CN1111329A

CN1111329A - Friction ring and clutch with same

Info

Publication number: CN1111329A
Application number: CN95101249A
Authority: CN
Inventors: 恩斯特·瓦尔特; 格奥尔格·魏德内尔
Original assignee: LuK Getriebe Systeme GmbH
Current assignee: LuK Getriebe Systeme GmbH
Priority date: 1994-01-21
Filing date: 1995-01-19
Publication date: 1995-11-08
Anticipated expiration: 2015-01-19
Also published as: GB9501113D0; FR2715448B1; SE9500134D0; GB2285851B; SE509739C2; CN1077968C; SE9500134L; KR100408334B1; DE19500814A1; JPH07208577A; GB2285851A; FR2715448A1; KR950033157A; DE19500814B4

Abstract

The invention is related to a friction ring for use in a wet-type clutch which has a cooling groove.

Description

Friction ring and clutch with same

The present invention relates to a friction ring or a friction pad, it is applied in the wet operation clutch, is specially adapted in the overlap joint clutch of a Hydrodynamic rotating moment convertor, simultaneously, this friction ring constitutes a friction surface, and it is provided with conduit or the passage that is used for the leading cooling liquid.

This friction ring or friction pad and the wet operation clutch that it is housed are open in US-PS4969543 and 056631.In these two U. S. Patents, described and had the fluid dynamic flow converter that overlaps clutch, wherein, the friction surface that is in contact is a structure like this setting, promptly under the overlap joint clutch situation of closure, also can form an oil stream between the chamber of ring piston both sides.This hydrodynamic flow change of variable utensil has a housing, a wherein ccontaining pump impeller, and a turbine, guide wheel and overlap joint clutch, this clutch is equipped with the ring piston.Constitute the chamber that usable oils is full of in ring piston both sides, simultaneously, the radially the inside at the friction surface that overlaps clutch forms first chamber and be provided with turbine at least in second chamber.This first chamber is limited by a radial wall of ring piston and housing.This oil stream is used for reducing the heating power load, the particularly thermal force in friction pad or friction surface zone that produces at member because overlap cltuch slipping.

Task of the present invention is, the described known wet operation clutch that has the friction ring of guiding cooling liquid conduit and it is housed is done the optimization setting aspect the attainable cooling action flowing by liquid volume.This point, should by one in the friction surface zone of wet operation clutch and between liquid and adjacent member good heat exchange realize.In addition, friction ring by structure setting of the present invention or wet operation clutch and the high torque (HT) performance of a wet operation clutch should be provided.In addition, this friction ring or friction disk that this friction ring is housed all should be able to be made in simple and economical especially mode with therefore relevant wet operation clutch.

According to the present invention, above-mentioned task is to realize that so promptly in the friction surface zone of friction ring cooling bath is set, their structure is, at least constitute at least one throttle position on a part of length of its extension, it has mainly been determined can be by the cooling liquid volume of conduit circulation.This conduit is so structure setting for this reason, and promptly they guarantee to form a connection between the outer diameter of friction ring or excircle and inner diameter or inner circumference.That is these conduit radial outward are gone and are radially gone inwardly all to open wide.Particularly advantageous mode is that the structure setting like this of at least one throttle position is promptly its region memory flowing at a vortex.These are positioned at the groove zone outside the throttle position, should so be provided with regard to its width and the degree of depth, promptly have flowing of laminar flow at least basically herein.

By cooling bath or the cooling channel that structure of the present invention is provided with and arranges, can realize a special direct cooling action when continuing to skid to the friction surface that is in contact.Just can desirable cooling of realization in the whole service scope of corresponding fluid dynamic torque torque-converters to the throttling action of cooling liquid volume stream by the present invention according to the pressure difference between the chamber of the piston both sides that are arranged on torque-converters overlap joint clutch.Organization plan of the present invention has special advantage, in the zone of throttle position,, then produce a quite high pressure and descend, in contrast owing to the swirl flow that exists herein, in remaining groove zone, these flow losses are to owing to exist big relatively flow cross but very little.In the prior art that beginning is mentioned, this groove is so to be provided with, and promptly mainly has one along the laminar flow throttling on its total length in them.Under this throttling action, volume flow increases along with pressure is linear, in other words, increases along with the pressure difference between two chambers of overlap joint clutch is linear.Under according to eddy current throttling situation of the present invention, volume flow is to increase with the pressure or the pressure difference that exist according to a radical function.This just means that the throttling action of a swirling flow is more favourable, because in fact have a bigger volume flow on the pressure range that whole fluid torque converter occurs and under the pressure that maximum allows.

Use by the present invention and to have the throttle position that is in a ratio of relative smaller length with the conduit total length, the distortion that causes in the time of can also making the machining error of the machining error of pad conduit (width and the degree of depth) and piston and opposed friction surface and operation in addition is less or reduce to minimum to the influence maintenance of the flow resistance of pad conduit.Because oil viscosity descends along with the increase of temperature, by throttle position of the present invention, just can realize the temperature that increases in addition along with cold oil, reach a bigger volume flow and better cooling action according to this.That is the flow resistance of this throttle position or pad conduit is along with increasing of oil temperature descends.But the oil volume that this positive-effect itself must be limited in hope by the setting of throttle position corresponding structure quantitatively, because under excessive flow situation, the pressure in the closed cavity of overlap joint clutch just no longer can keep.

Particularly advantageous can be that the throttling action of cooling medium is arranged in the arrow path, in other words, has the channel part of the weak point of the mobile inlet of sharp corner angle and/or the outlet of flowing.Just can guarantee the Turbulence Flow of a no problem according to this, like this, flow resistance only always depends on the width and the degree of depth of arrow path or throttle position with linear mode.As situation described in the prior, have under the mobile long-channel situation of base layer stream, flow resistance becomes 4 times the power dependence with hydraulic radius or diameter.This means that the error of groove size influences flow resistance very consumingly.

Conduit or passage can so be arranged in the friction surface of friction ring or friction pad, that is, this friction surface constitutes an in fact continuous ring zone in outside radially, this zone only by these radially or the throttling passage of diagonally extending interrupt.The groove zone or the passage area that are provided with in radially the inside of this annular region have than the obvious bigger cross section of throttling passage cross section, therefore, compare with the flow resistance that exists in throttling passage in these zones, only have a very little flow resistance.That is the major component of the whole flow resistance of this cooling bath is present in the zone of throttle position or throttling passage.

This throttle position preferably is placed in the diameter place, outside of overlap joint clutch or friction ring, because like this, the extruding force or the closing force of overlap joint clutch just can enlarge.This be owing to, on the largest portion that radially extends of the friction surface that is in contact, exists one to drop on the obvious lower stress level by throttling, therefore, closing force just can correspondingly enlarge.

Particularly advantageously in addition be, this throttle position is so settled, and promptly it always is arranged in a support region of friction surface, and like this, this throttling action just can not be avoided by a slot between pad surface and opposed friction surface.Can be about this point especially referring to Fig. 7 and 8.As long as remaining pad area that wherein is provided with the passage segmentation of big relatively cross section is not fully to rest on the counter surface and therefore cause overflow, then total fluid resistance drops on the degree that influences performance with regard to unlikely, because one of whole throttling action very fraction is only born in the passage segmentation of She Zhiing herein.Preferably cool off oil groove or passage and be dark relatively structure setting, therefore the machining error of pad and layout just reduce to minimum to the influence of flow resistance.This passage leading should so be realized,, does not have immobilising dead zone that is.This conduit that is provided with in friction surface or friction pad can constitute in punching out.

The length of a throttle position with advantageous manner can 2 and 8mm between the order of magnitude in, be preferably 3 and 5mm between the order of magnitude in.

Can be positioned at the order of magnitude of 3: 1 and 8: 1 in the channel region of length and the cross section ratio between the throttle position, be preferably in the order of magnitude of 4: 1 and 6: 1 with big cross section.But can be bigger and less ratio according to applicable cases.

The present invention proposes a kind of friction ring in the wet operation clutch that is applied in, and be used in particular for the overlap joint clutch of a Hydrodynamic rotating moment convertor, wherein, this friction ring has the friction surface of at least one band excircle and inner circumference, the cooling groove is set in the zone of friction surface, they guarantee to form a linkage structure between excircle and inner circumference, it is characterized in that: this conduit constitutes a throttle position at least on its a part of extended length, and it has been determined can be by the mobile cooling liquid volume of conduit.

This throttle position is configured to and is suitable for flowing of a swirling flow; And remaining groove zone is configured to and is suitable for flowing of a base layer stream.

The length of throttle position 2 and 8mm between the order of magnitude in, be preferably in 3 to 5mm the order of magnitude.

Be positioned at the order of magnitude between 3: 1 and 8: 1 in the long zone of the conduit with big cross section and the cross section ratio between the throttle position, be preferably in the order of magnitude between 4: 1 and 6: 1.

This throttle position is to constitute by a depression with jitty shape of the mobile inlet of sharp corner angle and/or the outlet of flowing.

At least one throttle position is arranged on the excircle of friction ring.

This friction ring is equipped with a plurality of radially that extend and circumferential throttle position that originate in excircle, they carry out the transition to the conduit segmentation of along the circumferential direction extending, and this segmentation position inside radially is connected with a discharge section of opening wide towards friction ring inward flange direction.

This throttle position carries out the transition to upwards the limit and that along the circumferential direction extend the outside conduit segmentation in a footpath, this segmentation is connected with a groove segmentation the inside and that extend at circumferencial direction by the groove segmentation of radially extending, and the groove segmentation that this circumferencial direction extends feeds one and discharges in the section.

The conduit segmentation of extending at circumferencial direction is a symmetrical placement with respect to the throttle position (seeing in a circumferential direction) that correspondence is provided with.

See diametrically and the opposite opposed discharge cross section (Abflu β querschnitt) of throttle position.

A plurality of throttle position that distribute on the friction ring circumference are set, and they carry out the transition to along the circumferential direction in the groove segmentation of zigzag or tortuous waveform leading.

This conduit has at least two turnovers.

With respect to the surface area that exists between friction ring excircle and inner circumference, this surface portion that is occupied by conduit is in 30% to 60% the order of magnitude, is preferably in 40% to 50% the order of magnitude.

The invention allows for a kind of friction ring, it is the composition member of the overlap joint clutch of a Hydrodynamic rotating moment convertor, wherein, this torque converter has a housing, wherein, a ccontaining pump impeller, a turbine, guide wheel and overlap joint clutch, this overlap joint clutch has a ring piston, be equipped with the chamber that a usable oils is full of respectively in its both sides, this annular piston supports at least one friction surface, it can place with an opposed friction surface and become rubbing contact, simultaneously, in radially the inside of friction surface and constitute between ring piston and the member that is loaded with opposed friction surface this first chamber and at least one friction surface by one according to above-mentioned friction ring formation, wherein by the conduit that in friction ring, is provided with and at friction surface axially by the situation of putting under, can form an oil flow owing to the pressure difference that between two chambers, exists.

In the zone of throttle position, should the pressure difference between two chambers have 60% to 80% approximately, be preferably 70% to 80% and fallen.

This throttle position and the chamber arranged adjacent that when the overlap joint clutch is closed, has elevated pressures.

This conduit is made by punching out processing or cutting in friction ring.

The organization plan that meets purpose that the present invention is other can be by drawing in dependent claims and the following description of drawings.

Describe the present invention in detail by accompanying drawing 1 to 11.Wherein:

Fig. 1 is the device sectional view that has wet operation clutch by, and it has friction ring of the present invention;

Fig. 2 is a friction pad partial view that requires setting according to invention;

Fig. 3 is the cross section enlarged view of III along the line among Fig. 2;

Fig. 4 is the sectional view of IV along the line among Fig. 2;

Fig. 5 requires configuration throttle position attainable diametrically a pressure distribution situation according to invention by the present invention in the friction surface zone or in the groove;

Fig. 6 is a diagram that is used to set forth the effect that improved groove structure is provided with;

Fig. 7 and 8 is the constructional variant schemes that are used for friction pad; With

Fig. 9 to 11 is other organization plans of cooling channel or cooling bath.

The device of describing in Fig. 11 has a housing 2, its ccontaining Hydrodynamic rotating moment convertor 3.This housing 2 can be connected with a live axle, this live axle can by an internal combustion engine output shaft for example crankshaft constitute.Antitorque connection between live axle and housing 2 can realize by a drive plate, and it radially can be connected with live axle the inside, radially the outside can with 2 antitorque connections of housing.Such drive plate is for example open by JP-POS 58-30532.

Housing 2 constitutes by a housing alms bowl 4 adjacent with internal-combustion engine in other words with live axle and another fixing on alms bowl 4 housing alms bowl 5.These two

housing alms bowls

4 and 5 are sealedly and fixedly connected mutually by welded structure 6 outside radially.In this embodiment, for constituting the outer alms bowl body of pump impeller 7, housing alms bowl 5 directly can be drawn and use.For this reason, blade 8 is fixed on the housing alms bowl 5 with known manner.This housing alms bowl 5 is planted on the regional 4a of limit sleeve shape outside the housing alms bowl 4 in the axial direction.Axially go up a turbine 10 is set between the radial wall 9 of pump impeller 7 and housing 4, it is fixed with power wheel hub 11 or rigidity is connected antitorquely, and this wheel hub 11 can be done antitorque the connection by an interior toothing with a transmission device input shaft.Axially go up between the zone, radially the inside of pump impeller and turbine a guide wheel 12 is set.This housing alms bowl 5 has a sleeve shape inside radially wheel hub 13, it is rotatable and is placed on the housing of a transmission device hermetically.In the inner chamber 14 that constitutes by two

housing alms bowls

4,5, an overlap joint clutch 15 is set in addition, it requires to settle abreast with torque converter 3 according to the mode of action.This overlap joint clutch 15 can be realized a torque clutch between power wheel hub 11 and drive shell alms bowl 4.But set up the damper 16 that an elasticity is rotated by the mode of action in the series of overlap joint clutch 15, it is between the annular piston 17 and power wheel hub 11 that are arranged on overlap joint clutch 15 under the present embodiment situation.But the damper 16 that should elasticity rotates comprises with known manner and forms helical spring power storage.This is arranged on radially in the axial direction, and radially the inside of the annular piston 17 between the wall extension 9 and turbine 10 is placed on the power wheel hub 11 axially can make restricted mobile mode.This annular piston 17 is divided into one first chamber 18 with inner chamber 14, and it is axially gone up at annular piston 17 and radially constitutes the inside that also is positioned at the rubbing contact district 19 that overlaps clutch 15 diametrically between the shell body wall 9; Also be divided into one second chamber 20, wherein ccontaining pump impeller 7, turbine 10 and guide wheel 12.

The perimeter radially of an annular of these housing alms bowl 4 usefulness constitutes a friction surface 21, and it can place with friction pad 22 and be in rubbing contact, and this pad 22 is being supported by the annular region 23 of piston 17.

In the newer for example driving section plan of establishment of a Motor Vehicle that is used for, the operation of skidding in (Stromungswandler) of fluid torque converter most of at least operation area of this overlap joint clutch produces the wasted power of a hot form in the stage rubbing contact district 19 of skidding simultaneously.It may be very high when the running state of determining and can reach several kilowatts.This running state for example occur in the mountain area transportation of band trailer and converter clutch with non-overlapping in the change procedure of reality overlap joint state.This operation plan of establishment with torque-converters overlap joint clutch of the effect of skidding was for example proposed by German patent application P4328182.6.

For avoiding in the rubbing contact district 19 to produce unallowed high temperature and for the damage on the surface of friction pad at least that stops so cause and prevent that a part is present in the destruction of oil in the inner chamber 14, under the present embodiment situation, be provided with the tank structure that is arranged in friction pad 22 or the device of passage 24, by this device, even under the actual closed situation of overlap joint clutch, can between second chamber 20 and first chamber 18, realize a continuous oil stream.This oil stream passes through the friction surface 22a and friction surface 21 leadings of friction pad 22 simultaneously.This oil duct 24 can on purpose be done the optimization setting with regard to its structure shape, that is, in zone 19, realize the member of rubbing contact and the fluid that flows through between can realize a good heat exchange.The organization plan of a preferred passage 24 will be described in detail in conjunction with Fig. 2 to 4.

End that radially extends in the outside arrangement of this passage 24 and chamber 20 are connected and are connected with chamber 18 with its end that radially extends in the inside arrangement.Under overlap joint clutch 15 situations of closure, this cold oil stream flows in the chambers 18 by passage 24 and therein towards the Radial Flow of rotating shaft 25.

This then cold oil stream can for example discharge and preferably at first enter in the oil cooler by quill shaft or by a passage to this setting in the zone of power wheel hub 11.Oil comes out to send in the oil groove from this oil cooler and is sent to again from here in fluid power adjusting or the control loop.

Describe the friction pad 22 of a ring in Fig. 2 with local mode, it can be applied in the torque-converters overlap joint clutch of Fig. 1.This friction pad 22 is equipped with the groove or the pouch 26 of distribution on circumference, it constitutes the connecting passage 24 between two

chambers

18 and 20.

This friction pad 22 has an excircle or outer diameter 27 and inner circumference or inner diameter 28.Shorter segmentation 29 with the passage 24 that outer diameter 27 is connected with inner diameter 28 constitutes a throttle position or throttling venturi 30.The segmentation 29 of this passage 24 be simultaneously radial location and along this radially carry out the transition to inward along the circumferential direction extend and be positioned at passage segmentation 31 diametrically than the outside, it again the turning 32 by hair fastener shape structure carry out the transition to the footpath and upwards continue the passage segmentation 33 that circumferencial direction extends that is similarly settled in the inside.This passage segmentation 33 is connected with an outlet area 34 that radially goes towards the inside to open wide, and it is used for the cooling medium of passage passage 26 guidings.Passage area that this connects on throttle position 30 or passage segmentation 31,32,33 and 34 is structure like this settings with respect to the cross section of throttle position 30 with regard to its cross section, promptly in them, in fact mainly there is a kind of Laminar Flow even between two

chambers

18 and 20 of Fig. 1 device, occur under the maximum pressure difference situation.In the zone of throttle position 30, and when the device run duration of Fig. 1 and rubbing contact, in fact always deposit flowing of a kind of vortex at overlap joint clutch 15.This passage 24 that is so structure setting, promptly not resemble the known technology be to determine by the flow resistance that works on the total length of passage to the volume of coolant that flows through by it (flow), but mainly by throttle position or throttling venturi 30 region memories resistance determine.As being found out by Fig. 2, this passage that extends in a circumferential direction 31 and 33 has segmentation 35,36 in addition, and their relative throttle position 30 are extended on different sense of rotation.This segmentation 35,36 is simultaneously observed in a circumferential direction, is symmetrical placement with respect to throttle position 30.

As finding out from Fig. 2 to 4, the extended length of throttle position 30 29 is one of passage 24 total lengths fraction very just.For external friction diameter 27 be 180 and 260mm between the order of magnitude general wet operation clutch or the overlap joint clutch 15 physical dimension, the length 29 of throttle position 30 according to applicable cases can be designed as 2 and 8mm between, be preferably in 3 and 5mm between.

The flow cross of this throttle position 30, the flow cross of the groove segmentation 31,32,33,34 that is connected with outlet side in this corresponding throttle position 30 is compared, and little a lot of times.Simultaneously this ratio can be arranged in 1: 3 to 1: 10 the order of magnitude.But for most applications, this ratio is just enough between 1: 4 and 1: 6.

Because the obvious bigger flow cross of passage segmentation 31,32,33,34 just can be guaranteed, a Laminar Flow in fact always mainly takes place in these segmentations in other words.

For desirable vortex motion of realization in by the zone of the recessed throttle position that constitutes 30 of jitty shape, according to the purpose requirement, the cross section in the entrance region of throttle position 30 is the structure of sharp corner angle at least.Under embodiment's situation that Fig. 2 shows, this throttle position 30 carries out the transition to one and the groove zone 31 corresponding structures of slick and sly expansion gradually at outlet side.But requiring according to purpose can be that the cross section transition of sharp corner angle is set between passage segmentation 31 and throttle position 30.

This can be preferably between 40% to 55% between 30% and 65% the order of magnitude for the surface area that exists between outer diameter 27 and the inner diameter 28 owing to the surperficial occupied surperficial share of conduit or passage 24 needs.Under the embodiment's situation according to Fig. 2, this share is about 50%.

This throttle position 30 is so structure setting preferably, promptly by this throttle position, makes the about 60% to 85% of the Maximum differential pressure that occurs between two

chambers

18 and 20, is preferably 75% to 80% maximum pressure differential and is fallen.This just means, soon, the pressure that exists in passage segmentation 31 is only also than the pressure in the chamber 18 high about 15% to 40% in other words 20% to 30% after throttle position 30 or after throttle position 30.This mode of action based on throttle position 30, according to the purpose requirement, as shown in Figure 2, these throttle position are placed on the outer region or outer radius of friction ring 22, that is on the zone of elevated pressures, because like this at friction surface 21, set up in the zone of 22a and can keep less with the pressure of the clossing pressure adverse effect of overlap joint clutch 15.Therefore, just can have the cooling channel and a corresponding overlap joint clutch of volume of coolant by overlap joint clutch 15 corresponding to a transferable torque of pressure difference that is present between two

chambers

18 and 20 greater than known so far.And, torque transmitted capacity minimizing in the time of just can making overlap joint clutch 15 corresponding to a given pressure difference between two

chambers

18 and 20 by radially moving inward to the single throttle position 30 of major general.

Can know that by Fig. 5 throttle position 30 layout diametrically is to the influence of transferable torque.In Fig. 5 left side housing alms bowl 4 and piston 17 these part areas that have friction pad 22 fixing on it have been described with magnification ratio.Possible idealized pressure diagram has been described when the configuration variation of the fooled throttle position in the radially elongated area of friction pad 22 on the right side of Fig. 5.Corresponding to one given in chamber 20 be higher pressure P 1 and one given in chamber 18 under lower pressure P 2 situations, in the radially extension of friction pad 22, observe, and when throttle position 30 is configured in radially the outside (situation as shown in Figure 2), in the friction surface 22a of friction pad 22 and the zone between the friction surface 21, may in passage 24 pressure distribution of describing according to dot and dash line 37 then.Can draw according to this tracing 37, in the zone of throttle position 30, the nearly pressure difference that exists between P1 and P2 80% has been fallen.Therefore, just less relatively in pressure Pa that exists near the outlet side of throttle position 30 and the difference between the pressure P in chamber 18 2.When throttle position 30 being configured in radially the inside that is Fig. 2 in the zone of outlet section 34, then in contact area 19, produce a pressure distribution according to dotted line 38.According to two

curves

37 and 38 as can be seen, corresponding to a definite pressure difference between two

chambers

18 and 20, should by being configured on the different diameters, throttle position 30 can control (influence) by the 15 transferable torques of overlap joint clutch.By throttle position 30 being configured in radially outside, then, for overlap joint clutch so far, just can reduce with the cold oil stream between two

chambers

18 and 20 in order to transmit a necessary pressure difference between two

chambers

18 and 20 of definite torque.According to the number and the structure shape of throttle position 30, the circulation width of such throttle position 30 can 0.4 and 2.5mm between the order of magnitude in, be preferably 0.5 and 1.5mm between the order of magnitude in.And the degree of depth of groove 26 can 0.2 and 1mm between the order of magnitude in, be preferably in 0.3 and 0.7mm between the order of magnitude in.The degree of depth of this groove 26 can be actual identical on its whole extended length.But this groove 26 can also have the zone of different depth.Favourable mode can be that a bigger degree of depth is set in the special transition region between throttle position 30 and all the other groove segmentations 31 in the zone of throttle position 30 and in case of necessity.This point has been done to represent with the dot and dash line of numbering 30a in Fig. 3.That is can be advantageously, obtain the flow cross of a hope for making throttle position 30, be provided with at this throttle position place than other the groove zone slightly deeply some so that compensate the structure of width narrow slightly (little) herein.Just can guarantee that according to this throttle position of throttle position 30 has reduced the dependence of the wearing and tearing of friction pad 22, because described wearing and tearing will cause the minimizing of the cross section of throttle position 30.

Like this, according to the present invention, volume of coolant stream in wet operation clutch can be regulated by a throttle structure 30, simultaneously, in the friction surface of leaving over (streamwise observation) and after corresponding throttle position 30 passage of growing relatively can be set, they have as far as possible little flow resistance and a big heat exchange surface.

Be illustrated in the pressure difference P1-P2(△ P between two

chambers

20 and 18 on the axis of abscissas in Fig. 6).The volume flow that expression is regulated according to the pressure difference that exists on axis of ordinates.

Volume flow on the slot length that is provided with in friction pad is under the throttling action situation of laminar flow, then has an in fact linear relation between pressure difference on the groove and volume flow.This pass ties up among Fig. 6 and represents by straight fine line.As the pressure difference on the groove, be interpreted as in the pressure of suction side and the difference between the outlet side pressure at respective grooves or a plurality of grooves.During being provided with, the prior art that in fact the laminar flow throttle structure of this form can be mentioned from the outset that is the groove structure of US-PS4969543 and 5056631 know.In this prior art, the part of the throttling action of laminar flow is about 70% of total throttling action of realizing in the passage.

This dotted line has then been described attainable volume flow, and it can be realized by the throttling action of turbulent flow of the present invention.The volume flow curve of the pressure difference between two

chambers

20,18 of this foundation is consistent with the change curve of a radical function basically.This dotted lines curve can by groove structure of the present invention particularly the groove structure of Fig. 2 realize.As can be seen from Figure 6, can provide a ratio big volume flow under laminar flow throttling situation under the throttling action situation of less pressure difference and eddy current especially.This point when between two

chambers

20 and 18 for less pressure difference and to locate to provide a big as far as possible volume flow at locking (Lock-up) be particularly advantageous when guaranteeing cooling action as well as possible.

Two corresponding groove structures of characteristic line are so to be provided with among this and Fig. 6, and promptly they give the △ Pmax that determines earlier for one identical volume flow can be provided.This △ Pmax under general fluid torque converter situation with overlap joint clutch be 7 and the 10bar(crust) between the order of magnitude in.But this △ Pmax can also be positioned on this bandwidth or under.

The groove structure that is used for a cold oil of setting of the present invention or passage can also reduce the dependence of temperature convection amount in addition by these passages, and this is because descend in main throttling action that is main pressure at relative region memory than short throttle position.Groove structure in the throttle position zone only provides the flow or the volume flow of linear relation, therefore, guarantees a dependence less to gemoetric error.Under the prior art groove structure situation of mentioning in front, the major component of throttling is a layer flow mode and on the whole length of groove.Under this throttling action situation, the groove height allows the flow or the volume flow of bipyramid relation.Therefore produce strong and the relevant dependence of gemoetric error pad or the groove structure.In addition, because the throttling action of the laminar flow that exists, also make volume flow produce the dependence of strong and viscosity cooling medium or a temperature correlation.

Always guarantee its throttling function for assurance groove structure of the present invention, must a friction pad device 22 be set on the opposed friction surface 21 and in the zone in throttle position.It should be able to guarantee at least, in the zone of throttle position and when running state not occurring, to split a slot in other words this slot should preferably not be not more than 0.01mm greater than 0.03mm.This slot can form based on the inadequate parallelism that exists between the friction surface that can place contact.

For guaranteeing to be in all running statees of contact at friction surface, the favourable mode of these throttle position 30 its functions of performance is that the friction pad 22 corresponding with Fig. 7 is by a member, that is ring piston 17 supports.

In Fig. 7 and 8, described to have the part zone of the housing alms bowl 4 and the piston 17 of fixing friction pad 22 in the magnification ratio mode.Described the structure setting of piston 17 in Fig. 7, it shows that in fact piston is in stand under load that is state unloading.This piston-shaped corresponding to the pressure that in fact exist to equate in 20 at two chambers 18 or the situation when only being a relative less pressure difference.Unloaded state at piston 17, the regional 17a of the ccontaining friction pad 22 of this outside does structure setting like this, promptly, the friction surface 22a of friction pad 22 and the friction surface 21 of housing 4 are at their the air slot 39 that comprises a wedge shape, its radially extends toward the inside and φ with an angle, it can be preferably the order of magnitude at 1 ° of angle in 0.5 ° to 3 ° the order of magnitude.

Described the position of piston 17 in Fig. 8, it shows that making piston be in a chamber 20 compares chamber 18 for to give under the fixed excess pressure situation.This excess pressure can be in the order of magnitude between 4 and 8, and according to the maximum overpressure of hope, this piston 17 must correspondingly be the elastic structure setting simultaneously.

As knowing from Fig. 7 and 8 common observations, when the pressure between two

chambers

18 and 20 equates or when being small pressure difference, this friction pad 22 only is in rubbing contact by the annular friction surface segment 40 of outside radially with friction surface 22, is provided with throttle position 30 in segmentation 40.Just can guarantee according to this, be that less pressure difference has been that this throttle position 30 is still brought into play its function under less overvoltage (for example 1 crust) situation in other words in chamber 20 between two chambers 18 and 20.Along with the overvoltage of chamber 18 increases relatively in chamber 20, the configuration state that this piston 17 is just described from Fig. 7 is deformed to the location status of describing among the figure.According to this, wiping contact area between surface 21 and the 22a in friction increases the angle φ that exists in other words gradually and becomes littler between friction surface 21 and 22a.And throttle position 30 is also guaranteed the control fully to the cooling liquid volume in addition.

Friction pad of describing in Fig. 2 or friction ring 22 are integral structures.But it also can be assembled by the fan-shaped pad bulk-breaking of putting arrangement on circumference by a plurality of.

Friction pad 122,222,322nd in Fig. 9 to 10, and local mode is described, and they are provided with conduit or the passage that the present invention proposes.

According to the friction pad of Fig. 9 to 11 common be to have throttle position 130,230,330, they are distributed on the circumference of friction pad.These throttle position 130,230,330 major decisions volume flow, it can flow by passage 124,224,324.This is connected to throttle position 130,230, and the passage segmentation on 330 has one than throttle position 130,230, and therefore 330 obvious big flow cross mainly exist flowing of a kind of laminar flow in these passage segmentations.Therefore the flowing velocity in these passage segmentations 124,224,324 then is significantly less than in throttle position 130,230, the flowing velocity in 330.According to this, can also between cooling medium flowing or cold oil and adjacent member, realize a desirable heat exchange.

In the organization plan of Fig. 9, this friction pad 122 has a circular groove 131 that is connected with throttle position 30, and itself is connected with a plurality of radial grooves 132 that extend inward again.The friction surface of this friction pad 122 is to be made of the protuberance 132a and the ring uplift 122a in the fringe region of friction ring 122 that exist between each groove 132, and this ring uplift 122a is divided into the segmentation that single fan is opened by throttle position 130.

Has the depression 231 of a plurality of annulars according to the friction pad 222 of Figure 10,231a, 231b, their groove zones 232,232a and interconnecting by radially extending.This directly upwards the circular groove of the inside zone 231b then radially open wide inwardly by radial slot zone 232b.These radial slot zones 232,232a and 232b are so to be misplaced mutually at circumferencial direction, that is, make the oily streams that flow by passage 24 will have turning to repeatedly.

In the embodiment of describing in Figure 11, this passage 324 is arranged in circumferencial direction and is connected on the throttle position 330 in tortuous waveform mode.Therefore, because the just good heat exchange of formation between cold oil and adjacent member or adjacent friction surface of the surface of these passage 324 tortuous wave regions and length.

According to another organization plan of the present invention, the cooling bath that should require be provided with according to invention is not arranged in the friction pad 22, and is arranged in the zone of friction surface 21 of housing 4.Yet these grooves can form by punching out in sheet material.In radially outside and radially the inside, the groove of these punching out must so constitute, and promptly they open wide towards the direction of chamber 18 and 20.In addition, this friction pad 22 can also be can't help piston 17 supporting, and is fixed on the housing 4.In addition, friction pad 22 can be with an intermediate plate supporting, several embodiments' situation in the prior art of having carried as the front.Cooling channel of the present invention in addition can be directly in the material that constitutes piston 17 punching out form, these friction pad 22 usefulness housings 4 or an intermediate plate support simultaneously.

Conduit that these are provided with in a friction pad or friction ring or passage can constitute in when pad of creating friction, that is made before for example on ring piston or the plate before friction pad being fixed on the support member.But these conduits, ditch is recessed or passage can also for example be processed at this friction pad by bonding friction pad being placed on the support member or after a kind of like this steady job during fixing.That is this friction pad for example 22 among Fig. 2 at first be fixed on the ring piston 17 and during this is fixing or after this in friction ring 22 punching out go out passage 24.It is finished by stamping tool, and this instrument should have corresponding type exterior feature certainly.

The present invention is not limited on that describe and embodiment explanation, but also comprises all modification, promptly they can be particularly by single and in conjunction with described feature of different embodiments or assembled scheme that element and functional mode constituted.

The applicant is the other protective right in the disclosed feature that belongs to the invention essential meaning in specification only so far of beachhead demand in addition.

Claims

1, a kind ofly is applied in a friction ring in the wet operation clutch, and be used in particular for the overlap joint clutch of a Hydrodynamic rotating moment convertor, wherein, this friction ring has the friction surface of at least one band excircle and inner circumference, the cooling groove is set in the zone of friction surface, they guarantee to form a linkage structure between excircle and inner circumference, it is characterized in that: this conduit constitutes a throttle position at least on its a part of extended length, and it has been determined can be by the mobile cooling liquid volume of conduit.

2, by the described friction ring of claim 1, it is characterized in that: this throttle position is configured to and is suitable for flowing of a swirling flow; And remaining groove zone is configured to and is suitable for flowing of a base layer stream.

3,, it is characterized in that by claim 1 or 2 described friction rings: the length of throttle position 2 and 8mm between the order of magnitude in, be preferably in 3 to 5mm the order of magnitude.

4, by one of claim 1 to 3 described friction ring, it is characterized in that: be positioned at the order of magnitude between 3: 1 and 8: 1 in the long zone of the conduit with big cross section and the cross section ratio between the throttle position, be preferably in the order of magnitude between 4: 1 and 6: 1.

5, by one of claim 1 to 4 described friction ring, it is characterized in that: this throttle position is to constitute by a depression with jitty shape of the mobile inlet of sharp corner angle and/or the outlet of flowing.

6, by one of claim 1 to 5 described friction ring, it is characterized in that: at least one throttle position is arranged on the excircle of friction ring.

7, by one of claim 1 to 6 described friction ring, it is characterized in that: this friction ring is equipped with a plurality of radially that extend and circumferential throttle position that originate in excircle, they carry out the transition to the conduit segmentation of along the circumferential direction extending, and this segmentation position inside radially is connected with a discharge section of opening wide towards friction ring inward flange direction.

8, by the described friction ring of claim 7, it is characterized in that: this throttle position carries out the transition to upwards the limit and that along the circumferential direction extend the outside conduit segmentation in a footpath, this segmentation is connected with a groove segmentation the inside and that extend at circumferencial direction by the groove segmentation of radially extending, and the groove segmentation that this circumferencial direction extends feeds one and discharges in the section.

9, by claim 7 or 8 described friction rings, it is characterized in that: the conduit segmentation of extending at circumferencial direction is a symmetrical placement with respect to the throttle position (seeing in a circumferential direction) that correspondence is provided with.

10, by one of claim 7 to 9 described friction ring, it is characterized in that: see diametrically and the opposite opposed discharge cross section (Abflu β querschnitt) of throttle position.

11, by one of claim 1 to 6 described friction ring, it is characterized in that: a plurality of throttle position that distribute on the friction ring circumference are set, and they carry out the transition to along the circumferential direction in the groove segmentation of zigzag or tortuous waveform leading.

12, by aforementioned claim described friction ring one of at least, it is characterized in that: this conduit has at least two turnovers.

13, by one of claim 1 to 12 described friction ring, it is characterized in that: with respect to the surface area that between friction ring excircle and inner circumference, exists, this surface portion that is occupied by conduit is in 30% to 60% the order of magnitude, is preferably in 40% to 50% the order of magnitude.

14, a kind of friction ring, it is the composition member of the overlap joint clutch of a Hydrodynamic rotating moment convertor, wherein, this torque converter has a housing, wherein, a ccontaining pump impeller, a turbine, guide wheel and overlap joint clutch, this overlap joint clutch has a ring piston, be equipped with the chamber that a usable oils is full of respectively in its both sides, this annular piston supports at least one friction surface, it can place with an opposed friction surface and become rubbing contact, simultaneously, in radially the inside of friction surface and constituting this first chamber and at least one friction surface between ring piston and the member that is loaded with opposed friction surface by a friction ring formation according to claim 1 to 13, wherein by the conduit that in friction ring, is provided with and at friction surface axially by the situation of putting under, can form an oil flow owing to the pressure difference that between two chambers, exists.

15, by the described friction ring of claim 14, it is characterized in that: in the zone of throttle position, should the pressure difference between two chambers have 60% to 80% approximately, and be preferably 70% to 80% and fallen.

16, by one of claim 14 to 15 described friction ring, it is characterized in that: this throttle position and the chamber arranged adjacent that when the overlap joint clutch is closed, has elevated pressures.

17, by one of claim 1 to 16 described friction ring, it is characterized in that: this conduit is made by punching out processing or cutting in friction ring.