CN205155526U - Engine lubrication system and crescent gear pump thereof - Google Patents
Engine lubrication system and crescent gear pump thereof Download PDFInfo
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- CN205155526U CN205155526U CN201520971547.6U CN201520971547U CN205155526U CN 205155526 U CN205155526 U CN 205155526U CN 201520971547 U CN201520971547 U CN 201520971547U CN 205155526 U CN205155526 U CN 205155526U
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Abstract
The utility model discloses an engine lubrication system and crescent gear pump thereof, crescent gear pump include the pump body, the pump body is equipped with oil absorption chamber, oil extraction chamber, and is located the oil absorption chamber with transition region between the oil extraction chamber, just, install inner rotor, the external rotor of mutually supporting in the pump body, when inner rotor, external rotor rotation, with transition region's lateral wall edge separates gradually, form switch on corresponding seal the oildom territory with the compensating groove in oil extraction chamber, the lateral wall edge has the slope, forms domaticly. Having domaticly with inside and outside rotor complex lateral wall edge in this scheme, then along with the rotation of inside and outside rotor, during with the separation of lateral wall edge, comparing in sharp -pointed lateral wall edge, the area of compensating groove changes and to be mild process in this scheme to the problem of oil pump impact, vibration and noise has been improved to a certain extent.
Description
Technical field
The utility model relates to field of engine lubrication technology, particularly a kind of engine lubrication system and crescent gear pump thereof.
Background technique
Oil pump is the vitals in engine lubrication system, and its effect is after machine oil is brought up to certain pressure, is sent on the moving surface of each part of motor forcibly, to realize lubrication effect.
The kind of oil pump mainly contains gear pump, rotor pump, vane pump etc.
Please refer to the structural representation that Fig. 1-3, Fig. 1 is a kind of crescent gear pump pump housing; Fig. 2 is structural representation when being provided with inner and outer Rotator in Fig. 1 middle pump body, and wherein dotted portion illustrates oil sucting cavity and the oil-discharging cavity of the pump housing; Fig. 3 is the schematic perspective view of Fig. 2.
The pump housing 11 of crescent gear pump is provided with oil-discharging cavity 11B and oil sucting cavity 11A, there is the transition region 11C of entity between oil-discharging cavity 11B and oil sucting cavity 11A.Internal rotor 12, external rotor 13 are rotated in a clockwise direction, as shown in Figure 2, from oil sucting cavity 11A position, the closed area volume formed between internal rotor 12, external rotor 13 increases gradually along with rotating, form negative pressure, fluid is sucked from crescent gear pump oil sucting cavity 11A; When this oil sealing area rotation is to transition region 11C between oil sucting cavity 11A and oil-discharging cavity 11B, closed area volume will reach maximum, then when being rotated further, the volume of closed area starts to reduce, the fluid being stored in this closed area is compressed, produces required pressure oil, and export.
The side that transition region 11C shown in Fig. 1 corresponds to oil-discharging cavity 11B window has protruding 111, when internal rotor 12, external rotor 13 are rotated further the volume compressing closed area, internal rotor 12, external rotor 13 are separated gradually by with the sidewall edge of projection 111, form compensating groove 1a, thus conducting closed area and oil-discharging cavity 11B, then the pressure oil compressing generation can export from oil-discharging cavity 11B.
But, when internal rotor 12, external rotor 13 are separated with the sidewall edge of the pump housing 11 projection 111, there will be the phenomenon that the pressure surge of fluid is larger, and produce larger shock and vibration and noise, affect the life-span of crescent gear pump.
Model utility content
In view of this, the utility model is intended to propose a kind of crescent gear pump, to reduce oil pump shock and vibration and noise as far as possible.
For achieving the above object, the technical solution of the utility model is achieved in that
The utility model provides a kind of crescent gear pump, comprise the pump housing, the described pump housing is provided with oil sucting cavity, oil-discharging cavity, and the transition region between described oil sucting cavity and described oil-discharging cavity, and, the internal rotor, the external rotor that cooperatively interact are installed in the described pump housing, when described internal rotor, external rotor rotate, be separated gradually with the sidewall edge of described transition region, form the compensating groove of oil sealing region corresponding to conducting and described oil-discharging cavity, described sidewall edge has the gradient, is formed domatic.
Further, described sidewall edge is provided with rounded corners, and described rounded corners is formed described domatic.
Further,
The position that described oil sealing region and described oil sucting cavity have just disconnected is defined as cut-off point;
The position of described sidewall edge is specially: when described internal rotor and described external rotor turn to described cut-off point or still have predetermined angle apart from described cut-off point, and described internal rotor and described external rotor have just been separated with described domatic extreme higher position and have formed described compensating groove.
Further,
Described domatic mild degree is specially:
Described drainage area variance ratio and described rate of volumetric change match, to make described fluid through the flow velocity smooth change of described compensating groove.
Relative to prior art, crescent gear pump described in the utility model has following advantage:
The sidewall edge coordinated with inner and outer Rotator in this programme has domatic, then along with the rotation of inner and outer Rotator, when being separated with sidewall edge, compared to sharp-pointed sidewall edge, in this programme, the area change of compensating groove in mild, uniform process, thus will improve the problem of oil pump shock and vibration and noise to a certain extent.
The utility model also provides a kind of engine lubrication system, and comprise motor and provide the oil pump of lubricant oil for described motor, described oil pump is the crescent gear pump described in above-mentioned any one.
Because above-mentioned crescent gear pump has above-mentioned technique effect, this engine lubrication system also has identical technique effect.
Accompanying drawing explanation
The accompanying drawing forming a part of the present utility model is used to provide further understanding of the present utility model, and schematic description and description of the present utility model, for explaining the utility model, is not formed improper restriction of the present utility model.In the accompanying drawings:
Fig. 1 is a kind of structural representation of the crescent gear pump pump housing;
Fig. 2 is structural representation when being provided with inner and outer Rotator in Fig. 1 middle pump body;
Fig. 3 is the schematic perspective view of Fig. 2;
Fig. 4 provides by the utility model the structural representation of a kind of specific embodiment of the crescent gear pump pump housing;
Fig. 5 is structural representation when being provided with inner and outer Rotator in Fig. 4 middle pump body;
Fig. 6 is the schematic perspective view of Fig. 5;
Fig. 7 is principle schematic when compensating groove is opened in the present embodiment;
Fig. 8 is principle schematic when compensating groove is opened in background technique;
Fig. 9 is the compensating groove area of crescent gear pump in crescent gear pump and Fig. 2 in Fig. 5, rotor angle, oil sealing volume change comparison diagram.
Description of reference numerals:
In Fig. 1-3:
11 pump housings, 11A oil sucting cavity, 11B oil-discharging cavity, 11C transition region, 111 protruding, 1a compensating grooves
12 internal rotors, 13 external rotors;
In Fig. 4-9:
21 pump housings, 21A oil sucting cavity, 21B oil-discharging cavity, 21C transition region, 211 sidewall edge, 211a rounded corners, 2a compensating groove;
22 internal rotors, 23 external rotors;
Embodiment
It should be noted that, when not conflicting, the embodiment in the utility model and the feature in embodiment can combine mutually.Below with reference to the accompanying drawings and describe the utility model in detail in conjunction with the embodiments.
To please refer to Fig. 4-6, Fig. 4 provides by the utility model the structural representation of a kind of specific embodiment of the crescent gear pump pump housing; Fig. 5 is structural representation when being provided with inner and outer Rotator in Fig. 4 middle pump body, and wherein dotted portion illustrates oil sucting cavity and the oil-discharging cavity of the pump housing; Fig. 6 is the schematic perspective view of Fig. 5.
This crescent gear pump, comprise the pump housing 21, and to be located in the pump housing 21 and the internal rotor 22 cooperatively interacted, external rotor 23, the part that internal rotor 22 periphery is given prominence to can contact all the time with external rotor 23 inner circumferential in rotation process, outer peripheral portion then between internal rotor 22 adjacent protrusions, with the inner peripheral portion of corresponding external rotor 23, and the pump housing 21, pump cover (not shown) can form corresponding closed area, each closed area increases gradually along with volume with oil suction, volume compression boosting the action of oil extraction in rotation process.The description that specific works process can refer to background technique is understood, and the working principle of crescent gear pump is ripe prior art, no longer describes in detail herein.
The present embodiment has made architecture advances to the edge of transition region 21C sidewall in the pump housing 21.As shown in Figure 4, in rotational direction oil sucting cavity 21A has transition region 21C between oil-discharging cavity 21B, and transition region 21C, towards the sidewall edge 211 of oil-discharging cavity 21B window, has carried out rounded corners 211a process.Similar with background technique, transition region 21C is also provided with projection in this position, correspondingly, and the edge that sidewall edge 211 is also namely protruding.So, this sidewall edge 211 is towards the surface of internal rotor 22, external rotor 23, and with the distance of two rotor surfaces, along with the rotation of two rotors, will increase gradually lentamente, namely this distance is presented as compensating groove 2a.
Can reference drawing to understand 7,8, Fig. 7 be principle schematic when compensating groove 2a opens in the present embodiment; Fig. 8 is principle schematic when compensating groove 1a opens in background technique.This two figure is only in compensating groove opening procedure, and the rough schematic that compensating groove gradually changes, is not limited in any way practical structures.
As shown in Figure 7, when internal rotor 22, external rotor 23 rotate, be separated with the sidewall edge 211 of the pump housing 21 transition region 21C gradually, then form the compensating groove 2a of oil sealing region corresponding to conducting and oil-discharging cavity 21B.After sidewall edge 211 is as above arranged, the process that compensating groove 2a area increases will be slowly cumulative process, as can be seen from Figure 7, due to the existence of rounded corners 211a, compensating groove 2a sector velocity is slowed down by the angle of rounded corners 211a, being increased to S2 ' from S2 is process very slowly, not only compensating groove 2a area increases slowly, and, the trend of whole drain path also in flaring, therefore fluid in oil sealing region is at the beginning of discharge, it is process very slowly.
And background technique scheme, the area change of its compensating groove 1a can be understood with reference to figure 8, and the area of compensating groove 1a directly depends on that rotor leaves the distance at protruding 111 edges, and aperture change is quickly.Comparison chart 7,8, clearly can find out, in the present embodiment, machine oil rotor pump can reduce the pressure surge of fluid, reduces shock and vibration and noise.Find one of too fast reason for producing shock and vibration and noise of oil pump compensating groove 1a aperture change in background technique just after deliberation, therefore the present embodiment has carried out design modifying to the change of compensating groove 2a aperture, thus improve the noise problem of oil pump, and extend the working life of oil pump.
In above-described embodiment, in sidewall edge 211, place arranges rounded corners 211a, and to make internal rotor 22, external rotor 23 is when being separated with it, and the area of compensating groove 2a can be cumulative lentamente.As long as be appreciated that sidewall edge does not take sharp-pointed setting, to present certain gradient, then along with the rotation of internal rotor 22, external rotor 23, the area change of compensating groove 2a can be made to be mild process.Therefore, sidewall edge 211 is not limited to arrange rounded corners 211a, also can be straight inclined-plane, or non-circular curved surface, certainly, rounded corners 211a is easy to realize from technique, and rounded corners 211a itself is more round and smooth, the mild property that compensating groove 2a opens can be ensured further.
Further, can the position configuration at oppose side wall edge 211 do further to optimize.
Please refer to Fig. 9, Fig. 9 is the compensating groove area of crescent gear pump in crescent gear pump and Fig. 2 in Fig. 5, rotor angle, oil sealing volume change comparison diagram.
In figure, when angle is 0, represent that oil sealing region turns to and oil sucting cavity 21A, 11A not conducting just.
Oil-discharging cavity 11B shape in the crescent gear pump pump housing 11 in background technique designs according to molded lines of rotor, please refer to Fig. 2, and sidewall locations corresponding to sidewall edge in towards the outstanding projection 111 of sense of rotation, and extends longer length.Understand incorporated by reference to Fig. 9 again, based on existing design, oil sealing region just and oil sucting cavity 11A not conducting time, with oil-discharging cavity 11B also not conducting, and after rotor also needs to be rotated further several angle a, just can depart from the sidewall edge of protruding 111 and form compensating groove 1a, prove through test, this angle a is at about 6 degree, and compensating groove 1a area also can be uprushed, as shown in Figure 8.
In background technique, oil sealing region and oil sucting cavity 11A, oil-discharging cavity 11B all not conducting time, be commonly called as pocketed oil region.When being in pocketed oil region, the volume in pocketed oil region reduces gradually along with the rotation of rotor, if now pocketed oil region can not in time and oil-discharging cavity 11B link up, pressure can continue to raise, and produces impact the pump housing 11; Once link up with oil-discharging cavity 11B, but the change of compensating groove 1a opening is very fast again, then cause shock and vibration and noise larger.
For this programme, the position that oil sealing region and oil sucting cavity 21A have just disconnected can be defined as cut-off point, position when namely angle is 0 in Fig. 9 is off a little.Now, the position of the sidewall edge 211 of transition region 21C is correspondingly specially:
When internal rotor 22 and external rotor 23 turn to cut-off point or still have predetermined angle apart from cut-off point, internal rotor 22 and external rotor 23 have just been separated with described domatic extreme higher position and have formed described compensating groove 2a.
Namely closed area just disconnects with oil sucting cavity 21A, or by when disconnecting with oil sucting cavity 21A, namely compensating groove 2a is opened.Comparison diagram 1 and Fig. 4 can find out, the projecting degree of the projection of the transition region 21C in this programme relatively reduces, and the size namely extended along sense of rotation reduces.
Visible, this programme shortens the time that pocketed oil region exists, and in fact, is almost pocketed oil is shortened to zero zone time, when still having predetermined angle namely to open apart from cut-off point, even can eliminate entrap phenomenon.Certainly, predetermined angle (being determined by the setting position of sidewall edge 211) herein can according to actual detection experiment or simulation analysis setting, ensure to be about to just open compensating groove 2a when disconnecting with oil sucting cavity 21A, avoid opening compensating groove 2a conducting oil sucting cavity 21A and oil-discharging cavity 21B too early and affecting volumetric efficiency, when such as turning over predetermined angle and arrive cut-off point, compensating groove area 2a can reach 0.5mm
2left and right, certainly this numerical value also can do suitable adjustment according to the oil pump of different model, those skilled in the art all can obtain according to existing simulation softward, therefore the present embodiment does not do concrete restriction to the actual size position of predetermined angle and side edge.That is, when being about to disconnect with oil sucting cavity 21A, just can open the compensating groove 2a of a very small size, in order to avoid Oil shocking, volumetric efficiency can be affected hardly again.
Visible, according to the position of above-mentioned restriction sidewall edge 211, the fluid of closed area can be avoided to raise again draining suddenly with forming pocketed oil region and pressure durations, but stably boost, enable oil pump gently draining by above-mentioned chamfering or other domatic designs again, reduce shock and vibration and noise.As shown in Figure 9, the scheme of the present embodiment, drainage area, from the break up location moment, continues gently to increase drainage area, and the scheme of background technique is then continue in pocketed oil region a period of time and then uprush.
In above-described embodiment, further optimal design can be made to domatic mild degree.The change (corresponding to angle change) of domatic mild degree and slope (corresponding to angle) and slope.Specifically domatic mild degree can be specially:
Drainage area variance ratio and rate of volumetric change match, to make fluid through the flow velocity smooth change of compensating groove.
As shown in Figure 7, drainage area area change is originally relevant with the angle of rounded corners 211a, simultaneously, the volume in oil sealing region is also carrying out compression reduction, and part fluid will be discharged, according to simulation analysis from compensating groove 2a, the rate of volumetric change in the variance ratio of drainage area and oil sealing region can be made to match, to ensure that flow velocity can smooth change, and be unlikely to occur uprushing phenomenon, thus reduce vibration and noise further.In fact, for existing internal rotor 22, external rotor 23, rate of volumetric change is known parameter, on this basis, the different designs that simulation chamfering is spent gently, corresponding change in flow curve can be obtained, until when change in flow curve meets smooth variation requirement, corresponding chamfering is spent gently and can be met design requirement.Domatic mild degree needed for those skilled in the art all can obtain based on this principle, therefore the concrete data of mild degree are not restricted herein.
Except above-mentioned crescent gear pump, the utility model also provides a kind of engine lubrication system, comprise motor and provide the oil pump of lubricant oil for described motor, described oil pump is the crescent gear pump described in above-mentioned any embodiment, because above-mentioned crescent gear pump has above-mentioned technique effect, this engine lubrication system also has identical technique effect.
These are only preferred embodiment of the present utility model, not in order to limit the utility model, all within spirit of the present utility model and principle, any amendment done, equivalent replacement, improvement etc., all should be included within protection domain of the present utility model.
Claims (5)
1. a crescent gear pump, comprise the pump housing (21), the described pump housing (21) is provided with oil sucting cavity (21A), oil-discharging cavity (21B), and the transition region (21C) be positioned between described oil sucting cavity (21A) and described oil-discharging cavity (21B), and, the internal rotor (22) cooperatively interacted is installed in the described pump housing (21), external rotor (23), described internal rotor (22), when external rotor (23) rotates, be separated gradually with the sidewall edge (211) of described transition region (21C), form the compensating groove (2a) of oil sealing region corresponding to conducting and described oil-discharging cavity (21B), it is characterized in that, described sidewall edge (211) has the gradient, formed domatic.
2. crescent gear pump as claimed in claim 1, it is characterized in that, described sidewall edge (211) is provided with rounded corners (211a), and described rounded corners (211a) is formed described domatic.
3. crescent gear pump as claimed in claim 1, is characterized in that,
The position that described oil sealing region and described oil sucting cavity (21A) have just disconnected is defined as cut-off point;
The position of described sidewall edge (211) is specially: when described internal rotor (22) and described external rotor (23) turn to described cut-off point or still have predetermined angle apart from described cut-off point, and described internal rotor (22) and described external rotor (23) have just been separated with described domatic extreme higher position and have formed described compensating groove (2a).
4. the crescent gear pump as described in any one of claim 1-3, is characterized in that,
Described domatic mild degree is specially:
Described drainage area variance ratio and described rate of volumetric change match, to make described fluid through the flow velocity smooth change of described compensating groove (2a).
5. an engine lubrication system, comprise motor and provide the oil pump of lubricant oil for described motor, it is characterized in that, described oil pump is the crescent gear pump described in any one of claim 1-4.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520971547.6U CN205155526U (en) | 2015-11-30 | 2015-11-30 | Engine lubrication system and crescent gear pump thereof |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520971547.6U CN205155526U (en) | 2015-11-30 | 2015-11-30 | Engine lubrication system and crescent gear pump thereof |
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| CN205155526U true CN205155526U (en) | 2016-04-13 |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107355664A (en) * | 2017-07-24 | 2017-11-17 | 中国第汽车股份有限公司 | A kind of rotor-type oil pump that can reduce charge oil pressure fluctuation intensity and flow noise |
| CN108061234A (en) * | 2018-01-12 | 2018-05-22 | 中国航发哈尔滨东安发动机有限公司 | A kind of oil pump interstage casings molded line structure |
| CN109000139A (en) * | 2018-08-06 | 2018-12-14 | 奇瑞汽车股份有限公司 | Rotor engine oil pump |
| CN111425391A (en) * | 2020-05-08 | 2020-07-17 | 潍柴动力股份有限公司 | Rotor pump |
-
2015
- 2015-11-30 CN CN201520971547.6U patent/CN205155526U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107355664A (en) * | 2017-07-24 | 2017-11-17 | 中国第汽车股份有限公司 | A kind of rotor-type oil pump that can reduce charge oil pressure fluctuation intensity and flow noise |
| CN108061234A (en) * | 2018-01-12 | 2018-05-22 | 中国航发哈尔滨东安发动机有限公司 | A kind of oil pump interstage casings molded line structure |
| CN109000139A (en) * | 2018-08-06 | 2018-12-14 | 奇瑞汽车股份有限公司 | Rotor engine oil pump |
| CN111425391A (en) * | 2020-05-08 | 2020-07-17 | 潍柴动力股份有限公司 | Rotor pump |
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