given piston shoes 39, makes plunger 36 reciprocating in plunger bushing 20.When swash plate during along limit position (position as shown in Figure 1) setting in motion, the delivery valve spool 31 of flow-distributing valve assembly 16 is in closed condition.Piston shoes 39 are under the impacting force effect of backhaul dish 24, driving plunger 37 moves right, plunger 37 increases with the volume of the hyperbaric chamber 19 that plunger bushing forms, pressure descends, when dropping to certain value, when suction valve spool 27 because of the pressure of pump intake during greater than the making a concerted effort of pressure in the hyperbaric chamber 19 and inhalation valve spring 29 active forces, suction valve is opened, water is flow in the hyperbaric chamber 19 by the suction valve suction port by pump intake, realizes suction.When swash plate after 180 ° of limit position (as the position of Fig. 1) motions, this moment, plunger 37 was in all overhanging states, and when rotary main shaft continued rotation, piston shoes 39 were subjected to the active force of swash plate, promote the moving fortune of plunger 37 left, the volume of hyperbaric chamber 19 reduces gradually, and chamber internal force raises, with suction valve closure, overcome making a concerted effort of delivery valve spring 32 power and pump discharge pressure simultaneously, delivery valve is opened, hyperbaric chamber 19 inner high voltage water are flowed out from pump discharge through the delivery valve outlet, realize draining.When rotary main shaft 1 rotates a circle, each plunger suction and setting-out each once, along with the continuous rotation of rotary main shaft 1, each plunger also independently is finished the action of suction and draining continuously, thereby makes the continuous output flow of pump.
Claims (7)
1. fully water lubricating ultrahigh pressure plunger type water pump comprises:
The pump main body, described pump main body comprises cavity, pump entrance and exit of pump;
Rotary unit, described rotary unit comprises rotary main shaft, and is located in the described pump main body; And
Piston valving unit, described piston valving unit are located in the described pump main body, and described piston valving unit comprises flow-distributing valve assembly and plunger piston slippery boots assembly;
Wherein, described plunger piston slippery boots assembly is located in the described cavity, and described cavity is divided into separate pressure chamber and lubricating cavity, described flow-distributing valve assembly and described pressure chamber fluid communication, described rotary unit is located in the described lubricating cavity, described lubricating cavity and pump entrance fluid communication;
Described plunger piston slippery boots assembly moves back and forth under the drive of described rotary main shaft, make described flow-distributing valve assembly absorb water and the draining action, provide fluid lubrication to lubricating cavity input water to give described rotary unit by pump entrance simultaneously by pump entrance and exit of pump.
2. plunger type water pump according to claim 1, it is characterized in that, described flow-distributing valve assembly comprises suction valve and the delivery valve that is wholely set, wherein, the inlet of described suction valve is communicated with described pump entrance fluid, the outlet of described delivery valve is communicated with described exit of pump fluid, and the outlet of described suction valve is communicated with the inlet fluid of described delivery valve.
3. plunger type water pump according to claim 1 is characterized in that,
Described rotary unit also comprises Returnning spring, backhaul dish and the swash plate of being located at successively on the described rotary main shaft,
Described plunger piston slippery boots assembly comprises ladder plunger and piston shoes, and wherein said ladder plunger can be dynamically connected by typed ball bearing pair and described piston shoes,
Also be provided with plunger channel in the described cavity, described ladder plunger slidably is arranged in the described plunger channel,
Wherein, one side of described backhaul dish contacts with described Returnning spring, the opposite side of described backhaul dish contacts with described piston shoes, described backhaul dish makes the bottom of described piston shoes be close to the surface of described swash plate under the effect of described Returnning spring, and then make rotatablely moving of described swash plate be delivered to described ladder plunger through described piston shoes, impel the to-and-fro motion in described plunger channel of described ladder plunger, form described pressure chamber, the cavity between the larger diameter end of described ladder plunger and described plunger channel and described lubricating cavity fluid communication between the smaller diameter end of described ladder plunger and described plunger channel.
4. plunger type water pump according to claim 3, it is characterized in that, described plunger piston slippery boots assembly also comprises the ladder plunger bushing of being located in the described plunger channel, and described ladder plunger is located in the described ladder plunger bushing, and directly slidably contacts with described ladder plunger bushing.
5. plunger type water pump according to claim 4 is characterized in that, described ladder plunger comprises the damping hole that is communicated with described pressure chamber fluid of being located at its surperficial pit and radially being provided with, and described pit is connected with described damping hole.
6. plunger type water pump according to claim 3 is characterized in that, described piston shoes bottom is provided with the stepped shaft supporting cavity, and described supporting cavity is communicated with described lubricating cavity fluid.
7. according to any described plunger type water pump in the claim 1 to 6, it is characterized in that, described rotary unit also comprises rolling bearing and the main shaft disk that cooperates with described rotary main shaft, main shaft disk acts on described swash plate by rolling bearing, guarantees that described swash plate and described piston shoes are along the circumferential direction relative static.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205389865U CN201786595U (en) | 2010-09-21 | 2010-09-21 | Full water-lubrication superhigh pressure plunger-type water pump |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2010205389865U CN201786595U (en) | 2010-09-21 | 2010-09-21 | Full water-lubrication superhigh pressure plunger-type water pump |
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| CN201786595U true CN201786595U (en) | 2011-04-06 |
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| CN2010205389865U Expired - Fee Related CN201786595U (en) | 2010-09-21 | 2010-09-21 | Full water-lubrication superhigh pressure plunger-type water pump |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101956685A (en) * | 2010-09-21 | 2011-01-26 | 华中科技大学 | Fully water-lubricated super-pressure plunger water pump |
| CN116576101A (en) * | 2023-06-27 | 2023-08-11 | 北京工业大学 | Bidirectional axial plunger device for flow distribution of motor valve |
-
2010
- 2010-09-21 CN CN2010205389865U patent/CN201786595U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101956685A (en) * | 2010-09-21 | 2011-01-26 | 华中科技大学 | Fully water-lubricated super-pressure plunger water pump |
| CN116576101A (en) * | 2023-06-27 | 2023-08-11 | 北京工业大学 | Bidirectional axial plunger device for flow distribution of motor valve |
| CN116576101B (en) * | 2023-06-27 | 2024-02-23 | 北京工业大学 | Bidirectional axial plunger device for flow distribution of motor valve |
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| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20110406 Termination date: 20130921 |