CN104895842A - Spiral flow constant pressure pump - Google Patents
Spiral flow constant pressure pump Download PDFInfo
- Publication number
- CN104895842A CN104895842A CN201510241925.XA CN201510241925A CN104895842A CN 104895842 A CN104895842 A CN 104895842A CN 201510241925 A CN201510241925 A CN 201510241925A CN 104895842 A CN104895842 A CN 104895842A
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- Prior art keywords
- pump
- linear leaf
- angle
- short blade
- spiral flow
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/24—Vanes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
Abstract
The invention relates to a spiral flow constant pressure pump. The technical problems that the friction is large, the service life is short, the adaptability to the high concentration and high viscosity of heavy pulp liquid is poor, the liquid outlet pressure is small and not constant, the flow rate is small and instable, the vibration is large, the size is large, the temperature of a bearing body is too high, the temperature difference of two ends of the bearing body is too large, the fault is easy to cause, and the like in the existing spiral flow constant pressure pump are solved. One side of a rear cover plate is provided with long blades and short blades which are uniformly distributed in an intersected mode; every long blade and every short blade are provided with a same direction of bend respectively; the long blades and the short blades form a rotary center through common surrounding respectively; the diameter of an internal opening of the common rotary center of the short blades is larger than that of an internal opening of the common rotary center of the long blades. The spiral flow constant pressure pump can be applied to liquid conveying.
Description
Technical field
The present invention relates to a kind of constant pressure pump, is a kind of spiral flow constant-pressure pump specifically.
Background technique
Authorization Notice No. is that the Chinese invention patent of CN101294580B discloses a kind of spiral flow constant-pressure pump, this constant pressure pump comprises the pump housing, pump case, pump shaft, impeller and motor, this design to high viscosity high concentration liquid and the high situation adaptability of stability of flow pressure requirements poor, and pulp pressure is little, flow not steadily, body vibratility is large, working life is short.Industry heavy slurry pump because of liquid stream concentration high, particle proposes very high requirement to the wear resistance corrosion resistance of the pump housing self greatly, simultaneously high-lift to pump, flow large and constant pressure proposes higher performance requirement.
More existing fire extinguishing pumps are in order to pressure of increasing export, improving lift relies on multistage centrifugal combination, and can not balancing axial thrust and radial force, shake large noise large, large to machine's sealing, poor sealing performance, easily leak, easily pressure release, RHVC or gear speedup case can only be relied on to improve pressure to increase rotating speed, and pressure transient, volume is large, and rate of fault is high.During pressure increase, flow reduces, the smooth instability of flow-lift curve.Existing external fire water pump two-stage centrifugal pump combination lift only has 300m, and flow is 90m
3/ h, belongs to mesolow fire water pump, can not meet current fire-fighting emergent rescue demand.Along with the quickening of Urbanization in China, building is more and more intensive more and more taller and bigger, scene of a fire situation becomes increasingly complex, and high building fire-proof technology does not catch up with the speed that high building rises far away, high building fire-proof becomes a difficult problem of puzzlement urban fire protection safety, therefore be badly in need of wanting a kind of pressure high and constant, flow is large and stable, small in volume, low without plugging fault, without RHVC or gear speedup case, cost is low, easy to operate, be applicable to the mesohigh fire water pump that various scenes of a fire situation can meet various operating environment requirements.
Summary of the invention
The present invention is exactly that the existing spiral flow constant-pressure pump friction large life-span is short, to little non-constant, the little instability of flow of the bad adaptability of the heavy slurries bodies such as high concentration high viscosity, fluid pressure, vibrations large volume is large, bearing support is overheated and the technical problems such as two ends temperature difference easy break-down bigger than normal in order to solve, and provides that a kind of little life-span of rubbing is long, good to the adaptability of the heavy slurries bodies such as high concentration high viscosity, fluid pressure is large and constant, flow large and stable, active balance axial force and radial force, shakes the little and spiral flow constant-pressure pump that rate of fault is extremely low of small volume.
The invention provides a kind of spiral flow constant-pressure pump, it is provided with pump postoperculum, the pump housing, impeller, bearing support and pump shaft, and pump postoperculum is located at the rear side of the pump housing and is fixedly connected with the pump housing, and pump postoperculum and the pump housing are jointly around forming pump chamber; Pump shaft stretches in pump chamber, and impeller is located at the front end of pump shaft in pump chamber; Be provided with chamber between pump postoperculum and pump shaft, in chamber, be provided with mechanical seal; Bearing support is connected with the pump housing, and pump shaft is supported on bearing support by two ends double rolling bearing; Impeller is provided with back shroud, back shroud is provided with both sides, side is provided with back blade, opposite side is provided with equally distributed linear leaf and short blade, linear leaf and short blade cross-distribution, linear leaf and short blade are equipped with the bending in same direction, and linear leaf and short blade are all common around forming respective gyration center, and the common gyration center internal orifice diameter of short blade is greater than the common gyration center internal orifice diameter of linear leaf.
Preferably, pump postoperculum to be provided with in zone of high pressure self-cooling channel in self-cooling channel and low pressure area, and they both all communicated with chamber, also all communicated with pump chamber.In zone of high pressure, self-cooling channel angle of inclination is 71 °, and in low pressure area, self-cooling channel angle of inclination is 64 °.
Preferably, pump postoperculum is provided with outside zone of high pressure that outside cooling channel and low pressure area cooling channel, and they all communicate with chamber.Outside zone of high pressure, angle of inclination, cooling channel is 15 ° or 90 °, and outside low pressure area, angle of inclination, cooling channel is 15 ° or 90 °.
Preferably, in the pump housing by radius be the pump housing fore-end of R, pump housing rear end part and radius be R1 the pump housing in the middle part of form, the radius R of pump housing fore-end is greater than the radius R 1 in the middle part of the pump housing.
Preferably, linear leaf and short blade all intersect vertically with back shroud, and the common gyration center internal orifice angle of linear leaf is 8 ° ~ 12 ° or 55 °.
Preferably, the front end of linear leaf and short blade is free edge, and rear end is bending, and bending is 2 ° ~ 6 ° than the intilted angle of free edge.
Preferably, the inlet angle that linear leaf and short blade are formed is 20 ° ~ 40 °.
Preferably, linear leaf and short blade respectively along back shroud outward edge tangent line counterclockwise bending angle be 20 ° ~ 40 °.
Preferably, linear leaf and short blade bending back root part exit angle are 100 ° ~ 130 °.
Preferably, linear leaf and short blade all intersect vertically with back shroud, and the common gyration center internal orifice angle of linear leaf is 10 °; The front end of linear leaf and short blade is free edge, and rear end is bending, and bending is 4 ° than the intilted angle of free edge; The inlet angle that linear leaf and short blade are formed is 30 °; Linear leaf and short blade respectively along back shroud outward edge tangent line counterclockwise bending angle be 30 °; Linear leaf and short blade bending back root part exit angle are 110 °.
The present invention compared with prior art, has the following advantages and quality effect:
(1) pump housing inwall three part forms smooth pump housing inwall along pump housing central rotation, plays guiding increase space behavior to impeller, increases suction stream liquid measure and reduces liquid stream to the friction between blade and back shroud simultaneously; The present invention is equipped with mechanical seal and with the inner cooling channel from zone of high pressure to low pressure area, angle of inclination, cooling channel, zone of high pressure is 71 °, angle of inclination, cooling channel, low pressure area is 64 °, with self hydraulic pressure, cooling equilibrium pressure is simultaneously carried out to mechanical seal, or adopt zone of high pressure to the outer cooling channel of low pressure area, angle of inclination, cooling channel, zone of high pressure is 15 ° or 90 °, and angle of inclination, cooling channel, low pressure area, for being 15 ° or 90 °, carries out cooling equilibrium pressure simultaneously by external hydraulic to mechanical seal.Above two kinds of types of cooling all can reduce mechanical seal and bear the friction that pressure causes, and ensure mechanical seal durable.
(2) all angles are precisely arranged, the rotated flowing liquid formed in pump chamber is repeatedly extruded lifting in the space between length piece blade, make fluid mouth pressure higher, to the better adaptability of the heavy slurries bodies such as high viscosity high concentration, be applicable to the useful pump of 0 ~ 500m lift.
(3) uniform back blade is positioned on rear side of rear end cover and forms one with rear end cover, when pump chamber internal pressure is too high, liquid flows in back blade space, form another longitudinal flow to pump postoperculum direction and can balance pump housing pressure, pump chamber internal pressure is made to keep constant, thus make flow keep stable, work more steady.
(4) bearing support adopts two ends duplex bearing to support double sealing structure, bearing is supported on bearing support by two ends double rolling bearing, active balance axial force and radial force, balancing axial thrust makes spiral flow constant-pressure pump work more steady, balance radial force can avoid spiral flow constant-pressure pump bearing support to produce too much heat, reach spin balancing, failure rate is low, improve liquid transport efficiency.
(5) this invention also have vibrations little, the advantage that volume is little.
Accompanying drawing explanation
Fig. 1 is the structural representation of the embodiment of the present invention 1;
Fig. 2 is the structural representation of the embodiment of the present invention 1 pump postoperculum;
Fig. 3 is the structural representation of the pump housing of the present invention;
Fig. 4 is the left view of impeller of the present invention;
Fig. 5 is the structural representation of impeller of the present invention;
Fig. 6 is the right elevation of impeller of the present invention;
Fig. 7 is bearing support of the present invention assembling schematic diagram;
Fig. 8 is the structural representation of the embodiment of the present invention 2;
Fig. 9 is the structural representation of the embodiment of the present invention 2 pump cover.
Symbol description in figure:
1. pump postoperculum; 2. the pump housing; 3. impeller; 4. bearing support; 5. pump shaft; 6. bearing; 7. bearing (ball) cover; 8. seal ring; 101. mechanical seal; Self-cooling channel in 102. zone of high pressure; Self-cooling channel in 103. low pressure areas; 104. cooling channels outside zone of high pressure; 105. cooling channels outside low pressure area; 201. pump housing fore-ends; 202. pump housing rear end parts; In the middle part of 203. pump housings; 204. liquid entering hole; 205. liquid outlet; 301. back shroud; 302. bending; 303. linear leaf; 304. short blade; 305. back blade.
Embodiment
Embodiment 1
As shown in Figure 1, the present invention is provided with pump postoperculum 1, the pump housing 2, impeller 3, bearing support 4 and pump shaft 5.Pump postoperculum 1 is located at the rear side of the pump housing 2 and is fixedly connected with the pump housing 2, and itself and the pump housing 2 are jointly around forming pump chamber.The front end of pump shaft 5 is stretched in pump chamber, and impeller 3 is arranged on the front end of pump shaft 5 in pump chamber by reverse nut screwing clamping.Be provided with chamber between pump postoperculum 1 and pump shaft 5, in chamber, be provided with mechanical seal; Bearing support 4 is connected with the pump housing 2 by nut, and pump shaft 5 rear end is supported on bearing support 4 by two ends double rolling bearing.The pump housing 2 front end is provided with horizontal liquid entering hole 204, and right side is provided with vertical liquid outlet 205.
As shown in Figure 2,101 is mechanical seal.Pump postoperculum 1 to be provided with in zone of high pressure self-cooling channel 103 in self-cooling channel 102 and low pressure area, and they both all communicated with the chamber residing for mechanical seal 101, also all communicated with pump chamber.In zone of high pressure, self-cooling channel angle of inclination is 71 °, and in low pressure area, self-cooling channel angle of inclination is 64 °.By self hydraulic pressure, cooling equilibrium pressure is simultaneously carried out to mechanical seal 101 when the spiral flow constant-pressure pump of the present embodiment runs, which reduces mechanical seal 101 and bear the friction that pressure causes, guarantee mechanical seal 101 durable.
As shown in Figure 3, pump housing fore-end 201 of the present invention unconventional single circular arc inwall, but many circular arcs inwall.The pump housing 2 inwall is 203 to form in the middle part of the pump housing of R1 by pump housing fore-end 201 (radius is the circular arc portion of R), pump housing rear end part 202 (straight portion) and their intersection radiuses, this three part forms smooth pump housing inwall along the pump housing 2 central rotation, guiding is played to impeller 3 and increases space behavior, reduce impeller 3 and rub.The radius R 1 that the radius R of pump housing fore-end 201 is greater than in the middle part of the pump housing 203.
As shown in Figure 4, Figure 5 and Figure 6, impeller 3 is provided with back shroud 301, the side of back shroud 301 is provided with equally distributed 7 pieces of linear leafs 303 and 7 pieces of short blades 304, and linear leaf 303 and short blade 304 cross-distribution, linear leaf 303 and short blade 304 are equipped with the bending 302 in same direction.The opposite side of back shroud 301 is provided with 13 back blades 305, and the height of linear leaf 303 and short blade 304 is higher than the height of back blade 305.The quantity of linear leaf 303, short blade 304 and back blade 305 all can quantity according to actual needs adjust.
7 pieces of linear leafs 303 and back shroud 301 intersect vertically, and the gyration center internal orifice that 7 pieces of linear leafs 303 are common and the angle a that liquid is come in are 10 °; 7 pieces of short blades 304 also intersect vertically with back shroud 301, and the common gyration center internal orifice diameter of 7 pieces of short blades 304 is greater than the common gyration center internal orifice diameter of 7 pieces of linear leafs 303.Linear leaf 303 is free edge with the front end of short blade 304, and rear end is bending 302, and bending 302 is 4 ° than the intilted angle b of free edge; The inlet angle c that linear leaf 303 and short blade 304 are formed is 30 °; Linear leaf 303 and short blade 304 respectively along back shroud 301 circular cut line edge counterclockwise bending angle d be 30 °.Linear leaf 303 and short blade 304 bending back root part exit angle e are 110 °.
As shown in Figure 7, pump shaft 5 forms one by two ends duplex bearing 6 and bearing support 4, the two ends of bearing support 4 are provided with bearing (ball) cover 7, seal ring 8 is provided with in bearing (ball) cover 7, this structure is dual-gripper double sealing structure, energy active balance axial force and radial force ensure pump shaft and vane rotary steadily, improve Liquid transfer efficiency.
Below the working procedure of spiral flow constant-pressure pump of the present invention is further detailed.
Liquid enters from liquid entering hole 204, because the present invention adopts equally distributed, that rear end is provided with bending 302 linear leaf 303 and short blade 304, the flow stream pressure of impeller 3 root is made to be greater than impeller 3 front end free edge pressure, liquid produces longitudinal flow from inside to outside, follows blade rotary further and produces rotational flow.Because blade length is uniform, make the pump interior space larger, when being pumped into a large amount of liquid stream, forming 2 different pressures difference in the space between linear leaf 303 and short blade 304 and liquid stream is constantly extruded, form spiral flow through repeatedly boosting and finally to discharge from liquid outlet 205.
Equally distributed back blade 305 is positioned on rear side of rear end cover 301 and forms one with rear end cover 301, when pump chamber internal pressure is too high, liquid flows in the space between 13 back blades 305, form another longitudinal flow to pump postoperculum 1 direction, like this can ballast pump room pressure, make fluid pressure reach pressure constant state.
Embodiment 2
The present embodiment and embodiment 1 major part is identical, and its difference is that the angle a of the gyration center internal orifice that 7 pieces of linear leafs 303 are common and liquid-inlet is 8 °; Linear leaf 303 is free edge with the front end of short blade 304, and rear end is bending 302, and bending 302 is 2 ° than the intilted angle b of free edge; The inlet angle c that linear leaf 303 and short blade 304 are formed is 20 °; Linear leaf 303 and short blade 304 respectively along back shroud 301 circular cut line edge counterclockwise bending angle d be 20 °.Linear leaf 303 and short blade 304 bending back root part exit angle e are 100 °.
The present embodiment pump postoperculum 1 is provided with outside zone of high pressure that outside cooling channel 104 and low pressure area cooling channel 105, and as shown in Figure 8,9, they both all communicated with the chamber between pump postoperculum 1 and pump shaft 5.Outside zone of high pressure, the angle of inclination of cooling channel 104 is 15 ° or 90 °, and outside low pressure area, the angle of inclination of cooling channel 105 is 15 ° or 90 °.By outer cooling water, cooling equilibrium pressure is simultaneously carried out to mechanical seal 101 when the spiral flow constant-pressure pump of the present embodiment runs, which reduces mechanical seal 101 and bear the friction that pressure causes, guarantee mechanical seal 101 durable.
Embodiment 3
The present embodiment and embodiment 1 major part is identical, and its difference is that the angle a of the gyration center internal orifice that 7 pieces of linear leafs 303 are common and liquid-inlet is 12 °; Linear leaf 303 is free edge with the front end of short blade 304, and rear end is bending 302, and bending 302 is 6 ° than the intilted angle b of free edge; The inlet angle c that linear leaf 303 and short blade 304 are formed is 40 °; Linear leaf 303 and short blade 304 respectively along back shroud 301 circular cut line edge counterclockwise bending angle d be 40 °.Linear leaf 303 and short blade 304 bending back root part exit angle e are 130 °.
Embodiment 4
The present embodiment and embodiment 1 major part is identical, and its difference is that the angle a of the gyration center internal orifice that 7 pieces of linear leafs 303 are common and liquid-inlet is 55 °; Linear leaf 303 is free edge with the front end of short blade 304, and rear end is bending 302, and bending 302 is 4 ° than the intilted angle b of free edge; The inlet angle c that linear leaf 303 and short blade 304 are formed is 30 °; Linear leaf 303 and short blade 304 respectively along back shroud 301 circular cut line edge counterclockwise bending angle d be 30 °.Linear leaf 303 and short blade 304 bending back root part exit angle e are 110 °.
In embodiment 1 ~ 3, the present invention chooses the angle a of the common gyration center internal orifice of 7 pieces of linear leafs 303 and water intake is 8 ~ 12 °, are all Non-traditional Techniques personnel with other angle to draw through theory calculate repeatedly and practice, it is more suitable for the transmission for heavy slurry class I liquid I, and a is 55 ° in embodiment 4, it is also the optimal selection being applicable to fire water pump that Non-traditional Techniques personnel draw through theory calculate repeatedly and practice.
The announcement of book and instruction according to the above description, above-mentioned example is the present invention's preferably mode of execution.Therefore, the present invention is not restricted to the described embodiments, the change done under other any does not deviate from essence of the present invention and principle, combination, modification, all should be the substitute mode of equivalence, is included within protection scope of the present invention.
Claims (10)
1. a spiral flow constant-pressure pump, it is provided with pump postoperculum, the pump housing, impeller, bearing support and pump shaft, and described pump postoperculum is located at the rear side of the described pump housing and is fixedly connected with the described pump housing, and described pump postoperculum and the described pump housing are jointly around forming pump chamber; Described pump shaft stretches in described pump chamber, and described impeller is located at the front end of pump shaft in described pump chamber; Be provided with chamber between described pump postoperculum and described pump shaft, in described chamber, be provided with mechanical seal; Described bearing support is connected with the described pump housing, and described pump shaft is supported on described bearing support by two ends double rolling bearing; Described impeller is provided with back shroud, described back shroud is provided with both sides, side is provided with back blade, it is characterized in that described back shroud opposite side is provided with equally distributed linear leaf and short blade, described linear leaf and described short blade cross-distribution, described linear leaf and described short blade are equipped with the bending in same direction, described linear leaf and described short blade all common around forming respective gyration center, the common gyration center internal orifice diameter of described short blade is greater than the common gyration center internal orifice diameter of described linear leaf.
2. spiral flow constant-pressure pump according to claim 1, it is characterized in that described pump postoperculum to be provided with in zone of high pressure self-cooling channel in self-cooling channel and low pressure area, they both all communicated with described chamber, also all communicated with described pump chamber; In described zone of high pressure, self-cooling channel angle of inclination is 71 °, and in described low but nip, self cooling channel slopes angle is 64 °.
3. spiral flow constant-pressure pump according to claim 1, is characterized in that described pump postoperculum is provided with outside zone of high pressure that outside cooling channel and low pressure area cooling channel, and outside described zone of high pressure, outside cooling channel and described low pressure area, cooling channel all communicates with described chamber; Outside described zone of high pressure, angle of inclination, cooling channel is 15 ° or 90 °, and outside described low pressure area, angle of inclination, cooling channel is 15 ° or 90 °.
4. the spiral flow constant-pressure pump according to Claims 2 or 3, it is characterized in that in the described pump housing by radius be the pump housing fore-end of R, pump housing rear end part and radius be R1 the pump housing in the middle part of form, the radius R of described pump housing fore-end is greater than the radius R 1 in the middle part of the described pump housing.
5. spiral flow constant-pressure pump according to claim 4, is characterized in that described linear leaf and described short blade all intersect vertically with described back shroud, and the common gyration center internal orifice angle of described linear leaf is 8 ° ~ 12 ° or 55 °.
6. spiral flow constant-pressure pump according to claim 5, it is characterized in that the front end of described linear leaf and described short blade is free edge, rear end is bending, and described bending is 2 ° ~ 6 ° than the intilted angle of described free edge.
7. spiral flow constant-pressure pump according to claim 6, is characterized in that the inlet angle that described linear leaf and described short blade are formed is 20 ° ~ 40 °.
8. spiral flow constant-pressure pump according to claim 7, it is characterized in that described linear leaf and described short blade respectively along described back shroud outward edge tangent line counterclockwise bending angle be 20 ° ~ 40 °.
9. spiral flow constant-pressure pump according to claim 8, is characterized in that described linear leaf and described short blade bending back root part exit angle are 100 ° ~ 130 °.
10. spiral flow constant-pressure pump according to claim 4, is characterized in that described linear leaf and described short blade all intersect vertically with described back shroud, and the common gyration center internal orifice angle of described linear leaf is 10 °; The front end of described linear leaf and described short blade is free edge, and rear end is bending, and described bending is 4 ° than the intilted angle of described free edge; The inlet angle that described linear leaf and described short blade are formed is 30 °; Described linear leaf and described short blade respectively along described back shroud outward edge tangent line counterclockwise bending angle be 30 °; Described linear leaf and described short blade bending back root part exit angle are 110 °.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510241925.XA CN104895842A (en) | 2015-05-13 | 2015-05-13 | Spiral flow constant pressure pump |
| PCT/CN2015/088551 WO2016179929A1 (en) | 2015-05-13 | 2015-08-31 | Spiral flow constant pressure pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510241925.XA CN104895842A (en) | 2015-05-13 | 2015-05-13 | Spiral flow constant pressure pump |
Publications (1)
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|---|---|
| CN104895842A true CN104895842A (en) | 2015-09-09 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510241925.XA Pending CN104895842A (en) | 2015-05-13 | 2015-05-13 | Spiral flow constant pressure pump |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN104895842A (en) |
| WO (1) | WO2016179929A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105648291A (en) * | 2016-01-27 | 2016-06-08 | 山东元昊机械有限公司 | High-strength alloy cast aluminum spiral-flow constant-pressure pump material and preparing method and application of high-strength alloy cast aluminum spiral-flow constant-pressure pump material |
| CN107143520A (en) * | 2017-07-13 | 2017-09-08 | 新兴际华科技装备有限公司 | A kind of voltage stabilizing centrifugal pump |
| CN109399214A (en) * | 2018-11-23 | 2019-03-01 | 艾迪机器(杭州)有限公司 | Rotation constant pressure blade wheel structure is flowed back in a kind of elastomer |
| CN109399215A (en) * | 2018-11-23 | 2019-03-01 | 艾迪机器(杭州)有限公司 | A kind of elastomer is interior to flow room structure constant pressure centrifugal pump |
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| CN109399214A (en) * | 2018-11-23 | 2019-03-01 | 艾迪机器(杭州)有限公司 | Rotation constant pressure blade wheel structure is flowed back in a kind of elastomer |
| CN109399215A (en) * | 2018-11-23 | 2019-03-01 | 艾迪机器(杭州)有限公司 | A kind of elastomer is interior to flow room structure constant pressure centrifugal pump |
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| Publication number | Publication date |
|---|---|
| WO2016179929A1 (en) | 2016-11-17 |
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Effective date of registration: 20160523 Address after: Rushan City, Weihai City, Shandong province 264509 Port Road Economic Development Zone No. 40 Applicant after: SHANDONG YUANHAO MACHINERY CO., LTD. Address before: Port Economic Development Zone, Rushan City, Weihai City, 264500 North Road in Shandong Province Applicant before: SHANDONG HAOAN GOLDTECH NEW MATERIALS CO., LTD. |
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Application publication date: 20150909 |