CN207229619U - Clutch fulcrum-variable is pressurized power assistant spring - Google Patents
Clutch fulcrum-variable is pressurized power assistant spring Download PDFInfo
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- CN207229619U CN207229619U CN201720933928.4U CN201720933928U CN207229619U CN 207229619 U CN207229619 U CN 207229619U CN 201720933928 U CN201720933928 U CN 201720933928U CN 207229619 U CN207229619 U CN 207229619U
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Abstract
The utility model discloses a kind of clutch fulcrum-variable supercharging power assistant spring, and the spring is two groups of disk springs, and two groups of disk springs are assemblied between clutch case and diaphragm spring side respectively, between diaphragm spring opposite side and support rivet head.The utility model has the advantages that replacing support ring using disk spring, increase the lever ratio excursion of clutch；The utility model increases the length of diaphragm spring reinforcing rib, improves the rigidity of diaphragm spring, increases the lift of clutch, ensures to be completely separated；Using the characteristic curve of disk spring, in the state of clutch separation power is not changed, the thrust of installment state clutch is increased, ensures engine driving torsional；At the same time during clutch separation, in the state of thrust is not influenced, the separating force of clutch is reduced, reduces pedal force.
Description
Technical field
A kind of elastomeric element is the utility model is related to, more particularly to a kind of clutch fulcrum-variable supercharging power assistant spring,
In the case of not changing clutch existing structure, change the position of the fulcrum of clutch, increase the excursion of lever ratio, and realize
The characteristic of high compressive force and low separating force.
Background technology
With the continuous improvement that consumer requires running car dynamic property, utilization of the torquey engine on vehicle by
It is cumulative more, and large torque is necessarily required to high compressive force to ensure the moment of torsion transmission of engine, is limited be subject to gearbox space, from
The specification of clutch can only be in certain scope, this can cause traditional clutch in the case of high compressive force, can correspond to compared with
High separating force, and then produce larger pedal force.This is the place that the application needs to improve emphatically.
Utility model content
Technical problem to be solved in the utility model is to provide for a kind of clutch fulcrum-variable supercharging power assistant spring,
Do not change realize on the basis of conventional clutch structure increase clutch lever than excursion, while increase thrust guarantee
The torsion pass of engine, while separating force is reduced, improve the comfort of pedal.
In order to solve the technical problem of the above, the utility model provides a kind of clutch fulcrum-variable supercharging power-assisted bullet
Spring, the spring are two groups of disk springs, and two groups of disk springs are assemblied between clutch case and diaphragm spring side respectively, film
Between flat spring opposite side and support rivet head.
One group of disk spring, which is stuck on the outside of diaphragm spring reinforcing rib, plays point action, and the maximum of this group of disk spring is outer
Footpath size is less than platen support mountain diameter size, and more than the diameter size of support rivet on clutch case.By adjusting dish
The outer diameter of spring, realizes the change of lever ratio, meets the needs of different lever ratios.
Shirt rim is in certain cone angle during the disk spring non-compressed state, 0 90 degree of ＜ α ＜.
Another group of disk spring, which is stuck in serve on the outside of diaphragm spring head, compresses power-assisted, this group of disk spring is non-depressed
Shirt rim is in certain cone angle beta and γ during contracting state, 0 90 degree of ＜ β ＜, 0 90 degree of ＜ γ ＜.
The reinforcing rib of the diaphragm spring lengthens, its outer diameter is more than the outer diameter of irregularly-shaped hole, improves diaphragm spring
Rigidity.
Superior effect of the utility model is：
1）The utility model replaces support ring using disk spring, increases the lever ratio excursion of clutch；
2）The utility model increases the length of diaphragm spring reinforcing rib, improves the rigidity of diaphragm spring, increases clutch
The lift of device, ensures to be completely separated；
3）The utility model utilizes the characteristic curve of disk spring, in the state of clutch separation power is not changed, increase
The thrust of installment state clutch, ensures engine driving torsional；At the same time during clutch separation, thrust is not being influenced
Under state, the separating force of clutch is reduced, reduces pedal force.
Brief description of the drawings
The accompanying drawings which form a part of this application are used to provide a further understanding of the present invention, this practicality
New schematic description and description is used to explain the utility model, does not form the improper restriction to the utility model.
In the accompanying drawings：
Fig. 1 and Fig. 2 is the matched diagrammatic cross-section of the utility model clutch cover and plate assembly；
Fig. 3 is the diagrammatic cross-section of conventional clutch cap assembly structure；
Fig. 4 is the matched structure decomposition figure of the utility model clutch cover and plate assembly；
Fig. 5 a, Fig. 5 b, the schematic diagram that Fig. 5 c are the utility model back-up spring；
Fig. 6 is the schematic top plan view of the utility model；
Fig. 7 is the schematic diagram of the utility model power-assisted spring；
Fig. 8 is the schematic diagram of the utility model pressing spring；
Fig. 9 is the diagrammatic cross-section of the utility model power-assisted spring, pressing spring and diaphragm spring；
Figure 10 is the schematic diagram of the utility model diaphragm spring；
Figure 11 is the schematic diagram of traditional diaphragm spring；
Figure 12 is the characteristic curve of the utility model diaphragm spring；
Figure 13 is the characteristic curve schematic diagram of the utility model pressing spring and power-assisted spring；
Figure 14 thrust and separating force performance curve schematic diagram in clutch cover and plate assembly for the utility model；
Figure 15 is the utility model lifting curve schematic diagram in clutch cover and plate assembly；
Figure label explanation
1- clutch cases；
2- diaphragm springs；
201-reinforcing rib；202-irregularly-shaped hole；
21-tradition diaphragm spring；
211-reinforcing rib；212-irregularly-shaped hole；
3- platens；4- back-up springs a；
5- back-up springs b；6- power-assisted springs；
7- pressing springs；8- supporting rivets.
Embodiment
The embodiment of the utility model is described in detail below in conjunction with attached drawing, but the utility model can be by right
It is required that the multitude of different ways for limiting and covering is implemented.
Describe the embodiment of the utility model in detail below in conjunction with the accompanying drawings.
Figures 1 and 2 show that the matched diagrammatic cross-section of the utility model embodiment clutch cover and plate assembly, Fig. 4 are shown
The matched structure decomposition figure of the utility model clutch cover and plate assembly.As depicted in figs. 1 and 2, the utility model provide it is a kind of from
Clutch fulcrum-variable is pressurized power assistant spring, and the spring is two groups of disk springs, 4,5 point actions of one of which back-up spring,
Substitute the support ring and supporting rib of conventional clutch（As shown in Figure 3）.The back-up spring card 4,5 is outside 2 reinforcing rib of diaphragm spring
Point action is played in side, and for the back-up spring 4,5 in free state, shirt rim is in certain cone angle（As shown in Figure 5 b）, 0 90 degree of ＜ α ＜.
The back-up spring 4,5 has multiple notches and supporting rivet 8 to coordinate on internal diameter direction, is installed to by supporting rivet 8 on assembly, peace
Back-up spring 4,5 is compressed during dress.By adjusting the maximum outside diameter size of back-up spring 4,5, clutch position of the fulcrum is realized
Change, meets the requirement of different lever ratios.Back-up spring 4,5 maximum outside diameter sizes are less than platen support mountain diameter size, and are more than
The diameter size of support rivet on clutch case.There are multiple notches on the outside diameter direction of back-up spring 4,5, correspond to diaphragm spring respectively
The position of 2 reinforcing ribs 201, avoids clutch from combining and is interfered with diaphragm spring in separation process 2 and back-up spring 4,5.Supporting
Spring 4,5 has certain height thick, for avoiding the avoidance in 2 space of diaphragm spring in clutch motion process；Supported in the present embodiment
The outer diameter of spring 4,5 is Φ 195.4mm, 55 ° of cone angle, expects thickness 2.2mm, and the height under free state is 8.2mm（As Fig. 5 a,
Fig. 5 b, Fig. 5 c）.
As shown in Fig. 6, Fig. 7, Fig. 8 and Fig. 9, another group of disk spring power-assisted spring 6 and pressing spring 7 are stuck in diaphragm spring 2
On the outside of portion, play a part of to reduce separating force respectively and increase thrust.In free state, shirt rim is in for power-assisted spring 6 and pressing spring 7
Certain cone angle beta and γ, 0 90 degree of ＜ β ＜, 0 90 degree of ＜ γ ＜.The cone angle gamma of power-assisted spring 6 is 27 ° in the present embodiment, pressing spring 7
Cone angle beta is 32 °.The change that force value is provided is realized by adjusting cone angle.Power-assisted spring 6 and pressing spring 7 are by changing its internal diameter size
Realize the change of pressing spring and power-assisted spring position of the fulcrum.Power-assisted spring 6 is identical with the internal diameter size of pressing spring 7 under normal circumstances, but
In special circumstances, both internal diameter sizes can be arranged to different sizes.The size of internal diameter size will consider that space whether can
Meet the requirement in space, do not cause to interfere, while the size of the value will be in supporting rivet 8 and 2 head position of diaphragm spring
Between.The thickness of power-assisted spring 6 and pressing spring 7 is selected by required force value size.Power-assisted spring 6 and pressing spring 7 in the present embodiment
Internal diameter size is 107 Φ mm, thickness 1.4mm.As shown in Figure 13, Figure 14 and Figure 15, power-assisted spring 6 and pressing spring 7 are being installed
During compressed；When clutch is in installment state, the force value of the offer of power-assisted spring 6, peak value is crossed in disk spring characteristic curve
Second half section（Such as Figure 15）FC areas, the force value that pressing spring 7 provides, in the characteristic peak value of disk spring（Such as Figure 15）FB areas；
When clutch is in discrete state, power-assisted spring 6 tends to free state by impaction state, the force value provided during this, by dish
Spring characteristic curve（Such as Figure 15）FC areas change to FA areas, and pressing spring 7 further compressed, there is provided force value, by dish-shaped bullet
Spring is characteristic（Such as Figure 15）FB areas change to FC areas；
Figure 10 shows the schematic diagram of the utility model diaphragm spring, with traditional diaphragm spring（As shown in figure 11）Compare,
It can draw, the utility model lengthens 201 outer diameter of reinforcing rib of diaphragm spring 2, and 201 outer diameter length of reinforcing rib exceedes
The outer diameter in diaphragm spring opposite sex hole 202, different in nature hole 202 are to be used to place supporting rivet 8.Conventional clutch diaphragm spring 21
（As shown in figure 11）211 outer diameter of reinforcing rib does not allow more than the maximum outside diameter size in diaphragm spring opposite sex hole 212.Diaphragm bullet
Spring 2 increases the length of its reinforcing rib, improves the ratio of height to thickness of diaphragm spring, increases thrust, reduces separating force.Tradition from
Clutch diaphragm spring characteristic curve compares as shown in figure 12 with the diaphragm spring characteristic curve in the present embodiment.Film in the present embodiment
Flat spring lengthens muscle outer diameter Φ 192mm, internal diameter size 132.5mm.
The foregoing is merely the preferred embodiments of the utility model, it is not intended to limit the present invention, for this
For the technical staff in field, various modifications and changes may be made to the present invention.It is all in the spirit and principles of the utility model
Within, any modification, equivalent replacement, improvement and so on, should be included within the scope of protection of this utility model.
Claims (4)
1. a kind of clutch fulcrum-variable is pressurized power assistant spring, it is characterised in that：The spring is two groups of disk springs, two groups of dish
Shape spring is assemblied between clutch case and diaphragm spring side respectively, between diaphragm spring opposite side and support rivet head；
One group of disk spring, which is stuck on the outside of diaphragm spring reinforcing rib, plays point action, and the maximum outside diameter size of this group of disk spring is small
Mountain diameter size is supported in platen, and more than the diameter size of support rivet on clutch case；Another group of disk spring card
Serve on the outside of diaphragm spring head and compress power-assisted.
2. clutch fulcrum-variable according to claim 1 is pressurized power assistant spring, it is characterised in that：It is described to be stuck in diaphragm bullet
Shirt rim is in certain cone angle when the disk spring non-compressed state of point action is played on the outside of spring reinforcing rib, 0 90 degree of ＜ α ＜.
3. clutch fulcrum-variable according to claim 1 is pressurized power assistant spring, it is characterised in that：It is described to be stuck in diaphragm bullet
Shirt rim is in certain cone angle beta and γ when playing the disk spring non-compressed state of compression power-assisted on the outside of spring head, 0 ＜ β ＜ 90
Degree, 0 90 degree of ＜ γ ＜.
4. clutch fulcrum-variable according to claim 1 is pressurized power assistant spring, it is characterised in that：The diaphragm spring
Reinforcing rib lengthens, and the outer diameter of reinforcing rib is more than the outer diameter of irregularly-shaped hole.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201720933928.4U CN207229619U (en) | 2017-07-30 | 2017-07-30 | Clutch fulcrum-variable is pressurized power assistant spring |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201720933928.4U CN207229619U (en) | 2017-07-30 | 2017-07-30 | Clutch fulcrum-variable is pressurized power assistant spring |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN207229619U true CN207229619U (en) | 2018-04-13 |
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ID=61856077
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201720933928.4U Active CN207229619U (en) | 2017-07-30 | 2017-07-30 | Clutch fulcrum-variable is pressurized power assistant spring |
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| CN (1) | CN207229619U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109139732A (en) * | 2018-10-26 | 2019-01-04 | 上海萨克斯动力总成部件***有限公司 | Monomer separation refers to formula diaphragm spring |
| CN111412225A (en) * | 2019-01-07 | 2020-07-14 | 舍弗勒技术股份两合公司 | Clutch device |
| CN112091340A (en) * | 2020-09-14 | 2020-12-18 | 中国航发贵州黎阳航空动力有限公司 | Machining method and clamp for split spring |
-
2017
- 2017-07-30 CN CN201720933928.4U patent/CN207229619U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109139732A (en) * | 2018-10-26 | 2019-01-04 | 上海萨克斯动力总成部件***有限公司 | Monomer separation refers to formula diaphragm spring |
| CN109139732B (en) * | 2018-10-26 | 2023-09-01 | 华域动力总成部件***(上海)有限公司 | Single body separating finger type diaphragm spring |
| CN111412225A (en) * | 2019-01-07 | 2020-07-14 | 舍弗勒技术股份两合公司 | Clutch device |
| CN112091340A (en) * | 2020-09-14 | 2020-12-18 | 中国航发贵州黎阳航空动力有限公司 | Machining method and clamp for split spring |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CP01 | Change in the name or title of a patent holder |
Address after: 201708 Qingpu District Shanghai City Huaxin Town Ji He Lu No. 3189 Patentee after: Huayu power assembly component system (Shanghai) Co., Ltd Address before: 201708 Qingpu District Shanghai City Huaxin Town Ji He Lu No. 3189 Patentee before: SHANGHAI SACHS POWERTRAIN COMPONENTS & SYSTEM Co.,Ltd. |
|
| CP01 | Change in the name or title of a patent holder |