CN105240236A - Multi-stage radial plunger booster pump - Google Patents
Multi-stage radial plunger booster pump Download PDFInfo
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- CN105240236A CN105240236A CN201510585246.4A CN201510585246A CN105240236A CN 105240236 A CN105240236 A CN 105240236A CN 201510585246 A CN201510585246 A CN 201510585246A CN 105240236 A CN105240236 A CN 105240236A
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Abstract
Disclosed is a multi-stage radial plunger booster pump. The multi-stage radial plunger booster pump mainly comprises a pump body, a rotor, a plurality of uniformly distributed plungers, a baffle tongue sleeve, an eccentric wheel and a rotor sleeve. By means of the moving principle of an eccentric mechanism, the suction and discharge functions of the pump is achieved; when the rotor is driven by power to rotate, one side of the corresponding plunger rotates around the eccentric wheel and the other side of the corresponding plunger reciprocates along radial holes in the rotor due to restriction of the eccentric wheel, volume change occurs, and liquid suction and discharging is performed; a medium coming out of a high pressure area of a first stage flows to a low pressure area of a second stage through a channel of the baffle tongue sleeve and is pressurized through the second stage; therefore, high pressure liquids can be discharged after repeated pressurizing; by means of the positive displacement pump principle, hydraulic loss and volume loss are small, the efficiency is high, and the self-suction capacity is high; a valve structure is omitted so that the pump can operate at high speed, the multiple uniformly distributed plungers are discharged alternately and sequentially during per revolution, the liquid flow is stable without fluctuation, the vibration is small, and the noise is low. A two-stage pump, a triple-stage pump or a more-stage pump can be formed, and higher pressure discharging can be achieved.
Description
Technical field
The present invention relates to a kind of displacement pump, particularly a kind of radial plunger type multi-stage booster pump.
Background technique
Small flow and high lift pump, is subject to increasingly extensive application in space flight, chemical industry, pharmacy, metallurgy and light industry, and the pump that can provide has multistage centrifugal pump, high speed centrifugal pump, peripheral pump, reciprocating pump etc., but they respectively have pluses and minuses.
For centrifugal pump, the specific speed of this small flow and high lift pump is all below 20, and belong to ultra-low specific speed pump, efficiency is very low, generally all below 30%; The single-stage lift of centrifugal pump is very low, reach high pressure, needs multi-stage superimposed, stainless steel multistage centrifugal pump as vertical in QDLA type, when flow is 0.6M
3when/h lift is 100M, need 12 grades of impeller serials, when lift is 198M, need 24 grades of impeller serials, efficiency only has 30%, and assembly process process is poor, and rigidity is not enough.
High speed centrifugal pump can reach high-lift, but the rotating speed of its impeller is high, at 5000-16000rpm, what have reaches 20000rpm, this just requires that motor is accelerated by gear, and composite impeller and preposition inducer will be adopted, therefore, complex structure, take up an area volume large, machining accuracy problem for gear at a high speed, bearing, mechanical seal will be solved, the series of problems such as heating problem, vibration problem, noise problem caused because of high speed needs to properly settle, therefore, the expense of its cost processed and maintaining is all very high.
Peripheral pump is because its structure is simple, easy to maintenance, volume is little, lightweight, price is low, and vortex pump with open impeller also has self-priming performance, can carry out vapour, liquid mixes defeated, be widely used in many departments of national economy; But it is extremely low that peripheral pump disadvantage is efficiency, be the highlyest no more than 50%, most of peripheral pump efficiency is at 20%-40%, and what have only has tens percent, and as patent ZL96203684.6 " axial inlet vortex pump ", efficiency only has 12-24%, is energy-consuming product; In addition peripheral pump can not be used for pumping the larger medium of viscosity, also can only carry pure liquid; Peripheral pump is also that floating ground is arranged on axle because of impeller, easily and two side generate heat because of friction, even motor damage.
Plunger pump, as metering pump, also can reach low-flow high-lift, and owing to there being valve arrangement to exist, reciprocal time is very low, and generally all within 100 beats/min, the pulse of liquid stream is serious, brings harmful effect, the defect such as applied vibration, noise to follow-up flow process; Although the pulsation of treble ram pump is wanted steadily, to need valve arrangement and reducing gear, volume is comparatively large, cost is higher.
The rotor pump of emerging valveless, self-priming performance is good, eliminate the retardation phenomenon of valve, structure is simple, volume is little, reciprocal time high also energy transporting viscous liquid, as " the rotator type plunger pump " of patent ZL021127763.8, ZL96228726.1 " double cylinder double acting rotor plunger pump ", ZL00211851.3 " synchonous suction-excavating rotor pump " etc. be, but it is can only small flow that these rotor pumps all exist same general character defect, can not be high-lift, application number is 201410122717.4 and is called that " rotator type multistage pump " proposes the new structure of multi-stage rotor pump, multistage pressure superposition is got up, produce high-head pump, obtain certain effect, its shortcoming is that every one-level only has a double-acting plunger, and this affects the steady output of liquid stream.
Summary of the invention
The object of the invention is to: the shortcoming existed for above-mentioned various high-pressure service pump and existing rotor high-pressure pump, propose a kind of compact structure, liquid stream sealability that is more steady, cut water is better, single stage of pressure is higher, and the radial plunger type multi-stage booster pump of energy multistage pressure superposition.
In order to achieve the above object, radial plunger type multi-stage booster pump of the present invention, comprise the pump housing 1 with suction port and exhaust port, the described pump housing 1 inner chamber is equipped with rotor 2 and the fixing cut water cover 3 of coaxial rotating, this rotor 2 has multiple uniform in radioactive radial hole 4, described radial hole 4 built with can be reciprocating plunger 5; Described cut water cover 3 is shaped with the cut water 6 pump housing 1 inner chamber being divided into zone of high pressure and low pressure area; An eccentric wheel do not turned 7 is fixed on protecgulum 8 through rotor 2 inner chamber; The inner of described plunger 5 contacts with the periphery of eccentric wheel 7 in the presence of a tensile force; Its special way is: the radial hole 4 that described rotor 2 has at least two rows above vertically; Described cut water cover 3 is shaped with multiple passage 9 leading to next stage low pressure area from upper level zone of high pressure.
The cylindrical of eccentric wheel 7 described in technical solution of the present invention can be fixed with rolling bearing 10.
The cylindrical of rotor 2 described in technical solution of the present invention can be fixedly mounted with a rotor cover 11, this rotor cover 11 corresponds to rotor 2 radial hole 4 position and is shaped with coaxial with radial hole 4, that diameter is less radial hole 12, these radial hole 12 both sides are shaped with the narrow groove 13 be communicated with it, form the radial passage of rotor cover 11.
The width of the cut water 6 of the cover of cut water described in technical solution of the present invention 3 can be greater than the width of radial passage on rotor cover 11.
Cut water 6 described in technical solution of the present invention can be shaped with and discharge one-way valve 14.
In the radial hole 4 of rotor 2 described in technical solution of the present invention, plunger 5 and elastic diaphragm 15 can be housed.
The present invention utilizes the motion principle of eccentric stiffener, realize the suction function of pump, when power rotor driven 2 rotates, due to the restriction of eccentric wheel 7, plunger 5 is while rotate around eccentric wheel 7, and the radial hole 4 on an edge rotor 2 is reciprocating, and the to-and-fro motion of plunger 5 produces volume-variation, suck liquid from suction chamber and discharge liquid from discharge side again, constantly circulate; Due to the obstruct of cut water 6, make to produce pressure difference between discharge side and suction chamber, define low pressure area and zone of high pressure; The present invention is multistage pump, and the zone of high pressure of previous stage has passage 9 to be communicated with the low pressure area of next stage, and the liquid stream entering next stage has first pressing, after supercharging, then inputs next stage; Pressure superposes step by step, exports high pressure liquid stream.
In order to improve the gap sealed performance of cut water 6, sealing area must be increased; According to " short stroke, high frequency " feature of plunger motion, its reciprocal time is very high, but the flow carried each time is little, and therefore add a rotor cover 11 at the cylindrical of rotor 2, on rotor cover 11, the diameter of radial hole 12 can diminish; In addition, quantity delivered in each stroke turned of plunger 5 is also unequal, plunger quantity delivered when two limit positions is minimum, then increases gradually, therefore, the narrow groove 13 communicated can be made in the both sides of radial hole 12, form less radial passage, pass through to adapt to small flow, thus reach the area increasing cut water sealing surface, strengthen sealing effect, reduce volumetric loss.
Good effect of the present invention is: the zone of high pressure of previous stage has passage 9 to be communicated with the low pressure area of next stage, and the liquid stream entering next stage has first pressing, after supercharging, then inputs next stage; Pressure superposes step by step, exports high pressure liquid stream; ; The displacement pump principle of this volume-variation, hydraulic loss and volumetric loss are all little, and efficiency is very high, and suction capacity is strong, multiple uniform plunger 5 output liquid in turn arranged in radioactivity, under motor runs up, the steady no pulse of liquid levelling, vibrate little, noise is low.
Accompanying drawing explanation
Fig. 1 is the structural drawing of embodiments of the invention-radial plunger type three grades of suction boosters.
Fig. 2 is the A-A sectional view of Fig. 1.
Fig. 3 is the B-B sectional view of Fig. 1.
Fig. 4 is the structural drawing of cut water cover 3.
Fig. 5 is the A-A sectional view of Fig. 4.
Fig. 6 is the B-B sectional view of Fig. 4.
Fig. 7 is the plan view of Fig. 4.
Fig. 8 is the schematic enlarged-scale view of cut water 6 and plunger 5.
Fig. 9 is the structural drawing of the width of cut water 6 and the equal diameters of plunger 5.
Figure 10 is the structural drawing that the width of cut water 6 is greater than that rotor overlaps the radial passage width of 11.
Figure 11 is that radial hole 4 is built with plunger 5 and elastic diaphragm 15 structural drawing.
Embodiment
Fig. 1 is the structural drawing of embodiments of the invention-radial plunger type three grades of suction boosters, and Fig. 2 is the A-A sectional view of Fig. 1, and Fig. 3 is the B-B sectional view of Fig. 1.
Show the pump housing 1 inner chamber in figure and the rotor 2 coaxial with it, rotor 2 two supports are housed on bearing 16,17, rotor 2 is shaped with multiple radial hole 4 be evenly arranged, and radial hole 4 is built with can reciprocating plunger 5 by eccentric wheel 7; The pump housing 1 inner chamber is also fixedly mounted with a coaxial cut water cover 3, and cut water cover 3 is shaped with the cut water 6 of being isolated in the zone of high pressure in the pump housing 1 and low pressure area; An eccentric wheel do not turned 7 passes rotor 2 inner chamber and is packed on protecgulum 8, and its other end is bearing on bearing 18, and bearing 18 is arranged on the axis place of rotor 2, and eccentric wheel 7 cylindrical is fixedly mounted with a rolling bearing 10; Plunger 5 is pressed to the surface of the rolling bearing 10 outside eccentric wheel 7 by the plunger 5 in radial hole 4 together with sheath 20 by Compress Spring 19; Rotor 2 projecting shaft side also has bonnet 21 and shaft seal 22.
When power rotor driven 2 rotates, due to the restriction of eccentric wheel 7, plunger 5 is while rotate around eccentric wheel 7, radial hole 4 on one edge rotor 2 is reciprocating, the to-and-fro motion of plunger 5 produces volume-variation, liquid is sucked from low pressure area, liquid is discharged to zone of high pressure, cut water 6 between zone of high pressure and low pressure area plays iris action, prevent the liquid of zone of high pressure from flowing to low pressure area backflow, the liquid of zone of high pressure is input to the low pressure area of next stage by the passage 9 on cut water cover 3, next stage low pressure area is transported to again after next stage plunger 5 again supercharging, so repeatedly obtain supercharging.
Fig. 4 is the structural drawing of cut water cover 3, and Fig. 5 is the A-A sectional view of Fig. 4, and Fig. 6 is the B-B sectional view of Fig. 4, Fig. 7 is the plan view of Fig. 4, and be shown as the structure of the cut water cover 3 of three grades of suction boosters in figure, every one-level has cut water 6, be shaped with in cut water 6 and discharge one-way valve 14, upper level to next stage has passage 9;
Fig. 8 is the schematic enlarged-scale view of cut water 6 and plunger 5, and the width showing cut water 6 in figure is greater than the radial passage width of rotor cover 11, is provided with and discharges one-way valve 14 in cut water 6; The radial hole 4 of rotor 2 is built with guide pin bushing 24, plunger 5, Compress Spring 19 and plunger sheath 20.
Fig. 9 is the structural drawing of the width of cut water 6 and the equal diameters of plunger 5, and this is the ideal structure of general classical Theoretical Design, and the width design of cut water 6 is become strictly equal with plunger 5 diameter, can not wide can not be narrow, wide to produce vexed car and be stranded liquid; Narrow zone of high pressure and low pressure area will be made to gang up, liquid backflow, volumetric efficiency declines, and head pressure reduces; But the sealing surface of this structure is minimum, and sealing effect is the poorest, this can confirm from sealing surface projection drawing.
Figure 10 is the structural drawing that the width of cut water 6 is greater than that rotor overlaps the radial passage width of 11, according to the feature of plunger motion " short stroke; high frequency ", the flow that it is carried each time is little, therefore be fixedly mounted with a rotor cover 11 at the cylindrical of rotor 2, the diameter of radial hole 12 coaxial with the radial hole 4 on rotor 2 on this rotor cover 11 can diminish; In addition, quantity delivered in each stroke turned of plunger 5 is also unequal, plunger 5 quantity delivered when two limit positions is minimum, then increases gradually, therefore, the narrow groove 13 communicated with it can be shaped with in the both sides of this radial hole 12, form the radial flow path of rotor cover 11, increase sealing area, overlap the width of 11 radial passages and the vexed car phenomenon of tired liquid that causes in order to avoid being greater than rotor due to the width of cut water 6, be provided with in cut water 6 and discharge one-way valve 14, during vexed car, carry out instantaneous drainage; The radial passage that the width of cut water 6 is greater than rotor cover 11 further increases the length of sealing surface, and this is confirmed from sealing surface projection drawing.
Figure 11 is that radial hole 4 is built with plunger 5 and elastic diaphragm 15 structural drawing, show plunger 5 in figure and be set with an elastic diaphragm 15, with pressing plate 23, elastic diaphragm 15 is packed on rotor 2, elastic diaphragm 15 is pre-stretching when mounted, therefore, plunger 5, under the elastic force effect of elastic diaphragm 15, is close to the surface of the rolling bearing 10 outside eccentric wheel 7 all the time; Another effect of elastic diaphragm 15 is isolated by lubricant oil in transported medium and plunger 5, avoids the pollution of oil; Elastic diaphragm 15 can make of rubber or elastomeric plastics.
Claims (6)
1. a radial plunger type multi-stage booster pump, comprise the pump housing (1) with suction port and exhaust port, the described pump housing (1) inner chamber is equipped with the rotor (2) of coaxial rotating and fixing cut water cover (3), this rotor (2) has multiple uniform in radioactive radial hole (4), described radial hole (4) built with can be reciprocating plunger (5); Described cut water cover (3) is shaped with the cut water (6) pump housing (1) inner chamber being divided into zone of high pressure and low pressure area; An eccentric wheel do not turned (7) is fixed on protecgulum (8) through rotor (2) inner chamber; The inner of described plunger (5) contacts with the periphery of eccentric wheel (7) in the presence of a tensile force; It is characterized in that: the radial hole (4) that described rotor (2) has at least two rows above vertically; Described cut water cover (3) is shaped with multiple passage (9) leading to next stage low pressure area from upper level zone of high pressure.
2. radial plunger type multi-stage booster pump according to claim 1, is characterized in that: the cylindrical of described eccentric wheel (7) is fixed with rolling bearing (10).
3. radial plunger type multi-stage booster pump according to claim 1, it is characterized in that the cylindrical of described rotor (2) is fixedly mounted with a rotor cover (11), this rotor cover (11) is shaped with and the radial hole (12) that radial hole (4) is coaxial, diameter is less corresponding to rotor (2) radial hole (4) position, this radial hole (12) both sides are shaped with the narrow groove (13) be communicated with it, form the radial passage of rotor cover (11).
4. radial plunger type multi-stage booster pump according to claim 1, is characterized in that: the width of the cut water (6) of described cut water cover (3) is greater than the width of the upper radial passage of rotor cover (11).
5. radial plunger type multi-stage booster pump according to claim 4, is characterized in that: described cut water (6) is shaped with and discharges one-way valve (14).
6. radial plunger type multi-stage booster pump according to claim 1, is characterized in that: the radial hole (4) of described rotor (2) is built with plunger (5) and elastic diaphragm (15).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510585246.4A CN105240236A (en) | 2015-09-11 | 2015-09-11 | Multi-stage radial plunger booster pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510585246.4A CN105240236A (en) | 2015-09-11 | 2015-09-11 | Multi-stage radial plunger booster pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105240236A true CN105240236A (en) | 2016-01-13 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510585246.4A Pending CN105240236A (en) | 2015-09-11 | 2015-09-11 | Multi-stage radial plunger booster pump |
Country Status (1)
| Country | Link |
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| CN (1) | CN105240236A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106368920A (en) * | 2016-08-25 | 2017-02-01 | 陈兆红 | Radial plunger type multi-stage booster immersible pump |
| CN106438253A (en) * | 2016-08-25 | 2017-02-22 | 陈兆红 | Radial plunger type multistage booster pump |
| CN115217733A (en) * | 2022-07-18 | 2022-10-21 | 中国民航大学 | Stroke-adjustable multistage reciprocating pump based on crank block |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1465876A (en) * | 1974-07-10 | 1977-03-02 | Bosch Gmbh Robert | Multiple pump |
| JPS62251475A (en) * | 1986-04-24 | 1987-11-02 | Toyota Motor Corp | Fixed displacement pump |
| CN101865100A (en) * | 2010-06-23 | 2010-10-20 | 余文凌 | Multi-cylinder radial piston pump |
| CN103775298A (en) * | 2014-02-24 | 2014-05-07 | 余文凌 | Radial plunger deep water submersible pump |
| CN103883496A (en) * | 2014-03-27 | 2014-06-25 | 余文凌 | Rotor type multistage pump |
-
2015
- 2015-09-11 CN CN201510585246.4A patent/CN105240236A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1465876A (en) * | 1974-07-10 | 1977-03-02 | Bosch Gmbh Robert | Multiple pump |
| JPS62251475A (en) * | 1986-04-24 | 1987-11-02 | Toyota Motor Corp | Fixed displacement pump |
| CN101865100A (en) * | 2010-06-23 | 2010-10-20 | 余文凌 | Multi-cylinder radial piston pump |
| CN103775298A (en) * | 2014-02-24 | 2014-05-07 | 余文凌 | Radial plunger deep water submersible pump |
| CN103883496A (en) * | 2014-03-27 | 2014-06-25 | 余文凌 | Rotor type multistage pump |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106368920A (en) * | 2016-08-25 | 2017-02-01 | 陈兆红 | Radial plunger type multi-stage booster immersible pump |
| CN106438253A (en) * | 2016-08-25 | 2017-02-22 | 陈兆红 | Radial plunger type multistage booster pump |
| CN106438253B (en) * | 2016-08-25 | 2019-03-19 | 陈兆红 | Radial plunger type multi-stage booster pump |
| CN115217733A (en) * | 2022-07-18 | 2022-10-21 | 中国民航大学 | Stroke-adjustable multistage reciprocating pump based on crank block |
| CN115217733B (en) * | 2022-07-18 | 2023-09-22 | 中国民航大学 | Stroke-adjustable multistage reciprocating pump based on crank sliding block |
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| PB01 | Publication | ||
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Application publication date: 20160113 |