CN103899726A - Locking type hydraulic torque converter for engineering machinery - Google Patents
Locking type hydraulic torque converter for engineering machinery Download PDFInfo
- Publication number
- CN103899726A CN103899726A CN201410173798.XA CN201410173798A CN103899726A CN 103899726 A CN103899726 A CN 103899726A CN 201410173798 A CN201410173798 A CN 201410173798A CN 103899726 A CN103899726 A CN 103899726A
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- Prior art keywords
- turbine
- hub
- torque converter
- pump impeller
- blade
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Classifications
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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
- F16H41/04—Combined pump-turbine units
- F16H41/22—Gearing systems consisting of a plurality of hydrokinetic units operating alternatively, e.g. made effective or ineffective by filling or emptying or by mechanical clutches
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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
-
- 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
- F16H41/26—Shape of runner blades or channels with respect to function
Abstract
The invention relates to a locking type hydraulic torque converter for engineering machinery. The locking type hydraulic torque converter comprises a clutch assembly and a piston assembly, wherein the clutch assembly and the piston assembly are arranged in a cover and turbine working chamber formed by a wheel cover assembly and a turbine assembly. The clutch assembly comprises a shock absorber, a friction plate, a disk hub and a baffle. The piston assembly comprises a piston, a first sealing component and a second sealing component. The baffle is fixed to a wheel cover shell. One end of the disk hub is connected with a turbine hub, and the other end of the disk hub makes contact with the shock absorber. The friction plate is fixed to the shock absorber. The inner surface of a circular ring body makes contact with a wheel cover hub through the first sealing component. The outer surface of the circular ring body makes contact with the wheel cover shell through the second sealing component. A spline is arranged on the inner wall of the wheel cover shell. A limiting stop dog conducts guide motion along the spline to act on the friction plate. In order to solve the technical problems that an existing three-element centripetal turbine type hydraulic torque converter is low in efficiency and a vehicle is high in fuel consumption, cascades of the hydraulic torque converter are reasonably designed, matching between the hydraulic torque converter and an engine is optimized, and consequently good dynamic properties are obtained.
Description
Technical field
The present invention relates to a kind of closed-end hydraulic torque converter, it is mainly used in engineering machinery vehicle.
Background technique
Fluid torque converter is a core component in engineering machinery transmission, be installed between motor and gearbox, utilize flowing of liquid that Engine torque is delivered to gearbox reposefully, can effective attenuation motor and torsional oscillation and the dynamic load of transmission system, make the engineering machinery vehicle that this element is housed there is good startability, stationarity and the automatic adaptability to external load.Remarkable working life to extending motor and transmission system, make vehicle obtain good low-speed performance, improve the passing capacity to various complex road surfaces.Existing three element centripetal turbine formula fluid torque converter comprises turbine, guide wheel and pump impeller, and its higher efficiency range is very narrow, very low in the efficiency of low speed and high velocity, makes Fuel consumption high.
Summary of the invention
In order to solve the technical problem that existing three element centripetal turbine formula fluid torque converter efficiency is low, Fuel consumption is high, the invention provides a kind of engineering machinery closed-end hydraulic torque converter.In order to improve engineering vehicle fuel efficiency and power character, by hydrodynamic torque converter cascade appropriate design, optimize and the mating of motor, obtain good power character.Increase lockup clutch element, in the time of fluid torque converter low speed and high-speed working condition, lockup clutch work, is directly delivered to turbine by engine power by lockup clutch simultaneously, reduces energy loss, improves fuel efficiency.And increase locking damper mechanism, in order to reducing vibration, noise and the impact to gearbox.
Solving the problems of the technologies described above adopted technological scheme is:
A kind of engineering machinery closed-end hydraulic torque converter, comprises hubcap assembly, turbine assembly, pump impeller assembly and guide wheel assembly;
Described hubcap assembly comprises hubcap hub 21, hubcap shell 22; Described turbine assembly comprises turbine hub 72, turbine body 71; Described pump impeller assembly comprises pump impeller hub 91, pump impeller body 92; Described guide wheel assembly comprises guide wheel body 81 and outer race 82;
Its special way is: also comprise the clutch pack and the piston assembly that are arranged in the cover whirlpool active chamber that hubcap assembly, turbine and turbine hub form;
Described clutch pack comprises vibration damper 10, friction plate 5, hub 13 and baffle plate 6;
Described piston assembly comprises piston 3, the first black box 1 and the second black box 4;
Described baffle plate 6 is fixed on hubcap shell 22, and one end of described hub 13 is connected with turbine hub by spline, and the other end of described hub 13 contacts with vibration damper 10, and described friction plate 5 is fixed on vibration damper, and friction plate 5 can contact with piston with baffle plate 6;
Described piston comprises annulus body 31 and is arranged on the positive stop 32 on annulus, the internal surface of described annulus body contacts with hubcap hub by the first black box 1, the outer surface of described annulus body contacts with hubcap shell 22 by the second black box 4, on described hubcap shell inwall, be provided with spline 15, described positive stop 32 can act on friction plate 5 along spline 11 guide movements on hubcap shell inwall.
Above-mentioned the first black box comprises the first seal ring 11 and the first surface ring 12 being in contact with one another and is arranged on the first seal groove in annulus body internal surface, between described first surface ring and hubcap hub, form sealing surface, described the first seal ring is installed in the first seal groove.
Above-mentioned the second black box comprises the second seal ring 41 and the second surface ring 42 being in contact with one another and the second seal groove on this external surface of annulus is set, between described second surface ring and hubcap shell 22, form sealing surface, described the second seal ring is arranged in the second seal groove.
Fluid torque converter circulate circle diameter phi D is 340 ± 4mm;
The average inlet/outlet radius of each active wheel center line of flow path:
The import mean radius ρ of pump impeller body center line of flow path
b1=97.4 ± 2mm;
The outlet mean radius ρ of pump impeller body center line of flow path
b1=158.5 ± 2mm;
The import mean radius ρ of turbine body center line of flow path
t1=158.5 ± 2mm;
The outlet mean radius ρ of turbine body center line of flow path
t2=97.4 ± 2mm;
The import mean radius ρ of guide wheel body center line of flow path
d1=91 ± 2mm;
The outlet mean radius ρ of guide wheel body center line of flow path
d2=91 ± 2mm;
Each runner vane center line of flow path into and out of bicker be:
B1=95 °～100 ° of pump impeller blade inlet angle β;
B2=103 °～108 ° of pump impeller blade exit angle β;
T1=29 °～34 ° of turbine blade inlet angle β;
T2=138 °～143 ° of turbine blade exit angle β;
D1=115 °～120 ° of guide vane inlet angle β;
D2=23 °～28 ° of guide vane exit angle β;
Each active wheel is imported and exported runner relative width B:
Pump impeller blade inlet channel width B
b1=0.23 ± 0.02;
Pump impeller blade outlet flow width B
b2=0.23 ± 0.02;
Turbine blade inlet channel width B
t1=0.15 ± 0.02;
Turbine blade outlet flow width B
t2=0.23 ± 0.02;
Guide vane inlet channel width B
d1=0.42 ± 0.02;
Guide vane outlet flow width B
d2=0.45 ± 0.02;
Each runner vane quantity:
Pump impeller blade is counted Z
b=31;
Turbine blade is counted Z
t=29;
Guide vane is counted Z
d=11;
Each active wheel normal thickness δ of inlet
n1normal thickness δ with outlet port blade
n2:
The normal thickness of blade δ of pump impeller inlet/outlet place
b1=δ
b2=1.5mm;
The normal thickness of blade δ of turbine inlet/outlet place
t1=δ
t2=1.5mm;
The normal thickness of blade δ of guide wheel inlet
d1=12mm, guide wheel outlet port normal thickness of blade δ
d2=2.2mm.
Above-mentioned vibration damper twisting characteristic is under torque limit 1295N.m, and ultimate angle is corner 7.5 ± 0.5 degree.
The present invention has advantages of:
1, TCC of the present invention adopts integral structure, integrates torsion damping and latch functions; Piston seal is cancelled traditional rectangular loop form, adopts new special seal structure, i.e. an O shape force application element and a surface ring that hardness is higher.
2, owing to adopting integral type clutch, lockup clutch modular construction compactness, torsion damping characteristic is better, has improved the travelling comfort of engineering vehicle, less to the impact of gearbox, and Product Assembly and maintenance cost reduce.
3, piston of the present invention adopts new sealing configuration, and sealing effect is better, and Sealing and sealing surface wear reduce, and sealing reliability is higher; Reasonably circulate circle and cascade parameter, reach desired properties, makes vehicle power coupling more reasonable; Make the engineering machinery that this fluid torque converter is housed obtain good fuel efficiency and power character.
4, lockup clutch delivery threshold moment of torsion of the present invention is 1295N.m; The zero-speed pump impeller thousand of fluid torque converter turns nominal moment M
bg0=150 × (1 ± 5%) N.m, zero-speed converter torque ratio is K
0=2.75 × (1 ± 5%), highest efficiency eta>=80%.
Accompanying drawing explanation
Fig. 1 is the structural drawing of one embodiment of the present of invention;
Fig. 2 is clutch pack schematic diagram;
Fig. 3 is pump impeller cascade configuration schematic diagram;
Fig. 4 is turbine cascade profile schematic diagram;
Fig. 5 is the unfolded drawing of each active wheel along center line of flow path section;
Fig. 6 is the axial plane figure of each active wheel;
Fig. 7 is fluid torque converter primary characteristic plotted curve;
Fig. 8 is the first seal component architecture figure;
Fig. 9 is the second seal component architecture figure;
Wherein reference character is: 1-the first black box, 11-the first seal ring, 12-first surface ring, 21-hubcap hub, 22-hubcap shell, 3-piston, 31-annulus body, 32-positive stop, 4-the second black box, 41-the second seal ring, 42-second surface ring, 5-friction plate, 6-baffle plate, 72-turbine hub, 71-turbine body, 81-guide wheel body, 82-outer race, 91-pump impeller hub, 92-pump impeller body, 10-vibration damper, 13-hub, 14-rivet, 15-spline.
Embodiment
As shown in Figure 1, engineering machinery closed-end hydraulic torque converter, comprises hubcap assembly, turbine assembly, pump impeller assembly and guide wheel assembly; Hubcap assembly comprises hubcap hub 21, hubcap shell 22; Turbine assembly comprises turbine hub 72, turbine body 71; Pump impeller assembly comprises pump impeller hub 91, pump impeller body 92; Guide wheel assembly comprises guide wheel body 81 and outer race 82; Also comprise the clutch pack and the piston assembly that are arranged in the cover whirlpool active chamber that hubcap assembly, turbine and turbine hub form.
As shown in Figure 2, clutch pack comprises vibration damper 10, friction plate 5, hub 13 and baffle plate 6; Piston assembly comprises piston 3, the first black box 1 and the second black box 4; Baffle plate 6 is fixed on hubcap shell 22, and one end of hub 13 is connected with turbine hub by spline, and the other end of hub 13 contacts with vibration damper 10, and friction plate 5 is fixed on vibration damper, generally fixing by rivet 14.Friction plate 5 can contact with piston 3 with baffle plate 6; Piston comprises annulus body 31 and is arranged on the positive stop 32 on annulus, the internal surface of annulus body contacts with hubcap hub 21 by the first black box 1, the outer surface of annulus body contacts with hubcap shell 22 by the second black box 4, on hubcap shell inwall, be provided with spline 15, positive stop 32 can act on friction plate 5 along spline 11 guide movements on hubcap shell inwall.
Each impeller concrete structure parameter is as follows:
Fluid torque converter circulate circle diameter phi D is 340 ± 4mm;
The average inlet/outlet radius of each active wheel center line of flow path:
The import mean radius ρ of pump impeller body center line of flow path
b1=97.4 ± 2mm;
The outlet mean radius ρ of pump impeller body center line of flow path
b1=158.5 ± 2mm;
The import mean radius ρ of turbine body center line of flow path
t1=158.5 ± 2mm;
The outlet mean radius ρ of turbine body center line of flow path
t2=97.4 ± 2mm;
The import mean radius ρ of guide wheel body center line of flow path
d1=91 ± 2mm;
The outlet mean radius ρ of guide wheel body center line of flow path
d2=91 ± 2mm;
Each runner vane center line of flow path into and out of bicker be:
B1=95 °～100 ° of pump impeller blade inlet angle β;
B2=103 °～108 ° of pump impeller blade exit angle β;
T1=29 °～34 ° of turbine blade inlet angle β;
T2=138 °～143 ° of turbine blade exit angle β;
D1=115 °～120 ° of guide vane inlet angle β;
D2=23 °～28 ° of guide vane exit angle β;
Each active wheel is imported and exported runner relative width B:
Pump impeller blade inlet channel width B
b1=0.23 ± 0.02;
Pump impeller blade outlet flow width B
b2=0.23 ± 0.02;
Turbine blade inlet channel width B
t1=0.15 ± 0.02;
Turbine blade outlet flow width B
t2=0.23 ± 0.02;
Guide vane inlet channel width B
d1=0.42 ± 0.02;
Guide vane outlet flow width B
d2=0.45 ± 0.02;
Each runner vane quantity:
Pump impeller blade is counted Z
b=31;
Turbine blade is counted Z
t=29;
Guide vane is counted Z
d=11;
Each active wheel normal thickness δ of inlet
n1normal thickness δ with outlet port blade
n2:
The normal thickness of blade δ of pump impeller inlet/outlet place
b1=δ
b2=1.5mm;
The normal thickness of blade δ of turbine inlet/outlet place
t1=δ
t2=1.5mm;
The normal thickness of blade δ of guide wheel inlet
d1=12mm, guide wheel outlet port normal thickness of blade δ
d2=2.2mm.
Fig. 2 adopts above-mentioned parameter, the pump impeller leaf grating outline drawing of design, and Fig. 3 is turbine cascade outline drawing;
Fig. 4 is the unfolded drawing of each active wheel along center line of flow path section; Fig. 5 is the axial plane figure of each active wheel;
Fig. 6 is fluid torque converter primary characteristic plotted curve; Wherein a curve is efficiency curve, and b curve is converter torque ratio curve, and c curve is for can hold curve, and abscissa represents speed ratio i, and the left longitudinal axis is for can hold Mbg (Nm), and the right longitudinal axis is converter torque ratio (efficiency).
The zero-speed pump impeller (can hold) thousand of fluid torque converter turns nominal moment M
bg0=150 × (1 ± 5%) N.m, zero-speed converter torque ratio is K
0=2.75 × (1 ± 5%), highest efficiency eta>=80%; Lockup clutch delivery threshold moment of torsion is 1295N.m; Vibration damper twisting characteristic is under torque limit 1295N.m, and ultimate angle is corner 7.5 ± 0.5 degree.As shown in Figure 7, the first black box comprises the first seal ring 11 and the first surface ring 12 being in contact with one another and is arranged on the first seal groove in annulus body internal surface, between first surface ring and hubcap hub, form sealing surface, the first seal ring is installed in the first seal groove.
As shown in Figure 8, the second black box comprises the second seal ring 41 and the second surface ring 42 being in contact with one another and the second seal groove on this external surface of annulus is set, between second surface ring and hubcap shell, form sealing surface, the second seal ring is arranged in the second seal groove.
Working principle of the present invention:
When locking work, spline plays bearing torque and leading role, transferring energy, and baffle plate is fixed in hubcap, and piston is set up a closed chamber by first, second black box ring.
In locking when work,, piston, along hubcap upper spline guiding, promotes the friction plate of clutch pack to the motion of baffle plate direction under the effect of locking oil pressure, is locked on baffle plate, realize engine power by hubcap to baffle plate, then arrive clutch, finally arrive turbine.
When release, piston right-side cavity pressure is greater than chamber, left side, and piston is toward the motion of hubcap components side direction, and clutch pack, in free state, rotates with turbine.
Claims (6)
1. an engineering machinery closed-end hydraulic torque converter, comprises hubcap assembly, turbine assembly, pump impeller assembly and guide wheel assembly;
Described hubcap assembly comprises hubcap hub (21), hubcap shell (22); Described turbine assembly comprises turbine hub (72), turbine body (71); Described pump impeller assembly comprises pump impeller hub (91), pump impeller body (92); Described guide wheel assembly comprises guide wheel body (81) and outer race (82);
It is characterized in that: also comprise the clutch pack and the piston assembly that are arranged in the cover whirlpool active chamber that hubcap assembly, turbine and turbine hub form;
Described clutch pack comprises vibration damper (10), friction plate (5), hub (13) and baffle plate (6);
Described piston assembly comprises piston (3), the first black box (1) and the second black box (4);
Described baffle plate (6) is fixed on hubcap shell (22), one end of described hub (13) is connected with turbine hub by spline, the other end of described hub (13) contacts with vibration damper (10), described friction plate (5) is fixed on vibration damper, and friction plate (5) can contact with piston with baffle plate (6);
Described piston comprises annulus body (31) and is arranged on the positive stop (32) on annulus, the internal surface of described annulus body contacts with hubcap hub by the first black box (1), the outer surface of described annulus body contacts with hubcap shell (22) by the second black box (4), on described hubcap shell inwall, be provided with spline (15), described positive stop (32) can act on friction plate (5) along spline (11) guide movement on hubcap shell inwall.
2. engineering machinery closed-end hydraulic torque converter according to claim 1, it is characterized in that: described the first black box comprises the first seal ring (11) and the first surface ring (12) being in contact with one another and is arranged on the first seal groove in annulus body internal surface, between described first surface ring and hubcap hub, form sealing surface, described the first seal ring is arranged in the first seal groove.
3. engineering machinery closed-end hydraulic torque converter according to claim 2, it is characterized in that: described the second black box comprises the second seal ring (41) and the second surface ring (42) being in contact with one another and the second seal groove on this external surface of annulus is set, between described second surface ring and hubcap shell (22), form sealing surface, described the second seal ring is arranged in the second seal groove.
4. according to arbitrary described engineering machinery closed-end hydraulic torque converter of claim 1-3, it is characterized in that:
Fluid torque converter circulate circle diameter phi D is 340 ± 4mm;
The average inlet/outlet radius of each active wheel center line of flow path:
The import mean radius ρ of pump impeller body center line of flow path
b1=97.4 ± 2mm;
The outlet mean radius ρ of pump impeller body center line of flow path
b1=158.5 ± 2mm;
The import mean radius ρ of turbine body center line of flow path
t1=158.5 ± 2mm;
The outlet mean radius ρ of turbine body center line of flow path
t2=97.4 ± 2mm;
The import mean radius ρ of guide wheel body center line of flow path
d1=91 ± 2mm;
The outlet mean radius ρ of guide wheel body center line of flow path
d2=91 ± 2mm;
Each runner vane center line of flow path into and out of bicker be:
B1=95 °～100 ° of pump impeller blade inlet angle β;
B2=103 °～108 ° of pump impeller blade exit angle β;
T1=29 °～34 ° of turbine blade inlet angle β;
T2=138 °～143 ° of turbine blade exit angle β;
D1=115 °～120 ° of guide vane inlet angle β;
D2=23 °～28 ° of guide vane exit angle β;
Each active wheel is imported and exported runner relative width B:
Pump impeller blade inlet channel width B
b1=0.23 ± 0.02;
Pump impeller blade outlet flow width B
b2=0.23 ± 0.02;
Turbine blade inlet channel width B
t1=0.15 ± 0.02;
Turbine blade outlet flow width B
t2=0.23 ± 0.02;
Guide vane inlet channel width B
d1=0.42 ± 0.02;
Guide vane outlet flow width B
d2=0.45 ± 0.02;
Each runner vane quantity:
Pump impeller blade is counted Z
b=31;
Turbine blade is counted Z
t=29;
Guide vane is counted Z
d=11;
Each active wheel normal thickness δ of inlet
n1normal thickness δ with outlet port blade
n2:
The normal thickness of blade δ of pump impeller inlet/outlet place
b1=δ
b2=1.5mm;
The normal thickness of blade δ of turbine inlet/outlet place
t1=δ
t2=1.5mm;
The normal thickness of blade δ of guide wheel inlet
d1=12mm, guide wheel outlet port normal thickness of blade δ
d2=2.2mm.
5. engineering machinery closed-end hydraulic torque converter according to claim 4, is characterized in that: described vibration damper twisting characteristic is under torque limit 1295N.m, and ultimate angle is corner 7.5 ± 0.5 degree.
6. engineering machinery closed-end hydraulic torque converter according to claim 4, is characterized in that: described friction plate (5) is fixed on vibration damper by rivet (14).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410173798.XA CN103899726B (en) | 2014-04-28 | 2014-04-28 | A kind of engineering machinery closed-end hydraulic torque converter |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410173798.XA CN103899726B (en) | 2014-04-28 | 2014-04-28 | A kind of engineering machinery closed-end hydraulic torque converter |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103899726A true CN103899726A (en) | 2014-07-02 |
| CN103899726B CN103899726B (en) | 2017-01-04 |
Family
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410173798.XA Active CN103899726B (en) | 2014-04-28 | 2014-04-28 | A kind of engineering machinery closed-end hydraulic torque converter |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105179633A (en) * | 2015-10-08 | 2015-12-23 | 金华市华海机械有限公司 | Pump hub gear sleeve and machining process thereof |
| CN105443711A (en) * | 2015-12-18 | 2016-03-30 | 陕西航天动力高科技股份有限公司 | Locking type hydraulic torque converter for small-tonnage forklift |
| CN105443712A (en) * | 2015-12-18 | 2016-03-30 | 陕西航天动力高科技股份有限公司 | Superflat automobile hydraulic torque converter |
| CN106481371A (en) * | 2015-08-26 | 2017-03-08 | 熵零股份有限公司 | Hydraulic mechanism and its device |
| CN107035840A (en) * | 2016-12-01 | 2017-08-11 | 陕西航天动力高科技股份有限公司 | A kind of high energy holds closed-end hydraulic torque converter |
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| CN202468895U (en) * | 2012-03-03 | 2012-10-03 | 陕西航天动力高科技股份有限公司 | High-power vehicle-used superflat hydraulic torque converter |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106481371A (en) * | 2015-08-26 | 2017-03-08 | 熵零股份有限公司 | Hydraulic mechanism and its device |
| CN105179633A (en) * | 2015-10-08 | 2015-12-23 | 金华市华海机械有限公司 | Pump hub gear sleeve and machining process thereof |
| CN105443711A (en) * | 2015-12-18 | 2016-03-30 | 陕西航天动力高科技股份有限公司 | Locking type hydraulic torque converter for small-tonnage forklift |
| CN105443712A (en) * | 2015-12-18 | 2016-03-30 | 陕西航天动力高科技股份有限公司 | Superflat automobile hydraulic torque converter |
| CN107035840A (en) * | 2016-12-01 | 2017-08-11 | 陕西航天动力高科技股份有限公司 | A kind of high energy holds closed-end hydraulic torque converter |
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| Publication number | Publication date |
|---|---|
| CN103899726B (en) | 2017-01-04 |
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