CN204572444U - For the crescent gear pump of SCR system - Google Patents
For the crescent gear pump of SCR system Download PDFInfo
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- CN204572444U CN204572444U CN201520252721.1U CN201520252721U CN204572444U CN 204572444 U CN204572444 U CN 204572444U CN 201520252721 U CN201520252721 U CN 201520252721U CN 204572444 U CN204572444 U CN 204572444U
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- gear
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- magnetic coupling
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Abstract
The utility model relates to a kind of crescent gear pump, and it comprises: motor; Magnetic coupling assembly; Rear end cover; Enclosing cover; There is the gear rotor of external tooth; There is the gear ring rotor of internal tooth; And axle; It is characterized in that, the number of teeth of described gear rotor is 10, and the number of teeth of described gear ring rotor is 11; The tooth curve of the half tooth of described internal tooth and external tooth is respectively: y
1=0.3162x
1 3-1.3895x
1 2+ 0.7771x
1+ 9.5775; And y
2=-0.2179x
2 3+ 0.8686x
2 2-0.3275x
2+ 8.992, wherein x
1scope be from 0mm to 2.53mm, x
2scope be from 0mm to 2.95mm.Gear pump of the present utility model, compared to prior art gear pump, had both improve and had held dirty ability, and again reduced the risk of leakage, also reduce the requirement to gear manufacture precision simultaneously, such that gear pump of the present utility model is durable in use and cost is low.Gear pump of the present utility model can be used for SCR system.
Description
Technical field
The utility model relates to a kind of crescent gear pump, and it is used in particular for SCR system.
Background technique
Selective catalytic reduction (SCR) system is used to the nitrogen oxide (NO reduced in the waste gas of internal-combustion engine particularly diesel engine
x) effective means.SCR system uses liquid SCR reactant as reducing agent usually, and it typically is urea liquid.This reducing agent is injected in waste gas in engine downstream, catalyst converter upstream usually, and through the series reaction that occurs in catalyst converter by NO
xbe converted into nitrogen and water, realize the minimizing of pollutant.
In SCR system, for the accurate quantification realizing urea liquid sprays, reliable and durable fluid pump is vital.This pump not only will meet low leakage requirement during conveying low viscosity solution operating mode, and will avoid causing pump performance to be degenerated because temperature arrising caused by friction is too high, and size is sufficiently little simultaneously, to meet the requirement of carrying out installing in the confined space of vehicle.
The fluid pump for SCR system has been there is in prior art.
Such as, CN 102654125 A discloses a kind of positive displacement fluid pump, and it comprises motor, inner gear rotor and external gear rotor.Inner gear rotor is driven by motor and rotates about the axis, and has multiple outward extending tooth.External gear rotor has the multiple teeth extended internally with the indented joint of inner gear rotor, and make when inner gear rotor rotates, external gear rotor is driven to rotate around the second axis.At least one in inner gear rotor and external gear rotor is made up of plastic gear.Gap between the tip of inner gear rotor tooth and external gear rotor tooth is between 10 and 30 microns.
Again such as, CN 203146313 U discloses a kind of crescent gear pump, and it comprises front cover, gear ring, gear and axle.Wherein, gear is driving link, is positioned by axle, gear is provided with and can connects powered attendant-controlled wheelchairs shift fork; Gear ring is driven member, with front cover Spielpassung; Gear ring and gear have and to engage each other and through tooth root correction of the flank shape and back chipping arc toothed.The material of gear and gear ring is the special engineering plastics of carbon fiber-containing, graphite, teflon.
But, above-mentioned two kinds of gear pumps are all based on Gerotor (being also called G-rotor) principle, although it can meet the requirement of miniaturization, but the dirt in convection cell is very responsive, thus the contradiction of reality is often: hold dirty ability for improving, need to increase the gap between inside and outside gear rotor crown end, but this gap increases and then easily causes again leaking, and therefore more difficultly takes into account.
Model utility content
Primary and foremost purpose of the present utility model is to provide a kind of crescent gear pump, and it can improve the dirty ability of appearance while the low leakage of guarantee, thus meets the injection demand of SCR system.
This object of the present utility model is achieved through the following technical solutions.A kind of crescent gear pump, it comprises: motor; Magnetic coupling assembly, comprises motor side magnetic coupling, and pump end magnetic coupling; Rear end cover, itself and described pump end magnetic coupling are arranged roughly coaxially; Enclosing cover, is provided with pump intake end and pump discharge end, described enclosing cover and described rear end cover vicinity; Have the gear rotor of external tooth, it is accommodated between described enclosing cover and described rear end cover, and is rotated around first axle by described motor driving; Have the gear ring rotor of internal tooth, it is accommodated between described enclosing cover and described rear end cover, and realizes internal messing with described gear rotor, and make when described gear rotor rotates, described gear ring rotor rotates around the second axis being different from first axle; And axle, it is through the center of described gear rotor, and two ends are supported by described pump end magnetic coupling and described enclosing cover respectively, thus limits described first axle;
Wherein, the number of teeth of described gear rotor is 10, and the number of teeth of described gear ring rotor is 11; The tooth curve of the half tooth of the external tooth of described gear rotor is expressed as in the rectangular coordinate system taking Gear center as true origin:
y
1＝0.3162x
1 3-1.3895x
1 2+0.7771x
1+9.5775，
The tooth curve of the half tooth of the internal tooth of described gear ring rotor is expressed as in the rectangular coordinate system taking gear ring center as true origin:
y
2＝-0.2179x
2 3+0.8686x
2 2-0.3275x
2+8.992，
Wherein x
1scope be from 0mm to 2.53mm, x
2scope be from 0mm to 2.95mm.
Alternatively, described gear rotor and described gear ring rotor are made by PEEK plastics.
Alternatively, described axle is made up of W-Co kind cemented carbide.
Alternatively, in described enclosing cover, be provided with chamber, described gear ring rotor to be accommodated in described chamber in the mode of Spielpassung and thus limit described second axis, the axial clearance between described chamber and described gear rotor and described gear ring rotor is between 10-40 micron.
Alternatively, described axle and described enclosing cover interference fit.
Alternatively, the front end of described pump end magnetic coupling comprises multiple projection for transmitting torque, and described gear rotor is provided with the groove of shape with described projection and location matches, and described projection is contained in described groove in the mode of form fit.
Alternatively, the gap between external tooth and the tip of internal tooth is between 10-60 micron, and preferably between 35-60 micron, the gap between external tooth tooth top and internal tooth tooth root is between 100-150 micron.
The utility model ensure that the large discharge of described gear pump, long engagement, stable transmission, pulseless specific by the specific profile of tooth of inside and outside gear; Further, by the specific profile of tooth characteristic of inside and outside gear, described gear pump can realize tiny leakage even No leakage when larger tip clearance, and larger gap improves the dirty ability of appearance, reduces friction, thus ensure that the serviceability of pump; Above-mentioned optional feature then further ensure that the advantageous feature of crescent gear pump of the present utility model in serviceability, sealing and compactedness etc.
Accompanying drawing explanation
Be described according to the preferred implementation of crescent gear pump of the present utility model hereinafter with reference to accompanying drawing.In figure:
Fig. 1 is the side view of the preferred implementation according to crescent gear pump of the present utility model;
Fig. 2 is the sectional view of the gear pump of Fig. 1;
Fig. 3 is the decomposition view of the gear pump of Fig. 1;
Fig. 4 is the perspective view being in gear rotor, gear ring rotor and enclosing cover in rigging position in the gear pump of Fig. 1;
Fig. 5 is the schematic diagram of the preferred tooth curve for the gear according to crescent gear pump of the present utility model, gear ring;
The enlarged diagram of the tooth curve of half external tooth A that Fig. 6 is gear marked in Figure 5; And
The enlarged diagram of the tooth curve of half internal tooth B that Fig. 7 is gear ring marked in Figure 5.
Embodiment
Fig. 1-3 shows according to crescent gear pump of the present utility model.The profile of Fig. 1 diagrammatically illustrates the profile of gear pump, and this gear pump can be divided into pump main body 101 and pump head 102 on the whole, and wherein pump main body 101 part comprises each element realizing pump function, and these elements will be discussed in more detail below; Pump head 102 part is used for being connected with outer carrier pipe road, such as, be communicated with urea bucket and spout part respectively in SCR system.
Detailed construction according to crescent gear pump of the present utility model illustrates in figs 2 and 3.Described gear pump comprises motor 11, and its dynamical element as this pump is used for driving the pump that will be described in detail later to realize pump function.For by the transmission of power of motor 11 to pump, preferably adopt magnetic coupling assembly, described magnetic coupling assembly comprises separable two parts, i.e. motor side magnetic coupling 7, and pump end magnetic coupling 5.When motor side magnetic coupling 7 follow motor 11 rotate time, the magnet arranged in motor side magnetic coupling 7 drives the magnet arranged in pump end magnetic coupling 5 by magnetic force, thus make pump end magnetic coupling 5 follow rotation with same rotating speed, and then by the transmission of power of motor to pump.
Pump mainly comprises gear rotor 15 and the gear ring rotor 2 of rear end cover 4, enclosing cover 1, axle 16 and a pair internal messing, and described gear rotor 15 and gear ring rotor 2 are contained between described rear end cover 4 and described enclosing cover 1.Wherein, described rear end cover 4 is arranged roughly coaxially with described pump end magnetic coupling 5, and a part for described pump end magnetic coupling 5 passes the center hole of rear end cover 4 to be connected in the mode of transmitting torque with gear rotor 15.Described enclosing cover 1 is positioned at pump head 102 place, or it forms described pump head 102.Described enclosing cover 1 is provided with pump intake end and pump discharge end.Described enclosing cover 1 is contiguous with described rear end cover 4, and is relative to each other fixed with the form of Fluid Sealing.For realizing described Fluid Sealing, being preferably formed the contact of direct face therebetween, or alternatively, also can the typical seal such as seal ring being set therebetween.Gear rotor 15 has external tooth, and also, it is external gear.When being driven by motor, described gear rotor 15 rotates around first axle.Gear ring rotor 2 has internal tooth, and also, it is ring gear.Form Inside gear drive between gear rotor 15 and gear ring rotor 2, thus when gear rotor 15 rotates, gear ring rotor 2 is rotated around the second axis by driving, wherein, described second axis is different from described first axle, such as, offsets certain radial distance therebetween.Axle 16 is through the center of described gear rotor 15, and two ends are supported by described pump end magnetic coupling 5 and described enclosing cover 1 respectively.Gear rotor 15 is limited around the described first axle rotated by described axle 16, and gear rotor 15 and pump end magnetic coupling 5 all coordinate with axle 16 slidably can rotate around axle 16.Follow gear rotor 15 for preventing axle 16 or pump end magnetic coupling 5 rotates together, described axle 16 is preferably by enclosing cover described in force fit 1.
The material of axle 16 can select any wear-resisting, corrosion resistant metal or alloy material.Preferably, axle 16 is made up of W-Co kind cemented carbide, wherein containing the cobalt of 8% and the Tungsten carbite of 92%.Other material, such as stainless steel, the alloyed steel etc. that is coated with wear-resistant plastic also can use.
For gear rotor 15 and gear ring rotor 2 are contained between described rear end cover 4 and described enclosing cover 1, the utility model is preferably provided with chamber in enclosing cover 1, and described gear ring rotor 2 is accommodated in described chamber in the mode forming Spielpassung between outer peripheral surface and the inner peripheral surface in described chamber.When described gear ring rotor 2 rotates, the inner peripheral surface in described chamber limits its spin axis, is also described second axis.For reducing to rub and ensure Fluid Sealing, the axial clearance between described chamber and described gear rotor 15 and described gear ring rotor 2 is between 10-40 micron.
Preferably, the front end of the part through rear end cover 4 of described pump end magnetic coupling 5 is provided with multiple projection for transmitting torque, described gear rotor 15 is then provided with the groove 18 matched in shape and position with described projection, described projection is contained in described groove in the mode of form fit, thus when motor 11 drives pump end magnetic coupling 5 to rotate, gear rotor 15 is followed pump end magnetic coupling 5 and is rotated together.
Also show motor plug-in unit 9 in Fig. 2-3, it is for applying corresponding control to motor 11.Owing to have employed the magnetic coupling assembly being separable into two parts, therefore can utilize capsul 6 that pump end magnetic coupling 5, enclosing cover 1, rear end cover 4, gear rotor 15, gear ring rotor 2 etc. are packaged into a unit (can be referred to as pumping unit at this), thus motor 11 and pump are reliably isolated, unexpectedly flow to motor place to avoid fluid.In addition, package casing 8 and protecting cover 10 can be adopted and motor 11 and aforesaid pumping unit are carried out overall package, thus obtaining the integrated type pump shown in Fig. 1.Wherein, for ensure magnetic coupling two parts between action radius, in package casing 8, be provided with setting sleeve 12, motor 11 and pumping unit relative to each other to be positioned in the axial direction.In addition, for preventing revealing, seal ring 3 can be set between capsul 6, enclosing cover 1, rear end cover 4 three.
Said structure is the basic structure of crescent gear pump of the present utility model, but, only there is above-mentioned basic structure, be also not enough to meet the requirement carrying out long-time stable reliably quantitative injection in SCR system, particularly for the composite request holding the indexs such as dirty ability, low leakage and serviceability.Because in crescent gear pump, as two wherein the most key parts, rationally whether the tooth-shape structure of gear rotor and gear ring rotor, whether the material selected suitable to the gap between whether appropriate, crown end and between tooth top and tooth root, all has influence on These parameters.
Such as, in document CN 102654125 A, the gap between the tip of inner gear rotor tooth and external gear rotor tooth is between 10 and 30 microns, and such gap easily meets the requirement of low leakage, but friction is simultaneously inevitable comparatively large, hold dirty ability and serviceability is also just difficult to ensure.In addition, gap is less, and also higher for the requirement manufactured, the grade of tolerance often improves one-level, and processing cost or difficulty usually increase exponentially, and the grade of tolerance is higher, and the degree of this increase is more remarkable.Therefore, for the gear-wheel gear-ring of internal messing, the crown splaying between 10 and 30 microns is a no small challenge for manufacture.In addition, the concrete structure of the profile of tooth openly adopted in the document.
Again such as, claim adopted arc toothed contrast cycloid in document CN 203146313 U, asymptotic profile of tooth have that pulsating quantity is little, flow large, advantage such as engagement line length, profile of tooth good airproof performance etc., but do not disclose the specifying information that it is arc toothed, do not provide concrete gap size yet.
For this reason, claimant of the present utility model has carried out further research on the basis of above-mentioned prior art, obtaining the tooth-shape structure of optimization, and by combining with final selected material, reaching the effect taken into account and hold dirty ability, low leakage, serviceability and low cost.Below be described in detail.
About material, in prior art, it is generally acknowledged that different materials preferably selected by gear and gear ring, because this is conducive to lowering friction, for example, see the preferred version in CN 102654125 A.But the material of the utility model gear rotor 15 and gear ring rotor 2 the most at last is all chosen as identical PEEK plastics, wherein containing the carbon fiber of at least 10% and the silicon carbide of at least 5%.Found by contrast, under equal conditions, such combination of materials is better than the combination of PEEK plastics and metal (such as stainless steel) in wear resistance, is also better than the combination of other plastics and metal.
The number of teeth of described gear rotor is 10, and the number of teeth of described gear ring rotor is 11, and their profile of tooth is arranged as follows:
As shown in Figure 6, the tooth curve of the half tooth A of the external tooth of the gear rotor marked in Fig. 5 is expressed as in the rectangular coordinate system taking Gear center as true origin:
Y
1=0.3162x
1 3-1.3895x
1 2+ 0.7771x
1+ 9.5775, wherein x
1scope be from 0mm to 2.53mm;
The profile of tooth of the internal tooth of gear ring rotor is then drawn by the engagement of described gear rotor, and carries out tooth root correction of the flank shape and back chipping.As shown in Figure 7, the tooth curve of the half tooth B of the internal tooth of the gear ring rotor marked in Fig. 5 is expressed as in the rectangular coordinate system taking gear ring center as true origin:
Y
2=-0.2179x
2 3+ 0.8686x
2 2-0.3275x
2+ 8.992, wherein x
2scope be from 0mm to 2.95mm.
By the profilogram of respective half tooth by mirror image with rotate and namely obtain the whole profile of tooth of gear, gear ring.
According to gap after mounting between external tooth and the tip of internal tooth of the gear after above-mentioned cog machining, gear ring between 10-60 micron, preferably between 35-60 micron, the gap between external tooth tooth top and internal tooth tooth root is between 100-150 micron.
For showing the technique effect that the form of gear tooth of the present utility model is brought compared to profile of tooth of the prior art, the gear of each reference examples listed in the gear of the present utility model adopting identical material to produce and table 1 has carried out Experimental Comparison.
Table 1:
For this reason, each gear mesh is arranged in identical pump by this, and carries out uninterrupted pumping test to the same fluid being wherein mixed with dirt at that same temperature.
Result shows, the gear of reference examples 1 is except discharge capacity is less than gear of the present utility model, also causing wearing and tearing comparatively obvious due to (even now make its initial stage sealing better) very close to each other, there is observable leakage in running after 60 hours in it.Meanwhile, the requirement of gear mesh accuracy of manufacturing of the present utility model is lower than reference examples 1, and thus cost is also low than it.
Although the gear discharge capacity of reference examples 2 is greater than gear of the present utility model, because the gap of this gear is comparatively large, just occur leaking at the use initial stage.Meanwhile, profile of tooth of the present utility model is little because of the gap of Gear Root and gear ring tooth top, engages line length, thus than its stable transmission, and simultaneously lower to the requirement of accuracy of manufacturing.
Although the gear discharge capacity of reference examples 3 is greater than gear of the present utility model, the pulsating nature of its flow is comparatively large, and this is obviously disadvantageous factor for the SCR system needing accurate quantification to spray.
The discharge capacity of the gear of reference examples 4 and gear of the present utility model are substantially suitable, but the wearing and tearing of its gear teeth tips are comparatively large, and power character is poor, occur observable leakage in running after 72 hours simultaneously.
And gear of the present utility model does not occur after 240 hours significantly leaking in running yet, transmission is still steady.
As can be seen here, gear pump of the present utility model has the gear of above-mentioned favourable profile of tooth because adopting, compared to the gear of the conventional tooth form of employing prior art, both improve and held dirty ability, again reduce the risk of leakage, also reduce the requirement to gear manufacture precision simultaneously, such that gear pump of the present utility model is durable in use and cost is low.
Be to be understood that, above-mentioned mode of execution is only exemplary, and it is nonrestrictive, when not departing from basic principle of the present utility model, the various obvious or equivalent amendment that those skilled in the art can make for above-mentioned details or replacement, all will be contained in right of the present utility model.
Claims (7)
1. for a crescent gear pump for SCR system, it comprises: motor; Magnetic coupling assembly, comprises motor side magnetic coupling, and pump end magnetic coupling; Rear end cover, itself and described pump end magnetic coupling are arranged roughly coaxially; Enclosing cover, is provided with pump intake end and pump discharge end, described enclosing cover and described rear end cover vicinity; Have the gear rotor of external tooth, it is accommodated between described enclosing cover and described rear end cover, and is rotated around first axle by described motor driving; Have the gear ring rotor of internal tooth, it is accommodated between described enclosing cover and described rear end cover, and realizes internal messing with described gear rotor, and make when described gear rotor rotates, described gear ring rotor rotates around the second axis being different from first axle; And axle, it is through the center of described gear rotor, and two ends are supported by described pump end magnetic coupling and described enclosing cover respectively, thus limits described first axle;
It is characterized in that, the number of teeth of described gear rotor is 10, and the number of teeth of described gear ring rotor is 11; The tooth curve of the half tooth of described gear rotor is expressed as in the rectangular coordinate system taking Gear center as true origin:
y
1＝0.3162x
1 3-1.3895x
1 2+0.7771x
1+9.5775；
The tooth curve of the half tooth of described gear ring rotor is expressed as in the rectangular coordinate system taking gear ring center as true origin:
y
2＝-0.2179x
2 3+0.8686x
2 2-0.3275x
2+8.992，
Wherein x
1scope be from 0mm to 2.53mm, x
2scope be from 0mm to 2.95mm.
2. crescent gear pump according to claim 1, is characterized in that, described gear rotor and described gear ring rotor are made by PEEK plastics.
3. crescent gear pump according to claim 1 and 2, is characterized in that, described axle is made up of W-Co kind cemented carbide.
4. crescent gear pump according to claim 1 and 2, it is characterized in that, chamber is provided with in described enclosing cover, described gear ring rotor to be accommodated in described chamber in the mode of Spielpassung and thus limit described second axis, the axial clearance between described chamber and described gear rotor and described gear ring rotor is between 10-40 micron.
5. crescent gear pump according to claim 1 and 2, is characterized in that, described axle and described enclosing cover interference fit.
6. crescent gear pump according to claim 1 and 2, it is characterized in that, the front end of described pump end magnetic coupling comprises multiple projection for transmitting torque, described gear rotor is provided with the groove of shape with described projection and location matches, and described projection is contained in described groove in the mode of form fit.
7. crescent gear pump according to claim 1 and 2, is characterized in that, the gap between external tooth and the tip of internal tooth is between 35-60 micron, and the gap between external tooth tooth top and internal tooth tooth root is between 100-150 micron.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520252721.1U CN204572444U (en) | 2015-04-22 | 2015-04-22 | For the crescent gear pump of SCR system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520252721.1U CN204572444U (en) | 2015-04-22 | 2015-04-22 | For the crescent gear pump of SCR system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204572444U true CN204572444U (en) | 2015-08-19 |
Family
ID=53865091
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520252721.1U Active CN204572444U (en) | 2015-04-22 | 2015-04-22 | For the crescent gear pump of SCR system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104791244A (en) * | 2015-04-22 | 2015-07-22 | 嘉兴东唐汽车科技有限公司 | Internal gear pump applied to SCR system |
-
2015
- 2015-04-22 CN CN201520252721.1U patent/CN204572444U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104791244A (en) * | 2015-04-22 | 2015-07-22 | 嘉兴东唐汽车科技有限公司 | Internal gear pump applied to SCR system |
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