CN201071916Y - Hydraulic moment changer - Google Patents
Hydraulic moment changer Download PDFInfo
- Publication number
- CN201071916Y CN201071916Y CNU200720124832XU CN200720124832U CN201071916Y CN 201071916 Y CN201071916 Y CN 201071916Y CN U200720124832X U CNU200720124832X U CN U200720124832XU CN 200720124832 U CN200720124832 U CN 200720124832U CN 201071916 Y CN201071916 Y CN 201071916Y
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- China
- Prior art keywords
- pump impeller
- assembly
- turbine
- outer shroud
- guide wheel
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Abstract
The utility model relates to a vehicle hydraulic torque converter, which comprises a pump impeller assembly (1), a turbine assembly (2) and an idler pulley assembly (3) which form a fluid circulatory circle. The utility model is characterized in that the fluid outlet openings of the three impellers of the pump impeller assembly (1), the turbine assembly (2) and the idler pulley assembly (3) in the axial cross section are all smaller than the adjacent fluid inlet openings. The locking type hydraulic torque converter provided by the utility model has the advantages that the structure and reasonable, the fluid flow loss is little, and the hydraulic torque converter is favorable to improve transmission efficiency.
Description
Technical field
The utility model relates to a kind of automobile torque converter, is specifically related to a kind of enclosed type fluid torque converter.
Background technique
Fluid torque converter is a key components and parts that is applied in the pattern automatic transmission speed changer cars such as AT and CVT, fluid torque converter is to utilize flowing of liquid reposefully Engine torque to be passed to speed changer, fluid torque converter inside is a ring device, wherein be full of automatic transmission fluid, between motor and speed changer.Extensively adopt the comprehensive fluid torque converter of forming by pump impeller, turbine, guide wheel and lock-up clutch of single-stage two-phase three element enclosed type at present on the car.Pump impeller is that driving link is connected with flywheel, guiding liquids impulse turbine blade, make blade rotation and drive turbine, turbine is that Passive part is connected with transmission input shaft, guide wheel between above-mentioned two impellers is to be fixed on the gearbox case by overrunning clutch and guide wheel shaft bush, and lock-up clutch then is installed between pump impeller end cap and the turbine.
The structural disadvantages of present automobile torque converter is: inlet/outlet measure-alike and just relative that constitutes pump impeller, turbine, the liquid stream of guide wheel between two impellers of fluid torque converter circulate circle, place, the medial and lateral part that liquid fails to be convened for lack of a quorum between inlet/outlet leaks, so just make the liquid stream of an impeller outlet can not all enter the inlet of next impeller, make hydraulic transmission oil that bigger liquid flowing loss be arranged between impeller, reduced the transmission efficiency of fluid torque converter.In addition, the present domestic car structure of fluid torque converter circulate circle, structures such as circular loop circle, egg type circulate circle, oval circulate circle are arranged, but the outer shroud of pump impeller and turbine is symmetric arrangement, and the axial dimension of above several circulate circles is all very big, under the condition of Hyundai Motor axial space restriction, bigger narrow limitation is arranged to developing many gears speed changer.
Summary of the invention
It is a kind of rational in infrastructure that the purpose of this utility model is to provide, and liquid flowing loss is little, helps improving the enclosed type fluid torque converter of transmission efficiency.
The purpose of this utility model is achieved in that a kind of fluid torque converter, comprise the pump impeller assembly that constitutes liquid stream circulate circle, turbine assembly and guide wheel assembly is characterized in that: the liquid outflow opening of three impellers that join successively in its axial cross section of described pump impeller assembly, described turbine assembly and described guide wheel assembly is all less than adjacent liquid inflow entrance.
The radial length of the liquid outflow opening of said pump wheel assembly is less than the radial length of the liquid inflow entrance of described turbine assembly, and its inner and outer end lays respectively at the outside of described liquid inflow entrance the inner of described turbine assembly and the inboard of outer end; The liquid outflow opening of described turbine assembly encircles the liquid inflow entrance outer end of the tangent line of inner camber line destination county and described guide wheel assembly in turbine inboard joins, and its described liquid outflow opening joins at the circumference of the guide wheel shaft of the described liquid inflow entrance end of the tangent line of the camber line destination county of turbine outer shroud the inner and described guide wheel assembly, and the liquid stream two ends of the liquid outflow opening of promptly described turbine assembly are positioned within the two ends of liquid inflow entrance of described guide wheel assembly; The inner of the liquid outflow opening of described guide wheel assembly and outer end lay respectively at the inner inboard of ring in the outside of pump impeller outer shroud the inner at liquid inflow entrance place of described pump impeller assembly and the pump impeller.
Central plane between the inlet/outlet plane of the guide vane of described guide wheel assembly is positioned at the axial centre of this liquid stream circulate circle by described pump impeller assembly one side.
The outer shroud of the turbine of the pump impeller of said pump wheel assembly and described turbine assembly can be the oblateness of asymmetric setting; The pump impeller outer shroud of described pump impeller and the turbine outer shroud of described turbine constitute by three sections different circular arcs are tangent respectively; Wherein, the ratio that constitutes the radius between three sections circular arcs of described pump impeller outer shroud is: 1.06: 2.91: 1, the ratio that constitutes the radius between three sections circular arcs of described turbine outer shroud was: 1.01: 2.97: 1.
For improving the liquid-flow state between impeller, the inlet vane angle of the pump impeller blade of said pump wheel assembly can be 137.48 °, and the outlet blade angle can be 88.03 °; The inlet vane angle of the turbine blade of described turbine assembly can be 50.74 °, and the outlet blade angle can be 145.67 °; The inlet vane angle of the guide vane of described guide wheel assembly can be 44.64 °, and the outlet blade angle can be 22.2 °.
The enclosed type fluid torque converter that the utility model provides because the liquid outflow opening of three impellers that join successively in its axial cross section all less than adjacent liquid inflow entrance, makes the liquid stream of an impeller outlet all enter the inlet of next impeller, reduces liquid flowing loss; The outer shroud of pump impeller and turbine is the oblateness of asymmetric setting, helps flowing of liquid, can realize the flattening requirement of fluid torque converter very easily, is that the layout of lockup clutch shock-absorbing spring has stayed installing space at roundlet arc place; By to the inlet vane angle of three impellers and the coordination setting of outlet blade angle, improved the mobile performance of liquid again, integral body has improved the transmission efficiency of fluid torque converter.
In sum, the enclosed type fluid torque converter that the utility model provides is rational in infrastructure, and liquid flowing loss is little, helps improving transmission efficiency.
Description of drawings
The utility model is described in further detail below in conjunction with drawings and Examples.
Fig. 1 is an embodiment's of the present utility model sectional structure schematic representation;
Fig. 2 is the structural representation of the outer shroud of impeller among the embodiment of the present utility model and liquid outflow opening, liquid inflow entrance;
Fig. 3 is the structural representation of the blade angle of pump impeller blade among the embodiment of the present utility model;
Fig. 4 is the structural representation of the blade angle of turbine blade among the embodiment of the present utility model;
Fig. 5 is the structural representation of the blade angle of guide vane among the embodiment of the present utility model.
Embodiment
Embodiment: referring to Fig. 1～Fig. 5, a kind of fluid torque converter, comprise the pump impeller assembly 1 that constitutes liquid stream circulate circle, turbine assembly 2 and guide wheel assembly 3, the cap assembly 4 of fixedlying connected with pump impeller assembly 1, and be connected lockup clutch assembly 5 in the fluid torque converter routinely, pump impeller thrust bearing 6, guide wheel thrust bearing 7 and thrust ring 8 is characterized in that: the liquid outflow opening of three impellers that join successively in its axial cross section of described pump impeller assembly 1, described turbine assembly 2 and described guide wheel assembly 3 is all less than adjacent liquid inflow entrance.
The radial length of the liquid outflow opening 1b of described pump impeller assembly 1 is less than the radial length of the liquid inflow entrance 2a of described turbine assembly 2, and its inner and outer end lays respectively at the outside of described liquid inflow entrance 2a the inner of described turbine assembly 2 and the inboard of outer end; The liquid outflow opening 2b of described turbine assembly 2 encircles the liquid inflow entrance 3a outer end of the tangent line of camber line destination county of 2-2 the inner and described guide wheel assembly 3 in turbine inboard joins, and its described liquid outflow opening 2b joins at the circumference of the guide wheel shaft 3-1 of the described liquid inflow entrance 3a end of the tangent line of the camber line destination county of turbine outer shroud 2-1 the inner and described guide wheel assembly 3; The inboard of ring 1-2 the inner in the outside of the pump impeller outer shroud 1-1 the inner at the liquid inflow entrance 1a place that the inner of the liquid outflow opening 3b of described guide wheel assembly 3 and outer end lay respectively at described pump impeller assembly 1 and the pump impeller; Relevant liquid outflow opening, liquid inflow entrance and liquid stream tangent line are referring to the dotted portion shown in Fig. 2.
The axial middle plane on the inlet/outlet plane of the guide vane 3-2 of described guide wheel assembly 3 is positioned at the axial centre of this liquid stream circulate circle by described pump impeller assembly 1 one sides.
The outer shroud of the pump impeller 1-3 of described pump impeller assembly 1 and the turbine 2-3 of described turbine assembly 2 is the oblateness of asymmetric setting; The pump impeller outer shroud 1-1 of described pump impeller 1-3 and the turbine outer shroud 2-1 of described turbine 2-3 constitute by three sections different circular arcs are tangent respectively; Wherein, constitute three sections circular arc R B1, RB2 of described pump impeller outer shroud 1-1, the ratio of the radius between the RB3 is: 1.06: 2.91: 1, constitute three sections circular arc R T1, RT2 of described turbine outer shroud 2-1, the ratio of the radius between the RT3 is: 1.01: 2.97: 1.
The inlet vane angle β B1 of the pump impeller blade 1-4 of described pump impeller assembly 1 is 137.48 °, and outlet blade angles B2 is 88.03 °; The inlet vane angle β T1 of the turbine blade 2-4 of described turbine assembly 2 is 50.74 °, and outlet blade angles T2 is 145.67 °; The inlet vane angle β R1 of the guide vane 3-2 of described guide wheel assembly 3 is 44.64 °, and outlet blade angles R2 is 22.2 °.
Other structure of the fluid torque converter of present embodiment is a conventional structure.
Claims (7)
1. fluid torque converter, comprise the pump impeller assembly (1) that constitutes liquid stream circulate circle, turbine assembly (2) and guide wheel assembly (3) is characterized in that: the liquid outflow opening of three impellers that join successively in its axial cross section of described pump impeller assembly (1), described turbine assembly (2) and described guide wheel assembly (3) is all less than adjacent liquid inflow entrance.
2. fluid torque converter as claimed in claim 1, it is characterized in that: the radial length of the liquid outflow opening (1b) of described pump impeller assembly (1) is less than the radial length of the liquid inflow entrance (2a) of described turbine assembly (2), and its inner and outer end lays respectively at the outside of described liquid inflow entrance (2a) the inner of described turbine assembly (2) and the inboard of outer end; The liquid outflow opening (2b) of described turbine assembly (2) encircles (2-2) inner camber line destination county in turbine tangent line joins with the inboard of liquid inflow entrance (3a) outer end of described guide wheel assembly (3), and the circumference of the guide wheel shaft (3-1) that its described liquid outflow opening (2b) is held at the described liquid inflow entrance (3a) of the tangent line of the inner camber line destination county of turbine outer shroud (2-1) and described guide wheel assembly (3) joins; The inner of the liquid outflow opening (3b) of described guide wheel assembly (3) and outer end lay respectively at inner inboard of ring (1-2) in the inner outside of pump impeller outer shroud (1-1) that the liquid inflow entrance (1a) of described pump impeller assembly (1) locates and the pump impeller.
3. fluid torque converter as claimed in claim 1 or 2 is characterized in that: the central plane between the inlet/outlet plane of the guide vane (3-2) of described guide wheel assembly (3) is positioned at the axial centre of this liquid stream circulate circle by described pump impeller assembly (1) one side.
4. fluid torque converter as claimed in claim 1 or 2 is characterized in that: the outer shroud of the pump impeller (1-3) of described pump impeller assembly (1) and the turbine (2-3) of described turbine assembly (2) is the oblateness of asymmetric setting; The pump impeller outer shroud (1-1) of described pump impeller (1-3) and the turbine outer shroud (2-1) of described turbine (2-3) constitute by three sections different circular arcs are tangent respectively; Wherein, the ratio that constitutes the radius between the three sections circular arcs (RB1), (RB2), (RB3) of described pump impeller outer shroud (1-1) is: 1.06: 2.91: 1, the ratio that constitutes the radius between the three sections circular arcs (RT1), (RT2), (RT3) of described turbine outer shroud (2-1) was: 1.01: 2.97: 1.
5. fluid torque converter as claimed in claim 3 is characterized in that: the outer shroud of the pump impeller (1-3) of described pump impeller assembly (1) and the turbine (2-3) of described turbine assembly (2) is the oblateness of asymmetric setting; The pump impeller outer shroud (1-1) of described pump impeller (1-3) and the turbine outer shroud (2-1) of described turbine (2-3) constitute by three sections different circular arcs are tangent respectively; Wherein, the ratio that constitutes the radius between the three sections circular arcs (RB1), (RB2), (RB3) of described pump impeller outer shroud (1-1) is: 1.06: 2.91: 1, the ratio that constitutes the radius between the three sections circular arcs (RT1), (RT2), (RT3) of described turbine outer shroud (3-1) was: 1.01: 2.97: 1.
6. fluid torque converter as claimed in claim 4 is characterized in that: the inlet vane angle (β B1) of the pump impeller blade (1-4) of described pump impeller assembly (1) is 137.48 °, and outlet blade angle (β B2) is 88.03 °; The inlet vane angle (β T1) of the turbine blade (2-4) of described turbine assembly (2) is 50.74 °, and outlet blade angle (β T2) is 145.67 °; The inlet vane angle (β R1) of the guide vane (3-2) of described guide wheel assembly (3) is 44.64 °, and outlet blade angle (β R2) is 22.2 °.
7. fluid torque converter as claimed in claim 5 is characterized in that: the inlet vane angle (β B1) of the pump impeller blade (1-4) of described pump impeller assembly (1) is 137.48 °, and outlet blade angle (β B2) is 88.03 °; The inlet vane angle (β T1) of the turbine blade (2-4) of described turbine assembly (2) is 50.74 °, and outlet blade angle (β T2) is 145.67 °; The inlet vane angle (β R1) of the guide vane (3-2) of described guide wheel assembly (3) is 44.64 °, and outlet blade angle (β R2) is 22.2 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU200720124832XU CN201071916Y (en) | 2007-07-27 | 2007-07-27 | Hydraulic moment changer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU200720124832XU CN201071916Y (en) | 2007-07-27 | 2007-07-27 | Hydraulic moment changer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201071916Y true CN201071916Y (en) | 2008-06-11 |
Family
ID=39550474
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU200720124832XU Expired - Lifetime CN201071916Y (en) | 2007-07-27 | 2007-07-27 | Hydraulic moment changer |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201071916Y (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103671801A (en) * | 2012-09-12 | 2014-03-26 | 通用汽车环球科技运作有限责任公司 | Fluid coupling |
| CN108980296A (en) * | 2018-09-14 | 2018-12-11 | 天津工程机械研究院有限公司 | A kind of face of fluid torque converter structure |
-
2007
- 2007-07-27 CN CNU200720124832XU patent/CN201071916Y/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103671801A (en) * | 2012-09-12 | 2014-03-26 | 通用汽车环球科技运作有限责任公司 | Fluid coupling |
| CN108980296A (en) * | 2018-09-14 | 2018-12-11 | 天津工程机械研究院有限公司 | A kind of face of fluid torque converter structure |
| CN108980296B (en) * | 2018-09-14 | 2024-03-19 | 天津工程机械研究院有限公司 | Pump wheel structure of hydraulic torque converter |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term |
Granted publication date: 20080611 |
|
| CX01 | Expiry of patent term |