CN101153651B - Torque converter - Google Patents
Torque converter Download PDFInfo
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- CN101153651B CN101153651B CN2007101544987A CN200710154498A CN101153651B CN 101153651 B CN101153651 B CN 101153651B CN 2007101544987 A CN2007101544987 A CN 2007101544987A CN 200710154498 A CN200710154498 A CN 200710154498A CN 101153651 B CN101153651 B CN 101153651B
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- torque converter
- joint
- clutch
- fluid torque
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/24—Details
- F16H2041/246—Details relating to one way clutch of the stator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
- F16H2045/0284—Multiple disk type lock-up clutch
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- Control Of Fluid Gearings (AREA)
Abstract
Disclosed is a torque converter (A), which comprises at least two thrust bearings (45) disposed on respective axially-opposite sides of a radially-inward portion (35) of a stator (30). The stator includes a non-rotatable member (43), a rotatable member (42) and a one-way clutch (40). The rotatable member (42) has a cylindrical portion having an inner peripheral surface interlocked with the one-way clutch (40), and an extension portion (37) which extends from an approximately axially-central region of the cylindrical portion in a radially-outward direction relative to the cylindrical portion (38), and has an axial thickness less than that of the cylindrical portion. The thrust bearings (45) are disposed to clamp the extension portion (37) from respective axially-opposite sides of the extension portion (37) at respective positions located radially outwardly relative to the cylindrical portion (38), so as to facilitate reduction in axial dimension of the torque converter.
Description
Technical field
The present invention relates to a kind ofly possess pump impeller (pump impeller), turbine (turbine runner) and blade (blade) and torque is delivered to the fluid torque converter (torqueconverter) of carry-out part from input part, particularly relate to the fluid torque converter that is tending towards compact in the axial direction by the fluid that between these parts, circulates.
Background technique
Known in the past fluid torque converter, comprise the pump impeller that contacts with input part, and turbine that with carry-out part contact opposed, have the stator (stator) of the blade between the interior perimembranous of the interior perimembranous that is arranged on pump impeller and turbine with this pump impeller, by pump impeller, turbine and blade each other (in their formed race ways) fluid of circulating torque is delivered to carry-out part from input part.
The employed fluid torque converter of the automatic transmission of vehicle for example, its input part is connected with motor, and its carry-out part is connected with the gear of automatic transmission.That is, because the Power Train (power train) from the motor to the automatic transmission is an arranged in series, so total length is elongated easily.In recent years, requirement to the miniaturization of the containing space of Power Train that is engine compartment (engineroom) is increased day by day, follow in this, shorten the requirement of the total length of Power Train, particularly the requirement of the axially compact degree of fluid torque converter is also increased thereupon.
As being tending towards compact fluid torque converter in the axial direction, known have the open communique spy of Japan Patent to open disclosed technology No. 2006118654.This fluid torque converter, have and mechanically directly connect input part (protecgulum) and carry-out part (lock-up clutch (lockup clutch) mechanism of turbine hub (turbine hub), but also possess buffer (damper) device that when it operates, absorbs the cogging between input part and the carry-out part.And, make fluid torque converter be tending towards compact in the axial direction by on the layout between turbine hub and buffer device, working hard.
In addition, be provided with overrunning clutch (one-way clutch), axially be provided with the thrust-bearing (thrust bearing) that bears the thrust that acts on stator in the both sides in the outside at it in interior all sides of stator.
Yet, be tending towards compact in the axial direction more in order to make fluid torque converter, also need further to realize compact scheme.
Summary of the invention
Purpose of the present invention is to provide a kind of fluid torque converter that addresses the above problem.
Fluid torque converter of the present invention comprises, input part; Carry-out part; The pump impeller that directly or indirectly is connected with input part; And turbine that with carry-out part directly or indirectly be connected opposed with this pump impeller; Stator with the blade between the interior perimembranous of the interior perimembranous that is arranged on above-mentioned pump impeller and above-mentioned turbine; Be separately positioned on the axial both sides of all sides in the said stator and bear the thrust-bearing of the thrust that acts on this stator; Torque is passed through at above-mentioned pump impeller, the fluid that circulates in above-mentioned turbine and the formed race way of above-mentioned blade is delivered to above-mentioned carry-out part from above-mentioned input part, said stator, comprise to forbid with respect to the support platform of fluid torque converter that the state that rotates is provided with and in the form of a ring non-rotatable member roughly, roughly in the form of a ring and be arranged on the rotatable components of above-mentioned non-rotatable member outer circumferential side, and be arranged between above-mentioned non-rotatable member and the above-mentioned rotatable components and support above-mentioned rotatable components and allow the overrunning clutch that it only rotates to direction with respect to above-mentioned non-rotatable member, above-mentioned rotatable components, comprise the cylindric portion that inner peripheral surface and above-mentioned overrunning clutch directly or indirectly contact, and roughly extend and axial thickness is thinner than the portion that extends of this cylindric portion to the radial outside of this cylindric portion from the axial central part of this cylindric portion, above-mentioned each thrust-bearing at the outer circumferential side of above-mentioned cylindric portion from the above-mentioned portion that extends of axial sandwich, the above-mentioned portion that extends, along with inside all side is extended and attenuation, with above-mentioned cylindric connecting part that engages near the thinnest.
Adopt above-mentioned hydraulic pitch device, can shorten the axial length of interior all sides (being equivalent to is the position that is provided with thrust-bearing of the portion that extends of stator at least) of fluid torque converter, to realize compactness.
Particularly, at first,, can guarantee as the necessary axial length of part that contacts with overrunning clutch in the cylindric portion of stator.Overrunning clutch, owing to bear the hydrokinetic reaction force that acts on blade, thereby effect has bigger torque.Therefore, overrunning clutch in order to ensure the intensity that can bear higher torque rightly, must have thickness (axial length) to a certain degree.With respect to this, because the cylindric portion of the rotatable components of stator, compare with the portion of extending and to have relative long axial length, so can suitably directly or indirectly contact with overrunning clutch.
On the other hand, the portion of extending is the parts of the blade of cylindric of all sides and outer circumferential side in directly or indirectly connecting with transmitting torque, but that its thickness need not is identical with cylindric.In addition, extend portion, can make it be thinner than cylindric (shortening axial length) fully by adopting suitable high-intensity material to form this.Extend portion's attenuation, can make cylindric and extend between the portion and to produce axial length poor (end difference).Among the present invention, end difference is arranged on the axial both sides of the portion of extending, and thrust-bearing is set herein.
Adopt above-mentioned setting because the part of the thickness of thrust-bearing absorbed by above-mentioned end difference, therefore, the length that the axial length from a side thrust-bearing to the opposing party's thrust-bearing is smaller than cylindric portion add the simple of 2 thrust-bearing thickness and.Can correspondingly shorten axial length thus, make structure be tending towards compact.
In addition, make fluid torque converter be tending towards compact in the axial direction, not only can shorten total length, also can shorten axial length as interior all side parts of fluid torque converter.As mentioned above, because fluid torque converter is arranged between input side mechanism (motor etc.) and the outlet side mechanism (gear etc.), therefore, even if the axial length of local (interior all side parts) is shortened, but the part of system can be arranged on above-mentioned axial length to be shortened in the formed space, back, can shorten the total length of whole system thus.
In above-mentioned fluid torque converter, comparatively it is desirable to, above-mentioned rotatable components comprises, comprises the outer circumferential side parts that above-mentioned blade and interior all sides have the 1st joint, and outer circumferential side has interior all side components of the 2nd joint that is connected with above-mentioned the 1st joint, all side components in above-mentioned are made of structural steel, comprise above-mentioned cylindric and the above-mentioned portion that extends, the above-mentioned portion that extends, its outer circumferential side is with respect to interior all side direction offset rearward.
Adopt above-mentioned fluid torque converter, the outer circumferential side parts that comprise blade can adopt the relatively low material of intensity (for example resin, light metal etc.) to guarantee higher formability, the interior all side components that comprise the portion of extending simultaneously can adopt the higher structural steel of intensity, with abundant reduction thickness, make the effect of compactness more remarkable.
As structural steel, particularly, adopt carbon steel, chromium steel, Cr-Mo steel etc. more suitable.In addition, quench as required, surface treatment such as carburizing, nitriding is also very effective.
In addition, in above-mentioned fluid torque converter, comparatively it is desirable to, the joint that above-mentioned the 1st joint is connected with above-mentioned the 2nd joint adopts spline chimeric, and both axially relatively moving forbidden by axial latch for printed circuit.
Adopt above-mentioned fluid torque converter, can easily connect each other independently outer circumferential side parts and interior all side components by joint.
In above-mentioned fluid torque converter, comparatively it is desirable to, the inner peripheral surface of above-mentioned cylindric portion forms the overrunning clutch outer ring with the snap-fit element butt of above-mentioned overrunning clutch.
Adopt above-mentioned fluid torque converter, because the inner peripheral surface of cylindric portion is used as the overrunning clutch outer ring, thus need not to be provided with separately the overrunning clutch outer ring, thus, but simplified structure.As mentioned above, because effect has bigger torque on the overrunning clutch, therefore require the overrunning clutch outer ring to have higher intensity.Among the present invention, constitute by the higher structural steel of intensity, therefore can directly be used as the overrunning clutch outer ring cylindric owing to comprise interior all side components of cylindric portion.
In above-mentioned fluid torque converter, comparatively it is desirable to, also comprise, mechanically directly connect the lock-up clutch of above-mentioned input part and above-mentioned carry-out part; When being in coupled condition, above-mentioned lock-up clutch absorbs the lock-up clutch buffer of the cogging between above-mentioned input part and the above-mentioned carry-out part; Above-mentioned lock-up clutch buffer is set up in parallel an axial side at this stator with respect to said stator, above-mentioned rotatable components, and its outer circumferential side is put to the lateral deviation in contrast to the lock-up clutch buffer in the axial direction with respect to interior all sides.
Adopt above-mentioned fluid torque converter, the outer circumferential side that the lock-up clutch buffer can be arranged on rotatable components is setovered in the axial direction with respect to interior all sides and in the space that obtains.Therefore, can more effectively utilize the space in the fluid torque converter, to promote compactness.
In addition, in above-mentioned fluid torque converter, comparatively it is desirable to, the outer shape of above-mentioned pump impeller one side of the support of this hydraulic pitch device is, the outer circumferential side that forms above-mentioned race way is that the protuberance starting point is swelled with the assigned position with respect to the base portion of interior all sides, the joint that above-mentioned the 1st joint is connected with above-mentioned the 2nd joint, its radial position is positioned at the outer circumferential side of above-mentioned protuberance starting point and is positioned at all sides of the most all positions of above-mentioned race way, above-mentioned in the axial thickness of assigned position of all sides that are positioned at above-mentioned joint of all side components be thinner than the axial thickness of above-mentioned joint.
Adopt above-mentioned fluid torque converter,, can guarantee necessary race way thickness at the outer circumferential side of fluid torque converter.Particularly, can guarantee that blade is to realize the necessary thickness of its function, and adopt the relatively low material (for example resin, light metal etc.) of intensity can obtain higher formability for stator.
On the other hand, in interior all sides of fluid torque converter, interior all side components of stator adopt the higher material of intensity, can make its thickness attenuation thus, so both can guarantee necessary strength, can shorten axial length again, to realize compactness.
In above-mentioned fluid torque converter, comparatively it is desirable to, at least one side of above-mentioned the 1st joint and above-mentioned the 2nd joint, the axial thickness of interior all sides is thinner than the axial thickness of outer circumferential side.
Adopt above-mentioned fluid torque converter, can guarantee the intensity (outer circumferential side) of joint and realize compactness (interior all sides).
Description of drawings
Fig. 1 is upper half part of the longitudinal sectional view of related fluid torque converter of expression embodiments of the present invention and circumferential component thereof.
Fig. 2 is the partial enlarged drawing of Fig. 1.
Embodiment
Below, with reference to accompanying drawing embodiments of the present invention are described.Fig. 1 is upper half part of the longitudinal sectional view of related fluid torque converter of expression embodiments of the present invention and circumferential component thereof.The fluid torque converter 1 of present embodiment is used to be equipped with the vehicle of automatic transmission.Be fluid torque converter 1, be arranged between the gear (generally constituting) of the outer automatic transmission of outer motor of figure and figure, carry out transmission of power thus by planetary gears and a plurality of clutch.Under state shown in Figure 1, the left side of fluid torque converter 1 is provided with motor, and the right side of fluid torque converter 1 is provided with the gear of automatic transmission.For simplicity, in the following description, the left side of Fig. 1 (starting pusher side) is called the front side, and right side (automatic transmission side) is called rear side.In addition, about sense of rotation, setting the direction identical with the sense of rotation of motor is positive veer, with the direction of the direction of rotation of motor be reverse direction.
Fluid torque converter 1 is housed in the transmission case (transmission case) 90 as its support platform.In addition, in the present embodiment, the rear of fluid torque converter 1 is provided with oil pump 80.
Fluid torque converter 1 mainly comprises, input side constituent element, outlet side constituent element, stator constituent element (stator 30 and peripheral constituent element thereof), lock-up clutch 60, lock-up clutch buffer 50.
The input side constituent element constitutes by input part (protecgulum 13) and with the parts of its unitary rotation.Protecgulum 13 is fixed with a plurality of bolts 18 that are positioned on the concentric circle and forwards give prominence to.The driver plate (drive plate) of these bolts 18 outside scheming engages with the bent axle of motor.Be that protecgulum 13 is unitary rotation with bent axle.
Interior all sides of pump impeller sleeve 11 have the cylindrical part of extending rearward, and the rear end of pump impeller sleeve 11 engages with the pump rotor (pump rotor) 82 of oil pump 80.In addition, above-mentioned cylindrical part is supported on the transmission case 90 freely by oil pump casing (pump housing) 81 rotations of oil pump 80.
The outlet side constituent element constitutes by carry-out part (turbine hub 23) and with the parts of its unitary rotation.The interior perimembranous of turbine hub 23, chimeric with turbine shaft (input shaft of the gear of the automatic transmission) spline that figure is outer, and with its formation unitary rotation.
The stator constituent element is made of stator 30 and thrust-bearing 45 of being arranged on all sides in its front and back etc.Relevant stator constituent element elaborates with reference to Fig. 2 after a while.
Lock-up clutch 60 is the clutches that mechanically directly connect input part (protecgulum 13) and carry-out part (turbine hub 23) (locking).The lock-up clutch 60 of present embodiment, the wet multi-plate clutch structure of control performance that the easy acquisition of employing is higher and higher transmitting torque, by lock-up clutch buffer (hereinafter to be referred as the locking buffer) 50, protecgulum 13 directly is connected with turbine hub 23.
Lock-up clutch 60 comprises, is fixed on the protecgulum 13 and interior all sides are formed with cylindric clutch hub drum (the clutch hub drum) 65 of spline 65a; The discoideus lockup piston 63 that in this clutch hub drum 65, moves up in front and back along spline 65a; On the interior circumferential position of regulation, make lockup piston 63 slip interior drum 61 and the external drum 62 that is supported possibly through sealed member.The zone that protecgulum 13, lockup piston 63, interior drum 61 and external drum 62 are surrounded, formation make the hydraulic chamber 64 of the working oil (adopting the ATF identical with the working oil of fluid torque converter 1 in the present embodiment) of lockup piston 63 runnings.
In the clutch hub drum 65, alternately respectively be provided with 2 mutually at the rear of lockup piston 63 friction plate 66 and plate 67, the rear of these parts also is provided with retaining plate (retaining plate) 68, and end by snap ring (snapring) 69 cards the rear end of this retaining plate 68.
On the other hand, be arranged between the plate 67 or plate 67 and retaining plate 68 between friction plate 66, be pasted with the annular metal sheet of friction material for the two sides.Friction plate 66, perimembranous engages with the buffer main body 51 of locking buffer 50 in it.Buffer main body 51 is fixed on the turbine hub 23 with turbine shell 21 by rivet 25.Thus, friction plate 66 reaches the turbine hub 23 that forms one with this buffer main body 51 with buffer main body 51 and is unitary rotation.
The buffer spring 52 of present embodiment has adopted than the general in the past spring that buffer spring is more large-scale and the cogging absorbability are higher.Follow the maximization of buffer spring 52, in order to ensure it space is set, turbine shell 21 is rearward crooked near buffer spring 52.
As shown in Figure 1, be provided with oil pump 80 at the rear of fluid torque converter 1.Oil pump 80 is the hydraulic powers that the working fluid ATF in the fluid torque converter 1 or the hydraulic chamber 64 of lock-up clutch 60 etc. provided hydraulic pressure.In addition, this oil pump 80 also is the clutch group's of the outer gear of figure a hydraulic power.
Fig. 2 is the partial enlarged drawing of Fig. 1, and it is represented in detail to the part that comprises pump impeller shell 12, turbine shell 21 and stator constituent element especially.Below, with reference to Fig. 2 above-mentioned part is described.
Between pump impeller shell 12 and the turbine shell 21, be provided with stator 30.Stator 30 has the blade 32 that is configured between pump impeller 15 interior perimembranous and the turbine 22 interior perimembranous, and this blade 32 is only to be supported to the state of a direction (positive veer) rotation around axle.
Like this, fluid torque converter 1, its outer circumferential side (position that is equivalent to race way 28) has suitable axial thickness, guaranteed suitable race way thus, (28 positions that are positioned at all sides of all sides in it than the race way, particularly be positioned at the position of all sides of base portion 12b) axial length significantly shortened than outer circumferential side, what make fluid torque converter 1 thus axially is tending towards compact.
Overrunning clutch inner ring 43, as shown in Figure 1, inner circumferential surface and oil pump cover 85 splines are chimeric.That is, overrunning clutch inner ring 43 is to be supported on non-rotatable member on the transmission case 90 by oil pump cover 85 and oil pump casing 81 with the state of forbidding rotating.
Joint 34, its radial position is positioned at the outer circumferential side of protuberance starting point 12c and the most all positions of 28 are positioned at all sides than the race way, comparatively it is desirable to, do not cause the position (near the position of race way 28) that is set in as much as possible in the dysgenic scope near periphery smooth and easy flowing to ATF.In addition, the axial thickness of interior all sides of the spline 33,36 of formation joint 34 is thinner than the axial thickness of outer circumferential side.
Outer circumferential side parts 31, the material relatively low by intensity constitutes.For example light metal of resin or aluminium, magnesium and so on etc. is more suitable.Outer circumferential side parts 31 have the thickness t 1 of regulation, and the thickness of setting but this thickness t 1 is based on the shape need of blade 32 is not necessarily to need this thickness t 1 on intensity.That is, outer circumferential side parts 31 because of the requirement of shape have aspect the intensity more than needed.Therefore, in the scope that can obtain necessary intensity, can adopt the relatively low material of intensity.Do like this, compare when adopting the higher material of intensity, not only can guarantee necessary strength but also can obtain higher formability (high efficiency).
In all side components 35, the portion that extends 37 that is thinner than cylindric 38 by cylindric 38 of interior all sides and axial thickness constitutes, wherein, cylindric 38 inner peripheral surface engages with overrunning clutch 40; Extending portion 37 roughly extends to radial outside from cylindric 38 axial central part.Cylindric 38 with extend portion 37 and form one.
Extend portion 37, the outer peripheral portion the thickest (axial dimension is longer) of its outermost perimembranous that is spline 36 is along with inside all sides are extended and attenuation gradually.With cylindric 38 connecting part that engages near (being positioned at the assigned position of all sides in interior all side components 35 than joint 34) the thinnest (thickness t 2).
In addition, extend portion 37 (also we can say in all side components 35), its outer circumferential side is with respect to interior all side direction offset rearward (side opposite with locking buffer 50).
As mentioned above, the base portion 12b of pump impeller shell 12 is forwards outstanding significantly.On the other hand, rearward crooked in the turbine shell 21 with the corresponding radial position of base portion 12b.Therefore, the portion that extends 37 between pump impeller shell 12 and turbine shell 21 is provided with the space, and near the radial dimension base portion 12b is the narrowest, and forwards setovers with respect to the axial position of blade 32 near this place.In the present embodiment, extend portion 37, and be set at above-mentioned biasing shape, also the portion of extending 37 can be set appropriately at the unfavorable factor that the space is set thus, thereby make axial length be tending towards compact by thin-walled property.
In addition, interior all side components 35, with outer circumferential side parts 31 be separate parts, it adopts the higher structural steel of intensity.Particularly, carbon steel (carbon steel) (for example S30C～S50C (JIS (Japanese Industrial Standard)) etc.), chromium steel (chrome steel) (for example SCr420 (JIS) etc.), Cr-Mo steel (chrome molybdenum) (for example SCM420 (JIS) etc.) etc. are more suitable.In addition, also can quench as required, surface treatment such as carburizing, nitriding.Do like this, both can guarantee the intensity of the portion of extending 37, can promote its thin-walled property as best one can again.
In addition,, therefore can ask the intensity of guaranteeing joint 34, ask compactness in interior all side force in the periphery side force because the axial thickness of interior all sides of spline 33 and spline 36 is thinner than the axial thickness of outer circumferential side.
Cylindric 38, its thickness (axial length) is the thickness t 3 identical with overrunning clutch inner ring 43 or overrunning clutch 40.Cylindric 38, the overrunning clutch outer ring (outerrace) that engages with the snap-fit element 41 of overrunning clutch 40 for inner peripheral surface.The overrunning clutch 40 of present embodiment is so-called wedge block type (sprag type), and snap-fit element 41 is a voussoir.
Overrunning clutch 40, owing to bear the hydrokinetic reaction force that acts on blade, thereby effect has bigger torque.Therefore, overrunning clutch 40 in order to ensure the intensity that can bear above-mentioned high torque (HT) rightly, must have axial length (thickness t 3) to a certain degree.Play a role as the overrunning clutch outer ring cylindric 38, have the thickness t 3 identical with overrunning clutch 40, and, owing to constituted, so can bring into play function rightly as the overrunning clutch outer ring by the higher structural steel of intensity.
In addition since with cylindric 38 inner peripheral surface as the overrunning clutch outer ring, therefore need not the overrunning clutch outer ring is set separately, but simplified structure thus.
Be positioned near cylindric 38 end difference, be provided with 2 thrust-bearings 45 that extend portion 37 from the front and back sandwich with the boundary that extends portion 37.Particularly, the thrust-bearing 45 of front side is arranged on turbine hub 23 and extends between the portion 37 by bearing race 46,47, and the thrust-bearing 45 of rear side is arranged on pump impeller sleeve 11 and extends between the portion 37 by bearing race 46,47.Thrust-bearing 45 positions stator 30 on fore-and-aft direction, and bears the thrust that acts on stator 30 (blade 32).
If setting the thickness of 1 thrust-bearing 45 that comprises bearing race 46,47 is t4, so, the leading flank of side bearing seat ring 46 can be expressed as t5=t2+2t4 to the axial distance t5 of the trailing flank of rear side bearing race 46 in the past.This than cylindric 38 and extend do not establish end difference between the portion 37 and when thrust-bearing 45 being set at thickness t 3 places the size t3+2t4 of (structure in the past) to lack.Promptly by making the portion's of extending 37 thin-walled properties, at cylindric 38 with extend between the portion 37 end difference is set, and thrust-bearing 45 is set at this end difference, can shorten the axial dimension at this place, to realize axial compactness.
Below, the running of fluid torque converter 1 is described.At first the rotating speed that lock-up clutch 60 is in off working state (locking open (OFF)) and turbine hub 23 (turbine 22) describes less than the situation of the rotating speed (speed ratio is little) of protecgulum 13 (pump impeller 15).Such state is when stopping (speed of turbine hub 23=0) or occur when just having started.
When locking is open, there is minimum gap between the plate 67 of lock-up clutch 60, retaining plate 68 and the friction plate 66, therefore can relatively rotate.Be that the protecgulum 13 of input part and the turbine hub 23 of carry-out part are in relatively turnable state.
At this moment, the flow direction of working fluid ATF in race way 28 shown in arrow A 1, is pump impeller 15 → turbine 22 → blade 32 → pump impeller 15.In fact, ATF also has a hoop (direction vertical with paper) mobile except that flowing of above-mentioned direction is, constitutes Three-dimensional Flow thus.The torque of input side passes to ATF from pump impeller 15, and then is passed to outlet side by turbine 22.Return the ATF of blade 32 from turbine 22, flow to the direction that blade 32 is rotated to reverse direction.Yet,, make the ATF conversion direction thus and return pump impeller 15 because this reverse forbidden that by unidirectional clutch 40 therefore, blade 32 (rotatable components 42) maintains halted state.
Play a part to strengthen circular flow (arrow A 1) owing to return the ATF of pump impeller 15 behind the conversion direction, thus, stronger torque just passes to turbine 22.Therefore, at this moment,, obtain greater than input part that is greater than the torque (effect of torque amplification) of the torque of protecgulum 13 at carry-out part that is in turbine hub 23.
Then, the rotating speed that lock-up clutch 60 is in open state and turbine hub 23 (turbine 22) describes greater than the situation of the rotating speed (speed ratio is big) of protecgulum 13 (pump impeller 15).Such state occurs when reaching certain speed of a motor vehicle after starting or when less stable the travelling of load.
At this moment, working fluid ATF also forms the circular flow of pump impeller 15 → turbine 22 → blade 32 → pump impeller 15 in race way 28.But different with above-mentioned situation is that the ATF that returns blade 32 from turbine 22 flows to the direction that blade 32 is rotated to positive veer.Because this is just transferring overrunning clutch 40 to and is allowing, therefore, blade 32 (rotatable components 42) is equally just changeing with pump impeller 15, turbine 22.Like this, just the fluid coupling (fluidcoupling) of the no torque amplification of 28 formation effect in the race way at carry-out part that is in turbine hub 23, obtains the slightly little torque of torque than the protecgulum 13 of input part.
Then, lock-up clutch 60 in running order situations are described.Such state reaches the speed of a motor vehicle of regulation after starting, the outer control unit of figure occurs when sending the locking instruction.
After sending the locking instruction, hydraulic pressure just supplies to hydraulic chamber 64, and lockup piston 63 just rearward moves.Each friction plate 66 and each plate 67 thus all are pressed towards retaining plate 68 1 sides at rear, and the frictional force by mutual effect stops and relatively rotates (jointing state).That is, do not have between protecgulum 13 and the turbine hub 23 and relatively rotate, thereby be in direct coupled condition (lockup state).
Because directly the locking mode of coupled condition is compared with the power delivery mode that is undertaken by fluid, can be because of fluid does not cause slip, so have the high advantage of transmission efficiency.Therefore, enlarge locking zone (zone that vehicle travels) under lockup state and will greatly help to improve burnup.From such viewpoint, in the present embodiment, set remarkable locking zone (for example the 1st grade of zone that speed is above, i.e. velocity band after the starting) greater than general in the past locking zone (for example the 4th grade of high-speed region that speed is above).Lock-up clutch 60 adapts to the expansion in locking zone by the wet multi-plate clutch structure that adopts higher control performance of easy acquisition and higher transmitting torque.
When locking, from the transmission of torque of protecgulum 13, undertaken, to absorb cogging by locking buffer 50 to turbine hub 23.When cogging relatively hour, only moderately absorb cogging by buffer spring 52, when cogging when to a certain degree above, also can absorb cogging forcefully by limit spring 53.
As mentioned above, in the present embodiment, just carry out locking from low speed segment (low speed of a motor vehicle zone) beginning.Because the cogging of motor is bigger in the low speed segment, when therefore in this zone, carrying out locking, the vehicle body vibrations is aggravated, thereby riding comfort is aggravated.Yet, in the present embodiment, eliminated this problem by adopting buffer spring 52 large-scale and that the cogging absorptivity is higher.
Below, the advantage that shortens the axial length of all sides in the fluid torque converter 1 is described.As shown in Figure 1, oil pump casing 81, stretch out significantly in all side direction the place ahead in it, and its front end is positioned at the place ahead than the rear end of pump impeller shell 12.Owing to be set at bigger size from the rear end of pump impeller shell 12 to the outstanding overhang 12d (as shown in Figure 2) of base portion 12b, so can realize above-mentioned configuration.
If fluid torque converter 1 adopts above-mentioned setting with oil pump 80, so, stretch into interior all sides of the fluid torque converter 1 of realizing compactness by the protuberance that makes oil pump 80, compare with the structure that merely oil pump 80 is arranged on fluid torque converter 1 rear (rears of pump impeller shell 12 rear ends), can shorten both and engage the required axial length in back.
More than, embodiments of the present invention are illustrated, but, these mode of executions can be done suitable variation in the scope that does not break away from purport of the present invention.For example, the structure of the structure of lock-up clutch 60 or locking buffer 50 is not limited to above-mentioned mode of execution, and it can be the structure of any kind.
In addition, overrunning clutch 40 is not limited to wedge block type, for example also can be roller type.At this moment, snap-fit element 41 is a roller.
In addition, fluid torque converter 1 is not limited the set parts of its periphery.For example, the parts beyond the oil pump 80 can be set also at the rear of fluid torque converter 1, and the interior perimembranous of the fluid torque converter 1 that its part is stretched into realize compactness.In addition, also be not limited to the layout that the interior perimembranous of fluid torque converter 1 is stretched in the part (or all) that makes some parts.
Claims (11)
1. fluid torque converter is characterized in that:
Comprise,
Input part;
Carry-out part:
The pump impeller that directly or indirectly is connected with above-mentioned input part;
And turbine that with above-mentioned carry-out part directly or indirectly be connected opposed with above-mentioned pump impeller;
Stator with the blade between the interior perimembranous of the interior perimembranous that is arranged on above-mentioned pump impeller and above-mentioned turbine;
Be separately positioned on the axial both sides of all sides in the said stator and bear the thrust-bearing of the thrust that acts on this stator;
Torque is delivered to above-mentioned carry-out part by the fluid that circulates from above-mentioned input part in above-mentioned pump impeller, above-mentioned turbine and the formed race way of above-mentioned blade,
Said stator, comprise, to forbid with respect to the support platform of fluid torque converter that the state that rotates is provided with and in the form of a ring non-rotatable member roughly, roughly in the form of a ring and be arranged on the rotatable components of above-mentioned non-rotatable member outer circumferential side, and be arranged between above-mentioned non-rotatable member and the above-mentioned rotatable components and support above-mentioned rotatable components and allow the overrunning clutch that it only rotates to direction with respect to above-mentioned non-rotatable member
Above-mentioned rotatable components comprises, the cylindric portion that inner peripheral surface and above-mentioned overrunning clutch directly or indirectly contact, and roughly extend and axial thickness is thinner than the portion that extends of this cylindric portion to the radial outside of this cylindric portion from the axial central part of this cylindric portion,
Above-mentioned each thrust-bearing, at the outer circumferential side of above-mentioned cylindric portion from the above-mentioned portion that extends of axial sandwich,
The above-mentioned portion that extends, along with inside all side is extended and attenuation, with above-mentioned cylindric connecting part that engages near the thinnest.
2. fluid torque converter according to claim 1 is characterized in that:
Above-mentioned rotatable components comprises, comprises the outer circumferential side parts that above-mentioned blade and interior all sides have the 1st joint, and outer circumferential side has interior all side components of the 2nd joint that is connected with above-mentioned the 1st joint,
All side components in above-mentioned are made of structural steel, comprise above-mentioned cylindric and the above-mentioned portion that extends,
The above-mentioned portion that extends, its outer circumferential side is with respect to interior all side direction offset rearward.
3. fluid torque converter according to claim 2 is characterized in that:
The joint that above-mentioned the 1st joint is connected with above-mentioned the 2nd joint adopts spline chimeric, and both axially relatively moving forbidden by axial latch for printed circuit.
4. fluid torque converter according to claim 2 is characterized in that:
The inner peripheral surface of above-mentioned cylindric portion forms the overrunning clutch outer ring with the snap-fit element butt of above-mentioned overrunning clutch.
5. fluid torque converter according to claim 1 is characterized in that:
Also comprise,
The lock-up clutch that mechanically directly connects above-mentioned input part and above-mentioned carry-out part;
When above-mentioned lock-up clutch is in coupled condition, absorb the lock-up clutch buffer of the cogging between above-mentioned input part and the above-mentioned carry-out part;
Above-mentioned lock-up clutch buffer is set up in parallel an axial side at this stator with respect to said stator,
Above-mentioned rotatable components, its outer circumferential side is put to the lateral deviation in contrast to the lock-up clutch buffer in the axial direction with respect to interior all sides.
6. fluid torque converter according to claim 2 is characterized in that:
The outer shape of above-mentioned pump impeller one side of the support of this hydraulic pitch device is, the outer circumferential side that forms above-mentioned race way is that the protuberance starting point is swelled with the assigned position with respect to the base portion of interior all sides,
The joint that above-mentioned the 1st joint is connected with above-mentioned the 2nd joint, its radial position are positioned at the outer circumferential side of above-mentioned protuberance starting point and are positioned at the most all sides of all positions of above-mentioned race way,
The axial thickness of assigned position of all sides that are positioned at above-mentioned joint of all side components in above-mentioned is thinner than the axial thickness of above-mentioned joint.
7. fluid torque converter according to claim 6 is characterized in that:
At least one side of above-mentioned the 1st joint and above-mentioned the 2nd joint, the axial thickness of interior all sides is thinner than the axial thickness of outer circumferential side.
8. fluid torque converter according to claim 7 is characterized in that:
The material of all side components is a structural steel in above-mentioned.
9. fluid torque converter according to claim 7 is characterized in that:
The above-mentioned joint of above-mentioned the 1st joint and above-mentioned the 2nd joint adopts spline chimeric, and both axially relatively moving forbidden by axial latch for printed circuit.
10. fluid torque converter according to claim 6 is characterized in that:
The inner peripheral surface of all side components forms the overrunning clutch outer ring with the snap-fit element butt of above-mentioned overrunning clutch in above-mentioned.
11. fluid torque converter according to claim 6 is characterized in that:
Also comprise,
The lock-up clutch that mechanically directly connects above-mentioned input part and above-mentioned carry-out part;
When above-mentioned lock-up clutch is in coupled condition, absorb the lock-up clutch buffer of the cogging between above-mentioned input part and the above-mentioned carry-out part,
Above-mentioned lock-up clutch buffer is arranged on the axial side of this stator side by side with respect to said stator,
All side components in above-mentioned, its outer circumferential side is put to the lateral deviation in contrast to the lock-up clutch buffer in the axial direction with respect to interior all sides.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006-258599 | 2006-09-25 | ||
| JP2006-258598 | 2006-09-25 | ||
| JP2006258598A JP4788545B2 (en) | 2006-09-25 | 2006-09-25 | Torque converter |
| JP2006258598 | 2006-09-25 | ||
| JP2006258599A JP4929947B2 (en) | 2006-09-25 | 2006-09-25 | Torque converter |
| JP2006258599 | 2006-09-25 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101153651A CN101153651A (en) | 2008-04-02 |
| CN101153651B true CN101153651B (en) | 2011-07-20 |
Family
ID=39255460
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007101544987A Expired - Fee Related CN101153651B (en) | 2006-09-25 | 2007-09-11 | Torque converter |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4788545B2 (en) |
| CN (1) | CN101153651B (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5115401B2 (en) * | 2008-08-28 | 2013-01-09 | トヨタ自動車株式会社 | Fluid transmission device |
| JP5684515B2 (en) * | 2010-08-20 | 2015-03-11 | 株式会社エクセディ | Torque converter |
| JP5505357B2 (en) * | 2011-03-31 | 2014-05-28 | アイシン・エィ・ダブリュ株式会社 | Clutch device and fluid transmission device including the same |
| JP5733390B2 (en) * | 2011-04-18 | 2015-06-10 | トヨタ自動車株式会社 | Torque converter for vehicles |
| JP5805704B2 (en) * | 2013-05-16 | 2015-11-04 | 株式会社エクセディ | Torque converter lockup device |
| CN105422780A (en) * | 2015-11-30 | 2016-03-23 | 陕西航天动力高科技股份有限公司 | Hydraulic torque converter for large-power AT |
| US10520040B2 (en) * | 2017-11-21 | 2019-12-31 | Schaeffler Technologies AG & Co. KG | Spring retainer for arc spring of a clutch |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6568180B2 (en) * | 2000-06-19 | 2003-05-27 | Aisin Aw Co., Ltd. | Torque converter |
| US6675941B1 (en) * | 1999-09-29 | 2004-01-13 | Valeo | Hydrokinetic coupling device comprising an improved reactor overrunning clutch |
| CN2786370Y (en) * | 2005-03-24 | 2006-06-07 | 广州市番禺华南摩托企业集团有限公司 | Hydrodynamic torque-converter |
-
2006
- 2006-09-25 JP JP2006258598A patent/JP4788545B2/en not_active Expired - Fee Related
-
2007
- 2007-09-11 CN CN2007101544987A patent/CN101153651B/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6675941B1 (en) * | 1999-09-29 | 2004-01-13 | Valeo | Hydrokinetic coupling device comprising an improved reactor overrunning clutch |
| US6568180B2 (en) * | 2000-06-19 | 2003-05-27 | Aisin Aw Co., Ltd. | Torque converter |
| CN2786370Y (en) * | 2005-03-24 | 2006-06-07 | 广州市番禺华南摩托企业集团有限公司 | Hydrodynamic torque-converter |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4788545B2 (en) | 2011-10-05 |
| CN101153651A (en) | 2008-04-02 |
| JP2008075842A (en) | 2008-04-03 |
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