CN103133557A

CN103133557A - Parallel dual clutch device and method for operating same

Info

Publication number: CN103133557A
Application number: CN2012104371406A
Authority: CN
Inventors: H·J·毫科
Original assignee: BorgWarner Inc
Current assignee: BorgWarner Inc
Priority date: 2011-11-10
Filing date: 2012-11-05
Publication date: 2013-06-05
Anticipated expiration: 2032-11-05
Also published as: DE102012017955A1; CN103104631B; CN103104631A; DE102012017951A1; CN103133557B

Abstract

The invention relates to a parallel dual clutch device which is arranged between a transmission unit and speed changing devices in a transmission train of a motor vehicle, wherein the parallel double clutch device is provided with a first sheet type clutch which matches with and belongs to an input shaft of a first speed changing device and a second sheet type clutch which matches with and belongs to an input shaft of a second speed changing device. The first sheet type clutch is provided with a first sheet group which is used for fulfilling a manipulating function by using a first manipulation element and used for transmitting torque selectively between the transmission unit and the input shaft of the first speed changing device. The second sheet type clutch is provided with a second sheet group which is used for fulfilling a manipulating function by using a second manipulation element and used for transmitting torque selectively between the transmission unit and the input shaft of the second speed changing device. A first manipulation unit runs through multiple concaved parts of clutch sheets of the second sheet group along the axial direction and extends to the first sheet group. The invention also relates to a method for operating the parallel dual clutch device.

Description

Parallel double engaging and disengaging gear and the method that is used for this type of parallel double engaging and disengaging gear of operation

Technical field

the present invention relates to the parallel double engaging and disengaging gear between gear unit and speed changer for the power train that is arranged in motor vehicle, this parallel double engaging and disengaging gear has attaches troops to a unit in first lamella clutch of first transmission input shaft and attaches troops to a unit in second lamella clutch of second transmission input shaft, this the first chip clutch appliance has a first group (Lamellenpaket), can handle by means of first actuating element, be used for optionally carrying out the moment of torsion transmission between this gear unit and this first transmission input shaft, this second lamella clutch has second group, can handle by means of second actuating element, be used for optionally carrying out the moment of torsion transmission between this gear unit and this second transmission input shaft.The invention still further relates in addition a kind of method for this type of parallel double engaging and disengaging gear of operation.

Background technique

By EP 1 568 906 A1, the parallel double engaging and disengaging gear of a kind of power train for being arranged in motor vehicle between gear unit and speed changer described.This known two engaging and disengaging gear have first lamella clutch of attaching troops to a unit in first transmission input shaft, and this first chip clutch appliance has a first group, can handle by means of first actuating element, be used for realizing optionally moment of torsion transmission between this gear unit and this first transmission input shaft.In addition, this known two engaging and disengaging gear have second lamella clutch of attaching troops to a unit in second transmission input shaft, and this second lamella clutch has one second group, can handle by means of second actuating element, be used for realizing optionally moment of torsion transmission between this gear unit and this second transmission input shaft.

This known two engaging and disengaging gear have been proved to be effectively, yet are needing improvement aspect its structure, and this known two engaging and disengaging gear need to occupy larger structure space in addition.。

Summary of the invention

Basic purpose of the present invention is, proposes a kind of parallel double engaging and disengaging gear with compact especially structure.In addition, basic purpose of the present invention also is, provides a kind of favourable method and is used for this type of parallel double engaging and disengaging gear of operation.

This purpose is to realize by the feature that provides in claim 1 or 15.The target that a plurality of favourable embodiment of the present invention is each dependent claims.

Parallel double engaging and disengaging gear of the present invention is designed to be arranged in the power train of motor vehicle between a gear unit and speed changer.This pair engaging and disengaging gear is two engaging and disengaging gear of a kind of wet type operation preferably, namely a kind of two engaging and disengaging gear that move in oil for example.This parallel double engaging and disengaging gear has first lamella clutch of attaching troops to a unit in first transmission input shaft, and this first chip clutch appliance has a first group, can handle by means of first actuating element, is used for optionally carrying out the moment of torsion transmission between this gear unit and this first transmission input shaft.In addition, this parallel double engaging and disengaging gear has second lamella clutch of attaching troops to a unit in second transmission input shaft, and this second lamella clutch has one second group, can handle by means of second actuating element, is used for optionally carrying out the moment of torsion transmission between this gear unit and this second transmission input shaft.Due to related be a kind of parallel double engaging and disengaging gear, these first and second groups are arranged to classification in the axial direction.According to the present invention, this first actuating element passes the depressed part in these sheets of this second group in the axial direction, extends to the first group of attaching troops to a unit in this first actuating element.On the contrary, first actuating element known by EP 1 568 906 A1 passes through this second group radially outwardly, in order to reach the first group of attaching troops to a unit in this first actuating element.Thus, parallel double engaging and disengaging gear of the present invention has compact especially structure, and wherein steering force directly transmits by this first actuating element.In addition, cancel known in EP 1 568 906 A1, piston that engage around this clutch, can obtain so the not only compactness of of the present invention pair of engaging and disengaging gear but also the structure of lightweight.

In a preferred implementation of parallel double engaging and disengaging gear of the present invention, this first actuating element is embodied as the depressed part of window type in the axial direction by these depressed parts that wherein extend.The special benefits of the depressed part of window type is, and is opposite with the entry of edge side, by the depression of these window types is set, makes inside and outside profile constant and can implement consistently.In this way, for example can be in the inside of this clutch-plate or the exterior contour place do not interrupted by depressed part, a coherent clutch-plate tooth section (Lamellenverzahnung) in a circumferential direction is set, its advantage is, might attach troops to a unit with one and carry out rotary synchronous engagement especially reliably in the clutch-plate tooth section of this clutch-plate support.

In one of parallel double engaging and disengaging gear of the present invention favourable mode of execution (it has formed an alternate embodiments of previous described mode of execution), these depressed parts are embodied as the entry of edge side.So the entry of these edge sides for example can be arranged on this inside or exterior contour place on these clutch-plates.At this preferably, these entries are embodied as the entry in a clutch-plate tooth section, particularly preferably are embodied as the extend radially section in the interdental spaces of a clutch-plate tooth section.As before illustrating, preferred although the depressed part of window type is set, yet the entry of edge side, especially be embodied as the entry in clutch-plate tooth section or/and be embodied as the entry of extending portion of the interdental spaces of clutch-plate tooth section and have the following advantages, namely they can be relatively simply be manufactured on clutch-plate when producing this clutch-plate tooth section simultaneously.Alternatively, in this embodiment, can also omit a plurality of teeth of clutch-plate tooth section, in order to the entry of these edge sides is provided, the first operating element be passed in the axial direction.

Parallel double engaging and disengaging gear of the present invention another preferred embodiment in, the input side of this first and second lamella clutch, namely the moment of torsion of gear unit is introduced in a side of this parallel double engaging and disengaging gear, formed by an outer clutch-plate support, and the outlet side of this first lamella clutch is to be formed and the outlet side of this second lamella clutch is formed by second an interior clutch-plate support by first an interior clutch-plate support.In following situation, this is favourable: on the transmission side of this pair engaging and disengaging gear, namely on the first and second transmission input shafts, be applied with less mass moment of inertia.In this embodiment, in addition further preferably, these depressed parts that the first actuating element passes wherein in the axial direction are implemented in the outer clutch-plate of second group.

In another favourable mode of execution of parallel double engaging and disengaging gear of the present invention, this first actuating element and this second actuating element have be used to compressing steering corresponding sheet group, identical.Being interpreted as at this for the steering that compresses the respective flap group is following direction (preferred axial direction): the first and second actuating elements must move up the party, first and second groups could be compressed and realize thus closing of the first and second lamella clutch.

Thereby in order to realize forcing spaced apart traction square in can reducing by the second lamella clutch with the interior clutch-plate adjacent one another are of depressed part or outer clutch-plate adjacent one another are when the second lamella clutch is opened, with interior clutch-plate depressed part, adjacent one another are or outside be provided with a plurality of clutch-plate dividing elements between clutch-plate.The clutch-plate dividing element is preferably flexible deformable clutch-plate dividing element.Under this background, can consider spring element for example, ripple spring or with the ring of ripple.In addition corresponding clutch-plate dividing element can be set between the inside adjacent one another are of this first group or outside clutch-plate.

Based on previously described mode of execution, in a particularly advantageous mode of execution of parallel double engaging and disengaging gear of the present invention, these clutch-plates with the window type depressed part have one be arranged in diametrically between these window type depressed parts and clutch-plate tooth section, consistently or the supporting section of sealing ground surrounding type in a circumferential direction, this clutch-plate dividing element can support or be thereon supported.As already mentioned above, due to the depressed part of these window types, can realize a kind of coherent, not affected by these window type depressed parts and clutch-plate tooth section with complete number of teeth.Due in addition in the axial direction arrange between these window type depressed parts and this clutch-plate tooth section and in a circumferential direction consistently or sealing the supporting section of surrounding type, further guaranteed, this clutch-plate dividing element above mentioned, that preferably be embodied as annular can support or be supported on this clutch-plate in the zone of the supporting section of this surrounding type.Also guaranteed thus, evenly and reliably will force spaced apart with the clutch-plate adjacent one another are of window type depressed part at the whole circumference of clutch-plate.In order to strengthen described advantage, this clutch-plate dividing element realizes between corresponding clutch-plate and this clutch-plate dividing element that in the support on the supporting section of this surrounding type an area of contact carries out, this area of contact formed area of contact between the supporting section of this clutch-plate dividing element and this clutch-plate more than 50%, more than 95% or 100%.In the end in described situation, wherein the area of contact between corresponding clutch-plate and this clutch-plate dividing element has formed 100% of area of contact between the supporting section of clutch-plate dividing element and this clutch-plate, so this clutch-plate dividing element only is supported on the supporting section of this clutch-plate and additionally is not supported on other sections of this clutch-plate, what guaranteed thus clutch-plate adjacent one another are especially reliably and uniformly supports and forces the interval.Point out in this, above mentioned area of contact is not to be necessary for forcibly a continuous area of contact, but described area of contact can be also to be combined into by a plurality of part area of contact that are spaced apart from each other.

In another favourable mode of execution of parallel double engaging and disengaging gear of the present invention, this first actuating element and this second actuating element are can be hydraulically powered.Thus in this embodiment, this parallel double engaging and disengaging gear is a kind of hydraulic operated parallel double engaging and disengaging gear.This first and second actuating element also can be called as the first and second application pistons.In this embodiment, more preferably, the first pressure chamber that the first actuating element is attached troops to a unit and loaded in an available hydraulic oil, and the second actuating element belongs to the second pressure chamber that an available hydraulic oil loads.So this first and second actuating element can be activated by the pressure that improves in the pressure chamber under corresponding.In this embodiment, more preferably, be provided be used to the spring element that makes the actuating element return.These spring elements are preferably helical spring, and they are supported on corresponding actuating element on the one hand, and be supported on the other hand on another assembly of this pair engaging and disengaging gear, be in the axial direction in due course.Yet, alternatively, can also use so-called disc spring as spring element.In order to realize a kind of compact especially structure of this parallel double engaging and disengaging gear at this, as long as be provided with the pressure equalizing chamber of attaching troops to a unit in actuating element, these spring elements just are arranged in this type of pressure balance chamber interior.

Parallel double engaging and disengaging gear of the present invention another preferred embodiment in, this first actuating element is attached troops to a unit first pressure equalizing chamber, and this second actuating element is attached troops to a unit second pressure equalizing chamber is arranged.These pressure equalizing chambers are used for so-called centrifugal oil balance

This first and second pressure equalizing chamber is preferably implemented or is configured at this, makes it correspondingly realize at least 60%, preferred at least 80% centrifugal oil balance.In the ideal case, at least 95% centrifugal oil balance or centrifugal oil balance have completely been realized.

For height and definite whereby equilibrant or the balance pressure of determining centrifugal oil column in these pressure equalizing chambers, in another favourable mode of execution of parallel double engaging and disengaging gear of the present invention, this first pressure equalizing chamber has first overflow, and this second pressure equalizing chamber has second overflow.Due to these overflows, can release excessive equilibrium oil from corresponding pressure equalizing chamber, these equilibrium oils preferably can be used in one of cooling these two sheet groups subsequently.In this embodiment, first incoming flow (Zulauf) of the first pressure equalizing chamber can converge with this first overflow, and second incoming flow of the second pressure equalizing chamber can converge with this second overflow, makes like this this first or second incoming flow similarly form this first or second overflow.Yet consequently, incoming flow and the overflow of corresponding pressure equalizing chamber can not be settled according to function, in order to realize that oil is by this pair engaging and disengaging gear, expedite and mobile targetedly.In order to overcome this shortcoming, in this embodiment more preferably, the first incoming flow that separates with this first overflow and the second incoming flow that separates with this second overflow are set.

In another favourable mode of execution of parallel double engaging and disengaging gear of the present invention, this first group can be undertaken by the oil that flows out from this second pressure equalizing chamber (suitably time by this second overflow) cooling and/or lubricated, and this second group can be undertaken cooling and/or lubricated by the oil that flows out from this first pressure equalizing chamber when suitable (by this first overflow).The oil that flows out from these two pressure equalizing chambers (suitably time by these overflows) can be had a mind to thus the free burial ground for the destitute be used for cooling these two sheet groups, and not with these oil in the situation that walk around these two sheet groups and lead and get back to oily the circulation.Realized thus the especially effectively Cooling and Lubricator of one of these sheet groups or this two sheet groups.

In another the favourable mode of execution based on parallel double engaging and disengaging gear above-described mode of execution, of the present invention, the oil that flows out from the second pressure equalizing chamber has formed at least 50% of the oil that is supplied to the first group, preferably at least 70%, particularly preferably at least 90%.Alternatively or complementally, the oil that flows out from the first pressure equalizing chamber has formed at least 50% of the oil that is supplied to second group, and preferably at least 70%, particularly preferably at least 90%.

In another favourable mode of execution of parallel double engaging and disengaging gear of the present invention, lamella clutch and sheet assembly thereof belong to the even number gear (geraden to a follow-up speed changer

), and another lamella clutch and sheet assembly thereof belong to the odd gear to a follow-up speed changer.The reverse gear of this speed changer at this preferably or attach troops to a unit to the first lamella clutch or is attached troops to a unit to the second lamella clutch.

Parallel double engaging and disengaging gear of the present invention another preferred embodiment in, this second group is arranged in this first group rear on axially at one, and this second pressure equalizing chamber is in same this first pressure equalizing chamber the place ahead of being arranged on axially.When the fuel feeding of first group needs to be undertaken and the fuel feeding of second group when being undertaken by this first pressure equalizing chamber at least in part by the second pressure equalizing chamber at least in part, by the arrangement of sheet group with respect to this counter-rotating of pressure equalizing chamber, guaranteed for example shorter and expend less fuel supply path.This advantage is further strengthened in another preferred variants of this mode of execution, and wherein this first pressure equalizing chamber is arranged to nested or/and this second pressure equalizing chamber is arranged to nested diametrically with this first group diametrically with this second group.This is preferably implemented variant and also has the following advantages: a kind of short especially axial structure length that can realize whereby this parallel double engaging and disengaging gear.

In the parallel double engaging and disengaging gear of routine, these two pressure equalizing chambers keep constant oily charging to supply with one respectively, its mode is that a public oily feed conduit is set, and this conduit is subdivided into the first feed conduit and second feed conduit that leads to this second pressure equalizing chamber that leads to this first pressure equalizing chamber in it further extends.In parallel double engaging and disengaging gear of the present invention, wherein these sheet groups can be cooled and lubricate by the oil that flows out from corresponding pressure equalizing chamber respectively, its the possibility of result is always corresponding sheet group to be supplied the oil of isodose, and close or open irrelevant with corresponding lamella clutch.Although may wish that oil mass is larger in the zone of corresponding sheet group when the lamella clutch of subordinate cuts out, yet when lamella clutch was opened, this relatively large oil mass had caused higher traction square.In order to overcome this shortcoming, parallel double engaging and disengaging gear of the present invention another preferred embodiment in, lead to the oily charging at least one in these pressure equalizing chambers, to lead to the oily charging in this first pressure equalizing chamber and lead to oily charging in this second pressure equalizing chamber in the time of suitably, being variable, is can control or/and adjustable in the time of suitably.So can for example be reduced in the oily charging in the first pressure equalizing chamber when the second lamella clutch is opened, reduce to draw thus square when the second lamella clutch is opened.Can also for example when opening, the first lamella clutch be reduced in the oily charging in the second pressure equalizing chamber, in order to also realize reducing the traction square in the zone of the first lamella clutch of opening.The centrifugal oil balance that realizes by pressure equalizing chamber remains unaffected thus substantially.

In another favourable mode of execution (based on previously described mode of execution) of parallel double engaging and disengaging gear of the present invention, can with the oily charging of leading to a pressure equalizing chamber with lead to oily charging in another pressure equalizing chamber and irrespectively reduce (suitably time be reduced to zero), increase or change.The oily charging that to lead to a pressure equalizing chamber irrespectively reduces with the oily charging of leading in another pressure equalizing chamber, be interpreted as at this, when the oily charging that will lead to a pressure equalizing chamber reduces, the oily charging of leading in another pressure equalizing chamber does not reduce simultaneously forcibly, but this oily charging of leading in another pressure equalizing chamber can remain unchanged or even improve.Be similar to this, the oily charging that to lead to a pressure equalizing chamber irrespectively increases with the oily charging of leading in another pressure equalizing chamber, be interpreted as, the oily charging of leading to a pressure equalizing chamber can be increased, and do not increase forcibly simultaneously the oily charging of leading in another pressure equalizing chamber, but this oily charging of leading in another pressure equalizing chamber can remain unchanged or even reduce.In addition, the oily charging that to lead to a pressure equalizing chamber irrespectively changes with the oily charging of leading in another pressure equalizing chamber, be interpreted as, lead to any change of the oily charging of a pressure equalizing chamber, do not cause forcibly leading to the change of the oily charging in another pressure equalizing chamber.

Parallel double engaging and disengaging gear of the present invention another preferred embodiment in, be provided with a control gear in these two pressure equalizing chambers at least one of these pressure equalizing chambers, suitably the time, be used for changing, reduce or increase oily charging.This control gear is preferably a valve positioner, so that can be especially simply and realize pointedly leading in these pressure equalizing chambers the control of the oily charging at least one.In this embodiment more preferably, this control gear is in to circulate to be connected and to be in circulation by at least one second feed conduit that separates with this first feed conduit with this second pressure equalizing chamber by at least one first feed conduit and this first pressure equalizing chamber and is connected thus in this enforcement variant, between this control gear and these pressure equalizing chambers, at this between at least one second feed conduit of at least one first feed conduit and this circulation is connected, in order to can realize independently oily charging control.

In another favourable mode of execution of parallel double engaging and disengaging gear of the present invention, in order to realize automatically by reducing oily charging that when lamella clutch is opened previously mentioned traction square reduces, this control gear and this first lamella clutch carry out acting in conjunction as follows, make the oily charging of leading to this first pressure equalizing chamber to reduce relatively with the on-state of this second lamella clutch, to increase or change.So the on-state that corresponding device is used for measuring this second lamella clutch can for example be set, and this device so that with this control gear acting in conjunction.At this preferably, this control gear as follows with this second lamella clutch acting in conjunction, make the oily charging of leading to when the second lamella clutch is opened in this first pressure equalizing chamber less than the oily charging when the second lamella clutch cuts out.Alternatively or complementally, in this embodiment this control gear as follows with this first lamella clutch acting in conjunction, make the oily charging of leading in this second pressure equalizing chamber and the on-state of this first lamella clutch reduce relatively, increase or change.At this, on-state that corresponding device is used for measuring this first lamella clutch can for example be set also, and this device and then with this control gear acting in conjunction or carry out communication.Equally, in this enforcement variant substituting or complementarity, this control gear be preferably as follows with this first lamella clutch acting in conjunction, make the oily charging of leading to when the first lamella clutch is opened in this second pressure equalizing chamber less than the oily charging when the first lamella clutch cuts out.

Guarantee simultaneously within this parallel double engaging and disengaging gear fast and pointedly will be from this first or/and the oil that the second pressure equalizing chamber flows out is fed to corresponding sheet group in order diametrically each independent component to be contained in, from this first or/and the oil that the second pressure equalizing chamber flows out can be guided through or be conducted through diametrically one of these actuating elements or/and a plurality of openings a tubular segments of a clutch-plate support.Be guided through diametrically the opening of this tubular segments for the major part at this oil that will flow out from this first or second pressure equalizing chamber, preferably be provided with a capture slot (Auffangbecken) of inwardly opening diametrically on the inner side surface of this tubular segments, implement described opening in the bottom of this capture slot thus.Therefore can outwards be caught and temporarily be blocked (aufgestaut) by this capture slot diametrically from the oil that this first or second pressure equalizing chamber flows out, in order to by the opening in this tubular segments, the oil of tackling little by little is supplied to the sheet group of subordinate.For realize in simple especially mode this inwardly open capture slot and the actuating element of simplifying thus subordinate or/and the final manufacturing of clutch-plate support, this inwardly open capture slot preferably by means of one radially inwardly outstanding, in a circumferential direction around the obstruction wall and be manufactured on the inboard of this tubular segments.So this capture slot can for example be implemented in the axial direction this inwardly outstanding, in a circumferential direction around the obstruction wall with this actuating element or/and between an at least part of radial section that extends diametrically of this clutch-plate support, this radial section is single-piece enforcement together with this tubular segments.Might arrange on the inboard of this tubular segments equally two that be spaced apart from each other in the axial direction, inwardly outstanding and in a circumferential direction around the obstruction wall, in order to implement in the axial direction betwixt this capture slot.Basically can a Sealing be set in this axially inwardly edge that stops wall, will stop on another parts that wall is directed to this pair engaging and disengaging gear hermetically by the seal.Yet this mode of execution also comprises an obstruction wall, does not arrange Sealing on it, and this is preferred on the meaning of simplifying this pair engaging and disengaging gear structure; Do not have in addition Packed obstruction wall energy enough to be suitable for implementation in obstruction volume within this capture slot, necessary.Although wherein said be one in a circumferential direction around the obstruction wall, yet it must not be embodied as in a circumferential direction continuously or sealing ground around, the break-through opening of the dispersion (vereinzelte) under this external concrete condition in this obstruction wall may be also favourable.Yet, in this embodiment preferably, this obstruction wall be embodied as in a circumferential direction continuously or seal ground around.

In order to ensure carrying out uniform power transmission from actuating element to the sheet group of correspondingly attaching troops to a unit, in another favourable mode of execution of parallel double engaging and disengaging gear of the present invention, a pressure portion (suitably time be embodied as annular or/and be embodied as pressure disk) is fixed on passes on this first actuating element that depressed part extends, wherein this pressure portion can be pressed against on the first group by this first actuating element, in order to close this first lamella clutch.Basically this pressure portion can be fixed on this first actuating element with getting loose.Yet may make thus installation and removal become difficult, if not making it complete impossible words.For this reason, this pressure portion preferably is releasably secured on this first actuating element, in order to simplify installation and removal, the size of such pressure portion is following definite in due course in addition: make this pressure portion not pass these depressed parts together with this first actuating element.At this maybe advantageously, be combined on extra immobilising device to tieback, for example guard ring or analog are in order to realize the fixing of this pressure portion getting loose on this first actuating element.Yet in order to carry out more simply in this embodiment installation and removal, this pressure portion preferably is fixed on this first actuating element engagingly.So a plurality of engagement lower dents can be set on the one hand and a plurality of mesh bulge section is set on the other hand, they can be engaged with each other to realize engagement type fixation.In this embodiment, this pressure portion can be fixed on this first actuating element, only basically realizes simultaneously reciprocally synchronizeing connection a kind of between this first actuating element and this pressure portion on one of axially at two.Yet in order to ensure the separating especially fast and pressing of clutch-plate of sheet group that opens and closes especially fast and simply corresponding lamella clutch and therefore guarantee the lamella clutch of subordinate, this pressure portion is preferably two reciprocal realizations on axially in the situation that this first actuating element is fixed on this first actuating element with the connection of synchronizeing between this pressure portion in this embodiment.

In another favourable mode of execution of parallel double engaging and disengaging gear of the present invention, this first actuating element has a plurality of axial dactylitic pieces, and these axial dactylitic pieces extend through these depressed parts.

Parallel double engaging and disengaging gear of the present invention another preferred embodiment in, the length of these axial dactylitic pieces of this first actuating element is embodied as, and makes their free end pass in the axial direction second group and give prominence to, make simultaneously this pressure portion to be releasably secured on free end.If arrange to have the intermediate disc that describes in detail after a while between these first and second groups, these axial dactylitic pieces preferably also extend through the depressed part in described intermediate disc so, wherein the free end of these axial dactylitic pieces also passes this intermediate disc in the axial direction and gives prominence to, in order to this pressure portion can be releasably secured on these free ends.The advantage of this mode of execution is, can mount and dismount simply, fixing on the free end of these axial dactylitic pieces of this pressure portion also can be relatively simple in addition, and these axial dactylitic pieces pass second group and pass in due course this intermediate disc on axially at this.In this embodiment more preferably, these axial dactylitic pieces and this first actuating element are single-piece ground enforcement.So this first actuating element can for example be embodied as the tinsel part of tank shape, be provided with a plurality of depressed parts in its tubular segments, in order to implement in a circumferential direction previously mentioned axial dactylitic piece between these depressed parts.

Parallel double engaging and disengaging gear of the present invention another preferred embodiment in, pass this first actuating element that depressed part extends outside these depressed parts preferably by this pressure portion, particularly preferably be in rotary synchronous by a kind of tooth section's engagement with an input side of this pair engaging and disengaging gear and be connected.By outside depressed part and therefore not via or only part carry out this rotary synchronous via these depressed parts in clutch-plate and connect, the working method that neither limits the first actuating element does not limit the working method with the clutch-plate of depressed part yet.In this embodiment more preferably, the first actuating element, be that it passes axial dactylitic piece that depressed part extends suitably the time, open with the marginating compartment of these depressed parts in a circumferential direction, in order to avoid the first actuating element and offside impact (gegenseitige Beeinflussung) with the clutch-plate of depressed part fully.

Parallel double engaging and disengaging gear of the present invention another preferred embodiment in, pass the first actuating element that depressed part extends, be its axial dactylitic piece suitably the time, ensured the impact avoid broadening effect (Aufweiten) this first actuating element (being suitably its axial dactylitic piece), that caused by centrifugal force outside these depressed parts, preferably supported in the axial direction, particularly preferably be subject to this pressure portion and support.Also got rid of significantly in this case the first actuating element and affected with a kind of negative offside on working method between the clutch-plate of depressed part.In order to strengthen this advantage, in this embodiment more preferably, the first actuating element, be its axial dactylitic piece suitably the time, outwards and finally also upcountry open with the marginating compartment of these depressed parts diametrically.

Illustrate as the front, in another favourable mode of execution of parallel double engaging and disengaging gear of the present invention, be provided with an intermediate disc between these first and second groups, this second group can support or be supported on this intermediate disc in the axial direction.For the installation and removal of simplifying this pair engaging and disengaging gear or or even make it and might carry out, within this intermediate disc preferably releasably is arranged in this pair engaging and disengaging gear in this embodiment or be arranged in a clutch-plate support, be arranged on outer clutch-plate support suitably the time.So this intermediate disc for example can support in the axial direction or be fastened on this clutch-plate support or outer clutch-plate support by means of a guard ring that can get loose.In order to reach this first group, in this embodiment, this first actuating element or its axial dactylitic piece preferably extend through the depressed part in this intermediate disc, and these depressed parts can be embodied as the entry of depressed part or the edge side of window type again.In this embodiment in addition further preferably, this intermediate disc has a convexly curved section in the axial direction

In order to form a supporting zone that is used for this second group.

Method in the parallel double engaging and disengaging gear work for making type of the present invention of the present invention, the oily charging of leading in the first pressure equalizing chamber is controlled as follows, the oily charging when making oily charging when the second lamella clutch is opened close less than the second lamella clutch.At this more preferably, the oily charging lead to the first pressure equalizing chamber when the second lamella clutch is opened in is prevented from.Oily charging when alternatively or complementally, in the method for the invention, the oily charging of leading in the second pressure equalizing chamber is controlled as follows, making oily charging when the first lamella clutch is opened close less than the first lamella clutch.It is also preferred that in this complementarity or substituting variant, the oily charging lead to the second pressure equalizing chamber when the first lamella clutch is opened in is prevented from.At the advantage aspect aspect this, can be with reference to the advantage of the mode of execution of above-described parallel double engaging and disengaging gear of the present invention, these advantages are applicable to the method in a corresponding way.Still need mention in this point, can significantly be reduced in traction square within the lamella clutch of opening by the method for this parallel double engaging and disengaging gear of operation of the present invention, and not have so the centrifugal oil balance that causes by pressure equalizing chamber is caused violent impact.

Description of drawings

To and explain orally in detail the present invention with reference to accompanying drawing by a plurality of exemplary mode of executions below.Shown in figure:

Fig. 1 is illustrated between gear unit and speed changer, mode of execution parallel double engaging and disengaging gear of the present invention in the power train of motor vehicle with sectional view;

The intercepting A of section of Fig. 2 Fig. 1 in the first alternate embodiments; And

The intercepting A of section of Fig. 3 Fig. 1 in the second alternate embodiments.

Embodiment

Fig. 1 shows a mode of execution of parallel double engaging and disengaging gear 2 of the present invention, and this parallel double engaging and disengaging gear is arranged in the power train of motor vehicle, the only gear unit 4 of schematic presentation and one only between the speed changer 6 of schematic presentation.Reciprocal axial 8,10 of two engaging and disengaging gear 2 have been shown by means of corresponding arrow in Fig. 1, reciprocal radially 12,14, with reciprocal

circumferencial direction

16,18, wherein a spin axis 20 of two engaging and disengaging gear 2 extends on axial 8,10.

Within two engaging and disengaging gear 2 are arranged in a moist chamber 22, wherein moist chamber 22 is implemented in a case of transmission cover 24, this case of transmission covers on axial 10 and radially 12 and has limited moist chamber 22, wherein by 26 restrictions of case of transmission lid, this case of transmission lid releasably is arranged in this case of transmission cover 24 places to this case of transmission cover 24 on axial 8.Therefore two engaging and disengaging gear 2 of showing are the two engaging and disengaging gear 2 of a kind of wet type.

Parallel double engaging and disengaging gear 2 has first lamella clutch 28 and second lamella clutch 30.The first lamella clutch 28 has a first group 32 that is comprised of a plurality of interior clutch-plates and outer clutch-plate, and the second lamella clutch 30 has second group 34 that is comprised of a plurality of outer clutch-plates 36 and a plurality of interior clutch-plate.First group 32 is attached troops to a unit first actuating element 38, and second group 34 attached troops to a unit second actuating element 40 is arranged.First group 32 can be handled by means of the first actuating element 38, so as between this gear unit 4 and first transmission input shaft 42 transmitting torque optionally.By contrast, second group 34 can be handled by means of the second actuating element 40, so as between this gear unit 4 and second transmission input shaft 44 transmitting torque optionally.In order to realize this point, the outlet side of the first lamella clutch 28 is formed by first an interior clutch-plate support 46, and this support is in rotary synchronous with the interior clutch-plate of first group 32 on the one hand and is connected and is in rotary synchronous with the first transmission input shaft 42 on the other hand and is connected; And the outlet side of the second lamella clutch 30 is formed by second an interior clutch-plate support 48, and this support is in rotary synchronous with the interior clutch-plate of second group 34 on the one hand and is connected and is in rotary synchronous with the second transmission input shaft 44 on the other hand and is connected.In the embodiment shown, the first and second transmission input shafts 42, the 44th, coaxial arrangement, wherein the second transmission input shaft 44 is embodied as hollow shaft, and the first transmission input shaft 42(constitutes solid shaft when suitable) extend on axial 8,10 by this hollow shaft.

On the contrary, the first and second lamella clutch 28,30 input side are formed by a public outer clutch-plate support 50, and this support not only also is in rotary synchronous with the outer clutch-plate 36 of second group 34 with these outer clutch-plates of first group 32 and is connected.The outer clutch-plate support 50 of tank shape is connected with a clutch input wheel hub 54 by a synchronizer dish 52 in its tail end towards axial 8 anti-rotationly in fact, this clutch input wheel hub extends to the direction of gear unit 4 from this moist chamber 22 by an opening in case of transmission lid 26, zone that be arranged in this spin axis 20, in order to be connected with an outlet side 56 of gear unit 4 there anti-rotationly.Outer clutch-plate support 50 is combined at the radial section 60 that abuts against on axis 10 on connecting sheet carrying section 58 by 58 and one of the clutch-plate carrying sections of a tubulose in fact, this radial section is radially extending inward into a tubular clutch hub 62 on 14, and outer clutch-plate support 50 is connected with this clutch hub anti-rotationly.Clutch hub 62 radially inwardly can support (passing through in due course ball bearing) on a fixing carrying pipe 64 around spin axis 20 on 14 rotatably, and wherein this carrying pipe 64 is arranged on case of transmission speed changer 6, that formed case of transmission cover 24 securely.Describe in detail after a while to the hydraulic oil supply of two engaging and disengaging gear 2 and centrifugal oil supply by carrying manage 64 and clutch hub 62 carry out, wherein hereinafter also to again explain orally in detail this.

Because two engaging and disengaging gear 2 are a parallel double engaging and disengaging gear 2, so first group 32 and second group 34 is classification on axial 8,10, and is arranged in the example shown and flushes each other.This is arranging have 66, the second groups 34 of an intermediate disc can support or be supported on this intermediate disc on axial 8 on external axial 8,10 between sheet group 32 and 34.Within intermediate disc 66 releasably is arranged in two engaging and disengaging gear 2, be exactly clutch-plate carrying section 58 places that releasably are arranged in outer clutch-plate support 50.For this purpose, intermediate disc 66 has an outer toothed portion 68, this outer toothed portion is in the internal tooth section of a correspondence that radially outwards joins clutch-plate carrying section 58 on 12 to, wherein in addition a guard ring 70 releasably is arranged on this clutch-plate carrying section 58, by this guard ring, intermediate disc 66 can be supported on connecting sheet carrying section 58 and therefore can be supported on outer clutch-plate support 50 on axial 8.In intermediate disc 66, also be provided with a plurality of window type depressed parts 72 that are spaced apart from each other on

circumferencial direction

16,18, also to explain orally in detail it after a while.In addition, intermediate disc 66 has one convexly curved 74 on axial 10, has formed like this a supporting zone that is used for second group 34.In other words, ground protruding upward, convexly curved 74 side second group 34 is crooked.

It is can be hydraulically powered each other that these two actuating

elements

38 and 40 are independent of respectively, so actuating

element

38,40 also can be called application piston.So the first pressure chamber 76 that the first actuating element 38 is attached troops to a unit and had an available hydraulic oil to load, and the second pressure chamber 78 that the second actuating element 40 is attached troops to a unit and had an available hydraulic oil to load.These two

pressure chambers

76,78 respectively same axially, be arranged in corresponding actuating

element

38 and 40 rears at this on for axial 10.Load correspondingly with hydraulic oil and undertaken by corresponding feed conduit in fixing carrying pipe 64 and support clutch hub 62 thereon.In other words, the first and

second pressure chambers

76,78 are supplied or load hydraulic oil in transmission side.In order to guarantee the sealing of system at this, be provided with corresponding swivel joint Sealing (Drehdurchf ü hrungsdichtungen) 80 between carrying pipe 64 and clutch hub 62.By

pressure chamber

76,78 is loaded, actuating

element

38,40 is moved, in order to

corresponding sheet group

32 or 34 is compressed and therefore realizes closing of corresponding lamella clutch 28 or 30 on a steering 82.Thus, the first actuating element 38 and the second actuating element 40 have identical steering 82, and this direction is corresponding to one of axial 8,10, at this corresponding to axial 8.

In order to realize at least part of centrifugal oil balance, the first actuating element 38 is also attached troops to a unit first pressure equalizing chamber 84, and the second actuating element 40 is also attached troops to a unit second pressure equalizing chamber 86 is arranged.

Pressure equalizing chamber

84,86 is arranged in respectively in the

pressure chamber

76 or 78 side of subordinate dorsad of corresponding the first actuating

element

38 or 40, thus these two

pressure equalizing chambers

84 and 86 each comfortable same axially, be on axial 8 at this, be arranged in the first actuating

element

38 or 40 rears of subordinate.Also arranging within

pressure equalizing chamber

84,86 has a plurality of spring elements 88, and when the

pressure chamber

76 or 78 of correspondence did not load with hydraulic oil, these spring elements were used for the first actuating

element

38 or 40 of subordinate is turned back to its initial position.In the embodiment shown, spring element 88 is embodied as helical spring, yet it also may be embodied as disc spring or analog.As seen from Figure 1, this second group 34 is arranged in this first group 32 rears on axial 10, and this second pressure equalizing chamber 86 is arranged in this first pressure equalizing chamber 84 the place aheads on identical axial 10.The first pressure equalizing chamber 84 is radially nestedly arranging with second group 34 on 12,14 in addition, and the second pressure equalizing chamber 86 is radially nestedly arranging with first group 32 on 12,14.Accordingly, not only realize the compactly designed of this parallel double engaging and disengaging gear 2, but also can realize that this point also will explain orally after a while in detail to

corresponding sheet group

32,34 the guiding of favourable cold oil or lubricant oil guiding.

For the compact especially structure that reaches this parallel double engaging and disengaging gear 2 and realize carrying out especially directly by the first actuating element 38 to first group 32 power imports, the depressed part 90 that the first actuating element 38 passes on axial 8 in the outer clutch-plate 36 of second group 34 extends to first group 32.For this purpose, the first actuating element 38 has the axial dactylitic piece 92 of implementing with this first actuating element 38 single-pieces, and these axial dactylitic pieces extend from the first depressed part 90 of actuating element 38s axial 8 pass outer clutch-plate 36.At this, axially the length of dactylitic piece 92 is implemented as, make its free end 94 pass second group 34 on axial 8 and pass in addition intermediate disc 66 and give prominence on axial 8, wherein these axial dactylitic pieces 92 further pass for this purpose the depressed part 72 of the intermediate disc 66 of having mentioned the front and give prominence to.

Depressed part 90 in outer clutch-plate 36, also have the depressed part 72 of intermediate disc 66 suitably the time, be embodied as the depressed part of window type and be not embodied as thus the entry of edge side, although this is also feasible basically, as will again explaining orally in detail after a while.The depressed part 90 of window type is surrounded by a boundary edge respectively fully.Radially on 12,14 the depressed part 90 of window type and one be embodied as implement outer clutch-plate 36 between clutch-plate tooth outer toothed portion, outer clutch-plate 36 section 96 one on

circumferencial direction

16,18 consistently or sealing ground around supporting section 98.Can also say, the supporting section 98 of outer clutch-plate 36 is embodied as in fact packing ring shape.The depressed part 90 of these window types does not have impact to the design of clutch-plate tooth section 96 thus, in the situation that for example the edge side entry is quite different.Even and in the situation that axially dactylitic piece 92 and depressed part 90 have larger width on

circumferencial direction

16,18, also produced the clutch-plate tooth section 96 with full-depth tooth number.

Outer clutch-plate 36, on

circumferencial direction

16,18 consistently or sealing ground around supporting section 98 also have another advantage.Be at second group excircle of 34 and arrange to have a plurality of flexible clutch-plate dividing elements 100 between these outer clutch-plates 36 adjacent one another are, when the second lamella clutch 30 was opened, these dividing elements were used for forcing the clutch-plate of second group 34 spaced apart and therefore having reduced the traction square of the second lamella clutch 30.Elasticity clutch-plate dividing element 100 is embodied as annular, and respectively in axial 8,10 upper supports on second group outer clutch-plate 36 adjacent one another are of 34.At this, clutch-plate dividing element 100 for example may be embodied as spring element, ripple spring or with the ring of ripple, axial 8,10 upper supports in outer clutch-plate 36, on

circumferencial direction

16,18 consistently or sealing ground around supporting section 98 on.Consequently, can realize supporting and can realizing thus especially reliably the pressure interval of these clutch-plates of second group 34 when the second lamella clutch 30 is opened.In order to take full advantage of this advantage, clutch-plate dividing element 100 the support on corresponding outer clutch-plate 36 on axial 8 or 10 preferred only on

circumferencial direction

16,18 consistently or sealing around supporting section 98 on carry out.Can also say, the support of clutch-plate dividing element 100 be in the situation that between corresponding outer clutch-plate 36 and clutch-plate dividing element 100 area of contact of formation carry out, this area of contact has formed 100% of area of contact between clutch-plate dividing element 100 and supporting section 98.In order to realize secure support and the advantage of forcing the interval, clutch-plate dividing element 100 should be supported at least as follows and maybe can be supported on outer clutch-plate 36, the support that makes this clutch-plate dividing element is in the situation that form an area of contact between corresponding outer clutch-plate 36 and clutch-plate dividing element 100 and carry out, this area of contact formed clutch-plate dividing element 100 and on

circumferencial direction

16,18 consistently or seal around supporting section 98 between area of contact more than 50%, preferably more than 95%.

Yet, illustrate as top, depressed part 90 can also be embodied as the entry of edge side alternatively, namely be embodied as clutch-plate 36 outside in the entry on outwardly edge on 12 radially.Yet should mention in this, due to this type of depressed part 90 that is in edge side entry form, do not have to realize on

circumferencial direction

16,18 consistently or sealing ground around this supporting section of supporting section 98(realized supporting especially reliably or pressure interval by clutch-plate dividing element 100 on clutch-plate dividing element 100).If still the form with this type of edge side entry arranges depressed part 90, the entry of these edge sides preferably is arranged in clutch-plate tooth section 96 so, and then these edge side entries can be made under the background of producing clutch-plate tooth section 96 especially simply simultaneously in addition.Also propose as favourable part relatively therewith, the edge side entry that forms depressed part 90 is embodied as clutch teeth section 96 in clutch-plate tooth section 96 interdental spaces is at inside extending portion on 14 radially.

For can enough oily supply pressures balance

cylinder

84,86 and realize that thus previously mentioned centrifugal oil balance, the first pressure equalizing chamber 84 have at least one first incoming flow 102, and the second pressure equalizing chamber 86 has at least one second incoming flow 104.Incoming flow 102,104 is embodied as the break-through opening in the clutch hub 62 at tubulose respectively at this.In addition in order radially to determine the height of centrifugal oil column within

pressure equalizing chamber

84,86 pointedly and with corresponding incoming flow 102,104 location independent ground on 12,14, the first pressure equalizing chamber 84 has at least one first overflow 106, and the second pressure equalizing chamber 86 has at least one second overflow 108, and wherein

pressure equalizing chamber

84,86 interior excessive oil can be in the situation that realize that a predetermined centrifugal oil column height flows out from corresponding

pressure equalizing chamber

84,86 by overflow 106,108.Also can mention overflow openings in the first and second overflows 106,108, wherein the first incoming flow 102 is implemented discretely with this first overflow 106, and the second incoming flow 104 is implemented discretely with this first overflow 108.First group 32 can be by the oil cooling that flows out by the second overflow 108 from the second pressure equalizing chamber 86 but, and second group 34 can be by the oil coolings that flow out by the first overflow 106 from the first pressure equalizing chamber 84.Due to previously mentioned the first pressure equalizing chamber 84 with second the group 34 radially nested, and second pressure equalizing chamber 86 and first group 32 radially nested,

overflow

106 or 108 and

corresponding sheet group

34 or 32 between produced short especially

oily transmission path

110 or 112, wherein oily transmission path 110,112 arrow by correspondence in Fig. 1 represents.

In order to design the first oily transmission path 110 short especially, the oil that will flow out from the first pressure equalizing chamber 84 by the first overflow 106 is at 12 a plurality of openings 114 being guided through a tubular segments 116 of the second actuating element 40 radially, and this tubular segments is organized between 34 with second radially being arranged in the first pressure equalizing chamber 84 on 12,14.In order equally the second oily transmission path 112 to be shortened in a corresponding way, the oil that will flow out from the second pressure equalizing chamber 86 by the second overflow 108 is at 12 a plurality of openings 118 being guided through a tubular segments 120 of the second interior clutch-plate direct 48 radially, wherein the tubular segments 120 of this second interior clutch-plate support 48 radially be arranged on 12,14 the second pressure equalizing chamber 86 with it radially between the first group 32 of nested arrangement.The opening that also is provided with a plurality of correspondences in these two interior clutch-plate supports 46,48 tubular interior clutch-plate carrying section is used for oil is passed, although do not show them for purpose clearly in Fig. 1.

Supply especially reliably second group 34 in order to realize using from the oil of the first pressure equalizing chamber 84 outflows, radially be provided with one on 14 on inwardly inner side surface at inside open capture slot 122 on 14 radially in tubular segments 116, can catch the oil of arrival and stop at short notice in this capture slot, oil is radially continuing to flow to second group 34 on 12 by opening 114 afterwards.Capture slot 122 this by means of one radially on 14 inwardly outstanding and on

circumferencial direction

16,18 around obstruction wall 124 and be created in tubular segments 116 radially on 14 on inwardly inner side surface.In other words, capture slot 122 on axial 10 by stop wall 124 and on axial 8 the shape of the correspondence by the second actuating element 40 limit self.Stop wall 124 and the second actuating element 40 single-pieces form, wherein stop wall 124 and be embodied as ring wedge angle (Ringzacke) in mode of execution shown in Figure 1, it can be manufactured on the second actuating element 40 places relatively simply.

The oily charging of leading to the oily charging in the first pressure equalizing chamber 84 and leading in the second pressure equalizing chamber 86 is all changeable or controlled and/or adjustable.For this purpose, be provided with a control gear 126 of schematic presentation in Fig. 1, this control gear is used for changing described oil supply.Control gear 126 is embodied as valve positioner.Control gear 126 is in to circulate to be connected and to be in to circulate with the second pressure equalizing chamber 86 by second feed conduit 130 that separates with this first feed pipe 128 by first feed conduit 128 and the first pressure equalizing chamber 84 and is connected, wherein in illustrated embodiment, each in these two feed conduits 128,130 is attached troops to a unit a controlled valve 132.At it dorsad on feed conduit 128,130 side, control gear 126 is connected with a public oil supply 134.Due to control gear 126, lead in the first pressure equalizing chamber 84 oil for should be able to lead to oil supply in the second pressure equalizing chamber 86 and irrespectively reduce (suitably time can be reduced to zero), increase or change, vice versa.

Control gear 126 also has the second lamella clutch 30 all to be in effective the connection with the first lamella clutch 28, and its mode be make the oil that leads in the first pressure equalizing chamber 84 for should be able to ground relevant to the on-state of the second lamella clutch 30, lead in the second pressure equalizing chamber 86 oil for should be able to the on-state of the first lamella clutch 28 relevantly, preferably automatically, reduce, increase or or change.Control gear 126 is designed at this, oily charging when making the oily charging of leading to when this second lamella clutch 30 is opened in the first pressure equalizing chamber 84 close less than the second lamella clutch 30 wherein is reduced to zero by means of valve 132 with described oil supply in the embodiment shown in the first feed conduit 128.Yet same possible be that although do not recommend, the oily charging lead to the first pressure equalizing chamber when the second lamella clutch 30 is opened in is only by throttling.In a corresponding way, control gear 126 is implemented as, and makes when the first lamella clutch 28 is opened, and leads to oily charging in this second pressure equalizing chamber 86 less than the oily charging when the second lamella clutch 28 cuts out.For the second pressure equalizing chamber 86 or the first lamella clutch 28, for example also represent by means of valve 132 in the second feed conduit 130, when the first lamella clutch 28 is opened, this valve is closed.Yet same possible be that although do not recommend, the oily charging lead to the second pressure equalizing chamber 86 when the first lamella clutch 28 is opened in is only by throttling.

Described control gear 126 or the associated method that is used for this parallel double engaging and disengaging gear 2 of operation have following substantial advantage, namely when the second lamella clutch 30 was opened, the oil from the first pressure equalizing chamber 84 still less reached second group 34 by the first overflow 106.Reduced thus the traction square in the zone of the second lamella clutch 30 of opening.Corresponding content also is applicable to the first lamella clutch 28.So there is following advantage, namely when the first lamella clutch 28 is opened, the oil from the second pressure equalizing chamber 86 still less reaches first group 32 by the second overflow 108, so also can be reduced in the traction square in the zone of the first lamella clutch 28 of opening.

In order can be advantageously the steering force of the first actuating element 38 to be delivered on first group 32, be fixed with pressure portion 136 annular, that be embodied as pressure disk on by second group 34 and the outstanding free end 94 of intermediate disc 66 at axial dactylitic piece 92 on axial 8.At this, pressure portion 136 is not releasably secured on the free end 94 of axial dactylitic piece 92 of the first actuating element 38, as illustrating by means of filling up (Verstemmung) free end 94 with pressure portion 136 in Fig. 1 basically.Yet in order to guarantee to install simple and can to carry out after a while simple dismounting, pressure portion 136 is releasably secured on the free end 94 of axial dactylitic piece 92 of the first actuating element 38.The fixation that can get loose can for example be passed through an extra immobilising device at this, and the guard ring that gets loose 138 as shown in Figure 3 carries out, and thereon, pressure portion 136 can be supported on the free end 94 of axial dactylitic piece 92 on axial 8.As an alternative more preferably, pressure portion 136 releasably is connected with the free end 94 of axial dactylitic piece 92 in the mode of engagement, as shown in the alternative enforcement variant in Fig. 2.Implement in variant at this, be provided with a plurality of engagement bumps or engagement nose shaped part 140 at free end 94, at the free end 94 of axial dactylitic piece 92 in the situation that on axial 8 in short time, flexibly curve inwardly in the depressed part 90 of the correspondence of free end 94 in being imported into pressure portion 136 on axial 14 after, these engagement bumps or engagement nose shaped part from rear activating pressure part 136, towards axial 8,10 side.With the various enforcement variants of pressure portion 136 or its fixation on the free end 94 of axial dactylitic piece 92 irrespectively, each in the pressure portion 136 of showing, be fixed on the first actuating element 38 in the situation that synchronize connection between the first actuating element 38 and pressure portion 136 realizing on axial 10 and axial 8.If the first actuating element 38 is moved on axial 10, engagement bump 140 and the guard ring 138 in Fig. 3 filled up in effect, Fig. 2 in Fig. 1 realized the synchronous of the correspondence of pressure portion 136 in axial 10.Yet, if the first actuating element 38 is moved on axial 8 within the first pressure chamber 76 because pressure raises, retainer 142 acts on the free end 94 of axial dactylitic piece 92 so, thereby pressure portion 136 is moved on axial 8, this retainer rest on pressure portion 136 on axial 10 side.Thus, clutch-plate dividing element 144 is also removed load between the clutch-plate adjacent one another are of first group 32, and these clutch-plate dividing elements can be completely or partially consistent with the clutch-plate dividing element 100 that type above is described.

The working method of clutch-plate 36 outside the axial dactylitic piece that passes these depressed parts 90 extensions 92 impacts of the first actuating element 38, the first actuating element 38 is outside these depressed parts 90, be connected by being in rotary synchronous in a kind of tooth section engagement 146 of pressure portion 136 and outer clutch-plate support 50 supports with the input side of two engaging and disengaging gear 2 in the embodiment shown, this input side is formed by clutch-plate support 50 outside this at this.Size at this axial dactylitic piece 92 and depressed part 90 is determined on

circumferencial direction

16,18 as follows, make the axial dactylitic piece 92 of the first actuating element 38 open with the marginating compartment of depressed part 90 on

circumferencial direction

16,18, thereby preferably can not come in contact or not have fully betwixt the moment of torsion transmission on

circumferencial direction

16,18 between the edge of axial dactylitic piece 92 and depressed part 90 when two engaging and disengaging gear 2 work.In addition, axial dactylitic piece 92, that caused by centrifugal force, outside on axial 12 broadening of the first actuating element 38 is avoided as follows, and namely the first actuating element 38 or its axial dactylitic piece 92 outwards are supported on outside this on clutch-plate support 50 by pressure portion 136 on axial 12.Axially the size of dactylitic piece 92 and depressed part 90 is also radially being determined on 12,14 as follows in this case, the axial dactylitic piece 92 that makes the first actuating element 38 is radially outside on 12 and also radially inwardly opening with the marginating compartment of depressed part 90 on 14 when suitable, thereby even when two engaging and disengaging gear 2 are worked axial dactylitic piece 92 be not supported on yet depressed part 90 radially external on 12 or in built-in edge on 14 radially.

The reference number inventory

2 parallel double engaging and disengaging gear

4 gear units

6 speed changers

8 is axial

10 is axial

12 radially

14 radially

16 circumferencial directions

18 circumferencial directions

20 spin axiss

22 moist chambers

24 case of transmission covers

26 case of transmission lids

28 first lamella clutch

30 second lamella clutch

32 first groups

34 second groups

36 outer clutch-plates

38 first actuating elements

40 second actuating elements

42 first transmission input shafts

44 second transmission input shafts

46 first interior clutch-plate supports

48 second interior clutch-plate supports

50 outer clutch-plate supports

52 synchronizer dishes

54 clutch input wheel hubs

56 outlet sides

58 clutch-plate carrying sections

60 radial sections

62 clutch hubs

64 carrying pipes

66 intermediate discs

68 outer toothed portion

70 guard rings

72 depressed parts

74 convexly curved sections

76 first pressure chambers

78 second pressure chambers

80 swivel joint Sealings

82 steerings

84 first pressure equalizing chambers

86 second pressure equalizing chambers

88 spring elements

90 depressed parts

92 axial dactylitic pieces

94 free ends

96 clutch-plate tooth sections

98 supporting sections

100 clutch-plate dividing elements

102 first incoming flows

104 second incoming flows

106 first overflows

108 second overflows

110 oily transmission paths

112 oily transmission paths

114 openings

116 tubular segments

118 openings

120 tubular segments

122 capture slots

124 stop wall

126 control gear

128 first feed conduits

130 second feed conduits

132 valves

134 oil supplies

136 pressure portion

138 guard rings

140 mesh bulge sections

142 retainers

144 clutch-plate dividing elements

The engagement of 146 tooth sections

Claims

1. be used for being arranged in the parallel double engaging and disengaging gear (2) of the preferred wet type of power train between gear unit (4) and speed changer (6) of motor vehicle, this parallel double engaging and disengaging gear has attaches troops to a unit in first lamella clutch (28) of first transmission input shaft (42) and attaches troops to a unit in second lamella clutch (30) of second transmission input shaft (44), this the first chip clutch appliance has a first group (32), can handle by means of first actuating element (38), be used for optionally carrying out the moment of torsion transmission between this gear unit (4) and this first transmission input shaft (42), this second lamella clutch has one second group (34), can handle by means of second actuating element (40), be used for optionally carrying out the moment of torsion transmission between this gear unit (4) and this second transmission input shaft (44), it is characterized in that, this first actuation unit (38) is axial (8,10) a plurality of depressed parts (90) that are passed in the clutch-plate (36) in this second group (34) extend to this first group (32).

2. parallel double engaging and disengaging gear according to claim 1 (2), it is characterized in that, these depressed parts (90) are embodied as the depressed part (90) of window type or the entry of edge side, preferably be embodied as a plurality of entries in a clutch-plate tooth section (96), particularly preferably be embodied as the extend radially section of the interdental spaces of a clutch-plate tooth section (96).

3. parallel double engaging and disengaging gear described according to any one in above claim (2), it is characterized in that, this first and second lamella clutch (28, 30) input side is formed by an outer clutch-plate support (50), and the outlet side of this first lamella clutch (28) is formed by first an interior clutch-plate support (46) and the outlet side of this second lamella clutch (30) is formed by second an interior clutch-plate support (48), wherein these depressed parts (90) preferably are implemented in these outer clutch-plates (36) of this second group (34), or/and this first actuating element (38) and this second actuating element (40) have be used to compressing corresponding sheet group (32, 34), identical steering (82).

4. the described parallel double engaging and disengaging gear of any one (2) according to claim 2 or 3, it is characterized in that, (36) are provided with and are in due course flexible a plurality of clutch-plate dividing elements (100) between with the clutch-plate adjacent one another are of depressed part (90), preferred spring element, ripple spring or with the ring of ripple, wherein these clutch-plates with window type depressed part (90) (36) particularly preferably have one radially (12, 14) be arranged between these window type depressed parts (90) and a clutch-plate tooth section (96), at circumferencial direction (16, 18) on consistently or sealing ground around supporting section (98), this clutch-plate dividing element (100) can support or be supported on this supporting section, form in due course, realize an area of contact between corresponding clutch-plate (36) and this clutch-plate dividing element (100), this area of contact formed area of contact between this clutch-plate dividing element (100) and this supporting section (98) more than 50%, more than 95% or 100%.

5. parallel double engaging and disengaging gear described according to any one in above claim (2), it is characterized in that, this first actuating element (38) and this second actuating element (40) are can be hydraulically powered, wherein this first actuating element (38) is preferably attached troops to a unit first pressure chamber (76) of an enough hydraulic oil loading of energy, and the second pressure chamber (78) that this second actuating element (40) is attached troops to a unit and had the enough hydraulic oil of energy to load, and particularly preferably be provided with a plurality of be used to making these actuating elements (38, 40) spring element of return (88), these spring elements are to be arranged in to attach troops to a unit in these actuating elements (38 in due course, 40) a plurality of pressure equalizing chambers (84, 86) within.

6. parallel double engaging and disengaging gear described according to any one in above claim (2), it is characterized in that, this first actuating element (38) is attached troops to a unit first pressure equalizing chamber (84), preferably have a kind of the first overflow (106) and a kind of the first incoming flow (102) that separates with this first overflow (106) in due course, and this second actuating element (40) is attached troops to a unit second pressure equalizing chamber (86), preferably have a kind of the second overflow (108) and a kind of the second incoming flow (104) that separates with this second overflow (108) in due course, wherein particularly preferably this first group (32) can be passed through from this second pressure equalizing chamber (86), cooling by the oil of this second overflow (108) outflow in due course, and this second group (34) can be passed through from this first pressure equalizing chamber (84), cooling by the oil of this first overflow (106) outflow in due course.

7. parallel double engaging and disengaging gear according to claim 6 (2), it is characterized in that, this second group (34) is arranged in the rear of this first group (32) on one axial (10), and this second pressure equalizing chamber (86) is arranged in the place ahead of this first pressure equalizing chamber (84) on identical axial (10), wherein preferred this first pressure equalizing chamber (84) with this second group (34) or/and the nestedly arrangement on radially (12,14) of this second pressure equalizing chamber (86) and this first group (32).

8. the described parallel double engaging and disengaging gear of any one (2) according to claim 6 or 7, it is characterized in that, lead to these pressure equalizing chambers (84,86) the oily charging at least one in, to lead to the oily charging in this first pressure equalizing chamber (84) and lead to oily charging in this second pressure equalizing chamber (86) in due course, be variable, wherein preferably can will lead to a pressure equalizing chamber (84; 86) oily charging with lead to another pressure equalizing chamber (86; 84) the oily charging in irrespectively reduces, increases or change, is reduced in due course zero, and a control gear (126) particularly preferably is set, is a valve positioner in due course, be used for changing corresponding oily charging, this control gear is in by at least one first feed pipe (128) and this first pressure equalizing chamber (84) that circulation is connected in due course and the second feed pipe (130) by at least one and this first feed pipe (128) separation is in to circulate with this second pressure equalizing chamber (86) and is connected.

9. the described parallel double engaging and disengaging gear of any one (2) according to claim 6 to 8, it is characterized in that, this control gear (126) as follows with this second lamella clutch (30) acting in conjunction, make the oily charging of leading in this first pressure equalizing chamber (84) to reduce relatively, to increase or to change with the on-state of this second lamella clutch (30), preferably the second lamella clutch (30) when opening less than at this second lamella clutch (30) when closing; Or/and this control gear as follows with this first lamella clutch (28) acting in conjunction, make the oily charging of leading in this second pressure equalizing chamber (86) to reduce relatively, to increase or to change with the on-state of this first lamella clutch (28), preferably the first lamella clutch (28) when opening less than at this second lamella clutch (28) when closing.

10. the described parallel double engaging and disengaging gear of any one (2) according to claim 6 to 9, is characterized in that, from this first or second pressure equalizing chamber (84; 86) oil that flows out can be guided through on radially (12) actuating element (38) or/and a tubular segments (116 of a clutch-plate support (48), 120) a plurality of openings (114 in, 118), wherein preferably be provided with one at radially (14) upper inwardly open capture slot (122) on the inboard of this tubular segments (116), this capture slot particularly preferably by means of one radially (14) upper inwardly outstanding, circumferencial direction (16,18) upper around obstruction wall (124) and be created on the inboard of this tubular segments (116).

11. parallel double engaging and disengaging gear described according to any one in above claim (2), it is characterized in that, a pressure portion (136), this pressure portion is embodied as annular in due course or/and be embodied as pressure disk, this pressure portion releasably, preferably be fixed on this first actuating element (38) engagement typely and can be pressed against on this first group (32), wherein this pressure portion (136) particularly preferably was fixed on the upper while of this first actuating element (38) at two axial (8, 10) upward realize a kind of connection of synchronizeing between this first actuating element (38) and this pressure portion (136).

12. parallel double engaging and disengaging gear described according to any one in above claim (2), it is characterized in that, this first actuating element (38) has a plurality of axial dactylitic pieces (92), these axial dactylitic pieces extend through these depressed parts (90), these axial dactylitic pieces (92) of wherein implementing with this first actuating element (38) single-piece in due course preferably are embodied as following length: make its free end (94) on axially (8) pass this second group (34) and give prominence to, and this pressure portion (136) is releasably secured on these free ends (94).

13. parallel double engaging and disengaging gear described according to any one in above claim (2), it is characterized in that, this first actuating element (38) is preferred by this pressure portion (136) outside these depressed parts (90), particularly preferably being in rotary synchronous by a kind of tooth section's engagement (146) with an input side of this pair engaging and disengaging gear (2) is connected, wherein this first actuating element (38) is in due course at circumferencial direction (16, 18) upper and marginating compartments these depressed parts (90) are opened, or/and this first actuating element (38) is guaranteed not to be subjected to the first actuating element (38) outside these depressed parts (90), the impact of the broadening that is caused by centrifugal force, preferably radially (12, 14) support on, particularly preferably supported by this pressure portion (136), wherein this first actuating element (38) in due course radially (12) outwards upper and final also inwardly and marginating compartment of these depressed parts (90) open.

14. parallel double engaging and disengaging gear described according to any one in above claim (2), it is characterized in that, these first and second groups (32, 34) be provided with an intermediate disc (66) between, this second group (34) can support or be supported on this intermediate disc, it is inner or be arranged in a clutch-plate support place that wherein this intermediate disc (66) preferably releasably is arranged in this pair engaging and disengaging gear (2), being arranged in due course this outer clutch-plate support (50) locates, and a plurality of depressed parts (72) that this first actuating element (38) particularly preferably passes in this intermediate disc (66) extend, these depressed parts (72) have convexly curved (74) on axial (10) in due course in order to be formed for a supporting zone of this second group (34).

15. be used for making the method for according to claim 6 to 9 described pair of engaging and disengaging gear of any one (2) work, wherein

The oily charging of leading in this first pressure equalizing chamber (84) is controlled as follows, make in the oily charging of this second lamella clutch (30) when opening less than the oily charging of the second lamella clutch (30) when closing, the oily charging of wherein leading to when opening in this first pressure equalizing chamber (84) at this second lamella clutch (30) is prevented from, or/and

The oily charging of leading in this second pressure equalizing chamber (86) is controlled as follows, make in the oily charging of this first lamella clutch (28) when opening less than the oily charging of the first lamella clutch (28) when closing, the oily charging of wherein leading to when opening in this second pressure equalizing chamber (86) at this first lamella clutch (28) is prevented from.