CN103582763A - Coolant pump for a coolant circuit of an internal combustion engine - Google Patents
Coolant pump for a coolant circuit of an internal combustion engine Download PDFInfo
- Publication number
- CN103582763A CN103582763A CN201280025832.8A CN201280025832A CN103582763A CN 103582763 A CN103582763 A CN 103582763A CN 201280025832 A CN201280025832 A CN 201280025832A CN 103582763 A CN103582763 A CN 103582763A
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- China
- Prior art keywords
- coolant
- impeller
- live axle
- coolant pump
- section
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
- F01P5/12—Pump-driving arrangements
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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
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0027—Varying behaviour or the very pump
- F04D15/0038—Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2270/00—Control
- F05D2270/60—Control system actuates means
- F05D2270/64—Hydraulic actuators
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A coolant pump (1) for a coolant circuit of an internal combustion engine comprises a drive wheel (4) driven preferably via a belt drive and connected to an impeller (5) via a drive shaft (3, 29) rotatably mounted in a pump housing (2), and has at least one coolant outlet (17) radially to the impeller (5). Said coolant outlet is under the control of a blocking ring (15, 26, 36) movable in an axial direction, said blocking ring serving to modify or block a cross-section of the coolant outlet (17) and being displaced by a pressure-medium-actuated actuator. To create a corresponding, controllable coolant pump (1) in a compact form, it is proposed that the actuator be arranged concentric to the drive shaft (3, 29) in the region of the end thereof facing the impeller (5), that the actuator be fastened to the end of the drive shaft (3, 29) and that the actuator be connected to a pressure medium supply via at least one longitudinal bore (32) disposed in the drive shaft (3, 29).
Description
Technical field
The present invention relates to a kind of according to the coolant pump of the circulate coolant for internal-combustion engine as described in the preamble of independent claims 1 and 5, this coolant pump has: preferably by the driven driving wheel of belt drive unit, this driving wheel is connected with impeller by the live axle being supported rotationally in pump case, wherein, radially in described impeller, be provided with at least one coolant outlet; Movable block ring in the axial direction, this block ring for change or locking described in the cross section of coolant outlet; And for adjusting the hydraulically controlled final controlling element of described block ring.
Background technique
Such coolant pump is constructed to centrifugal pump conventionally, and wherein, it is arranged in the distolateral of internal-combustion engine and is driven by the belt drive unit that is arranged on there.In this case, rotate and according to this rotating speed, determined amount of coolant be transported in circulate coolant thus to the live axle of coolant pump and the synchronization of internal-combustion engine, described circulate coolant is by being arranged on coolant room in crankcase and in cylinder head, forming for the heat exchanger of Vehicle heating and the cooler being circulated by cooling-air.At this, coolant pump designs as follows, that is, in order to reach cooling power required under all working condition, described coolant pump is also carried coolant flow when the idling speed of internal-combustion engine.
In the heat run stage of internal-combustion engine, the coolant flow of generally being guided by cooler is interrupted in whole or in part by heat control valve.Therefore, at internal-combustion engine, also do not reach in stage at operating temperature place of regulation, whole coolant flows or shunting, be that is to say by the bypass line parallel with freezing mixture and flow by this heat control valve in short circuit.
In addition, past is seeking solution, to shorten clearly this heat run stage, the frictional loss that also can avoid on a large scale thus occurring in the work of internal-combustion engine, the discharge value of raising and due to the former thereby higher fuel consumption of discharge value and frictional loss.At this, regulation, by driving the speed changer of coolant pump to regulate the driving rotating speed of coolant pump, or is switched on or switched off total driving of coolant pump by clutch in addition.Regulation has other known solution,, is provided with adjustment element on the coolant pump being constructed as centrifugal pump that is, by described adjustment element, can adjust coolant outlet until it entirely shuts with regulative mode.The present invention relates to a kind of corresponding design proposal of coolant pump.
A kind of coolant pump of the circulate coolant for internal-combustion engine of the type of mentioning in the preamble of claim 1 is open by DE 10 2,007 022 189 A1.At this, relate to a kind of depending on of guide plate is delivered to the adjustment of under-voltage or overvoltage of pressometer and adjustable coolant pump.At this, pressometer should work as pressure converter, and wherein, the work medium that is positioned at hydraulic pipe line is moved to the output cylinder of a plurality of little cross sections by the working piston that is disposed in the large cross section of under-voltage box.Described output cylinder is disposed in this pump case and takes in respectively piston rod via the pump case side face of coolant pump equably, and wherein, at it, the end of overflow chamber and the valve plug of axial motion are connected piston rod dorsad.Replace under-voltage adjustment (under-voltage being used in air-intake of combustion engine stroke for this reason), load the overvoltage from the lubricant circulates of internal-combustion engine also can to the working piston being arranged in pressure converter.
In addition, from the known a kind of adjustable coolant pump of DE 199 01 123 A1, wherein, in the inside of impeller, be provided with final controlling element, this final controlling element radially surrounds the sleeve of coolant outlet for axial adjustment.In the mode of execution shown in, this final controlling element should be comprised of wax formula expansion modulator (Wachsausdehnungssteller), the pin stretching on the longitudinal direction of coolant pump moves by described wax formula expansion modulator, and the pin by circumferentially extending is passed on sleeve.In addition, the document also comprises following prompting, that is, this final controlling element also can be electrically, ground or pneumatically handled surges.
Summary of the invention
Task of the present invention be improve as follows a kind of device that is provided with the control coolant outlet that is configured to block ring quilt, for the coolant pump of the circulate coolant of internal-combustion engine,, set final controlling element can be disposed in the inside of coolant pump for this reason, and need not change coolant pump not only in physical dimension in the radial direction but also in the axial direction or only change minutely described physical dimension.In addition, should manufacture at low cost and construct a kind of adjustable coolant pump that is provided with corresponding final controlling element very functional safety, so that this coolant pump is suitable for being applied in the internal-combustion engine of manufacture in enormous quantities.
This task is that the preamble of accessory rights requirement 1 starts to have combined with the characteristic of its representation feature.According to the part of the representation feature of claim 1, described final controlling element should be concentric with described live axle be arranged in this live axle in the end regions of described impeller, wherein, described final controlling element is fastened on the described end of described live axle, and the longitudinal drilling that described final controlling element should be arranged in described live axle by least one is connected with pressure medium feeding mechanism.By the corresponding arrangement via the longitudinal drilling in live axle of described final controlling element and pressure medium feeding mechanism thereof, obtain overall less radial dimension for the housing of coolant pump.This radial dimension can be in an advantageous manner roughly with drive the radial dimension of belt pulley of described coolant pump consistent.In addition, this arrangement of final controlling element also produces actively impact to axial dimension, because by described final controlling element is arranged on the end of described live axle, makes the structure length of the described housing of described coolant pump keep almost constant.This has a very big significance, because in the distolateral region of internal-combustion engine, that is to say in the region of its belt drive unit, only provide a small amount of for arranging and drive the space of described coolant pump, and described coolant pump must provide following axial dimension, that is, the belt pulley of this coolant pump is aimed at remaining belt pulley.
On the other hand, according to DE 10 2,007 022 189 A1, in the internal placement of the housing of coolant pump, there are a plurality of hydraulic type final controlling element that are single piston cylinder units form, on described hydraulic actuator, are fixed with guide plate.Due to the described layout to this set radial pressure medium to single final controlling element supply and final controlling element, obtain the disadvantageous radial and axial size of the housing of coolant pump.In addition, when the piston of piston cylinder units not being implemented to the longitudinal movement of absolute synchronization, also can disturb by generating function.
Contrary with solution according to the present invention, according to DE 199 01 123 A1, final controlling element is arranged in the wheel hub of freezing mixture pump runner, and therefore be not positioned at live axle on the end of impeller.In addition, from the document, only learn, the wax formula expansion modulator shown in replacement, also can arrange a kind of electronic, surge or the regulating device of pneumatic drive.But then the corresponding supply of hydraulic pressure medium should be completely significantly housing by coolant pump carry out.Not only the supply scheme of the arrangement of final controlling element but also hydraulic medium all causes that whole coolant pump is not only in the amplification of physical dimension in the radial direction but also in the axial direction.
According to the first favourable design proposal of the present invention, described final controlling element should be configured to hydraulic cylinder and be arranged in coaxially on the described end of described live axle.In this regard, hydraulic cylinder is interpreted as the general arrangement being comprised of the piston vertically moving and the cylinder that surrounds this piston.At this, preferably relate to the single hydraulic cylinder of a kind of letter, carry out whereby the pressure-operated adjustment of block ring in its closed position, that is to say that coolant outlet is radially closed in this closed position.Therefore in this case, the reset of block ring and the simple single hydraulic cylinder pressure spring that moves through in the opposite direction carry out, and described pressure spring can be arranged between impeller and block ring or in the inside of final controlling element.In addition; by for making closing plate reset to such arrangement of the pressure spring of its open position; can also generate a kind of failure protecting device, when the pressure supply of final controlling element was lost efficacy, by this failure protecting device, always guarantee: coolant pump is carried cooling water fully.
, there is different feasible programs in structural scheme and arrangement in view of hydraulic cylinder: on the one hand, advises that the cylinder bearing face of described hydraulic cylinder is directly configured in described live axle.In this case, the end towards described active wheel of described live axle is designed to hollow shaft, and wherein, the internal valve of this hollow shaft forms corresponding cylinder bearing face.Thus, can generate very compact arrangement, and final controlling element can be used for a small amount of production costs manufacturing.On the other hand, to this alternative be to have following feasible program,, piston is fastened on live axle, and be substantially layout and the coefficient cylinder of this piston on the guide plate design of tank shape, that form block ring, wherein, this member defines corresponding pressure chamber.At this, relate to equally the very compact arrangement of final controlling element, this arrangement is suitable for producing in enormous quantities.
According to the second design proposal of the present invention, described final controlling element is configured to diaphragm.Corresponding diaphragm allows very short axial arrangement length.At this, this diaphragm is fixed on the flange piece that radially surrounds described live axle, wherein, the pressure medium flowing out from the described longitudinal drilling of described live axle pushes this diaphragm against the bottom that is equally the guide plate of tank shape design, thereby described guide plate moves in its closed position of block ring after described diaphragm skew.And in this case, on described guide plate, being provided with return spring, described return spring makes described guide plate after the pressure drop of described diaphragm inside, again move to its open position.
In addition, for a kind of its generic character solution identical with the generic character of claim 1, proposition, described final controlling element is concentric with live axle and is arranged in the region of the end towards described impeller of this live axle and is constructed to diaphragm.Afterwards, pressure medium also can be directed in the pressure chamber being arranged on described diaphragm by the passage being arranged in the described housing of described coolant pump.Except this feasible program only just realizing with larger technical fee, according to this motion, also should primarily relate to, make hydraulic pressure medium under pressure be arranged on by least one the pressure chamber that longitudinal drilling in described live axle is supplied to described diaphragm.Except these one or more longitudinal drillings, if needed, certainly lateral bore can be set, these lateral bores for example stretch between corresponding pressure source or control valve and the longitudinal drilling of correspondence.
According to the improvement project of this solution, described live axle at it towards the first branch's section being roughly constructed as flange of taking in described impeller on the end of described impeller, wherein, described diaphragm is fixed in described first branch's section by its edge, and wherein, described diaphragm therebetween region inner support, being on the guide plate of tank shape design, is configured with block ring on described guide plate, described block ring in its locked position of coupler in the form of a ring around described coolant outlet.This of described impeller first branch's section with it, separate second branch's section that axially spaced-apart is arranged and be connected, wherein, between Gai Liangge branch section, be furnished with blade and the described guide plate of described centrifugal pump.At this, described guide plate can axially move between the Gai Liangge of described impeller branch section, and wherein, described guide plate is sealed by bearing ring seal part or piston ring during it is with respect to the axial motion of described first branch's section.Described diaphragm is fixed in the groove of rounded stretching, extension of described first branch's section.
In addition the described guide plate illustrating above, can also be set up at the arrangement of the inside of described impeller when described final controlling element is configured to piston cylinder units.In addition, diaphragm or piston cylinder units are not limited to such arrangement of described guide plate as the application of final controlling element.Replace described guide plate, can also between pump case and impeller, three-dimensionally arrange the fixture of taking in block ring.
In the improvement project of this layout, should be provided with Returnning spring, described return spring overcomes the motion being produced in locking direction by diaphragm of guide plate.That is to say and relate to the single hydraulic type adjustment of a kind of letter, wherein, from pressure medium feeding mechanism, by control valve, cause the pressure-loaded of diaphragm or with the emptying pressure chamber being arranged on diaphragm of mode with no pressure.The position that guide plate is moved to one or more coolant outlets are opened due to pressure spring; thereby generate by this way error protection and control; so also guaranteed when pilot pressure loses efficacy, coolant pump is always carried coolant flow by described circulate coolant.
In addition, what diaphragm should be stipulated in the situation that final controlling element is applied, be, described live axle is taken in the first branch's section being roughly constructed as flange at it on the end of described impeller, and described diaphragm at it towards being structured on the surface of described first branch's section or the described Duan Qi of branch is structured on the surface of described diaphragm.This surface structure that preferably relates to the groove stretching from the end regions radially outward of live axle guaranteed, the pressure medium flowing between the surface of diaphragm and the surface of branch's section distributes on all surfaces.Can cause thus by diaphragm guide plate and the undelayed adjustment that is configured in the block ring on this guide plate.
In addition, the blade that described first branch's section should be by described impeller with described first branch's section in the axial direction second branch's section of devices spaced apart be connected, wherein, described blade is guided through the recess in described guide plate.That is to say, described guide plate is carried out motion in the axial direction, wherein, described guide plate on the one hand in its closed position the second branch section stop of impeller and in its open position in the section stop of the first branch.
Finally propose, by being arranged in control pump in the housing of coolant pump, transport the final controlling element of pressure medium for being constructed as diaphragm or hydraulic cylinder.At this, this control pump should be directly by drive shaft.In addition, the housing planted agent of described coolant pump, be furnished with control valve, described control valve makes to lead to the work connected member of pressure chamber of diaphragm or hydraulic cylinder and the joint of pumping hole or reservoir port is connected selectively or inaccessible.The freezing mixture taking out from circulate coolant as pressure medium advantageous applications, thus when contingent leakage, avoid, and other pressure medium for example lubricant oil mixes with the freezing mixture of circulate coolant.
The present invention is not limited to the given combination of the feature of independent claims 1 and 5 and the feature of dependent claims.In addition also have other feasible program, that is, can make single feature, particularly from the Patent right requirement of embodiment's explanation below or the feature directly drawing from accompanying drawing, mutually combine.In addition, by application label, at attached chart display Patent right requirement, should never make the design example of the protection domain of Patent right requirement shown in being limited to.
Accompanying drawing explanation
In addition, further feature of the present invention is from following explanation and draw from accompanying drawing, simplifies three embodiments of the present invention are shown in the accompanying drawings.Wherein:
Fig. 1 illustrates the vertical profile parallax stereogram according to coolant pump of the present invention, and wherein, final controlling element is configured to be arranged in the hydraulic cylinder in live axle;
Fig. 2 illustrates the partial perspective view of coolant pump with the form of longitudinal section, the region of the impeller of this coolant pump is shown, and this impeller has the closed position of guide plate;
Fig. 3 illustrates the partial view of the impeller shown in Fig. 2, and this impeller has the open position of guide plate;
Fig. 4 illustrates the vertical profile parallax stereogram of the layout of impeller on live axle, and wherein, final controlling element is configured to diaphragm; And
Fig. 5 illustrates partial perspective view in the layout area of impeller on live axle, and wherein, final controlling element has first branch's section of impeller, and described first branch's section has structurized surface.
Embodiment
Coolant pump shown in Figure 1, described coolant pump has pump case 2 and is supported in the live axle 3 in this pump case 2.At this, live axle 3 is preferably bearing in pump case 2 by the rolling bearing not being shown specifically, and this live axle is taken in driving wheel 4 and takes in impeller 5 in its other end in one end.In addition, at it, the end towards impeller 5 is constructed to hollow shaft 6 to live axle, thereby forms in this end the hydraulic cylinder 7 coaxially stretching in live axle.At this, in the internal structure of hollow shaft 6, there is cylinder bearing face 8, on this cylinder bearing face, hydraulic piston 9 is directed hermetically.Piston rod 10 is from these hydraulic piston 9s, and this piston rod 1 centrally stretches by impeller 5.
In addition, impeller 5 is by being first branch's section 11 of flange shape structure and by forming with second branch's section 12 of first branch's section devices spaced apart in the axial direction.The blade 5a of impeller 5 stretches between these branch's sections, and described blade is carried the freezing mixture radially outward being sucked in the centre of impeller 5.On the piston rod 10 extending along the longitudinal axis, be furnished with guide plate 13, this guide plate has the wheel hub 14 of dish type and the block ring 15 of the cylindrical structure that engages with wheel hub 14.Guide plate 13 can move in the axial direction by piston rod 10, wherein, block ring 15 moves in the free space 16 of housing 2 in the open position of guide plate 13, and block ring 15 is arranged in the position that covers coolant outlet 17 in the locked position of coupler shown in Fig. 1.
At this, definite running parameter that the adjustment of guide plate 13 depends on internal-combustion engine carries out, and packs coolant pump 1 in this internal-combustion engine into.At this, should realize, freezing mixture does not rely on respective external temperature ground and is heated relatively rapidly after the starting process of internal-combustion engine, so internal-combustion engine reaches the operating temperature of its regulation at short notice.
For the hydraulic cylinder 7 by as final controlling element, adjust guide plate 13 and be provided with control pump 18, this control pump is supplied to control valve 20 by the pressure medium from fuel tank 19.In this case, control valve 20 is constructed to three position three-way change valve and is arranged in its locked position of coupler, and working line 21 quilt in this locked position of coupler that is directed to hydraulic cylinder inside is inaccessible.In two other position, pressure medium or be transported to hydraulic cylinder 7 from control pump 18, or from this hydraulic cylinder 7, in mode with no pressure, the direction at fuel tank 19 is discharged from.Can change the relevant position of guide plate 13 thus.Guide plate is provided with recess 22, and the blade 5a of impeller 5 is guided through described recess.In addition, first branch's section 11 of impeller 5 has the Sealing 23 stretching at its side face, and the block ring 15 being constructed on guide plate 13 is directed on described Sealing 23 slidably.
According to Fig. 2 and Fig. 3, be provided with the structural scheme with respect to Fig. 1 change for guide plate and final controlling element, thus the label of changing for these component applications.In addition, these labels are roughly consistent with the label according to Fig. 1.From learning according to the diagram of Fig. 2 and Fig. 3, impeller 5 with two branch's section 11 and 12 and the blade 5a that stretches between them take in guide plate 24, guide plate 24 has plate-like wheel hub 25 and cylindrical block ring 26.In addition, guide plate 24 is configured to one with cylinder 27, and cylinder 27 forms pressure chamber 31 together with being disposed in anti-relative rotation the hydraulic piston 28 on live axle 29.In addition, hydraulic piston 28 is provided with piston ring 30, and thus, pressure chamber 31 is inner sealed at cylinder 27.
Distolateral at cylinder 27, first branch's section 11 of impeller 5 has doughnut 11a, and when adjusting guide plate 24, cylinder 27 moves in doughnut 11a at the open position for a coolant outlet 17 or a plurality of coolant outlet 17.This position of guide plate 24 illustrates at Fig. 3.At this, the corresponding pressure initiation in the pressure chamber of cylinder 27 is undertaken by the longitudinal drilling 32 at least stretching through live axle 29 with portion's segmented mode.
In other design proposals of the present invention shown in Fig. 4 and Fig. 5, wherein, in view of the structural scheme of applied live axle and impeller, exist with according to the conformity of the design proposal of Fig. 1 to Fig. 3.With regard to this respect, also can apply same numeral.Compare essential difference with design proposal of the present invention above-mentioned and that illustrated and be, according to Fig. 4 and Fig. 5, in first branch's section 11, be furnished with diaphragm 33, wherein, the edge of this diaphragm 33 is taken in hermetically by the circular groove 34 of first branch's section 11.The pressure medium that longitudinal drilling 32 by live axle 29 is supplied to causes the skew of diaphragm 33, and at this, diaphragm 33 is supported on guide plate 35 and this guide plate 35 is moved in the axial direction.Applied diaphragm 33 occupies a position in the open position of block ring 36, in described position, is attached in first branch's section 11 to 33 formulas of diaphragm.For the pressure medium that makes to supply with by longitudinal drilling 32 can arrive the surface towards first branch's section 11 of diaphragm 33 fully, first branch's section 11 is provided with the surface structure with the form of the groove 37 of the exit region radially outward guiding from longitudinal drilling 32 in the region being surrounded by diaphragm 33.
Reference numerals list
Claims (10)
1. the coolant pump for the circulate coolant of internal-combustion engine (1), described coolant pump has: the driving wheel preferably driving by belt drive unit (4), this driving wheel is connected with impeller (5) by the live axle (3,29) being bearing in rotating mode in pump case (2), wherein, radially in described impeller (5), be provided with at least one coolant outlet (17); The block ring that can move in the axial direction (15,26,36), this block ring is for the cross section of coolant outlet (17) described in change or locking; And hydraulically controlled final controlling element, be used for adjusting described block ring (15,26,36), it is characterized in that, described final controlling element and described live axle (3,29) are arranged in the region of the end towards described impeller (5) of described live axle with one heart, described final controlling element is fixed on the described end of described live axle (3,29), and the longitudinal drilling (32) that described final controlling element is arranged in described live axle (3,29) by least one is connected with pressure medium feeding mechanism.
2. coolant pump according to claim 1 (1), is characterized in that, described final controlling element is constructed to hydraulic cylinder (7,27) and is arranged in coaxially on the described end of described live axle (3,29).
3. coolant pump according to claim 2 (1), is characterized in that, the cylinder bearing face (8) of described hydraulic cylinder (7) is directly configured in described live axle (3).
4. coolant pump according to claim 1 (1), is characterized in that, described final controlling element is configured to diaphragm (33).
5. the coolant pump for the circulate coolant of internal-combustion engine (1), described coolant pump has: the driving wheel preferably driving by belt drive unit (4), this driving wheel is connected with impeller (5) by the live axle (29) being bearing in rotating mode in pump case (2), wherein, radially in described impeller (5), be provided with at least one coolant outlet (17); The block ring that can move in the axial direction (36), this block ring is for the cross section of coolant outlet (17) described in change or locking; And hydraulically controlled final controlling element, be used for adjusting described block ring (36), it is characterized in that, described final controlling element and described live axle (29) are arranged in one heart in the region of the end towards described impeller (5) of described live axle and are configured to diaphragm (33).
6. according to the coolant pump described in claim 4 or 5 (1), it is characterized in that, described live axle (29) its towards take on the end of described impeller (5) described impeller (5) roughly as first branch's section (11) of flange configuration, described diaphragm (33) is fixed in described first branch's section (11) of described impeller (5) by its edge, and described diaphragm (33) therebetween region inner support on guide plate (35), on this guide plate, be configured with block ring (36), this block ring in its locked position of coupler in the form of a ring around described coolant outlet.
7. coolant pump according to claim 6 (1), is characterized in that, is provided with return spring (38), and this return spring overcomes the motion being produced in locking direction by described diaphragm (33) of described guide plate (35).
8. according to the coolant pump described in claim 4 or 5 (1), it is characterized in that, described live axle (29) at it towards first branch's section (11) of taking on the end of described impeller (5) roughly as flange configuration, and described diaphragm (33) at it towards being structured on the surface of described first branch's section (11) or described branch section (11) is structured on the surface of described diaphragm (33) at it.
9. coolant pump according to claim 1 (1), it is characterized in that, first branch's section (11) of described impeller (5) by blade (5a) and described impeller (5) follow described first branch's section in the axial direction isolated second branch's section (12) be connected, wherein, described blade (5a) is guided through the recess (22) in described guide plate (13,24,35).
10. coolant pump according to claim 1 (1), it is characterized in that, in the described pump case (2) of described coolant pump (1), be furnished with control pump (18) and control valve (20), wherein, the work connected member (21) of described control valve (20) is connected with described longitudinal drilling (32).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102011079310.0 | 2011-07-18 | ||
| DE102011079310A DE102011079310A1 (en) | 2011-07-18 | 2011-07-18 | Coolant pump for a coolant circuit of an internal combustion engine |
| PCT/EP2012/054224 WO2013010683A1 (en) | 2011-07-18 | 2012-03-12 | Coolant pump for a coolant circuit of an internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103582763A true CN103582763A (en) | 2014-02-12 |
Family
ID=45855744
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280025832.8A Pending CN103582763A (en) | 2011-07-18 | 2012-03-12 | Coolant pump for a coolant circuit of an internal combustion engine |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20140147304A1 (en) |
| CN (1) | CN103582763A (en) |
| DE (1) | DE102011079310A1 (en) |
| WO (1) | WO2013010683A1 (en) |
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| CN106536939A (en) * | 2014-07-21 | 2017-03-22 | 尼得科Gpm有限公司 | Coolant pump with integrated closed-loop control |
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| CN114341533A (en) * | 2019-09-04 | 2022-04-12 | 舍弗勒技术股份两合公司 | Coolant regulator with shaft seal |
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| CN103148018B (en) * | 2013-03-05 | 2017-08-25 | 湖南机油泵股份有限公司 | A kind of change displacement water pump for engine-cooling system |
| DE102014202979A1 (en) * | 2014-02-18 | 2015-08-20 | Volkswagen Aktiengesellschaft | pump |
| DE102017120191B3 (en) | 2017-09-01 | 2018-12-06 | Nidec Gpm Gmbh | Controllable coolant pump for main and secondary conveying circuit |
| KR102451915B1 (en) * | 2018-03-27 | 2022-10-06 | 현대자동차 주식회사 | Coolant pump and cooling system provided with the same for vehicle |
| DE102019122717A1 (en) * | 2019-08-23 | 2021-02-25 | Nidec Gpm Gmbh | Adjustable coolant pump with piston rod guide |
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| DE2110776A1 (en) * | 1971-03-06 | 1972-09-07 | Gulde Regelarmaturen Kg | Flow working machine with adjustable impeller channel cross-sections |
| DE2255503A1 (en) * | 1972-11-13 | 1974-05-16 | Heinz Knebel | DEVICE FOR CONTINUOUSLY ADJUSTABLE EMISSION VOLUME CONTROL FOR CENTRIFUGAL PUMPS, FANS AND BLOWERS |
| DE102006034960A1 (en) * | 2006-07-28 | 2008-01-31 | Audi Ag | Cooling fluid pump i.e. radial rotary pump, for internal combustion engine of motor vehicle, has valve gate movable between three different gate positions, where cooling fluid outlets are either opened or closed in different gate positions |
| CN101233338A (en) * | 2005-08-01 | 2008-07-30 | 蒂姆肯公司 | Coolant pump for internal combustion engine |
| CN101351631A (en) * | 2005-12-23 | 2009-01-21 | 欧根·施密特博士仪器和泵制造有限责任公司 | Controllable coolant pump |
| CN102046982A (en) * | 2008-05-30 | 2011-05-04 | 欧根·施密特博士仪器和泵制造有限责任公司 | Controllable coolant pump |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5211530A (en) * | 1992-04-20 | 1993-05-18 | The United States Of America As Represented By The Secretary Of The Navy | Variable breadth impeller that provides a specific shutoff head |
| US5800120A (en) * | 1995-11-07 | 1998-09-01 | A. W. Chesterton Co. | Pump impeller with adjustable blades |
| DE19901123A1 (en) | 1999-01-14 | 2000-07-20 | Bosch Gmbh Robert | Controllable radial pump, especially for supplying coolant for car has adjuster connected with sleeve which can be slid over pump blades in axial direction |
| DE102007022189A1 (en) | 2007-05-11 | 2008-11-27 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Pulley driven, controllable coolant pump for internal combustion engine of motor vehicle, has transmitter with end including actuating and working pistons at hydraulic pipe, where working piston operates in operating medium provided in pipe |
| DE102008046424A1 (en) * | 2008-09-09 | 2010-03-11 | Schaeffler Kg | Adjustable coolant pump |
-
2011
- 2011-07-18 DE DE102011079310A patent/DE102011079310A1/en not_active Withdrawn
-
2012
- 2012-03-12 WO PCT/EP2012/054224 patent/WO2013010683A1/en active Application Filing
- 2012-03-12 US US14/233,136 patent/US20140147304A1/en not_active Abandoned
- 2012-03-12 CN CN201280025832.8A patent/CN103582763A/en active Pending
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| US3407740A (en) * | 1967-04-14 | 1968-10-29 | Borg Warner | Variable geometry centrifugal pump |
| US3482523A (en) * | 1968-03-06 | 1969-12-09 | Crane Co | Centrifugal pump with flow control by pressure feedback |
| DE2110776A1 (en) * | 1971-03-06 | 1972-09-07 | Gulde Regelarmaturen Kg | Flow working machine with adjustable impeller channel cross-sections |
| DE2255503A1 (en) * | 1972-11-13 | 1974-05-16 | Heinz Knebel | DEVICE FOR CONTINUOUSLY ADJUSTABLE EMISSION VOLUME CONTROL FOR CENTRIFUGAL PUMPS, FANS AND BLOWERS |
| CN101233338A (en) * | 2005-08-01 | 2008-07-30 | 蒂姆肯公司 | Coolant pump for internal combustion engine |
| CN101351631A (en) * | 2005-12-23 | 2009-01-21 | 欧根·施密特博士仪器和泵制造有限责任公司 | Controllable coolant pump |
| DE102006034960A1 (en) * | 2006-07-28 | 2008-01-31 | Audi Ag | Cooling fluid pump i.e. radial rotary pump, for internal combustion engine of motor vehicle, has valve gate movable between three different gate positions, where cooling fluid outlets are either opened or closed in different gate positions |
| CN102046982A (en) * | 2008-05-30 | 2011-05-04 | 欧根·施密特博士仪器和泵制造有限责任公司 | Controllable coolant pump |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106536939A (en) * | 2014-07-21 | 2017-03-22 | 尼得科Gpm有限公司 | Coolant pump with integrated closed-loop control |
| CN106536939B (en) * | 2014-07-21 | 2019-09-06 | 尼得科Gpm有限公司 | Coolant pump with integrated closed-loop control |
| CN110475953A (en) * | 2017-03-17 | 2019-11-19 | 明和工业株式会社 | Water pump |
| CN114341533A (en) * | 2019-09-04 | 2022-04-12 | 舍弗勒技术股份两合公司 | Coolant regulator with shaft seal |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102011079310A1 (en) | 2013-01-24 |
| US20140147304A1 (en) | 2014-05-29 |
| WO2013010683A1 (en) | 2013-01-24 |
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