CN103206506A - Novel hydraulic torque converter - Google Patents
Novel hydraulic torque converter Download PDFInfo
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- CN103206506A CN103206506A CN2012104171753A CN201210417175A CN103206506A CN 103206506 A CN103206506 A CN 103206506A CN 2012104171753 A CN2012104171753 A CN 2012104171753A CN 201210417175 A CN201210417175 A CN 201210417175A CN 103206506 A CN103206506 A CN 103206506A
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- 239000012530 fluid Substances 0.000 claims abstract description 31
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Abstract
The invention relates to a novel hydraulic torque converter which mainly comprises a pump wheel (BL), a driven plate (CP) and a coupling differential mechanism (YO); the pump wheel (BL) is connected with an input shaft of the novel hydraulic torque converter; a rotary plane of the pump wheel (BL) is in a circular shape; an axial plane sectional view of the pump wheel (BL) is in a semi-circle arc shape and is provided with radial arc-shaped blades; the driven plate (CP) is connected with an output shaft of the novel hydraulic torque converter; a rotary plane of the driven plate (CP) is in a circular shape; an axial plane sectional view of the driven plate (CP) is in a semi-circle arc shape and is provided with radial arc-shaped blades; operating fluid is filled among the pump wheel (BL), the driven plate (CP) and the blades; the coupling differential mechanism (YO) is formed by an annular cylinder (GT), a spiral reinforcing plate (LJ), a rotary plate (P) and a coupling rotor (C); the driven plate (CP) and the pump wheel (BL) are assembled in a face-to-face mode; the coupling differential mechanism (YO) is arranged between the pump wheel (BL) and the driven plate (CP); and an outer area between the pump wheel (BL) and the driven plate (CP) is divided into a high pressure area and a low pressure area.
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 depicted in figs. 1 and 2.
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 and Fig. 2.
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), driven disc (CP), coupling differential mechanism (YO), wherein said pump impeller (BL) links with the input shaft of described novel fluid torque converter, its surface of revolution view is circular, its axial plane sectional view is semicircular arc, and the radial strut blade is arranged;
The output shaft of described driven disc (CP) and described novel fluid torque converter links, and its surface of revolution view be circle, and its axial plane sectional view is semicircular arc, and the radial strut blade is arranged, between pump impeller (BL) and the driven disc (CP) and be full of working solution between the blade;
Described coupling differential mechanism (YO) is made up of annulus cylinder body (GT), spiral gusset (LJ), rolling disc (P) and coupling rotor (C), and 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; Described spiral gusset (LJ) is arranged in described annular cavity, distributes along arc-shaped surface, and combines as a whole with described annulus cylinder body (GT), forms annulus duct cylinder body; Annulus duct cylinder body has the cylinder body annular groove along annular cavity, and described rolling disc (P) is arranged in the cylinder body annular groove;
Described coupling rotor (C) is installed on the rolling disc (P), be 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;
Described coupling rotor (C) has coupling slot along radial direction, ((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;
Described spiral gusset (LJ) distributes along the arc-shaped surface of described 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 described 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, the rotation under the thrust of spiral gusset (LJ) of coupling rotor (C), arrive the clearing end of the spiral gusset (LJ) of rolling disc (P) opposite side, then spiral gusset (LJ) breaks away from engagement with coupling slot, and be rotated further, get back to starting point one side of spiral gusset (LJ), begin the next engagement of sliding again;
Described annulus duct cylinder body is in the starting point of rolling disc (P) both sides spiral gussets (LJ) and near the position the clearing end, have the working solution gateway, 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);
The relative installation with described pump impeller (BL) of described driven disc (CP), described coupling differential mechanism (YO) are positioned between pump impeller (BL) and the driven disc (CP) and with the outer edge area between pump impeller (BL) and the driven disc (CP) and are separated into zone of high pressure and low pressure area.
Be full of working solution in the described novel fluid torque converter, the annulus duct cylinder body of described coupling differential mechanism (YO) connects with pump impeller (BL) or driven disc (CP) respectively mutually with rolling disc (P), the working solution gateway of rolling disc (P) both sides lays respectively at zone of high pressure and low pressure area, pump impeller (BL) rotates by the pressure official post driven disc (CP) of zone of high pressure and low pressure area, thereby drives output shaft output torque.
When the launched machine of pump impeller (BL) drives rotation, working solution rotation by the blade band of pump impeller (BL), and under centrifugal action, flow to outer rim from the inner edge of blade, working solution is got rid of to outer rim by pump impeller (BL), and the zone between pump impeller (BL) outer rim and coupling differential mechanism (YO) forms the high-pressure area.
Therefore zone between the outer rim of driven disc (CP) and the coupling differential mechanism (YO), its radius of gyration are called as low pressure area less than the radius of gyration of high-pressure area.The working solution gateway of rolling disc (P) side of coupling differential mechanism (YO) is positioned at the zone of high pressure, and the working solution gateway of rolling disc (P) opposite side is positioned at low pressure area.
At the starting initial stage, the rotating speed of driven disc (CP) is much smaller than the rotating speed of pump impeller (BL), therefore, relative rotation speed between the annulus cylinder body (GT) of coupling differential mechanism (YO) and the coupling rotor (C) is very big, a large amount of working solutions will overcome the pressure difference between zone of high pressure and the low pressure area, after being discharged to the zone of high pressure by low pressure area, from recirculation zone (inner edge district) circulating reflux between pump impeller (BL) and the driven disc (CP), therefore, speed discrepancy between driven disc (CP) and the pump impeller (BL) is more big, the suffered torque of driven disc (CP) is just more big, and the torque that provides to output shaft is also more big.
Along with the rotating speed of driven disc (CP) improves constantly, constantly reduce from the low pressure area working solution that coupling differential mechanism (YO) discharges to the zone of high pressure again of flowing through, up to driven disc (CP) and pump impeller (BL) speed together, then working solution stops to flow, and the pressure of the zone of high pressure of this moment is still greater than the pressure of low pressure area, when being enough to make working solution, this pressure difference overcomes the resistance of coupling differential mechanism (YO), and when flowing to low pressure area by coupling differential mechanism (YO), then the rotating speed of driven disc (CP) will be greater than the rotating speed of pump impeller (BL), increasing to suffered resistance up to the rotating speed of output shaft constantly raises the pressure difference of itself and zone of high pressure and low pressure area is balanced each other, then the rotating speed of driven disc (CP) will no longer raise, this is the present invention's biggest advantage compared with prior art, during low speed driving, big moment of torsion can be provided, when running at high speed, can provide big rotating speed.
Be full of working solution between pump impeller (BL) and the driven disc (CP), in the zone that working solution flows between pump impeller (BL) and driven disc (CP) worm gear (WL) is installed, the blade of described worm gear (WL) becomes angle with sense of rotation, make when worm gear (WL) rotates that worm gear (WL) blade pushing working solution flows to pump impeller (BL) direction.
Direct and pump impeller (BL) connection of worm gear (WL), perhaps connect by planetary gears (XC) and pump impeller (BL), described planetary gears (XC) is made up of sun gear (T), gear ring (R), planet carrier (S) and planetary pinion (u), planetary pinion (u) is installed on the planet pin of planet carrier (S), with gear ring (R) and both engagements of sun gear (T), planetary pinion (u) both can center on the planet pin rotation, also can walk in gear ring (R) around sun gear (T) revolution.Worm gear (WL) connects with sun gear (T), and pump impeller (BL) connects with planet carrier (S), and gear ring (R) is fixing.
The annulus duct cylinder body of coupling differential mechanism (YO) both can connect with pump impeller (BL), also can connect with driven disc (CP), corresponding then is: rolling disc (P) connects with driven disc (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, zone of high pressure just, the working solution of rolling disc (P) opposite side is imported and exported and is positioned at driven disc (CP) zone, just low pressure area.
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 radial direction linearly launches, also can launch with curve form from inside to outside, the blade of driven disc (CP) can be that radial direction linearly launches, and also can launch with curve form from inside to outside.
Coupling rotor (C) can be monomer structure, also can be the multi-disc composite structure.
She Ji novel fluid torque converter like this, because the effect of worm gear (WL) blade, no matter in slow-speed of revolution stage of starting initial stage driven disc (CP), or the high rotating speed stage in the later stage driven disc (CP), worm gear (WL) all pushes working solution to pump impeller (BL) zone, so just increased the pressure of zone of high pressure, reduced the pressure of low pressure area, driven disc (CP) will transmit higher moment of torsion to gearbox by output shaft, especially worm gear (WL) is linked together by planetary gears (XC) and pump impeller (BL), the rotating speed of worm gear (WL) will be than the rotating speed height of pump impeller (BL), increased the pressure difference of zone of high pressure and low pressure area, when high speed is travelled, will make the better effects if of rotating speed speedup on the basis of pump impeller (BL) rotating speed of driven disc (CP).
When pump impeller (BL) and driven disc (CP) adopt the blade of curve form, increased the pressure difference of zone of high pressure and low pressure area equally, pump impeller (BL) when rotated, pump impeller (BL) curve of the blade has applied one by the pushing force of pump impeller (BL) inner edge to pump impeller (BL) outer rim to working solution, this will improve the pressure of zone of high pressure, driven disc (CP) adopts the curve of the blade opposite with pump impeller (BL) blade curve expansion direction simultaneously, driven disc (CP) when rotated, blade has applied one by the pushing force of outer rim to inner edge to working solution, this will offset or partial offset centrifugal force and reduced the pressure of low pressure area, this shows, when high speed was travelled, the effect of driven disc (CP) speedup was obvious equally.
Description of drawings:
The axial plane sectional view of Fig. 1 first embodiment of the invention
The axial plane sectional view of Fig. 2 second embodiment of the invention
The 3-D view of Fig. 3 pump impeller
The surface of revolution view of Fig. 4 pump impeller
The another kind of form of the blade of Fig. 5 pump impeller and driven disc
Fig. 6 worm gear 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 first embodiment of the invention, as can be seen from the figure: the structure of novel fluid torque converter mainly comprises: the pump impeller (BL) that connects mutually with input shaft, with driven disc (CP) and coupling differential mechanism (YO) that output shaft connects mutually, in novel fluid torque converter, be full of working solution.
Fig. 3 and Fig. 4 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 driven disc (CP), its surface of revolution view are circular, and its axial plane sectional view is semicircular arc, and the radial strut blade is arranged.Between pump impeller (BL) and the driven disc (CP) and be full of working solution between the blade.
Coupling differential mechanism (YO) is positioned between pump impeller (BL) and the driven disc (CP).Fig. 7 has further shown 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, the axial plane sectional view of annular cavity is circular, spiral gusset (LJ) is arranged in annular cavity, distribute along the toroidal cavity arc-shaped surface, and be coupled as one with annulus cylinder body (GT) and become 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, the rotation axis of coupling rotor (C) is vertical with the rotation axis O of rolling disc (P), and it is tangent with the annulus axis Q of annular cavity, coupling rotor (C) has coupling slot along radial direction, from diagram as can be seen: four coupling slots are arranged, 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 keep 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), the rotation under the thrust of spiral gusset (LJ) of coupling rotor (C), 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, arrive the clearing end of spiral gusset (LJ) when the coupling slot of coupling rotor (C), 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 has 4 spiral gussets (LJ) evenly to distribute along the circular arc internal surface in the annulus cylinder body (GT), corresponding coupling rotor (C) has 4 symmetrical coupling slots that evenly distribute.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 driven disc (CP), then 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 driven disc (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 driven disc (CP) zone, discharge gateway in pump impeller (BL) zone, and the speed of pump impeller this moment (BL) is far above the speed of driven disc (CP), just the pressure of the regional gateway of pump impeller (BL) is greater than the pressure of the regional gateway of driven disc (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 driven disc (CP), the resistance of rotor (C) relative movement in annulus cylinder body (GT) of then being coupled is just more big, and the torque that output shaft provides is just more big.
As can be seen from Figure 1: the relative installation with pump impeller (BL) of driven disc (CP), coupling differential mechanism (YO) is positioned between pump impeller (BL) and the driven disc (CP) and with the outer edge area between pump impeller (BL) and the driven disc (CP) and is separated into zone of high pressure and low pressure area, as can be seen from Figure, zone between coupling differential mechanism (YO) and pump impeller (BL) outer rim is the zone of high pressure, zone between coupling differential mechanism (YO) and driven disc (CP) outer rim is low pressure area, pump impeller (BL) rotates by the pressure official post driven disc (CP) of zone of high pressure and low pressure area, thereby drives output shaft output torque.
First embodiment shown in Figure 1, zone between driven disc (CP) outer rim and the coupling differential mechanism (YO), its radius of gyration is less than the radius of gyration in the zone between pump impeller (BL) outer rim and the coupling differential mechanism (YO), therefore, pump impeller (BL) has produced the high pressure district of pump impeller (BL) outer edge area and the low pressure zone of driven disc (CP) outer edge area when rotating at a high speed.
At the starting initial stage, because of the rotating speed of driven disc (CP) rotating speed much smaller than pump impeller (BL), therefore, a large amount of working solutions is coupled pump impeller (BL) zone of differential mechanism (YO) from the regional pushing of the driven disc (CP) of low pressure area to the zone of high pressure, when pressure official post driven disc (CP) rotating speed between zone of high pressure and the low pressure area progressively raises and during near the rotating speed of pump impeller (BL), then working solution gradually reduces to the flow of zone of high pressure through coupling differential mechanism (YO) from low pressure area and stops to flow, if the pressure difference between zone of high pressure and the low pressure area is enough to overcome the resistance that driven disc (CP) stands, then working solution flows to low pressure area through coupling differential mechanism (YO) from the zone of high pressure, the rotating speed of driven disc this moment (CP) will progressively be higher than the rotating speed of pump impeller (BL), rotating speed up to output shaft progressively increases, it is equal with the pressure difference of zone of high pressure and low pressure area that resistance constantly is increased to, and then the rotating speed of driven disc (CP) will no longer raise.
Fig. 2 has shown the axial plane sectional view of second embodiment of the invention, compares with first embodiment, has increased worm gear (WL) and planetary gears (XC).Fig. 6 has shown the structure of worm gear (WL).Worm gear (WL) is positioned at the zone that the working solution between pump impeller (BL) and the driven disc (CP) flows between pump impeller (BL) and driven disc (CP), the blade of worm gear (WL) becomes angle with sense of rotation, make when worm gear (WL) rotates that the blade of worm gear (WL) pushing working solution flows to pump impeller (BL) direction.
Worm gear (WL) can be directly and pump impeller (BL) connect, also can be as shown in Figure 2, connect by planetary gears (XC) and pump impeller (BL), planetary gears (XC) is made up of sun gear (T), gear ring (R), planet carrier (S) and planetary pinion (u), planetary pinion (u) is installed on the planet pin of planet carrier (S), with gear ring (R) and both engagements of sun gear (T), planetary pinion (u) both can center on the planet pin rotation, also can walk in gear ring (R) around sun gear (T) revolution.Worm gear (WL) connects with sun gear (T), and pump impeller (BL) connects with planet carrier (S), and gear ring (R) is fixing.
The annulus duct cylinder body of coupling differential mechanism (YO) both can connect with pump impeller (BL), also can connect with driven disc (CP), corresponding then is: rolling disc (P) connects with driven disc (CP) or connects with pump impeller (BL), the working solution of rolling disc (P) side of coupling differential mechanism (YO) is imported and exported and is positioned at pump impeller (BL) zone, and the working solution of rolling disc (P) opposite side is imported and exported and is positioned at driven disc (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 to be radius lines to launch, also can launch with curve form from inside to outside, the blade of driven disc (CP) can be that radial direction linearly launches, and also can be to launch with curve form from inside to outside.
Fig. 5-1 has shown the another kind of blade shape of pump impeller (BL), its blade outwards launches with curve form from the lining, when illustrated pump impeller (BL) when rotating in a counter-clockwise direction, the action of centrifugal force that interlobate working solution produces when not only being subjected to pump impeller (BL) rotation flows to the zone of high pressure of pump impeller (BL) outer rim, and be subjected to blade to the thrust of outer rim direction, the blade of the driven disc that matches with it (CP) can adopt radial alignment radial, the driven disc (CP) identical with first embodiment just, the curve of the blade form that also can adopt the mounted blade side with pump impeller (BL) shown in Fig. 5-2 to launch in the opposite direction, driven disc (CP) counterclockwise rotates in the same way with pump impeller (BL), the blade of driven disc (CP) has applied by the thrust of outer rim to inner edge to working solution, this makes working solution overcome action of centrifugal force, and is mobile to inner edge from the low pressure area of driven disc (CP) outer rim.
At the starting initial stage, such blade shape has increased the output torque of driven disc (CP), when the running at high speed of later stage, further strengthened the pressure of zone of high pressure, reduced the pressure of low pressure area, make that the pressure difference of the zone of high pressure of working solution and area of low pressure is bigger, the easier rotating speed that surpasses pump impeller (BL) of the rotating speed of driven disc (CP).
The coupling rotor (C) of coupling differential mechanism (YO) can be monomer structure, it also can be the structure of multi-disc combination, during the multi-disc combination, can the impact force that monomer structure is suffered be born by a plurality of rotor sheets, increased the working life of coupling rotor (C), those skilled in the art are the such structure of design easily, gives unnecessary details no longer one by one at this.
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.
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 (10)
1. the present invention relates to a kind of novel fluid torque converter, its structure mainly comprises: pump impeller, driven disc, coupling differential mechanism, novel fluid torque converter of the present invention, it is characterized in that: the input shaft of described pump impeller and described novel fluid torque converter links, its surface of revolution view is circular, its axial plane sectional view is semicircular arc, and the radial strut blade is arranged;
The output shaft of described driven disc and described novel fluid torque converter links, 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 pump impeller and the driven disc and between the blade;
Described coupling differential mechanism is made up of annulus cylinder body, spiral gusset, rolling disc, coupling rotor, 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, distribute along arc surface, and be coupled as one with described annulus cylinder body, become annulus duct cylinder body, 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, be positioned at annular cavity, coupling rotor diameter edge contacts with the annular cavity internal surface, its rotation axis and turn disc axis normal, and it is tangent with the annulus axis of annular cavity, described coupling rotor has coupling slot along radial direction, 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 and annulus duct cylinder body and during with even rotational speed, the rotor that is coupled 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, the rotation under the thrust of spiral gusset of coupling rotor, 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 and are rotated further, and get back to a side of spiral gusset starting point, begin slip engagement next time again;
Near the position of described annulus duct cylinder body rolling disc both sides spiral gusset starting point and 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 driven disc is relative with described pump impeller to be installed, and described coupling differential mechanism is being separated into zone of high pressure and low pressure area between pump impeller and the driven disc and with the outer edge area between pump impeller and the driven disc;
Be full of working solution in the described novel fluid torque converter, the annulus duct cylinder body of described coupling differential mechanism connects with pump impeller or driven disc respectively mutually with rolling disc, the working solution gateway of rolling disc both sides lays respectively at zone of high pressure and low pressure area, pump impeller rotates by the pressure official post driven disc of zone of high pressure and low pressure area, thereby drives output shaft output torque.
2. novel fluid torque converter according to claim 1, it is characterized in that: be full of working solution between pump impeller and the driven disc, in the zone that working solution flows between pump impeller and driven disc worm gear is installed, the blade of described worm gear becomes angle with sense of rotation, make when worm gear rotates that wormwheel blade pushing working solution flows to the pump impeller direction.
3. according to claim 1 and 2 described novel fluid torque converters, it is characterized in that: described worm gear and described pump impeller are coupled as one.
4. according to claim 1 and 2 described novel fluid torque converters, it is characterized in that: described novel fluid torque converter is equipped with planetary gears, described planetary gears is made up of sun gear, gear ring, planet carrier and planetary pinion, planetary pinion is installed on the planet pin of planet carrier, with gear ring and sun gear engagement, planetary pinion both can center on the planet pin rotation, also can in gear ring, walk around the sun gear revolution, described worm gear and sun gear connect, described pump impeller and planet carrier connect, and described gear ring is fixed.
5. novel fluid torque converter according to claim 1, it is characterized in that: the annulus duct cylinder body of described coupling differential mechanism is bound up with pump impeller and rotates with pump impeller, and the rolling disc of coupling differential mechanism is bound up with driven disc and rotates with driven disc.
6. novel fluid torque converter according to claim 1, it is characterized in that: annulus duct cylinder body and the driven disc of described coupling differential mechanism are bound up, and rotate with driven disc, the rolling disc of coupling differential mechanism is bound up with pump impeller and rotates with pump impeller.
7. according to claim 1,5 and 6 described novel fluid torque converters, it is characterized in that: described coupling differential mechanism is equipped with many spiral gussets.
8. according to claim 1 and 7 described novel fluid torque converters, it is characterized in that: described coupling rotor can be monomer structure, also can be the multi-disc composite structure.
9. novel fluid torque converter according to claim 1, it is characterized in that: the blade of described pump impeller launches with curve form from inside to outside.
10. novel fluid torque converter according to claim 1, it is characterized in that: the blade of described driven disc launches with curve form from inside to outside.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810597563.1A CN108708956A (en) | 2012-10-26 | 2012-10-26 | Fluid torque-converter |
| CN201210417175.3A CN103206506B (en) | 2012-10-26 | 2012-10-26 | Fluid torque-converter |
| CN201810598022.0A CN108708957A (en) | 2012-10-26 | 2012-10-26 | Fluid torque-converter |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210417175.3A CN103206506B (en) | 2012-10-26 | 2012-10-26 | Fluid torque-converter |
Related Child Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810597563.1A Division CN108708956A (en) | 2012-10-26 | 2012-10-26 | Fluid torque-converter |
| CN201810598022.0A Division CN108708957A (en) | 2012-10-26 | 2012-10-26 | Fluid torque-converter |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103206506A true CN103206506A (en) | 2013-07-17 |
| CN103206506B CN103206506B (en) | 2018-10-16 |
Family
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Family Applications (3)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810598022.0A Withdrawn CN108708957A (en) | 2012-10-26 | 2012-10-26 | Fluid torque-converter |
| CN201210417175.3A Expired - Fee Related CN103206506B (en) | 2012-10-26 | 2012-10-26 | Fluid torque-converter |
| CN201810597563.1A Withdrawn CN108708956A (en) | 2012-10-26 | 2012-10-26 | Fluid torque-converter |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810598022.0A Withdrawn CN108708957A (en) | 2012-10-26 | 2012-10-26 | Fluid torque-converter |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810597563.1A Withdrawn CN108708956A (en) | 2012-10-26 | 2012-10-26 | Fluid torque-converter |
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| Country | Link |
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| CN (3) | CN108708957A (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20090282821A1 (en) * | 2008-05-13 | 2009-11-19 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Hydrodynamic component and force transmission device with a hydrodynamic component |
| EP2146115A1 (en) * | 2008-07-19 | 2010-01-20 | ZF Friedrichshafen AG | Hydrodynamic torque converter |
| CN201875086U (en) * | 2010-11-24 | 2011-06-22 | 贵州凯星液力传动机械有限公司 | Hydraulic torque converter with speed reducer |
| CN102661377A (en) * | 2012-04-28 | 2012-09-12 | 长城汽车股份有限公司 | Hydraulic torque converter |
| CN202484241U (en) * | 2012-01-09 | 2012-10-10 | 重庆红宇精密工业有限责任公司 | Lockup hydraulic torque converter with rectangular shifting forks |
-
2012
- 2012-10-26 CN CN201810598022.0A patent/CN108708957A/en not_active Withdrawn
- 2012-10-26 CN CN201210417175.3A patent/CN103206506B/en not_active Expired - Fee Related
- 2012-10-26 CN CN201810597563.1A patent/CN108708956A/en not_active Withdrawn
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20090282821A1 (en) * | 2008-05-13 | 2009-11-19 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Hydrodynamic component and force transmission device with a hydrodynamic component |
| EP2146115A1 (en) * | 2008-07-19 | 2010-01-20 | ZF Friedrichshafen AG | Hydrodynamic torque converter |
| CN201875086U (en) * | 2010-11-24 | 2011-06-22 | 贵州凯星液力传动机械有限公司 | Hydraulic torque converter with speed reducer |
| CN202484241U (en) * | 2012-01-09 | 2012-10-10 | 重庆红宇精密工业有限责任公司 | Lockup hydraulic torque converter with rectangular shifting forks |
| CN102661377A (en) * | 2012-04-28 | 2012-09-12 | 长城汽车股份有限公司 | Hydraulic torque converter |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108708956A (en) | 2018-10-26 |
| CN108708957A (en) | 2018-10-26 |
| CN103206506B (en) | 2018-10-16 |
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