CN1945013B - Plunger driving structure - Google Patents
Plunger driving structure Download PDFInfo
- Publication number
- CN1945013B CN1945013B CN2006101431838A CN200610143183A CN1945013B CN 1945013 B CN1945013 B CN 1945013B CN 2006101431838 A CN2006101431838 A CN 2006101431838A CN 200610143183 A CN200610143183 A CN 200610143183A CN 1945013 B CN1945013 B CN 1945013B
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- CN
- China
- Prior art keywords
- balace weight
- outer ring
- driving structure
- plunger driving
- roller bearing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
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- Reciprocating Pumps (AREA)
- Rolling Contact Bearings (AREA)
- Fuel-Injection Apparatus (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
An oil pump 11 comprises a rotation shaft 12 having an eccentric part 12a, a needle roller bearing 13 supporting the eccentric part 12a of the rotation shaft 12, a tappet 14 abutting on the outer ring of the needle roller bearing 13 and arranged in a radial manner, a plunger 15 arranged on the tappet 14and reciprocated by the rotation of the rotation shaft 12, and a balancer 16 arranged on both ends of the eccentric part 12a. The balancer 16 has a large diameter part and a small diameter part and when the large diameter part is arranged so as to face the direction opposite to an eccentric direction, the rolling space of a roller 13c can be projected from an axial direction through the balancer 16.
Description
Technical field
The present invention relates to a kind of plunger driving structure that in the petrolift of diesel engine or the oil pump of braking device etc., uses.
Background technique
Japan is real to open and has put down in writing all the time automobile in the flat 5-83372 communique with employed oil pumps such as braking device.As shown in Figure 9, the oil pump 1 of this communique record comprise the eccentric part 2a of running shaft 2 with eccentric part 2a, supporting rotating shaft 2 ball bearing 3, be provided with and reciprocating plunger 5 at the tappet 4 of radial configuration on the ball bearing 3, on tappet 4 by the rotation of running shaft 2.
In addition, as shown in figure 10, ball bearing 3 has inner ring 3a, outer ring 3b, a plurality of ball 3c that are provided with between inner ring 3a and outer ring 3b, retainer 3d, the Sealing 3e that is arranged on the bearing two ends and bearing interior space is sealed that keeps ball 3c.
The oil pump 1 of above-mentioned formation moves up and down plunger 6 by the rotation of running shaft 2, carries out the suction and the extrusion of oil thus.
In addition, point out following problem in this communique: the eccentric part 2a of running shaft 2 produces uneven when drive condition, thereby exists consequent vibration etc. to give the trouble of damage to the output shaft of bearing and motor etc., and the operational noise of drive pump becomes big.
Therefore, in order to address this problem, as shown in figure 11, use balace weight 6 with large-diameter portion 6a and minor diameter part 6b.Specifically, put down in writing following situation: by on the two ends of eccentric part 2a, oppositely disposing large-diameter portion 6a, can utilize the poor of centrifugal force between large-diameter portion 6a and the minor diameter part 6b, the dynamic unbalance when revising running shaft 2 and driving with eccentric direction.
In the plunger driving structure of above-mentioned formation,, produce the trouble of vibration when then driving, so the distance between ball bearing 3 and the balace weight 6 is very little usually, is 0.3mm～0.47mm owing to existence if the interval between eccentric part 2a and the balace weight 6 is big.
Consequently, though it is as ball bearing 3 that grease-enclosed bearing in the bearing interior space that is sealed by Sealing 3e is no problem, but concerning existing balace weight 6 to hinder the trouble of oiling agents from the bearing of the outside supply of lubricant of bearing to the inflow of bearing.
And in recent years, the requirement that is accompanied by the miniaturization of oil pump 1 uprises, and considers to replace ball bearing 3, and uses the little needle roller bearing of radial thickness size etc.This needle roller bearing usually need be from outside supplying lubricating oil, and, because the gap that forms between the track circle is little, so the problem of the oiling agent undersupply that causes because of configuration balace weight 6 is remarkable.
In addition, though the plunger driving structure running shaft 2 of above-mentioned formation, inner ring 3a and the rotation of balace weight 6 one, because outer ring 3b fixes, therefore at the contact segment generation surface friction drag of the end face of the wall of balace weight 6 and outer ring 3b.This surface friction drag might become the reason of extraordinary noise or vibration when oil pump 1 drives.
And, the wall of balace weight 6 does not carry out surface finishing such as abrasive machining, in addition, though the end face of outer ring 3b since become add man-hour reference level therefore in the original adoption abrasive machining, even in follow-up course of working, produce also intactly placement of damage.Consequently, the surface roughness of surface of contact is thick, and this becomes the reason that surface friction drag increases.
Summary of the invention
The object of the present invention is to provide a kind of plunger driving structure, it comprises the balace weight that does not hinder to the shape of the bearing supply of lubricant that supports eccentric part.
Another object of the present invention is to provide a kind of plunger driving structure, it alleviates the rotational resistance of the contact segment of bearing and balace weight, and extraordinary noise or vibration when suppress driving.
Plunger driving structure of the present invention comprises: the running shaft with eccentric part; Comprise the outer ring and along a plurality of rollers of the plane of trajectory orbital of outer ring configuration, and the roller bearing of supporting eccentric part; With the balace weight of the roller bearing adjoining position of running shaft configuration; And contact with the outer ring, and by the rotation of running shaft reciprocating plunger.And have following structure: the scroll space of roller can be from the axially projection by balace weight, and balace weight has through hole at the wall of facing with the scroll space of roller.
As the shape of concrete balace weight, for example, the external diameter profile line of balace weight intersects with the circumcircle of roller.In addition, so-called " circumcircle of roller " refers to the circle that the point that joins with the outer race track face with each roller links in this specification.In addition, so-called " scroll space of roller " refers to the space that clips between inner race track face and the outer race track face.
By above-mentioned structure, be lubricated the supply of oil smoothly, so can obtain the plunger driving structure of greasy property excellence to the roller bearing of supporting eccentric part.
Preferably, roller bearing is the needle roller bearing that comprises as the needle-like roller of roller.Give the plunger driving structure of the needle roller bearing of considerable influence by the present invention being applicable to used to lubricity, can expect higher effect because of the existence of balace weight.
Preferably, balace weight has large-diameter portion and minor diameter part, and the appearance profile line of minor diameter part is positioned at the inboard of the internal diameter of outer ring.As described in above-mentioned formation,, can alleviate the rotational resistance when driving by minor diameter part wall and the discontiguous structure of bearing outer ring that forms balace weight.Consequently, can obtain to have suppressed the plunger driving structure of extraordinary noise or vibration.
Preferably, the end face of the circumferencial direction of large-diameter portion has chamfered section.Because the circumferencial direction end face of large-diameter portion, promptly, produce big rotational resistance when contact with cycle surface with the bight of the end face that joins with minor diameter part of large-diameter portion, therefore, can more effectively suppress extraordinary noise or vibration by to this bight enforcement chamfer machining.
Preferably, the surface roughness of the end face of facing with balace weight of outer ring is Rz≤0.8 μ m, and the surface roughness of the wall of facing with the outer ring of balace weight is Rz≤3.2 μ m.As described in above-mentioned formation, the surface roughness of the end face by the outer ring that will be in contact with one another and the wall of balace weight forms below the specified value, can alleviate the rotational resistance when driving.Consequently, can obtain to have suppressed the plunger driving structure of extraordinary noise or vibration.In addition, so-called " Rz " refers to the surface roughness that obtained by 10 mean roughness in this specification.
Preferably, the end face of facing with balace weight of outer ring grinds.In addition, preferred, the wall of facing with the outer ring of balace weight has carried out barreling.Thus, can make the surface roughness of surface of contact is below the specified value.
In addition, what is called " grinding " refers to by goods being exerted pressure and it being slided on the mill that is covered by the working fluid that has mixed abrasive material in this specification, accurately the processing method of polished surface.In addition, in this specification so-called " barreling " refer to by workpiece is put into cup-like containers with emboliform polishing material, mixture, and the cup-like containers rotation is moved up and down and the polishing method that carries out.
According to the present invention, do not hinder the balace weight of oiling agent by using to the structure of the inflow of the bearing of supporting eccentric part, can obtain the plunger driving structure of lubricity excellence.
In addition, according to the present invention, the end face by making the outer ring that is in contact with one another and the wall of balace weight are level and smooth, can obtain to alleviate the rotational resistance when driving and suppress the plunger driving structure of extraordinary noise or vibration.
Description of drawings
Fig. 1 is the figure of the oil pump of expression one embodiment of the present invention with plunger driving structure;
Fig. 2 is the figure that is illustrated in the needle roller bearing that uses among Fig. 1;
Fig. 3 is the figure that is illustrated in the balace weight that uses among Fig. 1;
Fig. 4 A is the figure of other mode of execution of expression balace weight;
Fig. 4 B is the figure of other mode of execution of expression balace weight;
Fig. 5 is the figure of other mode of execution of expression balace weight;
Fig. 6 is the side view of the balace weight of Fig. 5;
Fig. 7 is the figure of the oil pump of expression other mode of execution of the present invention with plunger driving structure;
Fig. 8 is the figure that is illustrated in the needle roller bearing that uses among Fig. 7;
Fig. 9 is the figure of the existing oil pump of expression with plunger driving structure;
Figure 10 is the figure that is illustrated in the ball bearing that uses among Fig. 9;
Figure 11 is the figure that is illustrated in the balace weight that uses among Fig. 9.
Embodiment
With reference to Fig. 1～Fig. 3, the oil pump plunger driving structure of one embodiment of the present invention is described.
As shown in Figure 1, oil pump 11 comprise the needle roller bearing 13 of the eccentric part 12a of running shaft 12 with eccentric part 12a, supporting rotating shaft 12, contact with the outer ring of needle roller bearing 13 and the tappet 14 of radial configuration, on tappet 14, be provided with and by the rotation of running shaft 12 reciprocating plunger 15, at the balace weight 16 of the two ends of eccentric part 12a configuration.
As shown in Figure 2, needle roller bearing 13 comprises the retainer 13d of inner ring 13a, outer ring 13b, a plurality of needle-like roller 13c that dispose, maintenance needle-like roller 13c between inner ring 13a and outer ring 13b.Perhaps, needle roller bearing 13 also can be not have inner ring 13a, and disposes the type of needle-like roller 13c along the plane of trajectory orbital of outer ring 13b.By using so needle roller bearing 13 conducts to support the bearing of eccentric part 12a, can realize the miniaturization of oil pump 11.
As shown in Figure 3, balace weight 16 has large-diameter portion 16a and minor diameter part 16b, and the shape that to be external diameter profile line 16c intersect with the circumcircle of roller 13c.If this balace weight 16 is configured to large-diameter portion 16a as shown in Figure 1 and eccentric direction is reverse, then the scroll space of roller 13c can be from the axially projection by balace weight 16.
In addition, in the oil pump 11 of above-mentioned formation,, surface roughness is formed Rz≤0.8 by the end face of facing with balace weight 16 of outer ring 13b is implemented to grind.In addition, implement barreling, surface roughness is formed Rz≤3.2 by the wall of facing with outer ring 13b to balace weight 16.At this moment, give special heed to the not defective of residual overshooting shape.
As mentioned above, the end face by making the outer ring 13b that contacts when oil pump 11 drives and the wall of balace weight 36 are level and smooth, can alleviate the rotational resistance when driving.Consequently, can obtain to have suppressed the plunger driving structure of extraordinary noise or vibration.
In addition, also can use balace weight 36 as shown in Figure 5 as the balace weight that uses in the above-mentioned oil pump 11.Rotational resistance when this balace weight 36 can also alleviate oil pump 11 drivings except that above-mentioned effect between outer ring 13b and the balace weight 36.
In addition, in the above-described embodiment,, and cut off the example of intermediate portion of the circular arc of minor diameter part 16b, be not limited thereto, also can through hole be set at the wall of side's side of balace weight though represented to have large-diameter portion 16a and minor diameter part 16b.
For example, the balace weight 46 shown in Fig. 4 A also can be provided with big through hole 46a, and the balace weight 56 shown in Fig. 4 B also can be provided with a plurality of little through hole 56a.Under this situation, can pass through through hole 46a, 56a to the bearing supply of lubricant, and, can on balace weight 46,56, minor diameter part and large-diameter portion be set, and by the size of through hole 46a, 56a or the size of quantity regulating centrifugal force.
Below, with reference to Fig. 5 and Fig. 6, the alternate manner of balace weight is described.In addition, the explanation of the common ground of omission and above-mentioned mode of execution is that the center describes with the difference.
Owing to produce bigger rotational resistance when contacting with cycle surface with bight 36d in the oblique line portion of Fig. 5, therefore cut off the oblique line portion of Fig. 5, across corner 36d implements chamfer machining in addition, can suppress extraordinary noise or vibration effectively thus.
In addition, carry out the chamfer machining of bight 36d by roller process.Roller process refers to that balace weight 36 and iron plate put into rotating drum and be rotated, by friction or impact and make bight 36d have the method for fillet.
If the balace weight of above-mentioned formation 36 is configured to large-diameter portion 16a as shown in Figure 1 and eccentric direction is reverse, then can utilize the poor of centrifugal force between large-diameter portion 16a and the minor diameter part 16b, the dynamic unbalance when revising running shaft 12 and driving.
In addition, this balace weight 36 has large-diameter portion 36a and minor diameter part 36b, thereby and the oblique line among the appearance profile line cut-out figure of minor diameter part 36b part be positioned at the inboard of outer ring 13b.Thus, the rotational resistance in the time of can alleviating oil pump 11 drivings between outer ring 13b and the balace weight 36.
In addition, in the above-described embodiment, shown in Fig. 4 A and Fig. 4 B, also can through hole be set at the wall of balace weight 36.Thus, can be by through hole to the bearing supply of lubricant.In addition, use as the bearing of supporting eccentric part 12a, need under the situation of the needle roller bearing 13 of outside supply of lubricant, especially can expect effect.
Below, with reference to Fig. 7 and Fig. 8, illustrate that this invents the oil pump plunger driving structure of other mode of execution.In addition, the explanation of the common ground of omission and above-mentioned mode of execution is that the center describes with the difference.
As shown in Figure 7, oil pump 21 comprise the needle roller bearing 23 of running shaft 22, supporting rotating shaft 22, contact with the outer ring of needle roller bearing 23 and the tappet 24 of radial configuration, on tappet 24, be provided with and by the rotation of running shaft 22 reciprocating plunger 25, the configuration of the two ends of needle roller bearing 23 as Fig. 3～balace weight 26 shown in Figure 5.
In addition, as shown in Figure 8, needle roller bearing 23 comprises the retainer 23d of eccentric inner ring 23a, the outer ring 23b that along the circumferential direction the radial thickness size is different, a plurality of needle-like roller 23c that dispose, maintenance needle-like roller 23c between eccentric inner ring 23a and outer ring 23b.
Therefore this needle roller bearing 23 need not be provided with eccentric part at running shaft 22 owing to have eccentric inner ring 23a.Consequently, except the effect that in mode of execution, obtains, can reduce the manufacture cost of running shaft 22 as Fig. 1～shown in Figure 6.
Though have retainer 13d, the 23d that keeps needle- like roller 13c, 23c as Fig. 2 and needle roller bearing 13,23 shown in Figure 8, but be not limited thereto, also can be not have retainer 13d, 23d, the needle-like roller 13c of adjacency, total roller bearing that 23c is in contact with one another.Because load capacity is high more more at most for the radical of accommodating of needle- like roller 13c, 23c, therefore needle roller bearing 13,23 can obtain the plunger supporting bearing of anti-loading excellence by forming total roller bearing of having accommodated needle- like roller 13c, 23c to greatest extent.
In addition, in the respective embodiments described above,, be not limited thereto, need can expect identical effect from all rollers bearing of outside supply of lubricant by being applicable to though represented to use the example of needle roller bearing as the bearing of supporting eccentric part.
In addition, in the above-described embodiment, though represented and will be applicable in the example of automobile as Fig. 3～balace weight shown in Figure 5 with the plunger driving structure of the oil pump that uses in the braking device etc., be not limited thereto, the petrolift that can also be applicable to diesel engine is with plunger driving structure etc.
In addition, the present invention can expect the effect that multiplies each other by the characteristic of combination in any the respective embodiments described above.
More than, though with reference to description of drawings embodiments of the present invention, the present invention is not limited to illustrated mode of execution.Can apply various corrections or distortion to illustrated embodiment in the scope identical or in the scope of equal value with the present invention.
The present invention can advantageously be used in the plunger driving structure that oil pump is used.
Claims (8)
1. plunger driving structure, it comprises:
Running shaft with eccentric part;
Comprise the outer ring and along a plurality of rollers of the plane of trajectory orbital of described outer ring configuration, and support the roller bearing of described eccentric part;
With the balace weight of the described roller bearing adjoining position configuration of described running shaft; And
Contact with described outer ring, and by the rotation of described running shaft reciprocating plunger,
The scroll space of described roller can be from the axially projection by described balace weight,
Described balace weight has through hole at the wall of facing with the scroll space of described roller bearing.
2. plunger driving structure as claimed in claim 1, wherein, the external diameter profile line of described balace weight intersects with the circumcircle of described roller.
3. plunger driving structure as claimed in claim 1, wherein, described roller bearing is the needle roller bearing that comprises as the needle-like roller of described roller.
4. plunger driving structure as claimed in claim 1, wherein, described balace weight has large-diameter portion and minor diameter part, and the appearance profile line of described minor diameter part is positioned at the inboard of the internal diameter of described outer ring.
5. plunger driving structure as claimed in claim 4, wherein, the end face of the circumferencial direction of described large-diameter portion has chamfered section.
6. plunger driving structure as claimed in claim 1, wherein, the surface roughness of the end face of facing with described balace weight of described outer ring is Rz≤0.8 μ m, the surface roughness of the wall of facing with described outer ring of described balace weight is Rz≤3.2 μ m.
7. plunger driving structure as claimed in claim 6, wherein, the end face of facing with described balace weight of described outer ring grinds.
8. plunger driving structure as claimed in claim 6, wherein, the wall of facing with described outer ring of described balace weight has carried out barreling.
Applications Claiming Priority (9)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005277563A JP2007085289A (en) | 2005-09-26 | 2005-09-26 | Plunger driving structure |
| JP2005-277564 | 2005-09-26 | ||
| JP2005277562A JP4841212B2 (en) | 2005-09-26 | 2005-09-26 | Plunger drive structure |
| JP2005277564A JP2007085290A (en) | 2005-09-26 | 2005-09-26 | Plunger driving structure |
| JP2005-277563 | 2005-09-26 | ||
| JP2005277564 | 2005-09-26 | ||
| JP2005277562 | 2005-09-26 | ||
| JP2005-277562 | 2005-09-26 | ||
| JP2005277563 | 2005-09-26 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1945013A CN1945013A (en) | 2007-04-11 |
| CN1945013B true CN1945013B (en) | 2011-06-08 |
Family
ID=37972508
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2006101431838A Expired - Fee Related CN1945013B (en) | 2005-09-26 | 2006-09-25 | Plunger driving structure |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4841212B2 (en) |
| CN (1) | CN1945013B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TWI371617B (en) | 2008-08-15 | 2012-09-01 | Au Optronics Corp | Display device |
| DE102010028584A1 (en) * | 2010-05-05 | 2011-11-10 | Robert Bosch Gmbh | eccentric |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2030921U (en) * | 1988-03-18 | 1989-01-18 | 浙江大学 | High-damping spindle unit |
| US5362158A (en) * | 1992-04-13 | 1994-11-08 | Ntn Corporation | Bearing unit and electric pump using the same |
| US6202538B1 (en) * | 1998-08-29 | 2001-03-20 | Ina Walzlaber Schaeffler Ohg | Radial piston pump |
| US6240826B1 (en) * | 1998-11-05 | 2001-06-05 | Ina Walzlager Schaffler Ohg | Radial piston pump |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06185454A (en) * | 1992-07-07 | 1994-07-05 | Sumitomo Electric Ind Ltd | Plunger pump |
| JPH10288146A (en) * | 1997-04-11 | 1998-10-27 | Gijutsu Kaihatsu Sogo Kenkyusho:Kk | Radial plunger pump |
| JP4357988B2 (en) * | 2004-02-26 | 2009-11-04 | トヨタ自動車株式会社 | Plunger pump |
-
2005
- 2005-09-26 JP JP2005277562A patent/JP4841212B2/en not_active Expired - Fee Related
-
2006
- 2006-09-25 CN CN2006101431838A patent/CN1945013B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2030921U (en) * | 1988-03-18 | 1989-01-18 | 浙江大学 | High-damping spindle unit |
| US5362158A (en) * | 1992-04-13 | 1994-11-08 | Ntn Corporation | Bearing unit and electric pump using the same |
| US6202538B1 (en) * | 1998-08-29 | 2001-03-20 | Ina Walzlaber Schaeffler Ohg | Radial piston pump |
| US6240826B1 (en) * | 1998-11-05 | 2001-06-05 | Ina Walzlager Schaffler Ohg | Radial piston pump |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1945013A (en) | 2007-04-11 |
| JP2007085288A (en) | 2007-04-05 |
| JP4841212B2 (en) | 2011-12-21 |
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| C14 | Grant of patent or utility model | ||
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Granted publication date: 20110608 |
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