CN117703748A - Gear pump and gear pump housing - Google Patents
Gear pump and gear pump housing Download PDFInfo
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- CN117703748A CN117703748A CN202410018896.XA CN202410018896A CN117703748A CN 117703748 A CN117703748 A CN 117703748A CN 202410018896 A CN202410018896 A CN 202410018896A CN 117703748 A CN117703748 A CN 117703748A
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- 239000007788 liquid Substances 0.000 claims abstract description 73
- 230000007704 transition Effects 0.000 claims description 7
- 238000000034 method Methods 0.000 abstract description 10
- 230000008569 process Effects 0.000 abstract description 7
- 238000004880 explosion Methods 0.000 abstract description 3
- 230000008859 change Effects 0.000 description 13
- 238000013461 design Methods 0.000 description 11
- 238000010801 machine learning Methods 0.000 description 6
- 238000012549 training Methods 0.000 description 3
- 206010044038 Tooth erosion Diseases 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 230000013011 mating Effects 0.000 description 2
- 208000036595 non-bacterial tooth erosion Diseases 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
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- 238000000926 separation method Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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Abstract
The invention provides a gear pump and a gear pump housing, wherein the inner wall of the gear pump housing is provided with a region matched with a gear, and radial gaps between the region and the corresponding matched gear at least partially tend to be gradually increased along the rotation direction of the gear. In the rotating working process of the gear in the gear pump shell, bubbles can be gradually and slowly released while normal liquid suction is maintained, so that the bubbles can adapt to the pressure of the discharge chamber when entering the discharge chamber of the gear pump, and noise is not generated due to sudden explosion.
Description
Technical Field
The invention relates to the field of pumps, in particular to a gear pump, a gear pump shell and a liquid conveying system.
Background
Gear pumps are rotary pumps that rely on the change and movement of working volume created between a pump cylinder and an intermeshing gear to deliver or pressurize a liquid. The gear pump mainly comprises two gears, a pump body and a front cover and a rear cover to form two closed spaces, a suction chamber is close to one end of the liquid inlet, the suction chamber is connected with upstream equipment through a suction pipe, a discharge chamber is close to one end of the liquid outlet, the discharge chamber is connected with downstream equipment through a discharge pipe, and the suction chamber and the discharge chamber are mutually separated through a meshing line of the gears. When the driving gear and the driven gear rotate continuously and the meshing teeth on one side of the suction chamber are gradually separated, the volume of the suction chamber is increased, the pressure is reduced, liquid in the suction pipe is sucked into the pump, and the sucked liquid is pushed to the discharge chamber by the gears from tooth grooves on one side of the driving wheel and one side of the driven wheel respectively in two paths. After the liquid enters the discharge chamber, the gear pump can continuously suck and discharge the liquid because the gear teeth of the two gears are continuously meshed, so that the liquid is extruded to enter the discharge pipe from the discharge chamber.
However, during operation of the gear pump, noise is often present near the discharge chamber, which can lead to product failure.
Disclosure of Invention
The invention aims to provide a gear pump, a gear pump shell and a liquid conveying system, which are used for solving the problem of noise near a gear pump discharge chamber.
In order to achieve the above purpose, the present invention proposes the following technical scheme:
the gear pump shell is provided with a region matched with a gear on the inner wall, and the radial clearance between the region and the corresponding matched gear is at least partially in a gradually increasing trend along the rotation direction of the gear.
Further, in the rotational direction of the gear, the position of the radial gap on the inner wall includes a first region, a second region and a third region, the first region being located on the liquid inlet end side of the gear pump housing, the third region being located on the liquid outlet end side of the gear pump housing, the second region being located between the first region and the third region; the radial gap is smaller than or equal to the second area in size according to the position on the inner wall, and the second area is smaller than or equal to the third area.
Further, the radial gap in the third region tends to be gradually larger.
Further, the radial gap in the first area is kept within a predetermined gap range, and the predetermined gap range is the maximum gap range allowed by the side of the liquid inlet end for keeping effective liquid suction.
Further, the second region is smoothly transited to both the first region and the third region.
Further, the cross section of the inner wall in the direction passing through the tooth top and parallel to the end face of the gear forms a plurality of contour lines, the contour line corresponding to the first area is a first circular arc line, and the first circular arc line is concentric with the cross section of the gear corresponding to the inner wall.
Further, the contour line corresponding to the third area is a third circular arc line, the third circular arc line and the first circular arc line are in equal diameter, and the circle center of the third circular arc line is eccentrically arranged to one side of the liquid outlet end along the direction perpendicular to the line of the circle center of the section of the gear pair corresponding to the inner wall.
Further, the contour line corresponding to the second area is an arc line, the first arc line is intersected with the third arc line, and the intersected position is in smooth transition through the arc line.
Further, the contour line corresponding to the second area is a straight line, the straight line is parallel to the connecting line of the circle center of the section of the gear pair, and the first circular arc line, the straight line and the third circular arc line are sequentially and tangentially connected.
In a second aspect of the invention there is provided a gear pump comprising a gear pump housing incorporating the first aspect of the application.
The beneficial effects are that:
as can be seen from the above technical solutions, the technical solutions of the present invention provide a gear pump and a gear pump housing, wherein the inner wall of the gear pump housing has a region matching with a gear, and in the rotation direction of the gear, a radial gap between the region and the gear correspondingly matched with the gear is at least partially in a trend of gradually increasing. Through the arrangement of the shell, the gear pump can gradually release pressure slowly on bubbles while keeping normal liquid suction in the working process, so that the bubbles can adapt to the pressure of the discharge chamber when entering the discharge chamber of the gear pump, and the noise is not generated due to sudden explosion.
It should be understood that all combinations of the foregoing concepts, as well as additional concepts described in more detail below, may be considered a part of the inventive subject matter of the present disclosure as long as such concepts are not mutually inconsistent.
The foregoing and other aspects, embodiments, and features of the present teachings will be more fully understood from the following description, taken together with the accompanying drawings. Other additional aspects of the invention, such as features and/or advantages of the exemplary embodiments, will be apparent from the description which follows, or may be learned by practice of the embodiments according to the teachings of the invention.
Drawings
The drawings are not intended to be drawn to scale. In the drawings, each identical or nearly identical component that is illustrated in various figures may be represented by a like numeral. For purposes of clarity, not every component may be labeled in every drawing. Embodiments of various aspects of the invention will now be described, by way of example, with reference to the accompanying drawings, in which:
FIG. 1 is a cross-sectional view of the interior of a gear pump according to the prior art of the present invention;
fig. 2 is a cross-sectional view of the interior of a gear pump in an embodiment of the invention.
In the drawings, the meanings of the reference numerals are as follows:
a suction chamber 1, a discharge chamber 2, a first region 3, a second region 4, and a third region 5.
Detailed Description
For a better understanding of the technical content of the present invention, specific examples are set forth below, along with the accompanying drawings.
Aspects of the invention are described in this disclosure with reference to the drawings, in which are shown a number of illustrative embodiments. The embodiments of the present disclosure are not necessarily intended to include all aspects of the invention. It should be understood that the various concepts and embodiments described above, as well as those described in more detail below, may be implemented in any of a number of ways, as the disclosed concepts and embodiments are not limited to any implementation. Additionally, some aspects of the disclosure may be used alone or in any suitable combination with other aspects of the disclosure.
The gear pump sucks liquid from the liquid inlet end to the suction chamber 1 and discharges the liquid from the discharge chamber 2 at the liquid outlet end by generating negative pressure through the gear engagement and separation process. After entering the inside of the gear pump housing, the liquid is clamped between teeth due to the rotation of the gears, and is transferred to the liquid outlet side along with the movement of the gears. The liquid is at the liquid inlet end, and the suction chamber 1 at the liquid inlet end side has a larger space, so that the pressure of the liquid is smaller. After the liquid is driven to completely enter the teeth from the suction chamber 1 by the rotation of the gears, the pressure of the liquid in the teeth area is larger than that in the liquid inlet end side because the space formed by the teeth and the gear pump shell is smaller. And as the gear continues to rotate, the liquid is moved to the discharge chamber 2 side of the liquid outlet end, and the liquid pressure becomes smaller due to the larger space on the liquid outlet end side. Since bubbles are often entrained in the liquid, the pressure change process of the bubbles is consistent with the above change process of the liquid.
In combination with the above-described pressure change process and the position where the sound appears, the applicant found that the movement of the air bubbles from the nip between the teeth to the liquid outlet end was due to noise generated by the collapse of the air bubbles. The reason for the rupture of the air bubble is that the pressure in the space is suddenly reduced to cause the pressure inside the air bubble to be larger than the external pressure so as to expand, and the expansion speed is too high to cause the oil film wrapped outside the air bubble to be continuously maintained so as to rupture, thereby generating the explosion sound. Therefore, the invention adjusts the pressure change of the two areas through the following embodiments, so that the pressure change is smooth rather than suddenly reduced, the expansion speed and the amplitude of the bubbles are controllable, and the tension of an oil film outside the bubbles can support the switching process of the areas without breaking, thereby reducing noise.
As shown in fig. 2, in order to alleviate the abrupt pressure change in the two areas, the embodiment of the present application adjusts the shape of the gear pump housing so that the area on the inner wall of the gear pump housing, which is matched with the gear, has a tendency to be at least partially increased in radial clearance between the area and the corresponding gear along the rotation direction of the gear.
Through the adjustment, the design that the equidistant gap is kept between the gear pump shell and the large diameter of the gear in the prior art is changed, the space formed between the gear pump shell and the gear is gradually increased through the gradually increased gap, and the pressure difference between the bubbles in the process of switching between two different areas can be alleviated, so that the bubbles can not expand and crack to generate noise and tooth erosion due to sudden pressure reduction when entering the liquid outlet end side.
In certain preferred embodiments, the mating range between each gear and the inner wall of the gear pump housing is about 1/2 of the circumference of the gear wheel diameter in the direction of rotation of the gears. The 1/2 circumference is roughly divided into 3 parts according to the rotation direction of the gear, namely the position of the radial gap corresponding to each part on the inner wall is divided into a first area 3, a second area 4 and a third area 5, wherein the first area 3 is positioned on the liquid inlet end side of the gear pump shell, the third area 5 is positioned on the liquid outlet end side of the gear pump shell, and the second area 4 is positioned between the first area 3 and the third area 5. The radial gap is smaller than or equal to the second area 4 in the first area 3 and smaller than or equal to the third area 5 in the second area 4 according to the position on the inner wall.
In some preferred embodiments, the first region 3 is approximately the circumferential region corresponding to the major diameter of the first 1/6 gear which is just started to be matched with the gear pump shell at the liquid inlet end side. The second area 4 is approximately equal to the circumferential area corresponding to the major diameter of the gear from the front 1/6 to the front 1/3 of the gear matched with the gear pump shell. The third zone 5 is approximately the circumferential zone corresponding to the major diameter of the gear from the first 1/3 to 1/2 of the gear which is engaged with the gear pump housing. In these embodiments, if the pressure difference between the tooth space and the outlet end is small, and only a small stroke is required to meet the requirement for a gentle transition of pressure, it is preferred that the radial clearance in the first zone 3 is equal to the radial clearance in the second zone 4, and that the radial clearance in the second zone 4 is smaller than the radial clearance in the third zone 5. If the pressure difference between the tooth space and the discharge end is large and a long stroke is required for a gentle transition, it is preferred that the radial clearance in the first zone 3 is smaller than the radial clearance in the second zone 4, which radial clearance in the second zone 4 is smaller than the radial clearance in the third zone 5.
In some embodiments, the radial clearance in each of the regions described above may be maintained within a respective set range of deviations. I.e. the radial clearance in each region remains substantially unchanged, but the radial clearances in different regions are set differently.
In other embodiments, the radial clearance in each region may also be varied, where the radial clearance in a region is progressively greater with the direction of rotation of the gear. The above trend is consistent with the change rule of the overall radial gap, and in order to be able to smoothly transition with the pressure of the liquid outlet end, it is preferable that at least the radial gap in the third region 5 is in a trend of gradually increasing with the rotation direction of the gear, and the radial gaps in the second region 4 and the first region 3 are maintained in a set deviation range or are the same as the radial gap in the third region 5, that is, in a trend of gradually increasing with the rotation direction of the gear.
In the above embodiment, whether the radial gap of each region changes or not in the respective region, the junction of the regions should be smoothly transited, that is, the second region 4 and the first region 3 and the third region 5 are smoothly transited, so that the engagement between the regions is smooth, that is, the spatial change and the pressure change are relatively smooth.
In other embodiments, the division of the first area 3, the second area 4 and the third area 5 is not limited to the substantially equidistant manner in the above embodiments, and the size of the areas may be adjusted according to processing convenience, as long as the basic principle that the pressure transition is smooth and the pressure difference between the third area and the liquid outlet end does not cause the expansion and rupture of the bubbles can be satisfied.
As shown in fig. 2, in order to more intuitively describe the clearance between each region and the gear, the cross section of the inner wall passing through the tooth top and being parallel to the end face of the gear forms a plurality of contour lines.
In this embodiment, the contour line corresponding to the first area 3 is a first arc line, and the first arc line is concentric with the section of the gear corresponding to the inner wall, taking the gear pump housing above as shown in fig. 2 as an example, the boring cutter is located at the center O of the upper part in fig. 2 to form a first arc on the right side, and the first arc is about 1/4 of the arcs. The diameter of the first circular arc is R, a gap formed between the first circular arc and the outer diameter of the gear positioned at the circle center O is kept within a preset gap range, and the preset gap range is the maximum gap range allowed by the side of the liquid inlet end for keeping effective liquid suction.
In the above embodiment, the center O is used as a starting point, the boring tool is shifted to the left in the figure by X distance as a new center to form a third circular arc on the left as a contour line corresponding to the third region 5, and the third circular arc is also about 1/4 circular arcs with radius R, i.e. the diameter of the third circular arc is equal to the same diameter as the first circular arc, and the size of the third circular arc is equal to the same diameter as the first circular arc. In order to make the intersection point smoothly transition, in some preferred embodiments, the intersection point is adjusted to form a second arc with an arc smoothly transiting both left and right arcs, and the area corresponding to the second arc thus formed is taken as the second area 4.
In other embodiments, a tangent line is formed along the vertex of the upper edges of the two circular arcs in fig. 2, the tangent plane is actually adjusted to be a plane at the corresponding position of the gear pump shell, and the section shown in the figure shows that the tangent line is sequentially and tangentially connected with the first circular arc line and the third circular arc line, and the area corresponding to the thus formed straight line is taken as the second area 4.
And the gap formed between the third circular arc and the large diameter of the gear arranged at the circle center O is the smallest at the initial position of the third circular arc in the rotation direction of the gear, and smoothly transits with the gap formed between the first circular arc and the gear, and along with the rotation of the gear, the gap between the third circular arc and the gear bracket gradually becomes larger until the position where the third circular arc ends, and the gap reaches X.
In some specific embodiments, the value range of X may be adaptively adjusted according to the size of the gear pump, where X is smaller for a gear pump with smaller volume and X is larger for a gear pump with larger volume. In addition, the size of the X needs to be adaptively adjusted according to the size of the pressure difference, and when the pressure difference is large, the X is correspondingly large, and when the pressure difference is small, the X is correspondingly small. For the existing gear pump, the X is selected to be 0.1-3 mm.
In some embodiments, the air bubbles may also be crushed by entering the teeth from the side of the liquid inlet end due to excessive pressure or excessive pressure increase between the teeth, thereby generating noise and tooth erosion, so that in these embodiments, the radial clearance between the region and the corresponding mating gear wheel in the rotation direction of the gear wheel, at least in part, is in a gradually decreasing trend in the first region. If the pressure between teeth increases faster and exceeds the upper limit of bubble bearing under the condition of clearance fit of gears and gear pumps in the prior art, the area range corresponding to the corresponding trend of gradually decreasing is larger, and the method is not limited to the first area. If the pressure between the teeth increases slowly in the case of clearance fit between the gears and the gear pump in the prior art, but also exceeds the upper limit of the bubble bearing pressure, the corresponding area range of the tendency of the assembly to become smaller can be suitably reduced relative to the case where the pressure increases rapidly.
In some embodiments, the bubbles may collapse due to excessive pressure and sudden pressure increase in the gear pump, and may collapse due to too little pressure or sudden pressure decrease, which may cause noise and cavitation, although the reasons for the collapse may vary. Therefore, the gear pump needs to have moderate pressure and maintain a gentle pressure difference between the gear pump and the liquid inlet end and the liquid outlet end so as to ensure that bubbles are not broken. Therefore, the embodiment of the invention also provides a design method of the gear pump, which comprises the following steps:
step S102, acquiring oil images in front of a historical liquid inlet end and oil images behind a historical liquid outlet end, and corresponding inner wall design parameters of a historical gear pump; the design parameters of the inner wall of the gear pump comprise gaps of a plurality of points between a profile line formed by a section which is matched with the gear head of the gear and is parallel to the direction of the end face of the gear and the large diameter of the gear; the inner wall design parameters of the historical gear pump comprise a plurality of types which are at least partially gradually enlarged and/or at least partially gradually reduced according to the rotation direction of the gear;
step S103, forming a one-to-one corresponding training data set by using the oil liquid image in front of the historical liquid inlet end, the oil liquid image in back of the historical liquid outlet end and the inner wall design parameters of the corresponding historical gear pump, and training a machine learning model by taking the oil liquid image in front of the historical liquid inlet end, the oil liquid image in back of the historical liquid outlet end as input and the inner wall design parameters of the corresponding historical gear pump as output until the machine learning model converges;
step S104, obtaining a current liquid inlet end front oil image, copying a current liquid inlet end front oil image copy to serve as a current liquid outlet end rear oil image, and inputting the current liquid inlet end front oil image and the current liquid outlet end rear oil image into the trained machine learning model to obtain corresponding inner wall design parameters of a current gear pump;
and step 105, obtaining corresponding gaps at a plurality of corresponding points by using the obtained design parameters of the inner wall of the current gear pump, and sequentially connecting the gaps of the points in series by using a smooth curve to form a cross-sectional shape in a direction parallel to the end face of the gear and passing through the tooth top of the gear matched with the gear pump.
The gear pump housing obtained by the gear pump design method described above can ensure proper pressure to ensure that the bubbles do not collapse. The relation between the parameters of different gear pump shells and the front and rear oil liquid states is obtained through a machine learning mode, particularly, images between the gap change and the front and rear oil liquid which are shown in the above embodiments are added as training parameters, so that a machine learning model can master rules, finally, the input front and rear consistent oil liquid images, namely, the bubbles in the representing oil liquid, are kept consistent, and the design parameters of the gear pump are obtained through the machine learning model.
The above embodiments have small overall change range and convenient processing and forming, and the formed gear pump shell and the gear have gradually enlarged gaps in the rotation direction, so that the pressure change of bubbles in the liquid is gentle, and noise and cavitation are avoided.
While the invention has been described with reference to preferred embodiments, it is not intended to be limiting. Those skilled in the art will appreciate that various modifications and adaptations can be made without departing from the spirit and scope of the present invention. Accordingly, the scope of the invention is defined by the appended claims.
Claims (10)
1. The gear pump shell is characterized in that the inner wall of the gear pump shell is provided with a region matched with a gear, and the radial clearance between the region and the corresponding matched gear at least partially tends to be gradually larger along the rotation direction of the gear.
2. The gear pump housing of claim 1, wherein: the radial gap comprises a first area, a second area and a third area on the inner wall along the rotation direction of the gear, wherein the first area is positioned on the liquid inlet end side of the gear pump shell, the third area is positioned on the liquid outlet end side of the gear shell, and the second area is positioned between the first area and the third area; the radial gap is smaller than or equal to the second area in size according to the position on the inner wall, and the second area is smaller than or equal to the third area.
3. The gear pump housing of claim 2, wherein: the radial clearance in the third region tends to become gradually larger.
4. A gear pump housing according to claim 3, wherein: the radial clearance in the first area is kept in a preset clearance range, and the preset clearance range is the maximum clearance range allowed by the side of the liquid inlet end for keeping effective liquid suction.
5. A gear pump housing according to claim 3, wherein: the second region is smoothly transited to both the first region and the third region.
6. The gear pump housing of any one of claims 3 to 5, wherein: the inner wall forms a plurality of contour lines in the cross section passing through the tooth top and being parallel to the direction of the end face of the gear, the contour line corresponding to the first area is a first circular arc line, and the first circular arc line is concentric with the cross section of the gear corresponding to the inner wall.
7. The gear pump housing of claim 6, wherein: the contour line corresponding to the third area is a third circular arc line, the third circular arc line and the first circular arc line are in equal diameter, and the circle center of the third circular arc line is eccentrically arranged to one side of the liquid outlet end along the direction perpendicular to the line of the circle center of the section of the gear pair corresponding to the inner wall.
8. The gear pump housing of claim 7, wherein: the contour line corresponding to the second area is an arc line, the first arc line is intersected with the third arc line, and the intersected position is in smooth transition through the arc line.
9. The gear pump housing of claim 7, wherein: the contour line corresponding to the second area is a straight line, the straight line is parallel to the connecting line of the circle center of the cross section of the gear pair, and the first circular arc line, the straight line and the third circular arc line are sequentially connected in a tangent mode.
10. Gear pump, characterized in that it comprises a gear pump housing according to any of claims 1-9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410018896.XA CN117703748A (en) | 2024-01-05 | 2024-01-05 | Gear pump and gear pump housing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410018896.XA CN117703748A (en) | 2024-01-05 | 2024-01-05 | Gear pump and gear pump housing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN117703748A true CN117703748A (en) | 2024-03-15 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202410018896.XA Pending CN117703748A (en) | 2024-01-05 | 2024-01-05 | Gear pump and gear pump housing |
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| Country | Link |
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| CN (1) | CN117703748A (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101517235A (en) * | 2006-09-28 | 2009-08-26 | 罗伯特·博世有限公司 | Gear pump with reduced pressure impulses on the conveyor side |
| CN113323868A (en) * | 2021-05-14 | 2021-08-31 | 上海吉尔帕普泵业有限公司 | Liquid conveying system and lubricating oil conveying system for gear box of wind driven generator |
-
2024
- 2024-01-05 CN CN202410018896.XA patent/CN117703748A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101517235A (en) * | 2006-09-28 | 2009-08-26 | 罗伯特·博世有限公司 | Gear pump with reduced pressure impulses on the conveyor side |
| CN113323868A (en) * | 2021-05-14 | 2021-08-31 | 上海吉尔帕普泵业有限公司 | Liquid conveying system and lubricating oil conveying system for gear box of wind driven generator |
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