CN103195900A - Novel hydraulic torque converter - Google Patents
Novel hydraulic torque converter Download PDFInfo
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- CN103195900A CN103195900A CN 201210257544 CN201210257544A CN103195900A CN 103195900 A CN103195900 A CN 103195900A CN 201210257544 CN201210257544 CN 201210257544 CN 201210257544 A CN201210257544 A CN 201210257544A CN 103195900 A CN103195900 A CN 103195900A
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Abstract
The invention relates to a novel hydraulic torque converter which mainly structurally comprises a pump pulley, a driven wheel, a coupling differential and a worm wheel, wherein the rotary surface view of the pump pulley is circular, the axial surface cutaway view is half arc-shaped, and the pump pulley is provided with radial arc-shaped vanes, and is connected with an input shaft; the rotary surface view of the driven wheel is circular, the axial surface cutaway view is half arc-shaped, and the driven wheel is provided with radial arc-shaped vanes, is mounted relative to the pump pulley, and is connected with an output shaft; working liquid is filled between the pump pulley and the driven wheel as well as among vanes; the worm wheel is mounted in an area, where working liquid returns into the pump pulley from the driven wheel, between the pump pulley and the driven wheel, is close to one side of the pump pulley, and is connected with the pump pulley into a whole; vanes of the worm wheel and a rotating direction form an included angle, so that when the worm wheel rotates, vanes of the worm wheel push working liquid to flow in the direction of the pump pulley; and the coupling differential comprises circular ring cylinder bodies (GT), spiral rib plates (LJ), rotating discs (P) and coupling rotors (C).
Description
Invention field:
The present invention relates to a kind of novel fluid torque converter.
Background of invention:
Novel fluid torque converter involved in the present invention can be widely used in the transmission of the engine power of engineering machinery such as automobile, offroad vehicle, excavator, tractor, mining area transportation.
Existing widely used fluid torque converter, ability with stepless continuous speed change and change torque, externally load has good automatic adjusting and adaptability, it makes vehicle starting steady, accelerate rapidly evenly, its cushioning effect has reduced the dynamic load of transmission system and has turned round shake, has prolonged the working life of transmission system, the mean velocity that has improved travelling comfort, passing ability, Security and travelled.
But the present fluid torque converter that uses, the shortcoming that the ubiquity transmission efficiency is not high enough.When middle low speed was travelled, the power of motor can not pass to speed changer fully; When the high speed degree travels, must raise the efficiency by locking engagement again.And under the reduction of speed operation, locking engagement breaks away from locking again.Travel if be under the changeable work condition state, carry out the operation of speedup and reduction of speed continually, then fluid torque converter is in locking frequently and breaks away from locking alternately under the state of conversion, and the kinetic equation loss of system is increased, and is unfavorable for energy-saving and emission-reduction.Present existing fluid torque converter still more, when the resistance drop of travelling is low, there is not the function of speedup, for example disclosed patent has, D.B.P. technology No.94107829.9, No.99111343.8, Japan Patent technology No.00133785.8, No.200710154498.7 etc.
The present invention proposes brand-new design, not only kept every advantage of existing fluid torque converter, when middle low speed is travelled, make the power of motor can pass to speed changer more expeditiously simultaneously; When the high speed degree travels, under the situation that need not the locking engagement locking, still can transmit the power of motor expeditiously.Under the low operating mode of the resistance drop of travelling, the present invention can provide the function of speedup under the constant situation of motor input speed.
About the explanation of nouns in the patents state of the present invention:
1. axial plane sectional view: the view that dissects gained on the plane that coincides with rotation axis.As shown in Figure 1.
2. surface of revolution view: dissecing the view of gained with the perpendicular plane of rotation axis.As shown in Figure 3.
3. rotation axis: the rotation axis of rotor or revolution space.As the axes O among Fig. 1.
4. annulus axis: the axial plane sectional view is circular said three-dimensional body annulus, its circle around axis, as the axis Q among Fig. 1.
Summary of the invention:
The present invention relates to a kind of novel fluid torque converter, its structure mainly comprises: pump impeller (BL), follower (CP), coupling differential mechanism (YO) and turbine (WL).Wherein the surface of revolution view of pump impeller (BL) is circular, and the axial plane sectional view is semicircular arc, and the radial strut blade is arranged, and links with input shaft.
The surface of revolution view of follower (CP) is circular, and the axial plane sectional view is semicircular arc, and the radial strut blade is arranged.Relative installation with pump impeller (BL), and link with output shaft.Between pump impeller (BL) and the follower (CP) and be full of working solution between the blade.
The working solution that turbine (WL) is installed between pump impeller (BL) and the follower (CP) is back to the zone of pump impeller (BL) from follower (CP), and near pump impeller (BL) side, (BL) is coupled to one with pump impeller.The blade of turbine (WL) becomes angle with sense of rotation, makes when turbine (WL) rotates, and the blade of turbine (WL) pushing working solution flows to the direction of pump impeller (BL).
Coupling differential mechanism (YO) is made up of annulus cylinder body (GT), spiral gusset (LJ), rolling disc (P) and coupling rotor (C).Wherein annulus cylinder body (GT) is a cylinder body that annular cavity is arranged, and the axial plane sectional view of cavity is circular.Spiral gusset (LJ) is arranged in annular cavity, and distributes along arc-shaped surface, and (GT) combines as a whole with the annulus cylinder body, forms annulus duct cylinder body.Have the cylinder body annular groove on the annulus duct cylinder body, rolling disc (P) is arranged in annular groove.Coupling rotor (C) is installed on the rolling disc (P), is positioned at annular cavity.The external diameter edge of coupling rotor (C) contacts with the annular cavity internal surface, and its rotation axis is vertical with the rotation axis of rolling disc (P), and tangent with the annulus axis of annular cavity.Coupling rotor (C) has coupling slot along radial direction, and ((LJ) can pass coupling slot to the spiral gusset.When be coupled rotor (C) and rolling disc (P) relatively rotated with annulus duct cylinder body, spiral gusset (LJ) promoted to be coupled rotor (C) around self rotation axis rotation with the slip engagement of coupling slot.
Spiral gusset (LJ) distributes along the arc-shaped surface of annular cavity, make coupling rotor (C) produce relative rotation with rolling disc (P) with annulus duct cylinder body, and during with even rotational speed, coupling rotor (C) meshes because of the slip of coupling slot and spiral gusset (LJ) and centers on self rotation axis with even rotating speed rotation.
The starting point of spiral gusset (LJ) is positioned at a side of rolling disc (P), and with the engagement that begins to slide of the coupling slot of coupling rotor (C).Along with relatively rotating between rolling disc (P) and the annulus duct cylinder body, coupling rotor (C) about week of rotation under the thrust of spiral gusset (LJ), the clearing end of the spiral gusset (LJ) of the opposite side of arrival rolling disc (P), then coupling slot and spiral gusset (LJ) break away from engagement, be rotated further, get back to starting point one side of spiral gusset (LJ), begin the next engagement of sliding again.
Annulus duct cylinder body has the working solution gateway in the starting point of the spiral gusset (LJ) of the both sides of rolling disc (P) and near the position the clearing end.When rolling disc (P) and coupling rotor (C) and annulus duct cylinder body when producing relative rotation, working solution flows to by the gateway and flows out coupling differential mechanism (YO).
When the launched machine of pump impeller (BL) drove rotation, working solution rotation by the blade band of pump impeller (BL), and under centrifugal action, outwards mobile from the inner edge of blade.After working solution is thrown to the outer rim of pump impeller (BL), rush at the outer rim of follower (CP) again, the blade along follower (CP) flows to inner edge again, and the inner edge from follower (CP) flows to turbine (WL) again.Because turbine (WL) rotates with speed with pump impeller (BL), therefore, the blade of turbine (WL) pushing working solution, and make working solution be back to the inner edge of pump impeller (BL) rapidly.Be thrown to outer rim again by pump impeller (BL) again, so continuous circulation makes follower (CP) rotate, and drives output shaft output torque.
Coupling differential mechanism (YO) is positioned between pump impeller (BL) and the follower (CP), and annulus duct cylinder body wherein and rolling disc (P) connect with pump impeller (BL) or follower (CP).Pump impeller (BL) drives follower (CP) and rotates by the pressure difference of coupling differential mechanism (YO) turnover working solution, and drives output shaft output torque.
Working solution between turbine (WL) and follower (CP) is equipped with guide wheel (DL) by the zone that follower (CP) is back to turbine (WL) and pump impeller (BL).Guide wheel (DL) is bearing on the overrunning clutch (H).Overrunning clutch (H) can only rotate guide wheel (DL) in the same way with pump impeller (BL).The blade of guide wheel (DL) becomes angle with the sense of rotation of guide wheel (DL), changes direction when the working solution that makes follower (CP) reflux is flowed through guide wheel (DL), and is consistent with the sense of rotation of turbine (WL).
The annulus duct cylinder body of coupling differential mechanism (YO) both can connect with pump impeller (BL), also can connect with follower (CP), and corresponding then is that rolling disc (P) connects with follower (CP) or connects with pump impeller (BL).The import and export of rolling disc (P) side of coupling differential mechanism (YO) are positioned at pump impeller (BL) zone, and the working solution of the opposite side of rolling disc (P) is imported and exported and is positioned at follower (CP) zone.
Coupling differential mechanism (YO) can be wall scroll spiral gusset (LJ), also can be many spiral gussets (LJ).The blade of pump impeller (BL) can be that the radial direction straight line launches, and also can launch with curve form from inside to outside; The blade of follower (CP) can be that the radial direction straight line launches, and also can be to launch with curve form from inside to outside.
She Ji fluid torque converter like this, at the starting initial stage, follower (CP) is bigger with the relative speed difference of pump impeller (BL).The centrifugal force that pump impeller (BL) rotation produces makes the blade of working solution high speed impact follower (CP), be coupled simultaneously differential mechanism (YO) annulus duct cylinder body with the coupling rotor (C) the relative rotation speed difference bigger, make extensive work liquid flow to the gateway in opposite side pump impeller (BL) zone from a side gateway, the suffered torsion of follower (CP) is very large like this, this compares with existing fluid torque converter, has bigger output torque at the starting initial stage.
Simultaneously, because the effect of turbine (WL) blade, no matter follower (CP) is in the slow-speed of revolution at starting initial stage, still the later stage in high rotating speed, the passive process that turbine (WL) all refluxes working solution changes the initiatively process of suction backflow into.Angle by adjusting turbine (WL) blade and the flow section of turbine (WL) can obtain the capacity of reflux with pump impeller (BL) coupling, like this, have strengthened the increment of pump impeller (BL) working solution, thus the output torque that has increased follower (CP).
When follower (CP) under the driving of pump impeller (BL), after speed improves constantly, because the effect of the curve of the blade of pump impeller (BL), when pump impeller (BL) rotates, blade has applied the thrust to pump impeller (BL) outer rim to working solution, therefore, although the rotating speed of follower (CP) is near pump impeller (BL), even with speed, follower (CP) outer rim still is subjected to the impact force of working solution, simultaneously the working fluid pressure in pump impeller (BL) zone is higher than the pressure of the working solution in follower (CP) zone, and therefore, the parts of the coupling differential mechanism (YO) that connects with follower (CP) can be subjected to the pressure effect of working solution, make its rotating speed can be higher than the rotating speed of the parts of the coupling differential mechanism (YO) that another and pump impeller (BL) connect, like this, the output speed of follower (CP) can be higher than pump impeller (BL), the just speed of motor.
Cancellation coupling differential mechanism (YO) has then become the another kind of novel fluid torque converter that structure is made up of pump impeller (BL), follower (CP), turbine (WL), guide wheel (DL) in the structure of above-mentioned fluid torque converter.Under the situation that the main performance advantage of above-mentioned fluid torque converter is kept, make structure become simpler, reduced cost.
Description of drawings:
The axial plane sectional view of one of Fig. 1 embodiment of the invention
The 3-D view of Fig. 2 pump impeller
The surface of revolution view of Fig. 3 pump impeller
The another kind of form of the blade of Fig. 4 pump impeller and follower
Fig. 5 turbine view
Fig. 6 guide wheel view
The be coupled axial plane sectional view of differential mechanism of Fig. 7
The be coupled coupling rotor view of differential mechanism of Fig. 8
Fig. 9 differential mechanism working principle schematic representation that is coupled
In the description of drawings of patent of the present invention, the structure of illustrated component, size and shape do not represent structure, size and the shape of actual component, also do not represent the actual size proportionate relationship between the component, diagram is just illustrated the embodiment of the invention with simple and clear mode.
Fig. 1 has shown the axial plane sectional view of one of embodiment of the invention, as can be seen from the figure: the structure of fluid torque converter mainly comprises: the pump impeller (BL) that connects mutually with input shaft, with follower (CP), coupling differential mechanism (YO), turbine (WL) and guide wheel (DL) that output shaft connects mutually, in fluid torque converter, be full of working solution.
Fig. 2 and Fig. 3 have then shown 3-D view and the surface of revolution view of pump impeller (BL).Its surface of revolution view is circular, and the axial plane sectional view is shaped as semicircular arc, and the radial strut blade is arranged.The relative installation with pump impeller (BL) of follower (CP), and keep suitable gap.Its shape is similar to pump impeller (BL) with structure, and the surface of revolution view is circular, and the axial plane sectional view is semicircular arc, and the radial strut blade is arranged.
The working solution that turbine (WL) is installed between pump impeller (BL) and the follower (CP) is back to the zone of pump impeller (BL) from follower (CP), and near pump impeller (BL) side, (BL) is coupled to one with pump impeller.Fig. 5 has shown one of the axial plane sectional view of turbine (WL) and arrangement form of turbine blade.The blade of turbine (WL) becomes angle with sense of rotation, makes when turbine (WL) rotates, and the blade of turbine (WL) pushing working solution flows to the direction of pump impeller (BL).
Coupling differential mechanism (YO) is positioned between pump impeller (BL) and the follower (CP).Fig. 7 has further shown one of embodiment's internal structure by the axial plane sectional view of coupling differential mechanism (YO).Coupling differential mechanism (YO) mainly is made up of annulus cylinder body (GT), spiral gusset (LJ), rolling disc (P), coupling rotor (C).Wherein annulus cylinder body (GT) is a cylinder body that annular cavity is arranged, and the axial plane sectional view of annular cavity is circular.Spiral gusset (LJ) is arranged in annular cavity, distributes along the cavity arc-shaped surface, and is coupled as one with annulus cylinder body (GT) and becomes annulus duct cylinder body.Annulus duct cylinder body has the cylinder body annular groove along annular cavity, and rolling disc (P) is arranged in the cylinder body annular groove.Rolling disc (P) radially have a breach, coupling rotor (C) is installed in this breach, and is positioned at annular cavity.
Fig. 8 has shown the view of coupling rotor (C).The external diameter edge of coupling rotor (C) contacts with the internal surface of annular cavity, and the rotation axis of coupling rotor (C) and the rotation axis O of rolling disc (P) are perpendicular, and tangent with the annulus axis Q of annular cavity.Coupling rotor (C) has coupling slot along radial direction, from diagram four coupling slots is arranged as can be seen, and spiral gusset (LJ) can pass coupling slot.When be coupled rotor (C) and rolling disc (P) relatively rotated with annulus duct cylinder body, spiral gusset (LJ) promoted to be coupled rotor (C) around self rotation axis rotation with the slip engagement of coupling slot.
Spiral gusset (LJ) distributes along the arc-shaped surface of annulus cylinder body (GT), make coupling rotor (C) produce relative rotation with rolling disc (P) with annulus cylinder body (GT), and when rotating with homogeneous velocity, coupling rotor (C) centers on self rotation axis with the homogeneous velocity rotation because of the slip engagement of spiral gusset (LJ) and coupling slot.
The starting point of spiral gusset (LJ) is positioned at a side of rolling disc (P), and keeps in touch with the card of rolling disc (P).Its coupling slot with coupling rotor (C) begins the engagement of sliding, along with relatively rotating between rolling disc (P) and the annulus cylinder body (GT), coupling rotor (C) about week of rotation under the thrust of spiral gusset (LJ), the clearing end of the spiral gusset (LJ) of the opposite side of arrival rolling disc (P).The clearing end of spiral gusset (LJ) opposite side card same and rolling disc (P) keeps in touch.When the coupling slot of coupling rotor (C) arrives the clearing end of spiral gusset (LJ), then break away from engagement with spiral gusset (LJ), and be rotated further, get back to a side of the starting point of spiral gusset (LJ) again, begin the next engagement of sliding again.
Fig. 7 and Fig. 8 have shown four symmetrical coupling slots that evenly distribute in the annulus cylinder body (GT).Article 4, the starting point of spiral gusset (LJ) meshes with 4 coupling slots generation slips of coupling rotor (C) successively along a side panel face of rolling disc (P), after breaking away from the engagement of sliding successively with contacted 4 clearing ends of the opposite side card of rolling disc (P) again, enter the next engagement of sliding again successively.
Annulus duct cylinder body has the working solution gateway in starting point and near the position the clearing end of the spiral gusset (LJ) of the both sides of rolling disc (P).When rolling disc (P) and coupling rotor (C) and annulus cylinder body (GT) when producing relative rotation, working solution flows to by import and export and flows out coupling differential mechanism (YO).
Fig. 9 has shown the plane outspread drawing of spiral gusset (LJ) along the circular cross-section lmn expansion of the annular cavity of annulus cylinder body (GT).Can lose validity although expand into the plane oblique line along the spiral gusset (LJ) of annular cavity surface distributed,, the working principle of coupling differential mechanism (YO) can be described concisely.
If annulus cylinder body (GT) connects mutually with pump impeller (BL), rolling disc (P) connects mutually with follower (CP), when the gusset of spiral shown in the figure (LJ) when turning left, then pump impeller (BL) is positioned at the underside area of annulus cylinder body (GT), and follower (CP) is positioned at the upper-side area of annulus cylinder body (GT).At the starting initial stage, output shaft speed is lower than input shaft speed, and just the speed of rolling disc (P) and coupling rotor (C) is lower than the speed of annulus cylinder body (GT) and spiral gusset (LJ).Working solution sucks from the gateway in follower (CP) zone, discharge in the gateway in pump impeller (BL) zone, and the speed of pump impeller this moment (BL) is far above the speed of follower (CP).Just the pressure of the regional gateway of pump impeller (BL) is greater than the pressure of the regional gateway of follower (CP).This has just increased the resistance to motion of coupling rotor (C) in annulus cylinder body (GT).Pump impeller (BL) is more big with the speed difference of follower (CP), and the resistance of rotor (C) relative movement in annulus cylinder body (GT) that then is coupled is just more big, and the torque that output shaft provides is just more big.
On the other hand, during engine-driving pump impeller (BL) rotation, working solution rotation by the blade band of pump impeller (BL), and under action of centrifugal force, outwards flow from the inner edge of blade, working solution is thrown to the outer rim that rushes at follower (CP) after the outer rim of pump impeller (BL) again, blade along follower (CP) flows to inner edge again, finally return pump impeller (BL) again, be thrown to outer rim by pump impeller (BL) again, so continuous circulation makes follower (CP) rotate, and driving output shaft output torque, this point is similar to the principle of the fluid torque converter that uses at present.
As can be seen from Figure 1, the zone that is back to turbine (WL) and pump impeller (BL) by follower (CP) between turbine (WL) and follower (CP) is equipped with guide wheel (DL).Guide wheel (DL) is bearing on the overrunning clutch (H).Overrunning clutch (H) can only rotate guide wheel (DL) in the same way with pump impeller (BL).Fig. 6 has shown the 3-D view of guide wheel.The blade of guide wheel (DL) becomes angle with the sense of rotation of guide wheel (DL), changes direction when the working solution that makes follower (CP) reflux is flowed through guide wheel (DL), and is consistent with the sense of rotation of turbine (WL).
When the launched machine of pump impeller (BL) drove rotation, working solution rotation by the blade band of pump impeller (BL), and under centrifugal action, outwards mobile from the inner edge of blade.After working solution is thrown to pump impeller (BL) outer rim, rush at the outer rim of follower (CP) again, the blade along follower (CP) flows to inner edge again, and the inner edge from follower (CP) flows to guide wheel (DL) again.When the speed discrepancy of pump impeller (BL) and follower (CP) is big, the working solution of follower (CP) rushes at the front of guide wheel (DL), guide wheel (DL) is owing to the effect of overrunning clutch (H) can not be reversed, therefore, the working solution of guide wheel (DL) of flowing through has just changed flow direction, directly acts on the rear portion of turbine (WL) blade.Because turbine (WL) connects with pump impeller (BL), the torque that has just increased pump impeller, speed discrepancy is more big, and the degree that then rises square is just more big.When the rotating speed of follower (CP) constantly increases, during progressively with pump impeller (BL) speed together, the angle that working solution between follower (CP) and the guide wheel (DL) flows diminishes, make working solution rush at the back side of guide wheel (DL) blade, at this moment, guide wheel (DL) begin the rotation, make working solution with minimum drag stream to turbine (WL).
Working solution flows to turbine (WL) from guide wheel (DL), because turbine (WL) and pump impeller (BL) rotate with speed, therefore, the blade pushing working solution of turbine (WL), and make working solution be back to the inner edge of pump impeller (BL) fast, be thrown to outer rim again by pump impeller (BL) again then, so continuous circulation, make follower (CP) rotate, and drive output shaft output torque.
Fig. 4-1 has shown the another kind of blade shape of pump impeller (BL), and its blade is outside curved formal expansion from the lining.When illustrated pump impeller (BL) when rotating in a counter-clockwise direction, interlobate working solution not only is subjected to the action of centrifugal force that pump impeller (BL) rotation produces, and flows to the outer rim of pump impeller (BL), and is subjected to blade to the thrust of outer rim direction.The blade of follower (CP) adopts radial alignment radial, or the form launched in the opposite direction of the mounted blade side of employing and pump impeller (BL).Shown in Fig. 4-2, follower (CP) is rotation counterclockwise with pump impeller (BL) equally, then when the speed of the speed of pump impeller (BL) and follower (CP) was identical, working solution still continued to keep the state that circulates under the thrust of the blade of pump impeller (BL) and follower (CP).Because follower (CP) and pump impeller (BL) all move under the high speed degree, near the regional outer rim of pump impeller (BL) working fluid pressure will be higher than near the working fluid pressure the regional outer rim of follower (CP), at this moment, the working solution in two zones is because of action of pressure, the entrance regional from the pump impeller (BL) of coupling differential mechanism (YO) imports, coupling rotor (C) is subjected to elevated pressures effect meeting to lower pressure one lateral movement, just can rotate to the direction bigger than annulus cylinder body (GT) speed, the speed of this feasible coupling rotor (C) is greater than the speed of annulus cylinder body (GT).To the adjustment of position, working solution gateway and the change of gateway shape, can obtain different speedup effects.
Adopt a coupling rotor (C) in annulus cylinder body (GT), to rotate and then suck the working solution of discharging an annulus cylinder body (GT) content a week, if with a plurality of coupling rotors (C) and many group spiral gussets (LJ), the rotor (C) that then is coupled rotates in annulus cylinder body (GT) will suck the working solution of discharging a plurality of annulus cylinder bodies (GT) content a week.
With coupling differential mechanism (YO) cancellation embodiment illustrated in fig. 1, then formed another kind of novel fluid torque converter by pump impeller (BL), follower (CP), turbine (WL), guide wheel (DL), the working method of its each assembly is identical with above-mentioned embodiment shown in Figure 1, at this, give unnecessary details no longer one by one.
About overrunning clutch and seal arrangement, bearing device etc., those skilled in the art has all known, and in related domain extensive use, at this, gives unnecessary details no longer one by one.
Above-described embodiment has illustrated the present invention in illustrated mode, but the above-described embodiment that illustrates with diagramatic way is not limitation of the present invention, and the present invention is defined by the claims.
Claims (9)
1. the present invention relates to a kind of novel fluid torque converter, its structure mainly comprises: pump impeller, follower, coupling differential mechanism, turbine.
Fluid torque converter of the present invention is characterized in that: the input shaft of described pump impeller and described fluid torque converter links.Its surface of revolution view is circular, and its axial plane sectional view is semicircular arc, and the radial strut blade is arranged;
The output shaft of described follower and described fluid torque converter links, and install relative with pump impeller, and its surface of revolution view is circular, and its axial plane sectional view is semicircular arc, and the radial strut blade is arranged, and is full of working solution between the blade of pump impeller and follower.
The working solution that described turbine is installed between pump impeller and the follower is back to the zone of pump impeller from follower, and near pump impeller one side, is coupled to one with pump impeller.The blade of turbine becomes angle with sense of rotation, and when making turbine rotation, turbine blade pushing working solution flows to the pump impeller direction.
Described coupling differential mechanism is made up of annulus cylinder body, spiral gusset, rolling disc, coupling rotor, and wherein the annulus cylinder body is a cylinder body that annular cavity is arranged.The axial plane sectional view of annular cavity is circular.Described spiral gusset is arranged in described annular cavity, distributes along arc surface, and is coupled as one with described annulus cylinder body and becomes annulus duct cylinder body, and annulus duct cylinder body has the cylinder body annular groove along annular cavity, and described rolling disc is arranged in the cylinder body annular groove.
Described coupling rotor is installed on the rolling disc, is positioned at annular cavity.Coupling rotor diameter edge contacts with the annular cavity internal surface, its rotation axis and turn disc axis normal, and tangent with the annulus axis of annular cavity; Described coupling rotor has coupling slot along radial direction, and the spiral gusset can pass coupling slot.When be coupled rotor and rolling disc and annulus duct cylinder body relatively rotated, the slip engagement of spiral gusset and coupling slot promoted the coupling rotor around self rotation axis rotation.
Described spiral gusset distributes along the arc-shaped surface of described annular cavity, make the coupling rotor produce relative rotation with rolling disc with annulus duct cylinder body, and during with even rotational speed, the coupling rotor meshes because of the slip of coupling slot and spiral gusset and centers on self rotation axis with even rotating speed rotation.
The starting point of described spiral gusset is positioned at a side of rolling disc, and with the engagement that begins to slide of the coupling slot of coupling rotor, along with relatively rotating between rolling disc and the annulus duct cylinder body, a coupling rotor about week of rotation under the thrust of spiral gusset, the clearing end of the spiral gusset of the opposite side of arrival rolling disc, then spiral gusset and coupling slot break away from engagement.The coupling rotor is rotated further, and gets back to a side of spiral gusset starting point again, begins slip engagement next time again.
Described annulus duct cylinder body is in the rolling disc both sides, and near the position spiral gusset starting point and the clearing end has the working solution gateway.When rolling disc and coupling rotor and annulus duct cylinder body produced relative rotation, working solution flow to by the gateway and flows out the coupling differential mechanism.Described coupling differential mechanism is between pump impeller and follower, and annulus duct cylinder body wherein and rolling disc connect with pump impeller or follower respectively.Pump impeller drives follower and rotates by the pressure difference of coupling differential mechanism turnover working solution, and drives output shaft output torque.
2. by the described fluid torque converter of claim 1, it is characterized in that: working solution is equipped with guide wheel by the zone that follower is back to turbine and pump impeller between turbine and follower.Guide wheel is bearing on the overrunning clutch.Overrunning clutch can only rotate guide wheel in the same way with pump impeller.The blade of guide wheel becomes angle with the sense of rotation of guide wheel, changes direction when the working solution that makes follower reflux is flowed through guide wheel, and is consistent with the sense of rotation of turbine.
3. by the described fluid torque converter of claim 1, it is characterized in that: annulus duct cylinder body and the follower of described coupling differential mechanism are bound up, and rotate with follower, rolling disc and the pump impeller of coupling differential mechanism are bound up, and rotate with pump impeller.
4. by the described fluid torque converter of claim 1, it is characterized in that: annulus duct cylinder body and the pump impeller of described coupling differential mechanism are bound up, and rotate with pump impeller.Rolling disc and the follower of coupling differential mechanism are bound up, and rotate with follower.
5. by the described fluid torque converter of claim 1, it is characterized in that: the gateway of the rolling disc one side working solution of described coupling differential mechanism is positioned at the pump impeller zone, and then the working solution gateway of rolling disc opposite side is positioned at the follower zone.
6. by claim 1,3 and 4 described fluid torque converters, it is characterized in that: described coupling differential mechanism is equipped with many spiral gussets.
7. by the described fluid torque converter of claim 1, it is characterized in that: the blade of described pump impeller launches with curve form from inside to outside.
8. by the described fluid torque converter of claim 1, it is characterized in that: the blade of described follower launches with curve form from inside to outside.
9. novel fluid torque converter, its structure mainly comprises: pump impeller, follower, turbine, guide wheel.
Fluid torque converter involved in the present invention is characterized in that: the input shaft of described pump impeller and described fluid torque converter links.Its surface of revolution view is circular, and its axial plane sectional view is semicircular arc, and the radial strut blade is arranged;
The output shaft of described follower and described fluid torque converter links, and install relative with pump impeller, and its surface of revolution view is circular, and its axial plane sectional view is semicircular arc, and the radial strut blade is arranged, and is full of working solution between the blade of pump impeller and follower.
The working solution that described turbine is installed between pump impeller and the follower is back to the zone of pump impeller from follower, and near pump impeller one side, is coupled to one with pump impeller.The blade of turbine becomes angle with sense of rotation, and when making turbine rotation, turbine blade pushing working solution flows to the pump impeller direction.
Described guide wheel is installed in working solution between turbine and the follower and is back to the zone of turbine and pump impeller from follower, and guide wheel is bearing on the overrunning clutch.Overrunning clutch can only rotate guide wheel in the same way with pump impeller.The blade of guide wheel becomes angle with the sense of rotation of guide wheel, changes direction when the working solution that makes follower reflux is flowed through guide wheel, and is consistent with the sense of rotation of turbine.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201210257544 CN103195900A (en) | 2012-07-24 | 2012-07-24 | Novel hydraulic torque converter |
| CN201310314125.7A CN103939563A (en) | 2012-07-24 | 2013-07-23 | Novel hydraulic torque converter |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201210257544 CN103195900A (en) | 2012-07-24 | 2012-07-24 | Novel hydraulic torque converter |
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| Publication Number | Publication Date |
|---|---|
| CN103195900A true CN103195900A (en) | 2013-07-10 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201210257544 Pending CN103195900A (en) | 2012-07-24 | 2012-07-24 | Novel hydraulic torque converter |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103195900A (en) |
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2012
- 2012-07-24 CN CN 201210257544 patent/CN103195900A/en active Pending
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Application publication date: 20130710 |