CN103299081B - Coolant pump - Google Patents
Coolant pump Download PDFInfo
- Publication number
- CN103299081B CN103299081B CN201180058462.3A CN201180058462A CN103299081B CN 103299081 B CN103299081 B CN 103299081B CN 201180058462 A CN201180058462 A CN 201180058462A CN 103299081 B CN103299081 B CN 103299081B
- Authority
- CN
- China
- Prior art keywords
- pump
- coolant pump
- active wheel
- coolant
- upper saw
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 239000002826 coolant Substances 0.000 title claims abstract description 71
- 238000002485 combustion reaction Methods 0.000 claims abstract description 14
- 239000000659 freezing mixture Substances 0.000 claims abstract description 14
- 238000005452 bending Methods 0.000 claims abstract description 9
- 238000007789 sealing Methods 0.000 claims description 6
- 238000005086 pumping Methods 0.000 abstract description 11
- 238000004519 manufacturing process Methods 0.000 abstract description 5
- 238000009434 installation Methods 0.000 abstract description 4
- 238000005516 engineering process Methods 0.000 abstract description 3
- 230000008859 change Effects 0.000 description 5
- 230000007246 mechanism Effects 0.000 description 5
- 230000001276 controlling effect Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 239000010779 crude oil Substances 0.000 description 3
- 210000002105 tongue Anatomy 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 238000005457 optimization Methods 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005538 encapsulation Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 230000033001 locomotion Effects 0.000 description 1
- 238000012797 qualification Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000005096 rolling process 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
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D1/04—Helico-centrifugal pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/021—Units comprising pumps and their driving means containing a coupling
-
- 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
- F04D29/08—Sealings
- F04D29/10—Shaft sealings
- F04D29/12—Shaft sealings using sealing-rings
- F04D29/126—Shaft sealings using sealing-rings especially adapted for liquid pumps
-
- 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
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
- F04D29/448—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps bladed diffusers
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention relates to a kind of for internal-combustion engine mechanically driven by belt pulley, gear, grafting axle etc., with the coolant pump of the structural type of axial flow coolant pump.The object of the invention is to develop a kind of axial flow coolant pump for internal-combustion engine, its when the structure space/installation volume less relative to prior art with identical, that is pump shaft rotating speed common for coolant pump allow to significantly improve the pumping pressure in axial flow coolant pump; And its be characterised in that simultaneously for constant rotational speed coolant volume stream about pumping pressure obviously improve relative to prior art, stable characteristic curve, in addition insensitive for cavitation, avoid the vortex of delivered volume stream, guarantee very high efficiency simultaneously, in addition be characterised in that closely, manufacture and simple on mounting technology, cost advantages and firm structural type, even and if also guarantee higher safety in operation and reliability when freezing mixture is loaded with pollution load when working life is grown very much.Coolant pump according to the present invention is characterised in that, use half axial-flow blower with blade (15) bending on three dimensional space, Francis formula or diagonal flow type impeller are as active wheel (14), and the upper saw pulley (9) be arranged in pump case (2) has inner, guide cone (16) tapering gradually in the flowing direction and the guiding cap (17) of the taper with its outside arranged at intervals, and both are interconnected via guide vane (10) bending on three dimensional space symmetrically spaced apartly, wherein, active wheel (14) and upper saw pulley (9) are with annular space (13) so separately, make active wheel (14) not only side and guide cone (16) adjacent outer rim and also side and guiding cap (17) adjacent outer rim separately.
Description
Technical field
The present invention relates to a kind of for internal-combustion engine mechanically driven by belt pulley, gear, grafting axle etc., with the coolant pump of the structural type of axial flow coolant pump.
Background technique
Describe the axial flow coolant pump for internal-combustion engine in the prior art.It is mechanically such as driven by the bent axle of internal-combustion engine via belt pulley etc. by means of motor or also.
Describe a kind of coolant pump that do not driven by the reluctance motor connected via axle, that be equipped with half axial flow wing wheel in advance by file US6056518A, being bearing in in the inflow entrance of centre and the pump case of middle outflow opening in its outer periphery by half axial flow wing wheel of motoring of it in addition thus.
In file DE10047387A1 by claimant describe equally a kind of prove in practice feasible, electrically driven (operated), adjustable, with the structural type of adjustable axial flow coolant pump, with the coolant pump for internal-combustion engine of axial impeller.
In addition by claimant describe in file DE10207653C1 and DE10314526B4 other prove equally in practice feasible, adjustable, with the coolant pump for internal-combustion engine of axial impeller.
The major defect of these above-mentioned coolant pumps is also caused by its drive unit, and because motor arrangement is within freezing mixture stream, the motor used only transmits limited torque all the time by structure space restriction is corresponding.
In addition, motor must need, the encapsulation of waterproof also must cause higher manufacture cost.
In addition in these solutions because used electric member or electronic unit should follow the higher extreme value of temperature load, all the time to avoid the inefficacy of these components.
In addition, the coolant pump by means of these motorized motions can not guarantee " failure safe " (coolant pump continues to work after adjustment stops) after " power failure ".
In addition, pump (structural type such as introduced in file DE10207653C1 in addition) with axial impeller demonstrates when suction side throttling, pump needs to improve in flow technique, because there is cavitation and vortex consumingly, it causes wearing and tearing and the power loss of increase.
In addition, from file DE102006034952B4 known a kind of cool cycles for internal-combustion engine, the pump with axial impeller that mechanically drives.This coolant pump being configured to adjustable axial pump has the hollow shaft driven by toothed belt wheel (Zahnriemenscheibe), this hollow shaft is torsionally furnished with multiple rotor blade like this, its adjustment angle mechanically can be adjusted via the application mechanism be arranged in hollow shaft (Wirkmechanismus).
The manipulation of mechanical regulating mechanism realizes via adjustment element (Stellelement) at this, and it can electrically, electronically, hydraulically be gone back or pneumatically manipulate.
Depend on the adjustment angle of rotor blade, the freezing mixture flowing through pump case is accelerated so more or less.
By means of mentioned before this, with the coolant pump of the structural type of the adjustable axial pump driven by toothed belt wheel, cooling power and the driving power of coolant pump can be changed in certain boundary, wherein, transferable torque and " load carrying capacity/durability " of rotor blade that therefore also have maximum delivered volume stream to be supported adjustably limit.
Describe in file DE102008048893A1 that another mechanically drives, for the pump of the cool cycles of internal-combustion engine.For this structural type, be furnished with the axial pump impeller of one-sided supporting in pump case, wherein, pump has two freezing mixture exhaust ports, and one of them can be closed completely by means of the controlling mechanism be arranged in after axial pump impeller.
Disclosed in file DE102008048893A1, with the axial pump impeller of one-sided supporting solution however there is these shortcomings, namely the minimum possible diameter of belt pulley limits by bearing diameter, and supporting one-sided in addition affects the minimum clearance size needed at axial pump impeller place negatively, thus must force due to the high gap size by structure qualification to consider loss in efficiency.
In addition, from file US4865519A, known one is used for the oil-submersible pump (Tauchpumpe) from " immobilising " oil sources (lquelle) conveying crude oil.
In the solution that this illustrates in file US4865519A, active wheel coordinate in the contaminated crude oil of conveying special demand, be therefore provided with pressure relief vent and there is blade shape in addition that coordinate especially in user demand.
This solution feature illustrated in file US4865519A is also, the cover plate of impeller is positioned at the cover of upper saw pulley with the gap being arranged in cover side, and between impeller and upper saw pulley, be furnished with demand, the larger spatial transition coordinated in Crude Oil Transportation.
These of file US4865519A need in conjunction with custom-designed work and guide wheel impeller for the feature that the present invention is important, to realize oil conveying when cost of production obviously reduces and pump size reduces with the energy ezpenditure reduced by means of the oil-submersible pump introduced in file US4865519A (itself is with the head of single-stage).
The similar application of this oily delivery pump structure pattern of KFZ-coolant pump, the cavitation that must to cause in addition due to the temperature that experiences in coolant pump and speed range in cooling medium is combined as, with all shortcomings caused thus according to this solution of file US4865519A.
In addition by applicant describe in file DE102009012923B3 another proved equally in practice feasible, that mechanically drive, adjustable, with the coolant pump for internal-combustion engine of the adjustable pump structure pattern with the axial pump impeller at two-side supporting, wherein, freezing mixture exhaust port can be closed completely by means of the controlling mechanism be arranged in after axial pump impeller.
This solution with the axial impeller at two-side supporting allows to obviously reduce gap size and obviously improves pump efficiency thus in addition relative to aforementioned structural type.
All aforementioned structural type something in commons be fed sheet of a media, freezing mixture just before corresponding axial impeller about arc ground, to be also introduced in the working zone of axial impeller via import front jocket wheel (Vorleitrad) and to be transported to and to be provided with via the guiding device of circular cylindrical, upper saw pulley or not to be provided with in the pressure tap of controlling device therefrom.
Even if all axial impellers used in the axial flow coolant pump of prior art to cavitation responsive and obtain in the scope for the common rotating speed of coolant pump when minimum gap size with the blade geometry structure of its two dimension maximum 50% efficiency.At this, that specify in the engine compartment of Motor Vehicle, limited structure space must also only make strongly limited pressure improve becomes possibility.
In addition by file US2010/143109A1 known a kind of for carry simultaneously freezing mixture on the one hand in low-temperature circulating on the other hand to the coolant pump in high temperature circulation, its with together be in inner cryogen low temperature housing and together be in inner high temperature coil high temperature housing, with for carrying freezing mixture to the special coolant pump in cryogen and high temperature coil-radial active wheel, with the live axle for driving coolant pump-radial active wheel simultaneously.
In addition by file GB2088480A known a kind of in addition with radial structure form that is with axial flow entrance, radial active wheel and Radial Flow export coolant pump, between live axle and bearing element, be provided with the black box of two row's rolling elements and some wherein, it causes sealing between live axle and bearing element.One in black box has seal ring at this, and it is pressed to the back side of impeller by elastic element.
In addition, for the change of constant rotational speed coolant volume stream about the characteristic instability of pumping pressure for the axial flow coolant pump feature illustrated in the prior art, if be that is partly switched on or switched off user for constant rotational speed (generator speed) in circulate coolant, so therefore coolant volume stream change.
Due to the characteristic curve of the instability of this axial flow coolant pump of prior art, this however in the axial flow coolant pump of prior art, cause adversely work, the unexpected and mostly serious change of corresponding pumping pressure.
Summary of the invention
Therefore, the object of the invention be to develop a kind of that mechanically driven by belt pulley, gear, grafting axle etc., for the axial flow coolant pump of internal-combustion engine, it avoids the aforementioned shortcoming of prior art, when the structure space/installation volume less relative to prior art with identical, that is pump shaft rotating speed common for coolant pump the pumping pressure in axial flow coolant pump is significantly improved; And its be characterised in that simultaneously for constant rotational speed coolant volume stream about pumping pressure obviously improve relative to prior art, stable characteristic curve, in addition insensitive to cavitation, avoid the vortex of delivered volume stream, guarantee very high efficiency simultaneously, in addition be characterised in that closely, manufacture and simple on mounting technology, cost advantages and firm structural type, even and if also guarantee high safety in operation and reliability when very long working life for the freezing mixture being loaded with pollution load (Schmutzfracht).
According to the present invention, this object by the feature of independent claims according to the present invention a kind of for internal-combustion engine mechanically driven by belt pulley, gear, grafting axle etc., realize with the coolant pump of the structural type of axial flow coolant pump.
By dependent claims and the ensuing explanation according to solution of the present invention, combine and draw favourable mode of execution of the present invention, details and feature according to the accompanying drawing of solution of the present invention.
Accompanying drawing explanation
Next the present diagram (Fig. 1) be associated with this embodiment according to an embodiment, combination elaborates the present invention.
In FIG with side view illustrated in section mechanically driven by belt pulley 1, according to one of the axial flow coolant pump for internal-combustion engine of the present invention possible structural type.
Embodiment
This axial flow coolant pump according to the present invention is with pump case 2, be arranged in the inflow entrance 3 at pump case place in suction side and be on the pressure side arranged in the outflow opening 4 at pump case place, to can be rotated to support in pump case 2 by means of pump bearing 5 or its place, the pump shaft 6 that is torsionally connected with belt pulley 1, in the sealing seat 7 of inflow entrance 3 side in pump case 2, the pump shaft seals 8 between sealing seat 7 and pump shaft 6 is arranged at driving side, torsionally be arranged in pump case 2, with the upper saw pulley 9 of guide vane 10, bearing accommodating part 11 is there is in upper saw pulley 9, be furnished with sliding bearing 12 wherein, the pump shaft overhang bracket that pump shaft 6 is put with the relative with driving side (such as belt pulley 1) of it is in sliding bearing 12, wherein, on pump shaft 6, the direction of inflow entrance 3 is torsionally furnished with the active wheel 14 with blade 15 with annular space 13 upper saw pulley 9 be adjacent to sliding bearing 12, be characterised in that according to the present invention, active wheel 14 is half axial-flow blowers (Halbaxialschaufelrad) with blade 15 bending on three dimensional space, Francis formula or diagonal flow type impeller (Diagonalschaufelrad).
Half axial-flow blower, Francis formula and diagonal flow type impeller are characterised in that blade geometry mechanism bending on three dimensional space.
Under the boundary conditions of the best and when minimum gap size, though half such axial-flow blower, Francis formula and diagonal flow type impeller can due to the outflow opening of their spatially bending blade and radial direction the situation for the common rotating speed of coolant pump be issued to until 80% efficiency.
Relative to the axial impeller used in axial flow coolant pump in the prior art, half axial-flow blower, Francis formula and diagonal flow type impeller are more insensitive and make to realize obvious pressure in limited structure space and improve to cavitation.
Thus for the present invention importantly, the minimum annular space 13 between active wheel 14 and upper saw pulley 9 guaranteed by side, the both sides pump shaft 6 be bearing in the sliding bearing 12 that opposite side in pump bearing 5 is bearing in upper saw pulley 9, wherein, active wheel (14) and upper saw pulley (9) are with minimum annular space (13) so separately, make active wheel (14) not only side and guide cone (16) adjacent outer rim and also side and guiding cap (17) adjacent outer rim with annular space (13) minimally separately, make to be parallel to active wheel to discharge upper saw pulley that edge stretches and enter edge and construct two seal clearance geometrical constructioies spaced apart, guarantee that the delivered volume stream tiltedly flowed out from active wheel 14 is directly transitioned into best according in upper saw pulley 9 of the present invention on flow technique thus.
Because active wheel 14 is not only in the adjacent outer rim of side and guide cone 16 but also corresponding with minimum annular space 13 (" seal clearance ") separately in the adjacent outer rim of side and guiding cap 17, tiltedly outwards to be introduced best upper saw pulley 9 that is adjacent with minimum annular space 13, that build according to the present invention from active wheel 14 delivered volume stream out, and just " turned to " immediately in upper saw pulley 9 according to the present invention after the transition region limited by these two seal clearance geometrical constructioies.
At this, upper saw pulley 9 according to the present invention is characterised in that, its guiding cap 17 of the taper of outside that there is inner, guide cone 16 tapering gradually in the flowing direction and arrange at intervals with guide cone 16, and guide cone 16 is connected via the guide vane 10 bent on three dimensional space with guiding cap 17.
Be arranged in according in upper saw pulley of the present invention, be equipped with spatially bending guide vane 10, inwardly tapering gradually according to the present invention, this space between guide cone 16 and guiding cap 17 causes now, first tiltedly outside from active wheel 14 according to the present invention out and immediately again " turn to ground " enter delivered volume stream in upper saw pulley 9 when it enters and during it flows through according to upper saw pulley 9 of the present invention in the inside of upper saw pulley 9 according to the present invention on minimum structure space almost without loss, axially delivered volume stream out from upper saw pulley 9 is converted into again without vortex ground without ground, hole, wherein, even if even if the cooling medium of cavitation in very high engine speed range and for heat also can be excluded.
In addition, even if coolant pump according to the present invention guarantees high safety in operation and reliability and very long working life due to its firm design in flow technique when freezing mixture is loaded with pollution load.
According to of the present invention, when structural volume is minimum, high efficiency is guaranteed on the whole when it to cavitation this pump insensitive, although and spatial structure strongly limited obvious pressure is improved become may and be characterised in that at the same time closely, manufacture and simple on mounting technology, cost advantages and firm structural type.
At this should benly be, due to layout and the acting in conjunction of assembly according to the present invention, coolant pump according to the present invention relative to the known axial flow coolant pump of prior art surprisingly in addition feature be especially also for the characteristic stable change of constant rotating speed volume flow about pumping pressure.That is, when being such as partly switched on or switched off user for constant rotational speed (engine speed) in circulate coolant, coolant volume stream is inevitable to be changed immediately.
But relative to the axial coolant pump of the prior art with traditional axial impeller, this no longer causes the change of pumping pressure now due to stable characteristic curve according to the present invention.
At this, coolant pump according to the present invention makes the obviously raising of pumping pressure when structure space/installation volume is identical and rotating speed is identical become possibility relative to the axial coolant pump of prior art.
In series of trials, utilize the axial coolant pump of axial impeller that is equipped with of prior art to determine reduced value when structure space/installation volume is almost identical, its proof utilizes traditional axial coolant pump can obtain the pumping pressure of about 1bar when rotating speed 12000U/min (high engine speed range).On the other hand, the pumping pressure of obviously higher about 1.7bar is obtained herein when the similar rotating speed of identical structure space and 12000U/min by means of the axial coolant pump according to the present invention introduced.
Feature is also, in pump case 2, just existed before active wheel 14 Rotational Symmetry in pump shaft 6 arrange, with the inflow chamber 19 of internal diameter D, its cavity length L is approximately 0.7 to 1.5 times of internal diameter D.
Structural type shown in Figure 1 has inflow chamber 19, and its cavity length L is approximately 0.9 times of internal diameter D.
This inflow chamber 19 according to the present invention causes and does not have noisy inflow, is particularly useful for " homogenize (Vergleichm igung) " of draw volume stream and the further optimization obviously contributed to thus according to effect of the present invention.
Also it is important to the present invention, be furnished with guiding tongue (Leitzunge) 18 at the free end of the outflow side of guiding cap 17.
According to the present invention, this guiding tongue 18 avoids the vortex in the region of outflow opening on the pressure side to be formed and the same further optimization for effect according to the present invention.
But solution according to the present invention also causes on the whole at it, compared with the axial flow coolant pump of prior art, solution according to the present invention requires the obviously less driving power of pump shaft 6 when mainstream channel 21 is closed completely/completely cut off, thus also again improves the efficiency according to axial flow coolant pump of the present invention thus.
In the structural type that this is shown in Figure 1, be in the region of outflow opening 4 in the pump case 2 of axial flow coolant pump according to the present invention the freezing mixture be furnished with mainstream channel 21 and discharge flange (Kuehlmittelaustrittsflansch) 20.
As common in the prior art, this mainstream channel 21 to lead in circulate coolant and such as combine with final controlling element make to realize cylinder block crankshaft case, the best of cylinder head cools, and the cooling of special parts (such as EGR portion, gas exhaust manifold), and also realize the heat supply of the heating unit of passenger carriage and other etc.
List of numerals
1 belt pulley
2 pump case
3 inflow entrances
4 outflow openings
5 pump bearings
6 pump shafts
7 sealing seats
8 pump shaft seals
9 upper saw pulleys
10 guide vanes
11 bearing accommodating parts
12 sliding bearings
13 annular spaces
14 active wheels
15 blades
16 guide cones
17 guiding caps
18 guiding tongues
19 inflow chambers
Flange discharged by 20 freezing mixtures
21 mainstream channels
D internal diameter
L cavity length.
Claims (5)
1. for internal-combustion engine with a coolant pump for the structural type of the coolant pump mechanically driven, its with: with the pump case (2) of inflow entrance (3) and outflow opening (4), the pump shaft (6) in described pump case (2) or at described pump case (2) place is can be rotated to support on by means of pump bearing (5), be arranged in the pump shaft seals (8) between described sealing seat (7) and described pump shaft (6) in sealing seat (7) in described pump case (2), this pump shaft seals is arranged in driving side and is arranged in described inflow entrance (3) side, the upper saw pulley with guide vane (10) (9) in described pump case (2) can not be arranged in relative rotation, there is bearing accommodating part (11) wherein, sliding bearing (12) is furnished with in described bearing accommodating part (11), the pump shaft overhang bracket that described pump shaft (6) is put with the relative with driving side of it is in described sliding bearing (12), wherein, so that the active wheel (14) with blade (15) can not be furnished with in relative rotation in annular space (13) mode be adjacent to the described upper saw pulley (9) of described sliding bearing (12) on the direction of described inflow entrance (3) on described pump shaft (6), and described inflow entrance (3) is arranged in the side, medial axis of described pump shaft (6), the spin axis making freezing mixture favour described active wheel (14) by the inflow of described inflow entrance (3) realizes, it is characterized in that,
-described active wheel (14) is half axial-flow blower with blade (15) bending on three dimensional space, and
The guiding cap (17) of the taper of the outside that-described upper saw pulley (9) that can not be arranged in relative rotation in described pump case (2) has inner, guide cone (16) tapering gradually in the flowing direction and arranges at intervals with described guide cone (16), and
-described guide cone (16) and described guiding cap (17) are connected via bending on three dimensional space and the guide vane of symmetry (10) spaced apartly, and
-described active wheel (14) becomes the annular space (13) of the form of seal clearance separately with described upper saw pulley (9) with minimum, wherein, described active wheel (14) the adjacent outer rim of side and described guide cone (16) and also with the adjacent outer rim of described guiding cap (17) to become the annular space (13) of the form of seal clearance minimally separately
-in described pump case (2), just there is the inflow chamber with internal diameter (D) (19) that Rotational Symmetry arranges in described pump shaft (6) before the described active wheel (14), the cavity length (L) of described inflow chamber (19) is in the scope of 0.7 to 1.5 times of described internal diameter (D).
2. coolant pump according to claim 1, is characterized in that, is furnished with guiding tongue (18) at the free end of described guiding cap (17).
3. according to coolant pump according to claim 1 or claim 2, it is characterized in that, in the region of the described outflow opening (4) at described pump case (2) place, be furnished with freezing mixture discharge flange (20).
4. coolant pump according to claim 1 and 2, is characterized in that, belt pulley (1), gear or grafting axle make the described coolant pump mechanically driven be placed in rotation.
5. coolant pump according to claim 1 and 2, is characterized in that, described active wheel (14) is Francis formula with blade (15) bending on three dimensional space or diagonal flow type impeller.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102010053510.9 | 2010-12-04 | ||
| DE102010053510.9A DE102010053510B4 (en) | 2010-12-04 | 2010-12-04 | Coolant pump |
| PCT/DE2011/002061 WO2012072068A1 (en) | 2010-12-04 | 2011-12-01 | Coolant pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103299081A CN103299081A (en) | 2013-09-11 |
| CN103299081B true CN103299081B (en) | 2016-04-27 |
Family
ID=45528860
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201180058462.3A Expired - Fee Related CN103299081B (en) | 2010-12-04 | 2011-12-01 | Coolant pump |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US20130272848A1 (en) |
| EP (1) | EP2646693B1 (en) |
| JP (1) | JP5917549B2 (en) |
| CN (1) | CN103299081B (en) |
| BR (1) | BR112013013637B1 (en) |
| DE (1) | DE102010053510B4 (en) |
| WO (1) | WO2012072068A1 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| PL3172445T3 (en) * | 2014-07-21 | 2020-04-30 | Nidec Gpm Gmbh | Coolant pump with integrated closed-loop control |
| DE102014019609B4 (en) | 2014-12-30 | 2019-08-22 | Nidec Gpm Gmbh | Coolant pump |
| DE102016219273A1 (en) * | 2016-10-05 | 2018-04-05 | Bayerische Motoren Werke Aktiengesellschaft | Electric pump for a vehicle, in particular for a motor vehicle, and vehicle |
| CN107091238A (en) * | 2017-06-16 | 2017-08-25 | 北京富特盘式电机有限公司 | transformer axial-flow pump |
| DE102017120191B3 (en) | 2017-09-01 | 2018-12-06 | Nidec Gpm Gmbh | Controllable coolant pump for main and secondary conveying circuit |
| DE102020003431A1 (en) | 2020-06-08 | 2021-12-09 | Daimler Ag | Coolant pump for a motor vehicle, in particular for a motor vehicle |
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|---|---|---|---|---|
| DE3505385A1 (en) * | 1985-02-16 | 1986-08-28 | Papst-Motoren GmbH & Co KG, 7742 St Georgen | Duct blower |
| CN1009017B (en) * | 1988-02-12 | 1990-08-01 | 中国科学院工程热物理研究所 | Submersible pump |
| US5549451A (en) * | 1992-12-07 | 1996-08-27 | Lyda, Jr.; Eldon L. | Impelling apparatus |
| RU2215195C1 (en) * | 2002-04-27 | 2003-10-27 | Караджи Вячеслав Георгиевич | Centrifugal fan |
| JP2003343473A (en) * | 2002-05-27 | 2003-12-03 | Ishigaki Co Ltd | Mixed flow impeller with screw in mixed flow pump |
| WO2010102604A1 (en) * | 2009-03-12 | 2010-09-16 | Geräte- und Pumpenbau GmbH | Controllable coolant pump |
Family Cites Families (22)
| Publication number | Priority date | Publication date | Assignee | Title |
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| GB257111A (en) * | 1925-09-25 | 1926-08-26 | Hathorn Davey And Company Ltd | Improvements in or relating to centrifugal pumps |
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2011
- 2011-12-01 JP JP2013541207A patent/JP5917549B2/en active Active
- 2011-12-01 CN CN201180058462.3A patent/CN103299081B/en not_active Expired - Fee Related
- 2011-12-01 WO PCT/DE2011/002061 patent/WO2012072068A1/en active Application Filing
- 2011-12-01 EP EP11811520.3A patent/EP2646693B1/en active Active
- 2011-12-01 US US13/991,217 patent/US20130272848A1/en not_active Abandoned
- 2011-12-01 BR BR112013013637-5A patent/BR112013013637B1/en not_active IP Right Cessation
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Also Published As
| Publication number | Publication date |
|---|---|
| EP2646693A1 (en) | 2013-10-09 |
| DE102010053510B4 (en) | 2014-01-23 |
| WO2012072068A4 (en) | 2012-08-09 |
| BR112013013637A2 (en) | 2019-12-31 |
| JP2013545021A (en) | 2013-12-19 |
| EP2646693B1 (en) | 2016-01-13 |
| WO2012072068A9 (en) | 2012-12-13 |
| BR112013013637B1 (en) | 2020-12-29 |
| JP5917549B2 (en) | 2016-05-18 |
| DE102010053510A1 (en) | 2012-06-06 |
| CN103299081A (en) | 2013-09-11 |
| US20130272848A1 (en) | 2013-10-17 |
| WO2012072068A1 (en) | 2012-06-07 |
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