CN109519353A - Big flow low noise piston pump - Google Patents
Big flow low noise piston pump Download PDFInfo
- Publication number
- CN109519353A CN109519353A CN201910048000.1A CN201910048000A CN109519353A CN 109519353 A CN109519353 A CN 109519353A CN 201910048000 A CN201910048000 A CN 201910048000A CN 109519353 A CN109519353 A CN 109519353A
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- Prior art keywords
- spool
- piston pump
- guide
- valve
- big flow
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- 239000000872 buffer Substances 0.000 claims abstract description 34
- 230000003139 buffering effect Effects 0.000 claims abstract description 22
- 238000007789 sealing Methods 0.000 claims abstract description 22
- 238000005266 casting Methods 0.000 claims abstract description 17
- 239000007788 liquid Substances 0.000 claims abstract description 13
- 238000013016 damping Methods 0.000 claims description 10
- 230000005540 biological transmission Effects 0.000 claims description 3
- 239000007787 solid Substances 0.000 claims 1
- 238000005086 pumping Methods 0.000 abstract description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 14
- 239000012530 fluid Substances 0.000 description 9
- 239000010865 sewage Substances 0.000 description 9
- 238000010586 diagram Methods 0.000 description 7
- 230000006378 damage Effects 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000002351 wastewater Substances 0.000 description 3
- 238000005119 centrifugation Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000009977 dual effect Effects 0.000 description 2
- 230000033001 locomotion Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 235000008733 Citrus aurantifolia Nutrition 0.000 description 1
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- 240000006909 Tilia x europaea Species 0.000 description 1
- 235000011941 Tilia x europaea Nutrition 0.000 description 1
- 230000004913 activation Effects 0.000 description 1
- 230000001154 acute effect Effects 0.000 description 1
- 238000013019 agitation Methods 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 238000010009 beating Methods 0.000 description 1
- 239000000969 carrier Substances 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 239000012141 concentrate Substances 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 239000013013 elastic material Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000004571 lime Substances 0.000 description 1
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- 229920001778 nylon Polymers 0.000 description 1
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- 230000008569 process Effects 0.000 description 1
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- 230000035939 shock Effects 0.000 description 1
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- 238000003911 water pollution Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/001—Noise damping
- F04B53/003—Noise damping by damping supports
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
- F04B53/1087—Valve seats
Abstract
The invention discloses a kind of big flow low noise piston pump, driving device is at least sequentially connected with a piston pump；The piston rod overhanging end of piston pump is respectively connected with reciprocal guide, is fixedly installed in the crank of driving device output end and passes through connecting rod and reciprocal the guide mutually company of strand；The rodless cavity and rod chamber of piston pump are communicated with the check valve towards inlet and liquid outlet respectively, and expansion bearing has buffering valve seat in the valve body of check valve；Spool shock-absorbing spring one end is supported with cushion block, and the other end of spool shock-absorbing spring is supported on sliding guide；The sealing surface of the buffering valve seat and the sealing surface of spool are oppositely arranged, and when the sealing surface of the sealing surface and spool that buffer valve seat fits, buffer the gap a that the gap b between valve seat and buffer casting is greater than between guide rod locating part and limit top plate.The big flow low noise piston pump not only working efficiency with higher realizes the big flow conveying of pump, and running noises are low, and pumping efficiency is high.
Description
Technical field
The present invention relates to a kind of fluid delivery pump more particularly to a kind of dirts applied in waste water at watercraft bilge processing system
Water delivery pump.
Background technique
The harm of waste water at watercraft bilge has many aspects, and sewage not only has corrosiveness to ship in cabin, can also be to cargo
It is damaged with electromechanical equipment, the serious normal operation that also will affect ship；And biloge water also needs to handle by collection
Outboard can be discharged after up to standard, otherwise will cause the water pollutions such as ocean or inland river.So waste water at watercraft bilge processing system is
One of most important marine system, bilge-water delivery pump are then indispensable piths in sewage disposing system.
At present bilge-water delivery pump mostly using centrifugation delivery pump, although centrifugal pump have the characteristics that it is simple and compact for structure,
But centrifugal pump must can work, this means that without suction capacity by hydraulically full in the pump housing and suction line before activation
Bilge ponding must be waited to reach certain depth, just can be carried out the pump housing and pour water operation, start to drain to start delivery pump.Obviously this
It is not easy to very much realize the continuous discharge of the long-distance centralized control and sewage of sewage treatment, it is easy to form a large amount of ponding of the bilge.
Simultaneously because centrifugal pump is not suitable for the sewage transport of small flow, big pressure head, transfer efficiency is low, and centrifugation delivery pump is dfficult to apply to greatly
In type ship bilge water treatment system.If it is discontented not pour water or pour water in pump when being centrifuged pump operation, air is had in pump case, by
Very low in atmospheric density, the centrifugal force generated after rotation is small, so that impeller center area is formed by low pressure and is not enough to suck in sewage
In pump, form " air sinuses " phenomenon, even if centrifugal pump starting can not convey liquid, also will form very big fluid agitation noise and
Pump housing vibration, not only directly affects the concealment of ship and the ship of war, but also can be to the life and work of ship's staff
Environment brings very big influence.
The most obvious feature of reciprocating piston pump be with suction capacity, it is not very sensitive to sewage physical and chemical properties,
Liquid, gas mixture can be conveyed, and very high pressure can be reached, pressure change does not influence the flow of pump, and pulsation is required
Not high biloge water conveying is particularly suitable.But single action piston pump, since one way working efficiency is not high, sewage output ripple is made an uproar
Sound is larger；The rod chamber and rodless cavity of double acting piston pump are working chamber, not only increase the working efficiency of pump, and increase
The output flow of pump.But with the enlargement of ship, biloge water is not only measured greatly, and require be able to achieve remote operation,
Big flow concentrates transport process, and existing single-cylinder dual-action piston pump is not still able to satisfy the conveying needs of bilge-water big flow.
Check valve in especially existing piston pump can generate biggish beating knock in the opening and closing course of work, when nonreturn valve core is in cabin
Under the action of bottom water pressure, spool is separated with valve seat and is opened, and when biloge water reverse flow, Fluid pressure pushes spool to valve
Seat and close, to cut off flowing.Therefore the spool of check valve is constantly separated or is pasted with valve seat under the action of biloge water
It closes, is formed between spool and valve seat and continually flop and beat, and with the raising and loine pressure of non-return valve operational frequency
Increase, reciprocating motion of the pistons accelerates, and the impact of spool and valve base chamber is further violent.This spool and valve base chamber it is frequent and acute
Strong percussion will cause spool first or the damage of valve seat is broken, or even keep check valve entirely ineffective；Furthermore spool and valve base chamber
It is frequent tap the damage for easilying lead to sealing surface, cause poorly sealed and form reverse leakage；In addition the work of piston pump
Noise not only influences the concealment of the ship of war and the life and work of ship's staff, but also can seriously affect the use of pump
Performance and used life.
Summary of the invention
For above-mentioned deficiency present in the prior art, technical problem to be solved by the invention is to provide a kind of big flows
Low noise piston pump, not only working efficiency with higher, to realize that big flow conveys, and running noises are low, realize tranquil
Operation.
In order to solve the above-mentioned technical problem, big flow low noise piston pump of the invention, including driving device, and with drive
The piston pump of dynamic device transmission connection, the driving device are at least sequentially connected with a piston pump；The piston rod of each piston pump
Overhanging end is respectively connected with reciprocal guide, and the crank for being fixedly installed in driving device output end passes through connecting rod and reciprocal guide phase
The company of strand；Crank corresponding to each piston pump is arranged in a staggered manner each other；The rodless cavity of the piston pump has been respectively communicated with towards feed liquor
The check valve of mouth and liquid outlet, the rod chamber of the piston pump are also respectively communicated with the check valve towards inlet and liquid outlet；Institute
Stating check valve includes valve body, and expansion bearing has buffering valve seat in the valve body, and buffer spring is further fixedly arranged on valve body
Seat is provided with buffer spring between buffering valve seat and buffer casting；Fixation is supported by limit top plate on valve body, and sliding is led
Bar is actively supported on valve body by limit top plate, and sliding guide upper end is fixedly installed guide rod locating part, guide rod locating part with
Limit top plate position is corresponding；It is movably installed with spool on sliding guide, spool vibration damping is provided in the spring cavity of the spool
Spring, spool shock-absorbing spring one end are supported with cushion block, and the other end of spool shock-absorbing spring is supported on sliding guide；It is described
The sealing surface of the sealing surface and spool that buffer valve seat is oppositely arranged, when the sealing surface of buffering valve seat and the sealing surface of spool fit
When, buffer the gap a that the gap b between valve seat and buffer casting is greater than between guide rod locating part and limit top plate.
In above-mentioned piston pump, driving device and several piston pumps mutually parallel and are sequentially connected, and form more pumps simultaneously
The pump configuration of work can generate very high row pressure and biggish output flow, meet the work of quick big flow conveying sewage
It needs, effectively increases the working efficiency of pump, also simplify pump configuration.The overhanging end of piston pump piston bar is connected with reciprocal guiding
Device, the reciprocal guide not only ensure that piston pump piston bar moves back and forth in the axial direction always, it is ensured that piston pump it is efficient
Smooth working, reduces the operation troubles of piston pump, and piston rod is enabled to obtain longer reciprocating stroke, to guarantee to live
Fill in the increase of pump output flow, the raising of transfer efficiency.Driving crank corresponding to piston pump is mutually spatially arranged in a staggered manner, both
The unbalanced of driving device driving load can be effectively reduced, output fluid pulse and its microseismic noise are also effectively reduced.Due to each
The rod chamber and rodless cavity of piston pump are communicated with the check valve towards inlet and liquid outlet respectively, constitute Multi-cylinder dual
Piston pump, piston pump rod chamber and rodless cavity are working chamber, in addition the crank of driving piston rod movement is to be arranged in a staggered manner, into one
Step reduces output ripple, the balanced load of driving device.More since the sliding guide upper end of check valve is provided with guide rod limit
Position part, when buffering valve seat and spool fit close, the gap b buffered between valve seat and buffer casting is greater than guide rod locating part
Gap a between limit top plate；The pressure difference of spool two sides becomes larger when closed check valve, acts on lower valve in medium fluid pressure
Core is accelerated push to buffer valve seat, spool and valve seat close to when can reach maximum closing velocity, spool is with sliding guide at this time
Close to valve seat, when spool and buffering valve seat brush up against, buffering valve seat is gentle to be rushed spring and plays absorbing damping effect, and one first
And downlink a distance, so that spool closing velocity is slowed down；It is continued traveling downwardly with back valve core and sliding guide with valve seat,
When guide rod locating part brushes up against limit top plate, sliding guide is no longer gone, since spool shock-absorbing spring is supported on sliding guide,
The spool of downlink starts to compress spool shock-absorbing spring, so that spool shock-absorbing spring and buffer spring play a role jointly, and makes valve
Core slows down, so that the impact of spool and valve seat slows down, has not only avoided the damage of valve element and sealing surface, but also greatly reduce valve
Closing noise.When check valve is opened, medium fluid pushes spool uplink, with the separation of spool, valve seat, spool two sides
Pressure difference becomes smaller, and spool speed uplink can gradually slow down, when spool arrives limes superiors position close to limit top plate, cushion block and valve
Core shock-absorbing spring plays the role of slowing down impact vibration between spool and limit top plate jointly, achievees the purpose that vibration and noise reducing.
The preferred embodiment of the present invention, the driving device are sequentially connected with 2-6 piston pumps.It is structurally reasonable, it is convenient for
Implement.
Further embodiment of the invention, the driving device include speed changer, to drive the motor of speed changer.It is convenient for
Realize more pump drivings.
The preferred embodiment of the present invention, the reciprocal guide includes guiding carrier, and guiding carrier is slidably supported in guide rail
On road, piston rod overhanging end is fixedly connected with guiding carrier, and one end of connecting rod is mutually hinged with guiding carrier, the other end and crank of connecting rod
It is mutually hinged, the centerline parallel of guide rails and piston pump is arranged.It is simple with structure, piston rod smoothly edge can be effectively ensured
Axial line moves back and forth.
The preferred embodiment of the present invention, spatial intersecting angle α=80 ° -100 ° of adjacent two crank.The structure makes one to live
Stopper rod has relatively small moment pumping velocity, and another piston rod has relatively high moment pumping velocity, it is driven with balancing
Dynamic device load, reduces output ripple.
When the preferred embodiment of the present invention, the sealing surface of the buffering valve seat and the cover of spool fit, trimmer valve
(2-4) times of gap a of the gap b between guide rod locating part and limit top plate between seat and buffer casting.It can be effective
The speed of spool when slowing down closed check valve, reduces the impact of spool, valve base chamber, and one-way valve structures is made to become rationally compact.
Further embodiment of the invention is fixedly installed with guide rod lower slider, the sliding on the buffer casting
The upper end of guide rod is slidably supported in limit top plate, and the lower end of sliding guide is slidably supported on guide rod lower slider；The guide rod
Locating part is located at the top of limit top plate.Sliding guide bearing is reliable, and slide-and-guide is good, and limit is reliable.
One end of further embodiment of the invention, the spool shock-absorbing spring is supported on by shock-absorbing spring undersetting
On sliding guide, the spool shock-absorbing spring other end is supported with cushion block by shock-absorbing spring upper bracket, cushion block sliding
It is set on sliding guide；Spool cover board is fixedly connected on the spool, the cushion block is movably placed in spool cover board
Center, the shock-absorbing spring upper bracket are supported on the inside of spool cover board.Both the closing vibration damping that can have realized spool, can also be real
The opening vibration damping of existing spool.
Further embodiment of the invention is provided with valve base seal between buffering valve seat and the valve body；The valve
Seal spool part is provided between core and sliding guide.The sealing being reliably achieved between movable part.
The preferred embodiment of the present invention, the valve base seal and seal spool part are O-ring seal；The buffering
Cushion block is elastic cushion block；The limit top plate is fixedly supported on valve body by support rod.Sealing, damping property are reliable and stable,
Limit top plate support is reliable.
Detailed description of the invention
Big flow low noise piston pump of the present invention is described further with reference to the accompanying drawings and detailed description.
Fig. 1 is a kind of structure principle chart of embodiment of big flow low noise piston pump of the present invention；
Fig. 2 is a kind of overlooking structure diagram of specific embodiment of big flow low noise piston pump of the present invention；
Fig. 3 is the main cross section structure diagram of Fig. 2 illustrated embodiment；
Fig. 4 is A-A the schematic diagram of the section structure of Fig. 3；
Fig. 5 is the spatial position figure of two cranks in Fig. 2 illustrated embodiment；
Fig. 6 is the structural schematic diagram of check valve (being in close state) in Fig. 2 illustrated embodiment.
In figure, 1-connecting rod；2-cranks；3-speed changers；4-motors；5-reciprocal guides, 501-guide rails,
502-guide rollers, 503-guiding carriers, 504-shaft couplings；6-inlets；7-liquid outlets；8-check valves, 801-slidings
Guide rod, 802-guide rod lower sliders, 803-buffer castings, 804-valve bodies, 805-support rods, 806-limit top plates,
807-spool shock-absorbing springs, 808-shock-absorbing spring upper brackets, 809-guide rod locating parts, 810-cushion blocks, 811-spools
Cover board, 812-connection bolts, 813-spools, 814-buffering valve seats, 815-valve base seals, 816-buffer springs,
817-seal spool parts, 818-shock-absorbing spring undersettings；9-piston pumps, 901-piston rods, 902-cylinder bodies, 903-are lived
Plug, 904-rodless cavities, 905-rod chambers；10-manifolds, 101-go out sap cavity, 102-admission chambers.
Specific embodiment
Big flow low noise piston pump as shown in Figure 1.The piston pump includes driving device, and driving device is by 3 He of speed changer
It drives the motor 4 of speed changer 3 to form, is fixedly installed with crank 2 in two output shaft ends of speed changer 3, crank 2 is through corresponding
901 phase of piston rod of connecting rod 1 and reciprocal guide 5 and piston pump 9 is hinged.Piston pump 9 is using single rod pump to be formed with bar
Chamber and rodless cavity.Two check valves 8 for leading to inlet 6 and liquid outlet 7 are respectively communicated on rod chamber, equally on rodless cavity
Also two check valves 8 for leading to inlet 6 and liquid outlet 7 are respectively communicated with；Therefore 4 are at least communicated on each piston pump 9
Check valve 8.
In big flow low noise piston pump as shown in Figures 2 and 3, the motor 4 and speed changer 3 of driving device combine as a whole
And motor speed-changing device is constituted, and two output shafts are symmetrically stretched out in the two sides of speed changer 3, it is fixed on two output shafts
Crank 2 is installed.The outer end of crank 2 is hinged with connecting rod 1, and the other end of connecting rod 1 is hinged on guiding carrier 503, guiding carrier 503
Two side ends are symmetrically hinged with guide rails 501, and each 502 rolling bearing of guide roller is led in corresponding guide rails 501
Approach rail road 501 is rectilinear orbit and is parallel to each other that two rectilinear orbit is parallel to the center line of piston pump 9, and guide rails
501 are fixedly connected on the cylinder cap of 902 one end of cylinder body of piston pump 9, and it is protruding that piston rod 901 sealingly extends through the end cylinder cap,
The extension end of piston rod 901 is connected on guiding carrier 503 by shaft coupling 504.Guide rails 501, guide roller 502, guiding
Frame 503 and shaft coupling 504 constitute reciprocal guide 5.The cylinder cap of 902 other end of cylinder body of piston pump 9 is fixedly connected on manifold
On 10 cabinet.
Manifold 10 as shown in Figure 4, the manifold 10 are divided into out sap cavity 101 and admission chamber 102, out sap cavity 101
It is connected with liquid outlet 7, admission chamber 6 is connected with admission chamber 102, and eight check valves 8 are fixedly attached among manifold 10
On floor.Eight check valves 8 are respectively communicated with rod chamber 905 and rodless cavity in each piston pump 9 according to connected relation shown in FIG. 1
904, and it is connected to inlet 6 and liquid outlet 7.
As shown in figure 5, the diagram represents the space of two corresponding cranks 2 of piston pump 9 in the present embodiment with anticipating
Installation site.Angle α=90 ° of two cranks 2 spatially, the crank handle turns connecting rod in this way in diagram vertical position turn
When dynamic, the hinge point of the crank and connecting rod has biggish horizontal velocity component and displacement component, and turns with the crank
Dynamic, horizontal velocity component and displacement component will gradually become smaller；And the crank handle turns connecting rod for being now in diagram horizontal position turns
When dynamic, hinge point has lesser horizontal velocity component and displacement component, but as the crank rotates, horizontal velocity component
It will be become larger with displacement component, and so this structure can be with the load of balance drive device, and become the output ripple of pump
It obtains steadily.
Fig. 6 shows the specific structure of check valve, which includes the valve body 804 in short tube tubular, in valve body 804
End fixed bearing suitable for reading has 4 support rods 805, is fixedly installed with limit top plate 806 at the top of support rod 805.In valve body 804
Lower mouth end in be fixedly installed with buffer casting 803, be equipped in buffer casting 803 along the radially fixed of valve body 804
Guide rod lower slider 802.
There is buffering valve seat 814 in the inner tube wall expansion bearing of valve body 804, buffers the structure annular in shape of valve seat 814, buffering
Valve base seal 815 is installed between 804 inner wall of peripheral side and valve body of valve seat 814, which is O-shaped
Rubber seal.Four buffer springs 816 are supported by between the lower end surface and buffer casting 803 of buffering valve seat 814, are buffered
Spring 816 is compression cylindrical spring, and the lower end of the buffer spring 816 is located in the correspondence spring eye of buffer casting 803.
Sliding guide 801 along valve body 804 center line pass through limit top plate 806 and guide rod lower slider 802 it is slidably supported in
On valve body 804.The upper end of sliding guide 801 is slidably supported in the correspondence guide rod hole of limit top plate 806, in sliding guide 801
Upper end at the top of be fixedly installed with guide rod locating part 809, the guide rod locating part 809 can not also use separate structure and with sliding
Guide rod 801 is as an overall structure.The lower end of the sliding guide 801 then slidably supported correspondence guide rod in guide rod lower slider 802
Kong Zhong.It is set with spool 813 in the middle section position of sliding guide 801, the core position of spool 813 is provided with spring cavity, it should
Spool shock-absorbing spring 807 is provided in spring cavity.Spool shock-absorbing spring 807 is compression cylindrical spring, and lower end passes through vibration damping bullet
Spring undersetting 818 is supported on sliding guide 801, i.e., shock-absorbing spring undersetting 818 is fixedly connected on sliding guide 801 or slides
Dynamic guide rod 801 is integral structure.The upper end of spool shock-absorbing spring 807 is supported with cushion by shock-absorbing spring upper bracket 808
Block 810,810 sliding sleeve of cushion block is loaded on sliding guide 801, and the cushion block 810 can be slidably disposed in cartridge cover
The center of plate 811, the shock-absorbing spring upper bracket 808 in 813 spring cavity of spool are supported in spool cover board 811
Side.Spool cover board 811 is fixedly connected on spool 813 by connecting bolt 812, and cushion block 810 is made of elastic material, such as
Nylon cushion block, rubber cushion blocks etc..The other end of spool 813 is slidably socketed with sealing against each other with sliding guide 801, spool 813 with
Seal spool 817 is installed, which is also O-shaped rubber seal between sliding guide 801.
When 813 downlink of spool is closed, since the fluid pressure difference between 813 both ends of spool is increasing, downstream rate becomes faster.When
When the sealing surface of spool 813 and the sealing surface of buffering valve seat 814 fit and constitute sealing pair, the lower end surface of valve seat 814 is buffered
Gap b between buffer casting 803 is greater than the gap a between guide rod locating part 809 and limit top plate, and a in the present embodiment=
1mm,b=3mm；Preferably b=(2-4) a.
Spool 813 is under medium fluid effect, and after spool 813 fits with buffering valve seat 814, the continuation of spool 813 is being situated between
Continue to compress buffer spring 816 under the promotion of mass flow body and by buffering valve seat 814, when guide rod locating part 809 and limit top plate
806 collide in time, and sliding guide 801 stops with valve downlink, the downstream rate of spool 813 and push away to begin through spool cover board
811 and shock-absorbing spring upper bracket 808 compress spool shock-absorbing spring 807, spool shock-absorbing spring 807 and buffer spring 816 are total at this time
With playing a role, with further absorbing vibration damping, the impact vibration and impact noise for reducing spool and valve seat to the maximum extent are realized.
When check valve is opened, the uplink under medium fluid effect of spool 813, since the valve inner flow passage of check valve gradually becomes
Greatly, the pressure difference of 813 two sides of spool becomes smaller.Spool speed uplink can be gradually slack-off.When cushion block 810 brushes up against limit top plate 806
When inside, cushion block 810 plays the role of vibration damping absorbing first.Then spool 813 is further through shock-absorbing spring undersetting 818 and valve
Core shock-absorbing spring 807 plays vibration damping shock sucking function.
It is above-mentioned only to have enumerated a kind of preferred embodiment of the invention, but the present invention is not limited to the above embodiments,
It is fallen within the protection scope of the present invention without prejudice to made modifications and variations in the case where general principles.
Claims (10)
1. a kind of big flow low noise piston pump, including driving device, and the piston pump (9) with driving device transmission connection,
It is characterized by: the driving device is at least sequentially connected with a piston pump (9)；The piston rod (901) of each piston pump (9) is outside
Stretch end and be respectively connected with reciprocal guide (5), be fixedly installed in the crank (2) of driving device output end pass through it is connecting rod (1) and reciprocal
Guide (5) the mutually company of strand；Crank (2) corresponding to each piston pump (9) is arranged in a staggered manner each other；The piston pump (9) without bar
Chamber (904) is respectively communicated with the check valve (8) towards inlet (6) and liquid outlet (7), the rod chamber (905) of the piston pump (9)
Also it is respectively communicated with the check valve (8) towards inlet (6) and liquid outlet (7)；The check valve (8) includes valve body (804),
The interior expansion bearing of the valve body (804) has buffering valve seat (814), is further fixedly arranged on buffer casting on valve body (804)
(803), buffer spring (816) are provided between buffering valve seat (804) and buffer casting (803)；It is solid on valve body (804)
Surely it is supported by limit top plate (806), sliding guide (801) is actively supported on valve body (804) by limit top plate (806), sliding
Dynamic guide rod (801) upper end is fixedly installed guide rod locating part (809), guide rod locating part (809) and limit top plate (806) position phase
It is corresponding；It is movably installed with spool (813) on sliding guide (801), is provided with spool vibration damping in the spring cavity of the spool (813)
Spring (807), spool shock-absorbing spring (807) one end are supported with cushion block (810), the other end of spool shock-absorbing spring (807)
It is supported on sliding guide (801)；The sealing surface of the sealing surface and spool (813) of buffering valve seat (814) is oppositely arranged, when
When the sealing surface of the sealing surface and spool (813) that buffer valve seat (814) fits, valve seat (814) and buffer casting are buffered
(803) the gap b between is greater than the gap a between guide rod locating part (809) and limit top plate (806).
2. big flow low noise piston pump according to claim 1, it is characterised in that: the driving device and 2-6 work
Plug pump (9) transmission connection.
3. big flow low noise piston pump according to claim 1 or 2, it is characterised in that: the driving device includes becoming
Fast device (3), to drive the motor (4) of speed changer (3).
4. big flow low noise piston pump according to claim 1, it is characterised in that: the reciprocal guide (5) includes
Guiding carrier (503), guiding carrier (503) is slidably supported on guide rails (501), piston rod (901) overhanging end and guiding carrier
(503) it is fixedly connected, one end and the guiding carrier (503) of connecting rod (1) are mutually hinged, and the other end and the crank (2) of connecting rod (1) are mutually cut with scissors
Even, the centerline parallel of guide rails (501) and piston pump (9) is arranged.
5. big flow low noise piston pump according to claim 1, it is characterised in that: hand in the space of adjacent two crank (2)
Alternate angle α=80 ° -100 °.
6. big flow low noise piston pump according to claim 1, it is characterised in that: described to buffer the close of valve seat (814)
When cover and the cover of spool (813) fit, buffering the gap b between valve seat (814) and buffer casting (803) is guide rod
(2-4) of gap a between locating part (809) and limit top plate (806) times.
7. big flow low noise piston pump according to claim 1, it is characterised in that: on the buffer casting (803)
It is fixedly installed with guide rod lower slider (802), the upper end of the sliding guide (801) is slidably supported on limit top plate (806), slides
The lower end of dynamic guide rod (801) is slidably supported on guide rod lower slider (802)；The guide rod locating part (809) is located at limit top plate
(806) top.
8. according to claim 1, big flow low noise piston pump described in 6 or 7, it is characterised in that: the spool shock-absorbing spring
(807) one end is supported on sliding guide (801) by shock-absorbing spring undersetting (818), and spool shock-absorbing spring (807) is another
End is supported with cushion block (810) by shock-absorbing spring upper bracket (808), which leads loaded on sliding
On bar (801)；It is fixedly connected with spool cover board (811) on the spool (813), the cushion block (810) is movably placed in valve
The center of core cover plate (811), the shock-absorbing spring upper bracket (808) are supported on the inside of spool cover board (811).
9. according to claim 1, big flow low noise piston pump described in 6 or 7, it is characterised in that: the buffering valve seat (814)
Valve base seal (815) are provided between valve body (804)；Valve is provided between the spool (813) and sliding guide (801)
Core sealing element (817).
10. big flow low noise piston pump according to claim 9, it is characterised in that: the valve base seal (815) and
Seal spool part (817) is O-ring seal；The cushion block (810) is elastic cushion block；The limit top plate (806) is logical
Support rod (805) is crossed to be fixedly supported on valve body (804).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910048000.1A CN109519353B (en) | 2019-01-18 | 2019-01-18 | High-flow low-noise piston pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910048000.1A CN109519353B (en) | 2019-01-18 | 2019-01-18 | High-flow low-noise piston pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109519353A true CN109519353A (en) | 2019-03-26 |
| CN109519353B CN109519353B (en) | 2024-04-09 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910048000.1A Active CN109519353B (en) | 2019-01-18 | 2019-01-18 | High-flow low-noise piston pump |
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| Country | Link |
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| CN (1) | CN109519353B (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1323817A (en) * | 1970-05-22 | 1973-07-18 | Horn Armaturen | Centrifugal pumps |
| CN1379180A (en) * | 2002-03-15 | 2002-11-13 | 陈根生 | Rotor-type piston pump |
| CN101275555A (en) * | 2008-03-31 | 2008-10-01 | 浙江工业大学 | Hollow structure valve core for reciprocating pump in-out one-way valve set |
| JP2014214621A (en) * | 2013-04-23 | 2014-11-17 | 三菱電機株式会社 | Piston pump |
| CN104314802A (en) * | 2014-09-10 | 2015-01-28 | 北京航铱锘科技有限公司 | Crank pendulum rod metering pump |
| CN210049997U (en) * | 2019-01-18 | 2020-02-11 | 东台市东方船舶装配有限公司 | High-flow low-noise piston pump |
-
2019
- 2019-01-18 CN CN201910048000.1A patent/CN109519353B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1323817A (en) * | 1970-05-22 | 1973-07-18 | Horn Armaturen | Centrifugal pumps |
| CN1379180A (en) * | 2002-03-15 | 2002-11-13 | 陈根生 | Rotor-type piston pump |
| CN101275555A (en) * | 2008-03-31 | 2008-10-01 | 浙江工业大学 | Hollow structure valve core for reciprocating pump in-out one-way valve set |
| JP2014214621A (en) * | 2013-04-23 | 2014-11-17 | 三菱電機株式会社 | Piston pump |
| CN104314802A (en) * | 2014-09-10 | 2015-01-28 | 北京航铱锘科技有限公司 | Crank pendulum rod metering pump |
| CN210049997U (en) * | 2019-01-18 | 2020-02-11 | 东台市东方船舶装配有限公司 | High-flow low-noise piston pump |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109519353B (en) | 2024-04-09 |
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