US20060065495A1 - Dual disc spring - Google Patents
Dual disc spring Download PDFInfo
- Publication number
- US20060065495A1 US20060065495A1 US10/951,487 US95148704A US2006065495A1 US 20060065495 A1 US20060065495 A1 US 20060065495A1 US 95148704 A US95148704 A US 95148704A US 2006065495 A1 US2006065495 A1 US 2006065495A1
- Authority
- US
- United States
- Prior art keywords
- section
- fulcrum
- spring
- dual
- disc spring
- 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.)
- Abandoned
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
- F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
Definitions
- This invention relates to springs and, more particularly, to disc-type or washer-type springs.
- Washer or Belleville springs employ a conical-shaped washer or disc, which has spring properties.
- the disc spring is deflected from the conical shape towards a flat shape as reaction load increases.
- a typical disc spring has advantages over coiled wire springs in that less axial space is needed for a given reaction load requirement.
- the disc spring can be designed to have a constant load over a wide range of deflections. This makes this spring very useful in environments, such as torque-transmitting mechanisms, where it is desirable to provide control over the reaction force on the apply piston which is returning the piston to a disengaged condition in a torque-transmitting mechanism.
- the disc spring has two spring sections, which are joined at a common fulcrum.
- the spring sections are both conical in shape.
- the disc spring sections extend axially in the same direction.
- one of the spring sections has a castellated profile.
- the dual disc spring is employed in a dual piston torque-transmitting mechanism assembly.
- FIG. 1 is a plan view of a disc spring incorporating the present invention.
- FIG. 2 is a view taken along line 2 - 2 in FIG. 1 .
- FIG. 3 is an elevational view of a portion of a transmission incorporating the present invention.
- FIG. 1 a dual disc spring 10 having an outer disc section 12 , an inner disc section 14 , and a fulcrum point 16 .
- the disc sections 12 and 14 are both conically shaped, as that seen in FIG. 2 .
- the conical displacement from the fulcrum 16 is in the same axial direction and opposite radial directions.
- the inner disc 14 has a castellated profile 18 .
- the castellated profile could be placed in the outer disc section 12 wherein the inner disc section would then be a continuous disc or conical section.
- Each of the inner disc and outer disc portions will provide a reaction for loads when the fulcrum 16 is positioned in a stationary location and a load is applied through the respective disc portions.
- a dual torque-transmitting arrangement 20 is shown in FIG. 3 .
- This dual torque-transmitting arrangement 20 includes the dual disc spring 10 disposed on a stationary housing 22 .
- the stationary housing 22 has a plurality of protuberances or fingers 24 over which the castellated profile of inner disc 14 is disposed.
- the torque-transmitting arrangement 20 also includes a pair of apply pistons 26 and 28 .
- the apply piston 26 is slidably disposed in a cavity 30 and cooperates therewith to form an apply chamber 32 .
- the apply piston 28 is slidably disposed in a pair of cavities 34 and 36 and cooperates with these cavities to form an apply chamber 38 .
- the torque-transmitting arrangement 20 has an inner torque-transmitting mechanism 40 and an outer torque-transmitting mechanism 42 .
- the inner torque-transmitting mechanism 40 has a plurality of friction members 44 that are drivingly connected with and slidably disposed on a spline 46 formed in the housing 22 .
- the torque-transmitting mechanism 40 also includes a second plurality of friction members 48 , which are drivingly connected to and slidably disposed on a spline 50 formed on a hub member 52 .
- the hub member 52 is connectible with a gearing member within a power transmission, not shown.
- the torque-transmitting mechanism 42 includes a plurality of friction members 54 drivingly connected with and slidably disposed on a spline 56 formed on the housing 22 .
- a second plurality of friction members 58 are slidably disposed on and drivingly connected with a spline 60 formed on a hub 62 , which is also adapted to be connected with a planetary gear member, not shown.
- the housing 22 is secured in a transmission housing 64 , such that all the components connected therewith are stationary.
- the torque-transmitting mechanisms 40 and 42 are therefore stationary type torque-transmitting mechanisms in this application. These stationary type torque-transmitting mechanisms are commonly termed brakes or reaction clutches.
- the chambers 32 and 38 are in fluid communication with an axial hydraulic control system, not shown.
- the respective chambers 32 and 38 are pressurized with a fluid pressure sufficient to overcome the reaction force in the disc portions 14 and 12 .
- the piston 26 will move axially rightward to engage one of the friction members 44 , which will result in a frictional drive connection between the housing 22 and the hub 52 thereby retaining the planetary member connected therewith stationary.
- the load within the inner disc spring 14 reacts at the fulcrum point 16 , which is positioned stationary within the housing 22 by a conventional locking ring 66 .
- the piston 28 When the chamber 38 is pressurized, the piston 28 will move axially rightward against the reaction force in the disc spring 12 to engage one of the friction members 54 , which frictionally engages the friction members 58 to complete a torque-transmitting connection between the hub 62 and the housing 22 . Thus, at this point, the planetary member connected with the hub 62 will be held stationary.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
A dual spring includes a pair of conically-shaped spring sections, which are joined at a common fulcrum. One of the spring sections is disposed radially inward from the fulcrum and the other of the spring sections is disposed radially outward from the fulcrum. Both of the conical sections open axially in the same direction relative to the fulcrum section.
Description
- This invention relates to springs and, more particularly, to disc-type or washer-type springs.
- Washer or Belleville springs, as they are commonly termed, employ a conical-shaped washer or disc, which has spring properties. The disc spring is deflected from the conical shape towards a flat shape as reaction load increases. A typical disc spring has advantages over coiled wire springs in that less axial space is needed for a given reaction load requirement. Also, the disc spring can be designed to have a constant load over a wide range of deflections. This makes this spring very useful in environments, such as torque-transmitting mechanisms, where it is desirable to provide control over the reaction force on the apply piston which is returning the piston to a disengaged condition in a torque-transmitting mechanism.
- It is an object of the present invention to provide an improved disc-type spring member.
- In one aspect of the present invention, the disc spring has two spring sections, which are joined at a common fulcrum.
- In another aspect of the present invention, the spring sections are both conical in shape.
- In still another aspect of the present invention, the disc spring sections extend axially in the same direction.
- In yet still another aspect of the present invention, one of the spring sections has a castellated profile.
- In a further aspect of the present invention, the dual disc spring is employed in a dual piston torque-transmitting mechanism assembly.
-
FIG. 1 is a plan view of a disc spring incorporating the present invention. -
FIG. 2 is a view taken along line 2-2 inFIG. 1 . -
FIG. 3 is an elevational view of a portion of a transmission incorporating the present invention. - Referring to the drawings, wherein like characters represent the same or corresponding parts throughout the several views, there is seen in
FIG. 1 a dual disc spring 10 having anouter disc section 12, aninner disc section 14, and afulcrum point 16. Thedisc sections FIG. 2 . The conical displacement from thefulcrum 16 is in the same axial direction and opposite radial directions. - The
inner disc 14 has a castellatedprofile 18. The castellated profile could be placed in theouter disc section 12 wherein the inner disc section would then be a continuous disc or conical section. Each of the inner disc and outer disc portions will provide a reaction for loads when thefulcrum 16 is positioned in a stationary location and a load is applied through the respective disc portions. - A dual torque-transmitting
arrangement 20 is shown inFIG. 3 . This dual torque-transmittingarrangement 20 includes thedual disc spring 10 disposed on astationary housing 22. Thestationary housing 22 has a plurality of protuberances orfingers 24 over which the castellated profile ofinner disc 14 is disposed. The torque-transmittingarrangement 20 also includes a pair of applypistons piston 26 is slidably disposed in acavity 30 and cooperates therewith to form an applychamber 32. The applypiston 28 is slidably disposed in a pair ofcavities apply chamber 38. - The torque-transmitting
arrangement 20 has an inner torque-transmitting mechanism 40 and an outer torque-transmitting mechanism 42. The inner torque-transmitting mechanism 40 has a plurality offriction members 44 that are drivingly connected with and slidably disposed on aspline 46 formed in thehousing 22. The torque-transmitting mechanism 40 also includes a second plurality offriction members 48, which are drivingly connected to and slidably disposed on aspline 50 formed on ahub member 52. Thehub member 52 is connectible with a gearing member within a power transmission, not shown. - The torque-
transmitting mechanism 42 includes a plurality offriction members 54 drivingly connected with and slidably disposed on aspline 56 formed on thehousing 22. A second plurality offriction members 58 are slidably disposed on and drivingly connected with aspline 60 formed on ahub 62, which is also adapted to be connected with a planetary gear member, not shown. Thehousing 22 is secured in atransmission housing 64, such that all the components connected therewith are stationary. The torque-transmitting mechanisms - The
chambers mechanisms respective chambers disc portions chamber 32 is pressurized, thepiston 26 will move axially rightward to engage one of thefriction members 44, which will result in a frictional drive connection between thehousing 22 and thehub 52 thereby retaining the planetary member connected therewith stationary. As thepiston 26 is moved axially rightward, the load within theinner disc spring 14 reacts at thefulcrum point 16, which is positioned stationary within thehousing 22 by aconventional locking ring 66. - When the
chamber 38 is pressurized, thepiston 28 will move axially rightward against the reaction force in thedisc spring 12 to engage one of thefriction members 54, which frictionally engages thefriction members 58 to complete a torque-transmitting connection between thehub 62 and thehousing 22. Thus, at this point, the planetary member connected with thehub 62 will be held stationary. - When the
piston 26 moves rightward, the force ondisc spring 14 will be reacted at the outer end ofdisc spring 12, and when thepiston 28 is moved axially, the force ondisc spring 12 will be reacted at the radially inner end ofdisc spring 14. It is not recommended in certain systems to actuate thepistons piston 26, for example, changes the reaction force available at thedisc spring 12 and the operation ofpiston 28 changes the reaction force available at thedisc spring 14. When thepiston 26 is actuated, the pressure necessary to actuate thepiston 28 will be greater and when thepiston 28 is actuated, the pressure necessary to actuate thepiston 26 will be greater. In many systems, this will be of little consequence since the control pressure available is significantly greater than the maximum pressure needed to fully engage or energize the torque-transmittingmechanisms - Obviously, those skilled in the art will find modifications and variations of the above-described disclosure. Therefore, it is to be understood that the scope of the present invention is limited only by the appended claims.
Claims (3)
1. A dual torque transmitting with a dual acting spring comprising;
a first piston member;
a second piston member:
a first conical spring section;
a second conical spring section;
a fulcrum section joining said first and second conical spring sections;
means for positioning said fulcrum section at a stationary position; and
said first conical spring section extending outward from said fulcrum section to engage said first piston member and said second conical spring section extending inward from said fulcrum section to engage said second piston member.
2. The dual torque transmitting with a dual acting spring defined in claim 1 further comprising:
one of said conical spring sections having a plurality of castellations.
3. The dual torque transmitting with a dual acting spring defined in claim 1 further wherein:
both of said first conical spring section and said second conical spring section opens in the same axial direction relative to said fulcrum section.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/951,487 US20060065495A1 (en) | 2004-09-28 | 2004-09-28 | Dual disc spring |
DE102005045322A DE102005045322A1 (en) | 2004-09-28 | 2005-09-22 | Double glazing spring |
US11/242,541 US7111833B2 (en) | 2004-09-28 | 2005-10-03 | Dual disc spring |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/951,487 US20060065495A1 (en) | 2004-09-28 | 2004-09-28 | Dual disc spring |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/242,541 Continuation US7111833B2 (en) | 2004-09-28 | 2005-10-03 | Dual disc spring |
Publications (1)
Publication Number | Publication Date |
---|---|
US20060065495A1 true US20060065495A1 (en) | 2006-03-30 |
Family
ID=36062377
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/951,487 Abandoned US20060065495A1 (en) | 2004-09-28 | 2004-09-28 | Dual disc spring |
US11/242,541 Expired - Fee Related US7111833B2 (en) | 2004-09-28 | 2005-10-03 | Dual disc spring |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/242,541 Expired - Fee Related US7111833B2 (en) | 2004-09-28 | 2005-10-03 | Dual disc spring |
Country Status (2)
Country | Link |
---|---|
US (2) | US20060065495A1 (en) |
DE (1) | DE102005045322A1 (en) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006035649B4 (en) | 2006-07-31 | 2022-03-10 | Zf Friedrichshafen Ag | Clutch assembly for a vehicle |
DE102007018968B4 (en) * | 2007-04-21 | 2016-06-09 | Zf Friedrichshafen Ag | Arrangement of a plate spring in a piston of a switching element |
DE102007018969A1 (en) | 2007-04-21 | 2008-10-30 | Zf Friedrichshafen Ag | Arrangement of a plate spring in a piston of a switching element |
DE102007022421B4 (en) * | 2007-05-10 | 2020-03-05 | Borgwarner Inc. | Coupling system for motor vehicle drives |
WO2008138296A1 (en) * | 2007-05-14 | 2008-11-20 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Force transmission device |
DE102008064299A1 (en) * | 2008-12-20 | 2010-07-01 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | loader |
US9234551B2 (en) * | 2012-09-12 | 2016-01-12 | GM Global Technology Operations LLC | Transmission and a clutch assembly for a vehicle |
JP6538047B2 (en) * | 2014-06-20 | 2019-07-03 | 日本発條株式会社 | Disc spring |
CN106602289A (en) * | 2016-11-30 | 2017-04-26 | 常州安费诺福洋通信设备有限公司 | Elastic contact structure for 4G direct current blocking device |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1176632A (en) * | 1915-04-17 | 1916-03-21 | Frithjof Werner | Electrical machine. |
US1850566A (en) * | 1928-03-14 | 1932-03-22 | Roed Thorvald | Sealing device |
US2229319A (en) * | 1939-05-24 | 1941-01-21 | Chrysler Corp | Vehicle power transmission |
US3107766A (en) * | 1961-05-03 | 1963-10-22 | Gen Motors Corp | Friction engaging devices having a lever spring |
US3483888A (en) * | 1967-12-15 | 1969-12-16 | Waldes Kohinoor Inc | Self-locking retaining rings and assemblies employing same |
US3951393A (en) * | 1974-07-22 | 1976-04-20 | Borg-Warner Corporation | Fulcrums for Belleville springs |
US4135283A (en) * | 1974-10-23 | 1979-01-23 | Luk Lamellen U. Kupplungsbau Gmbh | Resilient structural member such as a plate spring |
US4538716A (en) * | 1982-02-10 | 1985-09-03 | Luk Lamellen Und Kupplungsbau Gmbh | Multiple-disc friction clutch and diaphragm spring therefor |
-
2004
- 2004-09-28 US US10/951,487 patent/US20060065495A1/en not_active Abandoned
-
2005
- 2005-09-22 DE DE102005045322A patent/DE102005045322A1/en not_active Withdrawn
- 2005-10-03 US US11/242,541 patent/US7111833B2/en not_active Expired - Fee Related
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1176632A (en) * | 1915-04-17 | 1916-03-21 | Frithjof Werner | Electrical machine. |
US1850566A (en) * | 1928-03-14 | 1932-03-22 | Roed Thorvald | Sealing device |
US2229319A (en) * | 1939-05-24 | 1941-01-21 | Chrysler Corp | Vehicle power transmission |
US3107766A (en) * | 1961-05-03 | 1963-10-22 | Gen Motors Corp | Friction engaging devices having a lever spring |
US3483888A (en) * | 1967-12-15 | 1969-12-16 | Waldes Kohinoor Inc | Self-locking retaining rings and assemblies employing same |
US3951393A (en) * | 1974-07-22 | 1976-04-20 | Borg-Warner Corporation | Fulcrums for Belleville springs |
US4135283A (en) * | 1974-10-23 | 1979-01-23 | Luk Lamellen U. Kupplungsbau Gmbh | Resilient structural member such as a plate spring |
US4538716A (en) * | 1982-02-10 | 1985-09-03 | Luk Lamellen Und Kupplungsbau Gmbh | Multiple-disc friction clutch and diaphragm spring therefor |
Also Published As
Publication number | Publication date |
---|---|
US7111833B2 (en) | 2006-09-26 |
US20060071382A1 (en) | 2006-04-06 |
DE102005045322A1 (en) | 2006-04-06 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: GENERAL MOTORS CORPORATION, MICHIGAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:WITTKOPP, SCOTT H.;REEL/FRAME:015479/0032 Effective date: 20040910 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |