CN201086705Y - Master pump structure - Google Patents
Master pump structure Download PDFInfo
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- CN201086705Y CN201086705Y CNU2007201723249U CN200720172324U CN201086705Y CN 201086705 Y CN201086705 Y CN 201086705Y CN U2007201723249 U CNU2007201723249 U CN U2007201723249U CN 200720172324 U CN200720172324 U CN 200720172324U CN 201086705 Y CN201086705 Y CN 201086705Y
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- 239000012530 fluid Substances 0.000 claims description 24
- 239000010985 leather Substances 0.000 claims description 15
- 239000000446 fuel Substances 0.000 claims description 9
- 241000269799 Perca fluviatilis Species 0.000 claims description 5
- 238000007789 sealing Methods 0.000 abstract description 23
- 238000005516 engineering process Methods 0.000 abstract description 5
- 238000000034 method Methods 0.000 abstract description 4
- 230000005540 biological transmission Effects 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 17
- 230000002950 deficient Effects 0.000 description 6
- 238000012545 processing Methods 0.000 description 6
- 239000010720 hydraulic oil Substances 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 239000003344 environmental pollutant Substances 0.000 description 3
- 230000033001 locomotion Effects 0.000 description 3
- 231100000719 pollutant Toxicity 0.000 description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 2
- 239000004411 aluminium Substances 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000001802 infusion Methods 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 238000012795 verification Methods 0.000 description 2
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 229910001018 Cast iron Inorganic materials 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000003749 cleanliness Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 210000001699 lower leg Anatomy 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
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- Details Of Reciprocating Pumps (AREA)
Abstract
The utility model relates to a clutch hydraulic operating device for walking apparatus and a master cylinder structure in hydraulic type brake transmission devices. The master cylinder structure includes a pump body; a cylinder drum in the pump body is composed of a piston that can slide longitudinally and a piston return spring; one rubber cup is arranged at the front and rear section of the piston respectively; a front rubber cup on the piston divides the cylinder drum into a front chamber and a rear chamber; the rear chamber in the cylinder drum communicates with a reservoir through an inlet hole; a compensation valve communicated with the front and rear chamber channels in the cylinder drum and sealing the channels is arranged on the front end of the piston; a longitudinal slot with the length larger than that of the piston stroke is arranged between the front and rear rubber cups on the piston; the rear end of the compensation valve rod goes through the piston before reaching the longitudinal slot; the pump body is provided with a shift lever; the shift lever is inserted in the longitudinal slot on the piston; when the piston returns to the limit position, the compensation valve rod leans against the shift lever, so as to push the compensation valve open. Compared with traditional structure of master cylinders, the utility model has the advantages of simple process technology, low product cost, reliable operation and long service life. Compared with master cylinder in the compensation hole structure, the utility model can be improved by more than 100 percent.
Description
Technical field
The utility model relates to the clutch hydraulic pressure operating control and the fluid pressure type brake transsmission device of walking arrangement, relates in particular to the master cylinder in clutch hydraulic pressure operating control and the fluid pressure type brake transsmission device.
Background technology
Walking arrangements such as automobile, trac., construction machinery and equipment and agricultural vehicle have much adopted clutch hydraulic pressure operating control and fluid pressure type brake transsmission device.The fluid pressure type steering unit of power-transfer clutch one surpasses by pedal of clutch, push rod, master cylinder (master cylinder), clutch release slave cylinder and pipeline system etc. and forms.Fluid pressure type brake transsmission device and clutch hydraulic pressure operating control are roughly the same.It is to utilize special fluid as the power transmission medium, reaches drg after chaufeur the power on the pedal of imposing on is amplified, and produces brake action, mainly is made up of brake pedal, push rod, master brake cylinder (master cylinder), brake wheel cylinder and pipeline system etc.Master brake cylinder and clutch master cylinder are plunger pumps, the former has single-piston, floating-caliper brake structure and series connection dual-piston structure, the latter is the single-piston, floating-caliper brake structure, its function is power and the displacement that brake pedal or pedal of clutch Motion Transmission are come, by the motion of piston, the volume that converts hydraulic oil to is discharged and is set up certain hydraulic pressure by the compression of hydraulic oil and export.Hydraulic oil discharge and pressure foundation after, being as the criterion is equipped with next actuation cycles, must replenish hydraulic oil in piston the place ahead when piston retreats, and when piston is in the rearmost position equilibrium of pressure.Thereby, need the balanced compensated mechanism of hydraulic oil and pressure in master brake cylinder and the clutch master cylinder.Traditional master brake cylinder and clutch master cylinder generally have two kinds, the fluid infusion structure of compensator jet or the fluid infusion mechanism of central valve formula.
Figure 1 shows that the master cylinder of compensation orifice structure, the pump housing 1 mostly is cast iron or aluminum alloy is made.The running surface precision of pump housing cylinder barrel is high and bright and clean, and fuel feed hole 4 and compensation orifice 5 are arranged on the cylinder barrel, in the tube aluminium piston 3 is housed. Rubber cup 2 and 6 before and after being equipped with on the aluminium piston 3.The reservoir compartment communicates with the back cavity B of cylinder barrel by the bigger fuel feed hole 4 of diameter.The outer round surface of preceding rubber cup 6 is shaped on a circular groove more, and has some axial grooves to communicate with it.So that when work, can make the unidirectional compensation of fluid.Pull back spring 10 has certain predetermincd tension, and piston 3 is pushed against on the back shield, begins to compress the braking liquid of cylinder barrel ante-chamber A piston 3 is crossed compensation orifice 5 when moving ahead in the cylinder barrel at the pump housing under the effect of push rod 7 after, discharged liquid or build pressure.When piston 3 retreats, unidirectional oil sealing repairing that can be by leather cup 6, the anterior lip of leather cup 6 fall back on abdicate compensation orifice after, can also pass through compensation orifice 5 further repairings, make the equilibrium of pressure of oil sealing 6 front and back.The push rod that usable length is adjustable is gone into piston back side recess 7 second month in a season, and keeps certain clearance.
The master brake cylinder and the hydraulic clutch master cylinder of tradition compensator jet structure, because compensation orifice 5 is apertures that diameter has only the 0.6-0.8 millimeter, and compensation orifice is positioned at the above degree of depth of cylinder barrel 30mm, perpendicular to cylinder barrel, the processing small holes difficulty is big, the sharp edge of aperture and cylinder barrel intersection, burr must adopt special process means to remove, and work efficiency is low, the cost height.Even adopt special process to remove burr and sharp edge, during the piston front-rear reciprocation movement, compensation orifice and cylinder barrel junction are cut the lip limit of rubber cup repeatedly, make that the life-span of master brake cylinder and clutch master cylinder is lower, are no more than general service life 400,000 times.Simultaneously, because the compensation orifice diameter is less, be easy to be stopped up by the pollutants in the hydraulic tubing and master cylinder was lost efficacy, the poor reliability of total pump work.
Fig. 2 is the master cylinder of traditional central valve structure, when piston 2 moves ahead, central valve packing seal 8 is under the effect of retracing spring, move ahead and the contact seal of pump housing bottom surface, braking liquid is to clutch release slave cylinder or wheel cylinder discharge or build pressure by compression, and when piston retreated, check valve driven by piston and pump housing bottom surface breaks away from, produce the gap, realize repairing and equilibrium of pressure.
Tradition central valve formula hydraulic braking master cylinder and clutch master cylinder, because the center of employing check valve-type structure, the sealing surface of central valve is a side seal in pump housing cylinder barrel bottom surface, pollutants easily fills up in the sealing surface place in the hydraulic tubing, and master cylinder was lost efficacy.Simultaneously, because unidirectional valve rod 9 is elongated, it is poor to lead, easy unstability, the master cylinder of this structure often exists to build presses insecure defective, as clutch master cylinder, it is not thorough that autoist finds that sometimes first pin steps down disengaging of clutch, steps on the pin power-transfer clutch phenomenon of combination again again.In addition, because sealing surface is in the bottom of cylinder barrel deep hole, cylinder barrel bottom surface and cylinder barrel squareness are had relatively high expectations, and surface quality is also higher, must be the concentric circles texture, and roughness of surface is less than Ra1.6, and this has all increased difficulty to processing.
Summary of the invention
It is comparatively simple that the technical problems to be solved in the utility model provides a kind of processing technology, and cost of product is lower, reliable operation, long service life and total pump configuration.
In order to solve the problems of the technologies described above, the technical solution adopted in the utility model is, a kind of total pump configuration, comprise the pump housing, the piston that slides before and after in the cylinder barrel of the pump housing, piston return spring, the front and rear of piston respectively is equipped with 1 leather cup, the preceding leather cup of piston is separated into ante-chamber and back cavity with cylinder barrel, the cylinder barrel back cavity communicates with fluid reservoir by fuel feed hole, piston nose has passage that is communicated with chamber, cylinder barrel front and back and the throttle compensating valve that seals this passage, between the leather cup pod of length greater than piston stroke is arranged before and after the piston, and the rear end of described throttle compensating valve valve rod is passed piston and stretched into described pod; Be fixed with 1 lever on the pump housing, lever inserts the pod on the piston; The valve rod of throttle compensating valve withstands on the fixing lever when piston retreats into end position, and throttle compensating valve is backed down.
The above total pump configuration, described pod is preferably open-minded along piston radial, and described lever passes the pod of opening along piston radial.
Above-described total pump configuration, the passage in chamber can be a spline-like hole or equilateral polygon hole before and after the described connection cylinder barrel, the valve rod of described throttle compensating valve circle passes the endoporus in spline-like hole or equilateral polygon hole and its and makes free-running fit, and the keyway in described spline-like hole or equilateral polygon hole sharp corner are with the chamber, front and back of the channel connection cylinder barrel that forms between valve rod.The passage in chamber also can be a cylindrical hole before and after the described connection cylinder barrel, the valve rod of described throttle compensating valve is spline-like axle or equilateral polygon axle, spline-like axle or equilateral polygon axle pass cylindrical hole, its external diameter is made free-running fit with cylindrical hole, and the keyway of described spline-like axle or equilateral polygon axle are communicated with the chamber, front and back of cylinder barrel with the gap between the cylindrical hole.
Above-described total pump configuration, described lever preferably inserts from the oil input channel of the pump housing, is fixed on the pump housing wall of oil input channel bottom.
Above-described total pump configuration, the axis of described valve rod preferably overlaps with the axis of piston.
Above-described total pump configuration, the spring perch of described pull back spring preferably are enclosed within outside the throttle compensating valve, and an end of the spring of throttle compensating valve withstands on the throttle compensating valve spool, and the other end withstands on the inner end surface of pull back spring spring perch.
Above-described total pump configuration, the driving surface of the valve seat of described throttle compensating valve can be inner conical surfaces, and this moment, the driving surface of spool can be a sphere; The driving surface of the valve seat of described throttle compensating valve also can be an end face, and this moment, the driving surface of spool can be an anchor ring.
The utility model redeeming be the through hole of piston nose and the throttle compensating valve that seals this through hole, sealing surface technical requirements with respect to the master cylinder cylinder barrel deep hole bottom of the compensation aperture of the master cylinder of compensation orifice structure and central valve structure is lower, processing technology is much simple, and cost of product is relatively low; The through hole of the utility model piston nose is more much bigger than the compensation aperture of the master cylinder of compensation orifice structure, be difficult for during work stopping up, the throttle compensating valve valve rod is wanted much shorter than the length of the unidirectional valve rod of master cylinder of central valve structure, so the utility model reliable operation is difficult for breaking down; Only in smooth cylinder barrel, slide when leather cup of the present utility model front and back are reciprocating, avoided compensation orifice and cylinder barrel junction in the prior art to cut the defective on rubber cup lip limit repeatedly, leather cup is not fragile, and the utility model is than being enhanced about more than once the service life of the master cylinder of compensation orifice structure.
Description of drawings
Below in conjunction with the drawings and specific embodiments the utility model is described in further detail.
Fig. 1 is the structural representation of the master cylinder of prior art compensator jet structure.
Fig. 2 is the structural representation of the master cylinder of prior art central valve structure.
Fig. 3 is the structural representation of total pump configuration embodiment 1 piston of the utility model throttle compensating valve open mode when the end position of back.
Fig. 4 is the partial enlarged drawing at the I position among Fig. 3.
Fig. 5 is the structural representation of total pump configuration embodiment 1 piston of the utility model throttle compensating valve closed condition when moving ahead.
Fig. 6 is the structural representation of the total pump configuration embodiment 2 throttle compensating valve shapes of the utility model.
The specific embodiment
To the total pump configuration embodiment 1 of the utility model shown in Figure 5, comprise the pump housing 1 at Fig. 3, the piston 3 that slide in front and back in the cylinder barrel of the pump housing 1, piston return spring 10, the front and rear of piston respectively are equipped with 1 leather cup 6 and 2.The preceding leather cup 6 of piston is separated into ante-chamber A and back cavity B with cylinder barrel, and cylinder barrel back cavity B communicates with the fluid reservoir C in the fluid reservoir 16 by fuel feed hole 4.There are splined hole 13 that is communicated with cylinder barrel ante-chamber A and back cavity B and throttle compensating valve 11, the axis of throttle compensating valve 11 valve rods and the dead in line of piston 3 of sealing splined hole 13 in front end and centre at piston 3.The spring perch 14 of pull back spring 10 is enclosed within on the throttle compensating valve valve seat of piston 3, and an end of throttle compensating valve spring 15 withstands on the spool of throttle compensating valve 11, and the other end withstands on the inner end surface of pull back spring spring perch 14.Throttle compensating valve 11 columniform valve rods pass the endoporus in spline-like hole 13 and with the endoporus free-running fit in spline-like hole 13.When the spool of throttle compensating valve 11 was opened, the keyway of splined hole was communicated with chamber, the front and back A and the B of cylinder barrel.The pod 3a of 1 length greater than piston stroke arranged between the front and back of piston 3 leather cup 6 and 2, and pod 3a is radially open-minded along piston 3.The front portion that pod 3a is stretched in spline-like hole 13 in the piston is passed in the rear end of throttle compensating valve 11 valve rods.Be fixed with 1 lever 12 on the pump housing, lever 12 inserts from the oil input channel 17 of the pump housing 1, and its upper end is fixed on the pump housing wall of oil input channel 17 bottoms the next door of fuel feed hole 4 with screw thread.Lever 12 passes pod 3a, and the lower end is inserted in the hole of cylinder barrel bottom.The valve rod of throttle compensating valve 11 withstands on the fixing lever 12 when piston 3 retreats into the rear end end position, and lever 12 backs down throttle compensating valve, and the ante-chamber A of cylinder barrel is communicated with back cavity B.The valve seat driving surface of piston 3 throttle compensating valves is front end faces, the driving surface anchor ring of spool, and sealing surface between the two is a linear sealing.
The service condition of present embodiment is as follows:
(1) glancing impact--piston 3 does not fall back on and retreats into the rear end end position, the valve rod of throttle compensating valve 11 withstands on the fixing lever 12, lever 12 backs down throttle compensating valve, and the keyway of splined hole is communicated with chamber, the front and back A and the B of cylinder barrel, and chamber, the front and back A of cylinder barrel communicates with fluid reservoir C in the fluid reservoir 16 through back cavity B.
(2) glancing impact--push rod 7 moves to left piston 3 and leather cup 6, as shown in Figure 5, after the valve rod of throttle compensating valve 11 leaves fixing lever 12, the ante-chamber A (pressure chamber) of cylinder barrel promptly is closed, and hydraulic pressure begins to raise, and pushes delivery valve immediately open fluid is pressed into pipeline, hydraulic pressure in the wheel cylinder is raise,, produce brake action, the height of oil pressure and treadle effort increase in direct ratio.
(3) keep glancing impact--keep pedal in a certain position, piston 3 is promptly kept motionless, and oil pressure no longer increases in the ante-chamber A (pressure chamber) of cylinder barrel and the wheel cylinder.Oil pressure balance before and after the delivery valve (not shown), and under the effect of its spring, close, certain rate of braking kept.
(4) if lentamente during loosen the brake--brake pedal, total pump piston 3 and wheelcylinder piston are all actuated return down at pull back spring separately, and high-voltage oil liquid flows back to the ante-chamber A of cylinder barrel from pipeline, and braking is removed thereupon.
(5) if rapidly during loosen the brake--piston 3 moves to right rapidly under the effect of pull back spring 10, the ante-chamber A internal volume of cylinder barrel enlarges rapidly, oil pressure reduces rapidly, fluid in the pipeline is because the influence of pipe resistance phase fuel-return valve resistance, have little time fully to flow back to the ante-chamber A of cylinder barrel, make the ante-chamber A of cylinder barrel form certain vacuum degree (negative pressure), and the fluid reservoir C in the fluid reservoir 16 is a bar pressure, under action of pressure, fluid reservoir C fluid in order to the crus secunda braking, increases oil pump capacity promptly through piston crown and overthrow the ante-chamber A that the leather cup edge flows into cylinder barrel, pedal is promptly more stepped on higher, and brake action is strengthened.
(6) behind the loosen the brake pedal--as shown in Figure 4, piston is complete return, and the valve rod of throttle compensating valve 11 withstands on the fixing lever 12 when piston 3 retreats into the rear end end position, and lever 12 backs down throttle compensating valve, and the ante-chamber A of cylinder barrel is communicated with back cavity B.The excess fluid of discharging flow back to fluid reservoir C in the fluid reservoir 16 through throttle compensating valve 11 more in the pipeline.
The driving surface of the valve seat of the throttle compensating valve of embodiment 2 shown in Figure 6 is an inner conical surface, and the driving surface of throttle compensating valve 11 spools is spheres, so sealing surface between the two also is a linear sealing.
Among the above embodiment, be to cooperate between the splined hole of columniform valve rod of throttle compensating valve and valve seat.Certainly, can also adopt opposite form: promptly, piston valve base is a cylindrical hole with the cooperation of throttle compensating valve valve rod, and the valve rod of throttle compensating valve is a castellated shaft, the valve rod castellated shaft of throttle compensating valve passes the cylindrical hole of piston valve base, its external diameter is made free-running fit with cylindrical hole, and when throttle compensating valve was opened, the keyway of the valve rod castellated shaft of throttle compensating valve was communicated with the chamber, front and back of cylinder barrel.
In addition, valve rod and valve seat as deformation-compensated valve can also adopt following distortion: the passage that piston nose is communicated with chamber, cylinder barrel front and back can be the equilateral polygon hole, the circular valve rod of throttle compensating valve employing this moment passes the equilateral polygon hole and it makes free-running fit, and equilateral polygon hole sharp corner is used for being communicated with the chamber, front and back of cylinder barrel with the passage that forms between valve rod.The passage that piston nose is communicated with chamber, cylinder barrel front and back also can be a cylindrical hole, be equipped with the valve rod of throttle compensating valve equilateral polygon, the equilateral polygon valve rod passes cylindrical hole, and its external diameter is made free-running fit with cylindrical hole, and equilateral polygon axle valve rod is used for being communicated with the chamber, front and back of cylinder barrel with the gap between the cylindrical hole.
The above embodiment of the utility model has following beneficial effect:
1. embodiment 1 adopts the inner conical surface on the piston valve base and the leak free mode of spherical valve core, from centering, self-centering, sealing is avoided in traditional central valve formula repairing balanced structure accurately and reliably because the central valve guide rod is long, and easy unstability causes sealing insecure defective.Embodiment 2 adopts the mode of preceding transverse plane of piston valve base and spool semi-ring face sealing, and guide rod is short, and the guiding clearance can be done little and be guaranteed that guiding is stable, can overcome the defective of the easy unstability of traditional central valve formula repairing equalizing gear equally.
2. these two kinds of central valve structures are because the oil-feed sealing surface on spool, is processed easy economy, and quality is controlled easily, avoids traditional central valve structure medium-length hole bottom surface sealing surface problem of difficult processing.
3. these two kinds of structures all are linear sealings, and sealing is reliable, are not easy contaminated thing pad and firmly cause seal failure.
4. the novel central valve formula of this shirt structure, before oil sealing is positioned at fuel feed hole, when avoiding traditional compensator jet structure total pump piston to move, oil sealing is always caused low drawback of oil sealing life-span by the cutting of compensation orifice and intersection place, pump housing hole sharp edge repeatedly, thereby the life-span of assembly is far above traditional compensation orifice structure master cylinder, according to our verification experimental verification, the life-span is up to more than 1,000,000 times, is the former twice.Simultaneously, because do not deposit into the cutting when work of oilhole and pump housing hole intersection sharp edge to Rubber Parts, fuel feed hole can be done big to Φ 1.5-2.5, avoid Φ 0.6 little compensation orifice easily to be stopped up the defective that lost efficacy by pollutants in the hydraulic tubing, also avoided the easy contaminated thing pad of traditional central valve formula repairing mechanism to live, easy to leak is built and is pressed unsettled defective; Improve the reliability of master cylinder serviceability effectively; Together with the 3rd advantage, this structure is more suitable for China's auto trade hydraulic efficiency pressure system and makes the uppity national conditions of fitting process cleanliness level.
5. the pump housing fuel feed hole of this mechanism can be designed as Φ 1.5-2.5, and than the easier processing of Φ 0.6 little compensation orifice, tooling cost can reduce.
6. the valve core reset lever inserts from oil input channel, is fixed on the pump housing wall of oil input channel bottom, does not exist from the lever that resets to the problem of outside draining, omits sealing member, and cost is low, and the leak tightness of assembly is good.
Claims (9)
1. total pump configuration, comprise the pump housing, the piston that slides before and after in the cylinder barrel of the pump housing, piston return spring, the front and rear of piston respectively is equipped with 1 leather cup, the preceding leather cup of piston is separated into ante-chamber and back cavity with cylinder barrel, the cylinder barrel back cavity communicates with fluid reservoir by fuel feed hole, it is characterized in that, piston nose has passage that is communicated with chamber, cylinder barrel front and back and the throttle compensating valve that seals this passage, between the leather cup pod of length greater than piston stroke arranged before and after the piston, the rear end of described throttle compensating valve valve rod is passed piston and is stretched into described pod; Be fixed with 1 lever on the pump housing, lever inserts the pod on the piston; The valve rod of throttle compensating valve withstands on the fixing lever when piston retreats into end position, and throttle compensating valve is backed down.
2. according to the described total pump configuration of claim 1, it is characterized in that described pod is open-minded along piston radial, described lever passes the pod of opening along piston radial.
3. total pump configuration according to claim 1, it is characterized in that, the passage in chamber is a spline-like hole or equilateral polygon hole before and after the described connection cylinder barrel, the valve rod of described throttle compensating valve circle passes the endoporus in spline-like hole or equilateral polygon hole and its and makes free-running fit, and the keyway in described spline-like hole or equilateral polygon hole sharp corner are with the chamber, front and back of the channel connection cylinder barrel that forms between valve rod.
4. total pump configuration according to claim 1, it is characterized in that, the passage in chamber is a cylindrical hole before and after the described connection cylinder barrel, the valve rod of described throttle compensating valve is spline-like axle or equilateral polygon axle, spline-like axle or equilateral polygon axle pass cylindrical hole, its external diameter is made free-running fit with cylindrical hole, and the keyway of described spline-like axle or equilateral polygon axle are communicated with the chamber, front and back of cylinder barrel with the gap between the cylindrical hole.
5. total pump configuration according to claim 1 is characterized in that described lever inserts from the oil input channel of the pump housing, be fixed on the pump housing wall of oil input channel bottom.
6. according to claim 3 or 4 described total pump configurations, it is characterized in that the axis of described valve rod and the dead in line of piston.
7. according to claim 3 or 4 described total pump configurations, it is characterized in that the spring socket sleeve of described pull back spring is outside throttle compensating valve, an end of the spring of throttle compensating valve withstands on the throttle compensating valve spool, and the other end withstands on the inner end surface of pull back spring spring perch.
8. according to the described total pump configuration of arbitrary claim in the claim 1 to 5, it is characterized in that the driving surface of the valve seat of described throttle compensating valve is an inner conical surface, the driving surface of spool is a sphere.
9. according to the described total pump configuration of arbitrary claim in the claim 1 to 5, it is characterized in that the driving surface of the valve seat of described throttle compensating valve is an end face, the driving surface of spool is an anchor ring.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007201723249U CN201086705Y (en) | 2007-09-29 | 2007-09-29 | Master pump structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007201723249U CN201086705Y (en) | 2007-09-29 | 2007-09-29 | Master pump structure |
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| Publication Number | Publication Date |
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| CN201086705Y true CN201086705Y (en) | 2008-07-16 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNU2007201723249U Expired - Fee Related CN201086705Y (en) | 2007-09-29 | 2007-09-29 | Master pump structure |
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Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102213280A (en) * | 2010-04-01 | 2011-10-12 | 李立军 | Double-section automobile clutch master cylinder |
| CN102869553A (en) * | 2010-05-04 | 2013-01-09 | 大陆-特韦斯贸易合伙股份公司及两合公司 | Master cylinder for a hydraulic motor vehicle brake system |
| CN103253336A (en) * | 2012-02-17 | 2013-08-21 | 亨通机械股份有限公司 | Brake master cylinder |
| CN103410883A (en) * | 2013-07-12 | 2013-11-27 | 永康市宏跃动力机械有限公司 | Handheld agricultural machine hydraulic clutch |
| CN103968075A (en) * | 2014-05-22 | 2014-08-06 | 湖州市千金宝云机械铸件有限公司 | Rubber cup of automobile brake |
| CN106015393A (en) * | 2016-08-05 | 2016-10-12 | 林伟 | Clutch master cylinder |
| CN106090069A (en) * | 2016-08-05 | 2016-11-09 | 林伟 | Low abrasion clutch master cylinder |
| CN106122313A (en) * | 2016-08-05 | 2016-11-16 | 林伟 | The control valve assembly of clutch master cylinder |
| CN106949174A (en) * | 2017-04-17 | 2017-07-14 | 常州机电职业技术学院 | Clutch master cylinder |
| CN109969151A (en) * | 2019-04-30 | 2019-07-05 | 厦门永裕机械工业有限公司 | A kind of novel ladder shaft type master cylinder piston for saving production cost |
| CN115805925A (en) * | 2022-11-11 | 2023-03-17 | 浙江名洲汽车零部件股份有限公司 | Brake master cylinder |
| CN116675137A (en) * | 2023-07-18 | 2023-09-01 | 南通巴兰仕机电有限公司 | Lifting engine oil cylinder system |
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2007
- 2007-09-29 CN CNU2007201723249U patent/CN201086705Y/en not_active Expired - Fee Related
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102213280A (en) * | 2010-04-01 | 2011-10-12 | 李立军 | Double-section automobile clutch master cylinder |
| CN102869553B (en) * | 2010-05-04 | 2015-11-25 | 大陆-特韦斯贸易合伙股份公司及两合公司 | For the master cylinder of automotive hydraulic brake system |
| CN102869553A (en) * | 2010-05-04 | 2013-01-09 | 大陆-特韦斯贸易合伙股份公司及两合公司 | Master cylinder for a hydraulic motor vehicle brake system |
| CN103253336A (en) * | 2012-02-17 | 2013-08-21 | 亨通机械股份有限公司 | Brake master cylinder |
| CN103253336B (en) * | 2012-02-17 | 2016-01-27 | 亨通机械股份有限公司 | Brake master cylinder |
| CN103410883A (en) * | 2013-07-12 | 2013-11-27 | 永康市宏跃动力机械有限公司 | Handheld agricultural machine hydraulic clutch |
| CN103968075A (en) * | 2014-05-22 | 2014-08-06 | 湖州市千金宝云机械铸件有限公司 | Rubber cup of automobile brake |
| CN106015393A (en) * | 2016-08-05 | 2016-10-12 | 林伟 | Clutch master cylinder |
| CN106090069A (en) * | 2016-08-05 | 2016-11-09 | 林伟 | Low abrasion clutch master cylinder |
| CN106122313A (en) * | 2016-08-05 | 2016-11-16 | 林伟 | The control valve assembly of clutch master cylinder |
| CN106949174A (en) * | 2017-04-17 | 2017-07-14 | 常州机电职业技术学院 | Clutch master cylinder |
| CN106949174B (en) * | 2017-04-17 | 2022-11-15 | 常州机电职业技术学院 | Clutch master cylinder |
| CN109969151A (en) * | 2019-04-30 | 2019-07-05 | 厦门永裕机械工业有限公司 | A kind of novel ladder shaft type master cylinder piston for saving production cost |
| CN115805925A (en) * | 2022-11-11 | 2023-03-17 | 浙江名洲汽车零部件股份有限公司 | Brake master cylinder |
| CN116675137A (en) * | 2023-07-18 | 2023-09-01 | 南通巴兰仕机电有限公司 | Lifting engine oil cylinder system |
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