GB2144495A - Pressure regulation of torque converter lock-up clutch - Google Patents
Pressure regulation of torque converter lock-up clutch Download PDFInfo
- Publication number
- GB2144495A GB2144495A GB08320734A GB8320734A GB2144495A GB 2144495 A GB2144495 A GB 2144495A GB 08320734 A GB08320734 A GB 08320734A GB 8320734 A GB8320734 A GB 8320734A GB 2144495 A GB2144495 A GB 2144495A
- Authority
- GB
- United Kingdom
- Prior art keywords
- clutch plate
- blade wheel
- pressure
- turbine blade
- torque converter
- 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.)
- Granted
Links
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
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
-
- 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
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
- F16H2045/0294—Single disk type lock-up clutch, i.e. using a single disc engaged between friction members
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Fluid Gearings (AREA)
Abstract
The clutch plate (9) of a torque converter lock-up clutch is arranged to be so axially movable as to be either engaged with or disengaged from the input casing (4) of the torque converter according to a difference between fluid pressures acting on opposite side surfaces thereof. The clutch plate and the turbine blade wheel (7) are so interconnected through a damper spring means as to be relatively turnable. The clutch plate is provided with a communication hole for communicating between said opposite side surfaces thereof with an opening and closing member comprising a pressure regulating valve (18) of which a set pressure is adjustable. This valve is so adjusted that the set pressure is increased and decreased in accordance with an amount of relative turning displacement between the clutch plate and the turbine blade wheel. In use, temperature change does not result in pressure change and consequent change in the engaging force of the clutch plate. <IMAGE>
Description
SPECIFICATION
Torque converters
This invention relates to torque converters such as are used in motor vehicle transmissions.
There has been proposed a torque converter in which an internal space of a main body of the torque converter is surrounded by an input casing on one side connected to an input shaft. A pump blade wheel on the other side connected to the input casing is provided therein with a turbine blade wheel connected to an output shaft. A clutch plate interposed between the turbine blade wheel and the input casing is axially movable so as to be either engaged with or disengaged from the input casing according to a difference between fluid pressures acting on both side surfaces thereof.The clutch plate and the turbine blade wheel are so interconnected through a damper spring arrangement as to be relatively turnable, and the clutch plate is provided with a communication hole communicating between both the side surfaces thereof, and with an opening and closing member for opening and closing this communication hole. The open area of the communication hole is adjusted, by the opening and closing member, in accordance with an amount of relative turning displacement between the clutch plate and the turbine blade wheel.In a region in which driving force is small, and amount of relative turning displacement is also small, the open area of the communication hole is increased and thereby a leak amount of fluid through the communication hole is increased, resulting in decrease in the pressure difference between the opposite side surfaces of the clutch plate, and thereby the engaging force of the clutch plate is weakened in accordance with a decrease in a driving torque and thereby the clutch plate is placed in an easy to slip condition, and torque change in this region can be absorbed by this slipping.The inconvenience arises, however, that even if the open area of the communication hole remains unclosed, the leakage amount of the fluid varies with change of viscosity of the fluid caused by change of temperature, and accordingly the difference in fluid pressure across the clutch plate varies with change in temperature, and the engaging forces of the clutch plate at the time of a low temperature and at the time of a high temperature differ.
According to the present invention there is provided a torque converter having in an internal space of a main body of the torque converter that is surrounded by an input casing on one side connected to an input shaft and a pump blade wheel on the other side connected to the input casing, a turbine blade wheel connected to an output shaft and a clutch plate interposed between the turbine blade wheel and the input casing; the clutch plate being arranged to be so axially movable as to be either engaged with or disengaged from the input casing according to a difference between fluid pressures acting on opposite side surfaces thereof; the clutch plate and the turbine blade wheel being so interconnected through a damper spring means as to be relatively turnable; and the clutch plate being provided with a communication hole for communicating between said opposite side surfaces thereof and with an opening and closing member for opening and closing the communication hole; this opening and closing member comprising a pressure regulating valve of which a set pressure is adjustable, this valve being so adjusted that the set pressure is increased and decreased in accordance with an amount of relative turning displacement between the clutch plate and the turbine blade wheel. In use of this torque converter, even if temperature conditions change, the fluid pressure in the internal space of the main body is adjusted in accordance with the set pressure of the regulating valve and thus temperature change does not result in pressure change and consequent change in the engaging force of the clutch plate.
For a better understanding of the invention and to show how the same may be carried into effect, reference will now be made, by way of example, to the accompanying drawings in which:
Figure 1 is a sectional side view of a torque converter,
Figures 2 and 3 are sectional views taken along lines ll-ll and Ill-Ill in Fig. 1, and
Figure 4 is a sectional view taken along line
IV-IV in Fig. 2.
In the Figures, numeral 1 denotes a main body of a torque converter having an input shaft 2 connected to an internal combusion engine and an output shaft 3 connected to a load such as a driving wheel of a vehicle. The shafts 2 and 3 are disposed along a common single axis line. The main body 1 is provided with a front side input casing 4 on a front side connected to the input shaft 2 and a pump blade wheel 5 on a rear side connected to the input casing 4. An internal space 6 surrounded by the input casing 4 and the pump blade wheel 5 has therein a turbine blade wheel 7 connected to the output shaft 3 and a stator blade wheel 8 interposed between the turbine blade wheel 7 and the pump blade wheel 5. When the input shaft 2 is turned, internal fluid is circulated through these blade wheels 5, 7, 8 and thereby fluid torque is transmitted to the output shaft 3.A clutch plate 9 is provided between the turbine blade wheel 7 and the input casing 4 and is so axially movable as to be either engaged with or disengaged from the input casing 4 in accordance with change of a difference betweeh fluid pressures acting on front and rear side surfaces thereof, and additionally the clutch plate 9 and the turbine blade wheel 7 are so interconnected through a damper spring means 10 as to be relatively turnable, so that, when the clutch plate 9 is engaged with the input casing 4, there is given a mechanical torque transmission through the path input shaft 2-input casing 4-clutch plate 9-damper spring means 1 O-turbine blade wheel 7-output shaft 3.
In more detail, in the illustrated example, the clutch plate 9 is acted upon at its rear surface by a fluid pressure in the internal space 6 and at its front surface by a fluid pressure in a gap 11 formed between the plate 9 and the input casing 4, and is so arranged that, if the fluid pressure in the gap 11 is decreased by a fluid pressure control means (not illustrated) connected to the gap 11 through an axial opening passage 12 made in the output shaft 3, the plate 9 is caused to advance and is brought into frictional engagement, at a friction material 1 3 on the front surface of an outer peripheral portion thereof, with the input casing 4.
As shown in Fig. 2, the damper spring means 10 comprises a plurality of coil springs 1 0a disposed circumferentially at regularly spaced intervals in an annular recess portion 9a in the rear surface of the outer peripheral portion of the clutch plate 9; a plurality of supporting members 14 fixed to the clutch plate 9, one for each of the coil springs 1 ova, for preventing the coil springs 1 0a from coming off inwards; a pair of input side retainers 15, 1 5 for holding each coil spring 1 0a therebetween and so provided as to protrude from both end portions of each supporting member 14; and output side retainers 16 each protruding forwards from the turbine blade wheel 7 and placed in the spaces between the coil springs 10a.
If it is now assumed that the drive turning direction effected by the engine, that is, the regular turning direction of the clutch plate 9 is counterclockwise as viewed in Fig. 2, at the time of transmission of the driving torque from the engine, the turbine blade wheel 7 is given a relative turning in the clockwise direction, that is, in the reverse turning direction in relation to the clutch plate 9. In this situation, each coil spring 1 0a is given, through the output side retainer 15, a compression displacement thereof until there is developed a spring force corresponding to the driving torque, and thus the amount of relative turning displacement of the turbine blade wheel 7 in the clockwise direction is increased according as the driving torque is increased.
When there is generated any torque change, each coil spring 1 0a is caused to expand or contract around its compressed displacement position corresponding to the changed driving torque and thus serves to absorb the torque change. In this case, the coil springs 10a are required to have a comparatively high spring constant in order to eliminate such an unfavourable situation that, at a region of comparatively large driving torque, a torque change after a coil spring has been compressed to its maximum compression position under a steady condition cannot be absorbed by the coil spring. If, however, such a coil spring is used, a torque change at a region of comparatively small driving torque cannot be fully absorbed by the coil spring.
For this reason, the clutch plate 9 is provided with a communication hole 1 7 communicating between the opposite side surfaces thereof. At a region of comparatively small driving torque this communication hole 1 7 is opened by an opening and closing member to permit fluid to flow from the internal space 6 into the gap 11, and thereby difference between the fluid pressures on the opposite side surfaces of the clutch plate 9 is decreased to weaken the engaging force of the clutch plate 9, and consequently a torque change in this region of small driving torque can be effectively absorbed by slipping of the clutch plate 9.
The opening and closing member comprises a pressure regulating valve 1 8 of which a set pressure is adjustable, so arranged that the set pressure thereof is increased and decreased in accordance with the amount of relative turning displacement between the clutch plate 9 and the turbine blade wheel 7.
In more detail. in the illustrated example, the pressure regulating valve 1 8 is so constructed that, as shown clearly in Fig. 4, a valve housing 1 9 having an output port 1 9a connected to the communication hole 1 7 in the outer peripheral portion of the clutch plate 9, and an inlet port 1 9b connected to the internal space 6, is fixedly provided in the recess portion 9a in the outer periphery portion of the clutch plate 9. A pressure regulating valve body 21, which is urged by a pressure regulating spring 20 towards its closing side on the right-hand side in Fig. 4 and which is pushed towards its opening side on the left-hand side by the fluid pressure in the internal space 6 acting thereon through the inlet port 1 9b, is housed in the valve housing 19. The pressure regulating spring 20 is adjustable in its spring pressure by a plunger 22 acting on the left end thereof and so arranged as to be brought, at its left side surface, in abutment with an operation member 23 projecting from the turbine blade wheel 7.
As shown in Fig. 3, the friction material 1 3 on the front surface of the outer peripheral portion of the clutch plate 9 has a cut-out portion 1 3a which is in alignment with the communication hole 1 7 so that the fluid from the communication hole 1 7 may flow into the gap 11 through the cut-out portion 1 3a.
Operation is as follows:
The pressure regulating valve 1 8 operates in such a manner that when the fluid pressure in the internal space 6 is higher than the predetermined set pressure determined by the spring pressure of the pressure regulating spring 20, the valve is opened to cause fluid to leak out through the communication hole 17, and thus the fluid pressure in the space 6 is automatically adjusted to become the set pressure. When, on this occasion, there takes place relative turning in the clockwise direction of the turbine blade wheel 7 in relation to the clutch plate 9, the plunger 22 is pushed through the operation member 23 toward the right in Fig. 4 to increase the spring pressure of the pressure regulating spring 20.Thus, the set pressure is increased and decreased in accordance with the amount of relative displacement of the turbine blade wheel 7, and the set pressure becomes small at a region which is small in a small torque change of driving force and small in an amount of relative turning displacement, and the fluid pressure difference between both the side surfaces of the clutch plate 9 is decreased and the engaging force of the clutch plate 9 against the input case 4 is weakened according to a decrease in driving torque.
In this case, even when temperature changes, the fluid pressure in the internal space 6 is adjusted accurately to the set pressure of the pressure regulating valve 18, and thus there is not caused any pressure change as a result of temperature change, and accordingly any change in engaging force of the clutch plate 9 is not caused by a change in temperature.
The pressure acting on the clutch plate is controlled by the pressure regulating valve, so that there is eliminated a pressure change resulting from temperature change such as is caused in the previously proposed torque converter wherein pressure control is effected by changing the opening area of the communication hole, and consequently the engaging force of the clutch plate can be controlled accurately in accordance with driving torque.
Claims (4)
1. A torque converter having in an internal space of a main body of the torque converter that is surrounded by an input casing on one side connected to an input shaft and a pump blade wheel on the other side connected to the input casing, a turbine blade wheel connected to an output shaft and a clutch plate interposed between the turbine blade wheel and the input casing; the clutch plate being arranged to be so axially movable as to be either engaged with or disengaged from the input casing according to a difference between fluid pressures acting on opposite side surfaces thereof; the clutch plate and the turbine blade wheel being so interconnected through a damper spring means as to be relatively turnable; and the clutch plate being provided with a communication hole for communicating between said opposite side surfaces thereof and with an opening and closing member for opening and closing the communication hole; this opening and closing membr comprising a pressure regulating valve of which a set pressure is adjustable, this valve being so adjusted that the set pressure is increased and decreased in accordance with an amount of relative turning displacement between the clutch plate and the turbine blade wheel.
2. A torque converter as claimed in claim 1, wherein the pressure regulating valve comprises a valve housing fixed to an outer peripheral portion of the clutch plate and a pressure regulating valve body housed therein; and wherein the pressure regulating valve body is arranged to be pushed toward its closing side by a pressure regulating spring and toward its opening side by a fluid pressure in the internal space, the pressure regulating spring being adjustable in its spring pressure by action of an operation member extending from the turbine blade wheel.
3. A torque converter as claimed in claim 2, wherein the operation member is in abutment with a plunger on one end of the pressure regulating spring.
4. A torque converter substantially as hereinbefore described with reference to the accompanying drawings.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB08320734A GB2144495B (en) | 1983-08-02 | 1983-08-02 | Pressure regulation of torque converter lock-up clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB08320734A GB2144495B (en) | 1983-08-02 | 1983-08-02 | Pressure regulation of torque converter lock-up clutch |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| GB8320734D0 GB8320734D0 (en) | 1983-09-01 |
| GB2144495A true GB2144495A (en) | 1985-03-06 |
| GB2144495B GB2144495B (en) | 1986-06-18 |
Family
ID=10546636
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB08320734A Expired GB2144495B (en) | 1983-08-02 | 1983-08-02 | Pressure regulation of torque converter lock-up clutch |
Country Status (1)
| Country | Link |
|---|---|
| GB (1) | GB2144495B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5385222A (en) * | 1992-08-21 | 1995-01-31 | Luk Getriebe-Systeme Gmbh | Coupling for a hydrodynamic flow converter |
| US5899311A (en) * | 1996-08-15 | 1999-05-04 | Kabushiki Kaisha Yutaka Giken | Apparatus for holding spring of clutch |
| DE19810355B4 (en) * | 1998-03-10 | 2004-01-29 | Zf Sachs Ag | torque converter |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2127112A (en) * | 1982-07-24 | 1984-04-04 | Honda Motor Co Ltd | Pressure regulation of torque convertor lock-up clutch |
-
1983
- 1983-08-02 GB GB08320734A patent/GB2144495B/en not_active Expired
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2127112A (en) * | 1982-07-24 | 1984-04-04 | Honda Motor Co Ltd | Pressure regulation of torque convertor lock-up clutch |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5385222A (en) * | 1992-08-21 | 1995-01-31 | Luk Getriebe-Systeme Gmbh | Coupling for a hydrodynamic flow converter |
| US5899311A (en) * | 1996-08-15 | 1999-05-04 | Kabushiki Kaisha Yutaka Giken | Apparatus for holding spring of clutch |
| DE19810355B4 (en) * | 1998-03-10 | 2004-01-29 | Zf Sachs Ag | torque converter |
Also Published As
| Publication number | Publication date |
|---|---|
| GB2144495B (en) | 1986-06-18 |
| GB8320734D0 (en) | 1983-09-01 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PCNP | Patent ceased through non-payment of renewal fee |
Effective date: 19970802 |