CN210623178U - Fuel pump - Google Patents
Fuel pump Download PDFInfo
- Publication number
- CN210623178U CN210623178U CN201921151735.9U CN201921151735U CN210623178U CN 210623178 U CN210623178 U CN 210623178U CN 201921151735 U CN201921151735 U CN 201921151735U CN 210623178 U CN210623178 U CN 210623178U
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- China
- Prior art keywords
- disc spring
- bearing
- fuel pump
- deformation
- shaft receiving
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- 239000000446 fuel Substances 0.000 title claims abstract description 54
- 230000036316 preload Effects 0.000 claims description 15
- 125000006850 spacer group Chemical group 0.000 claims 2
- 238000005096 rolling process Methods 0.000 description 10
- 238000005299 abrasion Methods 0.000 description 5
- 238000007792 addition Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 239000000126 substance Substances 0.000 description 2
- 230000006735 deficit Effects 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
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Abstract
The utility model relates to a fuel pump, it includes: a pump body having a shaft receiving cavity therein and a shaft receiving opening formed in a side wall thereof; a drive shaft rotatably received at least partially in the shaft receiving cavity and supported at one end thereof at the shaft receiving opening by a bearing adapted to receive axial thrust; a side cover covering the shaft receiving opening; a disc spring compressed between an inner end surface of the side cover and an outer end surface of the bearing, wherein a ratio of a height of the disc spring to a thickness thereof is set such that a pre-tightening force provided by the disc spring does not significantly vary with deformation, at least within a certain deformation range.
Description
Technical Field
The present invention relates to a fuel pump, and particularly, to a fuel pump which can be smoothly operated and has a long life.
Background
Fuel pumps are a common component of mechanical power systems that draw oil from a fuel tank and discharge the oil to an actuator. Typically, the fuel pump is driven by a drive shaft, and in particular, rotation of the drive shaft about its axis drives the fuel pump to draw and discharge oil. The drive shaft is often fixed in the fuel pump by means of bearings, for example conical bearings. However, when the conical bearing is installed, a clearance often exists, so that the number of rolling bodies effectively carried by the bearing is reduced, and the stress of the inner ring, the rolling bodies and the outer ring of the bearing is increased, so that the fuel pump cannot run smoothly, and the service life of the conical bearing and even the service life of the whole fuel pump is shortened. Therefore, an elastic member is generally provided in the fuel pump to apply a preload to the conical bearing, thereby eliminating a play thereof. However, the elastic component wears with the operation of the fuel pump, and when the wear develops to a certain extent, the elastic component will have difficulty in applying a sufficient preload to the conical bearing again, which leads to the occurrence of play again and thus to an impairment of the operation and service life of the fuel pump.
Therefore, there is a need for a fuel pump whose play in the conical bearing can be constantly eliminated and thus can be operated smoothly and has a long life.
SUMMERY OF THE UTILITY MODEL
In order to solve at least one of the problems in the prior art, the utility model provides a fuel pump, it includes:
a pump body having a shaft receiving cavity therein and a shaft receiving opening formed in a side wall thereof;
a drive shaft rotatably received at least partially in the shaft receiving cavity and supported at one end thereof at the shaft receiving opening by a bearing adapted to receive axial thrust;
a side cover covering the shaft receiving opening;
a disc spring compressed between an inner end surface of the side cover and an outer end surface of the bearing,
wherein the height of the disc spring is 1.2-1.6 times of the thickness of the disc spring.
According to an alternative embodiment of the invention, the height of the disc spring is equal to 1.4 times its thickness.
According to an alternative embodiment of the invention, wherein the ratio of the height of the disc spring to its thickness is set such that a horizontal section is present in the pretension-deformation curve of the disc spring.
According to an optional embodiment of the present invention, wherein a plurality of grooves are provided in the disc spring.
According to an optional embodiment of the present invention, wherein the number and size of the plurality of grooves are set such that, when the deformation of the disc spring is in a deformation range corresponding to a small slope section in a pretightening force-deformation curve thereof, the bearing is applied with its desired pretightening force.
According to an optional embodiment of the present invention, wherein the plurality of grooves are evenly distributed around the axis of the disc spring and extend along a generatrix of the surface of the disc spring.
According to the utility model discloses an optional embodiment, wherein, when the fuel pump assembly was accomplished, the deformation of dish spring was greater than the deformation that the left end of the little slope section in its pretightning force-deformation curve corresponds.
According to an optional embodiment of the invention, wherein the bearing is arranged with its outer ring big end face outwards and its inner ring big end face abutting against the outer shoulder of the drive shaft, wherein the small end of the disc spring abuts against the inner end face of the side cover and its big end abuts against the outer ring big end face of the bearing.
According to the utility model discloses an optional embodiment, wherein, the fuel pump still includes the adjusting washer, the adjusting washer is by the centre gripping the big terminal surface of inner circle of bearing with between the outer shoulder of drive shaft.
According to an optional embodiment of the present invention, wherein the bearing is a tapered roller bearing.
According to the present invention, play in a bearing in a fuel pump can be constantly eliminated and thus can be smoothly operated and have a long life.
The invention may be embodied in the exemplary embodiments shown in the drawings. It is to be noted, however, that the drawings are designed solely for purposes of illustration and that any changes which come within the teachings of the invention are intended to be embraced therein and are limited only by the scope of the invention as defined in the appended claims.
Drawings
The accompanying drawings illustrate exemplary embodiments of the invention. These drawings should not be construed as necessarily limiting the scope of the invention, wherein:
FIG. 1 is a schematic view of a fuel pump according to an alternative embodiment of the present invention, wherein the vertical height of the fuel pump is omitted from the drawing for clarity and brevity;
FIG. 2 is a schematic view with parts broken away along the axial direction XX';
FIG. 3 is a pre-tightening force-deformation curve of a conventional disc spring;
fig. 4 is a pre-load force-deflection curve for a disc spring of a fuel pump according to an alternative embodiment of the present invention;
fig. 5 is a perspective view of a disc spring of a fuel pump according to an alternative embodiment of the present invention;
FIG. 6 is a top view of a disc spring of a fuel pump according to an alternative embodiment of the present invention;
fig. 7 is a sectional view of the disc spring taken along line CC in fig. 6.
Detailed Description
Alternative embodiments of the present invention will now be described with reference to the accompanying drawings, in which exemplary embodiments of the invention are shown, and which are not necessarily drawn to scale. This invention may, however, be embodied in many different forms and should not be construed as necessarily limited to the exemplary embodiments set forth herein. Rather, these exemplary embodiments are provided only to illustrate the present invention and to convey the spirit and substance of the invention to those skilled in the art.
As used herein, the directional terms "inner …", "inner …" refer to a direction toward the inside of the fuel pump, i.e., in the axial direction XX 'directed from the shaft receiving opening 111 to the shaft receiving cavity 110, while "outer …", "outer …" refer to a direction toward the outside of the fuel pump, i.e., in the axial direction XX' directed from the shaft receiving cavity 110 to the shaft receiving opening 111, wherein the axial direction refers to the direction along which the axis of the drive shaft extends.
As shown in fig. 1 and 2, a fuel pump according to an alternative embodiment of the present invention includes: a pump body 100, the pump body 100 having a shaft receiving cavity 110 therein; a driving shaft 300, the driving shaft 300 being rotatably received at least partially in the shaft receiving cavity 110, and one end thereof being supported on the side cover 200 through a bearing 500 (e.g., a tapered roller bearing) adapted to receive an axial thrust. The side cover 200 is bolted to the pump body 100, and the other end is supported on the pump body 100 by another bearing 700 (e.g., a tapered roller bearing) adapted to receive axial thrust, and rotation of the drive shaft 300 about its axis drives the fuel pump to draw and discharge oil.
When a roller bearing is used to assemble a drive shaft in a fuel pump, if a play exists in the bearing, that is, a gap exists between an inner ring, a rolling body and an outer ring of the bearing, when the drive shaft rotates, the number of the rolling bodies effectively carried by the bearing is reduced, so that the stress on the inner ring, the rolling body and the outer ring of the bearing is increased, and the service life of the bearing and the service life of the whole fuel pump are greatly reduced.
According to the utility model discloses an above-mentioned embodiment's fuel pump still includes: the disc spring 400 compressed between the inner end surface 210 of the side cover 200 and the outer end surface of the bearing 500.
According to the above scheme, because the disc spring 400 is in a compressed state, the disc spring 400 applies a pretightening force to the bearing to press the inner ring, the rolling body and the outer ring of the bearing towards each other, so that a gap among the inner ring, the rolling body and the outer ring of the bearing is eliminated, namely, a play of the bearing is eliminated, the stress state of the roller bearing is improved, and the service lives of the bearing and the whole fuel pump are prolonged.
However, the deformation of the disc spring is reduced along with the increase of the abrasion loss, so that the pretightening force provided by the disc spring is reduced along with the increase of the abrasion loss, and when the pretightening force is not enough to counteract the axial force derived from the stress of the tapered roller bearing, the bearing play is generated, and the service life of the bearing is reduced again. To describe this more clearly, reference is made to the curve of pre-tension F-deformation X of the conventional disc spring in FIG. 3, for example, when the assembly is completed, the disc spring in the compressed state has a deformation XAAnd generates a preload force FA(ii) a After experiencing abrasion Delta X, the deformation of the disc spring is changed from XADown to XBResulting in a pretension force FADown to FB。
In order to solve the problemThe inventor finds that when the height of the disc spring is 1.2-1.6 times of the thickness of the disc spring, a small slope section with a obviously smaller slope exists in a curve of the pretightening force F-deformation X, and in the small slope section, the pretightening force F can not be obviously changed along with the change of the deformation X. To more clearly describe this principle, referring to the pre-tightening force F-deformation X-curve of the disc spring of the fuel pump according to an alternative embodiment of the present invention shown in fig. 4, in the case where the height h of the disc spring is set to be between 1.2-1.6 times its thickness t, there is a small slope section in the pre-tightening force F-deformation X-curve. In particular, when the height h of the disc spring is equal to 1.4 times its thickness t, the slope of the small slope section is close to zero, and the small slope section appears as an approximately horizontal section AB in fig. 4, and in the approximately horizontal section AB, the pretightening force F hardly changes with the change of the deformation X. For example, in the case where the height h of the disc spring is equal to 1.4 times its thickness t, the disc spring in the compressed state has a deformation X at the completion of assemblyAAnd generates a preload force FA(ii) a After experiencing Δ X wear, the disc spring deforms by XADown to XBBut the pretension remains almost constant. On the basis of the above teaching, it is expected to be advantageous when the ratio of the height h of the disc spring to its thickness t is set such that a horizontal segment with a slope of zero is present in the curve of its pretension force F-deflection X.
Thus, the height h of the disc spring 400 is optionally between 1.2 and 1.6 times its thickness t, in particular equal to 1.4 times its thickness t. It should be noted that the height h of the disc spring 400 refers to the distance between the small end 410 and the large end 420 thereof as measured along the axis thereof, and the thickness t of the disc spring 400 refers to the thickness of the disc spring body 430 as measured along the normal of the surface thereof.
According to the technical scheme, when the deformation of the disc spring 400 is in the deformation range corresponding to the small slope section in the pretightening force-deformation curve, the disc spring 400 can provide the pretightening force which is not changed or changed obviously along with the abrasion, so that the play of the bearing is eliminated constantly, and the service life of the bearing and the whole fuel pump is prolonged.
However, since such a bearing tends to have its desired preload force, when the desired preload force is applied, the play of the bearing is just eliminated and the inner ring, the rolling elements, and the outer ring are not excessively tightened, so that smooth operation thereof can be ensured. However, the preload corresponding to the small slope segment in the preload-deformation curve of the disc spring 400 is not necessarily equal to the desired preload of the bearing, and is often greater than or even much greater than the desired preload of the bearing. The pretension provided by the disc spring 400 in the small slope section of its pretension-deformation curve may cause the inner ring, the rolling elements and the outer ring of the bearing to be pressed too tightly against each other, which results in a high bearing stress and further influences the service life of the bearing.
To this end, optionally, as shown in fig. 5-7, a plurality of grooves 440 are provided in the disc spring 400. According to this technical solution, the stiffness of the disc spring 400 will decrease due to the existence of the plurality of grooves 440, so that the pre-tightening force corresponding to the small slope section in the pre-tightening force-deformation curve is reduced compared to the case without the grooves, so that the pre-tightening force provided by the disc spring 400 in the small slope section in the pre-tightening force-deformation curve is suitable for eliminating the play of the bearing, but the inner ring, the rolling body, and the outer ring of the bearing are not pressed against each other too tightly. This enables the bearing to run smoothly while the play is eliminated.
Alternatively, the plurality of grooves 400 are arranged in number and size such that the bearing 500 is applied with its desired preload force when the deformation of the disc spring 400 is in a deformation range corresponding to a small slope section in its preload-deformation curve. According to the technical scheme, the pretightening force provided by the disc spring 400 in the small slope section in the pretightening force-deformation curve just eliminates the play of the bearing, and simultaneously can ensure the optimal smooth operation of the bearing.
Optionally, the plurality of grooves 440 are evenly distributed around the axis of the disc spring 400 and extend along a generatrix of the surface of the disc spring 400. According to the technical scheme, the rigidity distribution of the disc spring 400 is more uniform, so that the performance and the service life of the disc spring are improved.
Optionally, the plurality of channels 440 are open at the small end 410 or the large end 420 (not shown). According to this solution, the groove 440 can more effectively reduce the stiffness of the disc spring 400, so that it is adapted to provide the desired preload of the bearing, i.e. to eliminate play of the bearing and to ensure smooth operation of the bearing.
Alternatively, in an embodiment not shown, the plurality of grooves 440 are disposed in the disc spring body 430 of the disc spring 400 connecting the small end 410 to the large end 420, but are not open at the small end 410 or the large end 420. According to this technical solution, since the groove 440 does not interrupt the small end 410 or the large end 420 of the disc spring 400, the disc spring 400 has a strong wear resistance and thus a longer service life.
Optionally, each of the plurality of grooves 440 has rounded edges, such as "U" shaped edges. According to the technical scheme, each of the plurality of grooves 440 has a rounded edge, so that stress concentration at the edge of the groove 440 can be avoided, and the risk of tearing or breaking of the disc spring at the edge of the groove is reduced, thereby further improving the service life of the disc spring 400.
Optionally, when the fuel pump is assembled, the deformation of the disc spring 400 is greater than the deformation corresponding to the left end of the small slope section in the pre-tightening force-deformation curve. According to the technical scheme, when the fuel pump is assembled, the deformation X of the disc spring 400 is larger than the deformation X corresponding to the left end B with the minimum deformation of the small slope section in the pretightening force-deformation curve in the figure 4BThus, the disc spring 400 is able to wear over a range of wear (i.e., X-X) at least to some extent after assembly from the fuel pumpB) The preload force is provided so as not to significantly change with wear to constantly eliminate play of the bearing, thereby improving the service life of the bearing and the fuel pump.
Optionally, when the fuel pump is assembled, the deformation of the disc spring 400 is equal to the deformation corresponding to the right end of the small slope section in the pre-tightening force-deformation curve. According to the technical scheme, the disc spring 400 can provide the pretightening force which is not obviously changed along with abrasion to the maximum extent from the time when the fuel pump is assembled, and the pretightening force is specifically represented as (referring to fig. 4), when the fuel pump is assembled, the deformation of the disc spring 400 is equal to the right end A opposite to the right end A with the maximum deformation of the small slope section in the pretightening force-deformation curveStrain XAThe disc spring 400 can be deformed up to XBThe ground, i.e. the wear up to Δ X, provides a not significantly changing pretension. That is, the disc spring 400 can stably eliminate the play of the bearing with wear to the maximum extent.
Alternatively, the bearing 500 is arranged with its outer ring large end face 511 outward and its inner ring large end face 521 against the outer shoulder 310 of the drive shaft 300, with the small end 410 of the disc spring 400 against the inner end face 210 of the side cover 200 and its large end 420 against the outer ring large end face 511 of the bearing 500. According to this technical solution, since the disc spring 400 abuts against the inner end surface 210 of the side cover 200 and the outer ring large end surface 511 of the bearing 500, the disc spring 400 does not rotate with the rotation of the drive shaft 300, which significantly reduces the wear rate of the disc spring 400, and thus improves the service life of the disc spring 400.
Optionally, the fuel pump further comprises an adjusting washer 600, and the adjusting washer 600 is clamped between the inner ring large end surface 521 of the bearing 500 and the outer shaft shoulder 310 of the driving shaft 300. According to the technical scheme, the deformation of the disc spring and the pretightening force of the disc spring can be adjusted more conveniently and flexibly by setting the thickness of the adjusting washer 600 along the axial direction XX'.
Alternatively, the other end of the drive shaft 300 is rotatably supported in the shaft receiving chamber 110 by another bearing 700 that is operative to generate axial thrust, the other bearing 700 being disposed with its outer race large end face 711 facing inwardly (e.g., against a side wall of the shaft receiving chamber 110) and its inner race large end face 721 facing outwardly (e.g., against the inner shoulder 320 of the drive shaft 300).
Optionally, the number and size of the plurality of grooves 440 are set such that when the deformation of the disc spring 400 is in a deformation range corresponding to a small slope section in its pretension-deformation curve, both the bearing 500 and the further bearing 700 are applied with their desired pretension.
Optionally, the bearing 500 and the further bearing 700 are tapered roller bearings.
An alternative but non-limiting embodiment of a fuel pump according to the invention is described in detail above with the aid of the accompanying drawings. Modifications and additions to the techniques and structures, as well as re-combinations of features in various embodiments, which do not depart from the spirit and substance of the disclosure as defined by the following claims, are deemed to be covered by the present invention. Accordingly, such modifications and additions as can be envisaged within the teachings of the present invention are considered to be part of the present invention. The scope of the invention is defined by the following appended claims, and includes both equivalents as known at the time of filing and equivalents as not yet foreseen.
Claims (10)
1. A fuel pump, comprising:
a pump body (100), the pump body (100) having a shaft receiving cavity (110) provided therein, and a shaft receiving opening (111) formed in a side wall of the pump body (100);
a drive shaft (300), said drive shaft (300) being rotatably received at least partially in a shaft receiving cavity (110) and supported with one end at a shaft receiving opening (111) by a bearing (500) adapted to take up axial thrust;
a side cover (200), the side cover (200) covering a shaft receiving opening (111);
a disc spring (400) compressed between an inner end surface (210) of the side cover (200) and an outer end surface of the bearing (500),
characterized in that the height (h) of the disc spring (400) is between 1.2 and 1.6 times its thickness (t).
2. A fuel pump according to claim 1, characterized in that the height (h) of the disc spring (400) is equal to 1.4 times its thickness (t).
3. The fuel pump as claimed in claim 1, characterized in that the ratio of the height (h) of the disc spring (400) to its thickness (t) is set such that a horizontal section is present in the pretension-deformation curve of the disc spring (400).
4. The fuel pump of claim 1, wherein the disc spring (400) has a plurality of grooves (440) therein.
5. The fuel pump of claim 4, characterized in that the plurality of grooves (440) are sized and numbered such that the bearing (500) is applied with its desired preload when the deformation of the disc spring (400) is in a deformation range corresponding to a small slope segment in its preload-deformation curve.
6. The fuel pump of claim 4 or 5, characterized in that the plurality of grooves (440) are evenly distributed around the axis of the disc spring (400) and extend along a generatrix of the surface of the disc spring (400).
7. The fuel pump according to one of claims 1 to 5, characterized in that, when the fuel pump is assembled, the deformation of the leaf spring (400) is greater than the deformation corresponding to the left end of the small-slope segment in its pre-load force-deformation curve.
8. The fuel pump as claimed in one of claims 1 to 5, characterized in that the bearing (500) is arranged with its outer ring large end face (511) facing outwards and its inner ring large end face (521) abutting against the outer shoulder (310) of the drive shaft (300), wherein the small end (410) of the disc spring (400) abuts against the inner end face (210) of the side cover (200) and its large end (420) abuts against the outer ring large end face (511) of the bearing (500).
9. The fuel pump of claim 8, further comprising a spacer washer (600), the spacer washer (600) being clamped between an inner race large end face (521) of the bearing (500) and an outer shaft shoulder (310) of the drive shaft (300).
10. The fuel pump of one of claims 1 to 5, characterized in that the bearing (500) is a tapered roller bearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921151735.9U CN210623178U (en) | 2019-07-22 | 2019-07-22 | Fuel pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921151735.9U CN210623178U (en) | 2019-07-22 | 2019-07-22 | Fuel pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN210623178U true CN210623178U (en) | 2020-05-26 |
Family
ID=70758586
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201921151735.9U Active CN210623178U (en) | 2019-07-22 | 2019-07-22 | Fuel pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN210623178U (en) |
-
2019
- 2019-07-22 CN CN201921151735.9U patent/CN210623178U/en active Active
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