CN2814025Y - Disengaging hydraulic couplings - Google Patents
Disengaging hydraulic couplings Download PDFInfo
- Publication number
- CN2814025Y CN2814025Y CNU2004201507852U CN200420150785U CN2814025Y CN 2814025 Y CN2814025 Y CN 2814025Y CN U2004201507852 U CNU2004201507852 U CN U2004201507852U CN 200420150785 U CN200420150785 U CN 200420150785U CN 2814025 Y CN2814025 Y CN 2814025Y
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- CN
- China
- Prior art keywords
- bearing
- valve
- oil
- output
- way
- Prior art date
- 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.)
- Expired - Fee Related
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Abstract
The utility model relates to a disengaging hydraulic coupling, which is composed of a box body, a bearing supporting mechanism, an input shaft, a pump wheel, a back shell, a turbine, an output shaft, an oil path system and a control system. The utility model is characterized in that the input part of the bearing supporting mechanism is supported by adopting the supporting mode of the output part of an embedded bearing structure, and the output parts of the bearing supporting mechanism are respectively supported by adopting the supporting mode of the output part of a supported coupling. The oil path system is one valve controlled oil path system which is composed of an oil tank, a filtering device, an oil charging valve and a pressure and temperature detecting device, wherein the oil charging valve is an electromagnetic proportion regulating valve which is formed by that one two-position 3-way valve, one two-position two-way valve and one electromagnetic proportioning valve are assembled. The utility model has the advantages that the disengaging hydraulic coupling has a small radial dimension and can not easily generate vibration, the valve controlled oil charge is adopted, the disengaging function is realized and the disengaging hydraulic coupling has the function of overload protection.
Description
Technical field
The utility model belongs to the hydraudynamic drive technical field.
Background technique
The fluid coupling of prior art has following deficiency:
1, the fluid coupling of prior art adopts conduit to draw oily mode and discharges liquid in the active chamber, because the restriction that conduit is drawn oily structure can not be emptied completely the liquid of active chamber, does not reach the purpose of throwing off fully.
2, the bearing support structure of the fluid coupling of prior art has two kinds of forms: supporting structure and imbed bearing structure respectively.The coupler of supporting structure makes the coupler axial dimension bigger because of input shaft, output shaft are supported on respectively on the bearing support on the casing respectively; Imbed bearing structure, because the front end of the output shaft of output is imbedded input shaft, the spring bearing of its front end is installed on the input shaft, easily produces vibrations, and bearing is also fragile.
Summary of the invention
In view of above-mentioned deficiency of the prior art, the purpose of this utility model is a kind of clutch type hydraulic coupler of design, and it is little to make it axial dimension, is difficult for producing vibration, and input, output can be thrown off fully.The technical solution of the utility model is: clutch type hydraulic coupler, constitute by casing, bearings mechanism, input shaft, pump impeller, shell on the back, turbine, output shaft, oil-way system, control system, its structure is that the input part of described bearings mechanism adopts the supporting way of imbedding bearing type coupler input part to support, and output adopts respectively that the supporting way of supporting type coupler output supports;
Clutch type hydraulic coupler described in the utility model, its structure is that the end of input shaft of the input part of described bearings mechanism is supported on the input bearing of the input shaft bearing that is installed on the casing, and the other end is supported on by shell on the back on the shell on the back bearing on the output shaft bearing that is installed on the casing; One end of the output shaft of output is supported on the output bearing of output shaft bearing one end that is installed on the casing, and the other end is supported on the output bearing of the output shaft bearing the other end;
Clutch type hydraulic coupler of the present utility model, its structure is that the described output shaft bearing that is installed on the casing is a stepped shaft bearing support, the front end of bearing support is installed with the bearing of output shaft front end, and the bearing support rear end is installed with the bearing of output shaft rear end, and the bearing of shell on the back is installed at the ladder place;
Clutch type hydraulic coupler of the present utility model, its structure are that described oil-way system is a valve control oil-way system that comprises fuel tank, oil feed pump, filter, oil charge valve, pressure and temperature detection device;
Clutch type hydraulic coupler of the present utility model, its structure are that the oil charge valve in the described oil-way system is by a two-position three way magnetic valve, a two-position two-way solenoid valve, the solenoid-operated proportional modulating valve that electromagnetic proportional valve is combined into;
Clutch type hydraulic coupler of the present utility model, its structure are that described control system comprises the automatic control system of the processing rear driving solenoid valve of temperature, the rotating speed of feedback, pressure signal being opened by the PLC programmable controller and by the three-way valve manual control system.
Description of drawings
The utility model has accompanying drawing 3 width of cloth.
Accompanying drawing 1 is the structural representation of the utility model mode of execution
Accompanying drawing 2 is oil-way system figure of the present utility model
Accompanying drawing 3 is control system figure of the present utility model,
In the accompanying drawing: 1, input end cap 2, input shaft 3, input bearing 4, input shaft bearing
5, pump impeller 6, quick fuel outlet valve 7, shell on the back 8, turbine 9, output shaft bearing 10, output shaft 11, output end cap 12, output bearing 13, output bearing 14, casing 15, shell on the back bearing 16, two-position three way magnetic valve 17, two-position two-way solenoid valve 18, electromagnetic proportional valve 19, temperature transducer 20, fuel tank 21, filter cleaner
22, pressure gauge 23, cooling unit 24, display device
25, programmable controller 26, manual three-way valve 27, load 28, coupler 29, motor
Embodiment
With reference to the accompanying drawings 1, shown in the accompanying drawing 2, input shaft 2 one ends are supported on the input bearing 3 of the input shaft bearing 4 that is installed on the casing 14, the other end is supported on the shell on the back bearing 15 at ladder place of the output shaft bearing 9 that is installed on the casing 14.On the excircle of shell on the back, have 2～3 holes, the deep fat in the active chamber (hydraudynamic drive has 1.5%～3% hydraulic losses) is discharged, oil pump is thrown cold oil into the coupler rotor chamber, realizes thermal equilibrium.Pump impeller 5 rigid joint in the front end of input shaft and the casing, the rear end connects with prime mover.One end of output shaft 10 is supported on the output bearing 13 of cascade output shaft bearing 9 front ends that are installed on the casing 14, the other end is supported on the output bearing 12 of stepped shaft bearing 9 rear ends, turbine 8 rigid joint in the front end of output shaft 10 and the casing, the rear end of output shaft connects with working machine.During work, input shaft is by motor drives and drive pump impeller 5 rotations, the pump impeller that has many radial blades quickens and pours the turbine 8 that has many radial blades with pump impeller equally with the centrifugal in the active chamber, drive the rotation of turbine and output shaft, thereby give the load that is attached thereto transmission of power.Liquid in the active chamber is provided by oil-way system, and oil feed pump sucks working oil and behind supercooler 23, enters oil rectifier 21 from 20 li of fuel tanks, and after the filtering, part oil is for bearing lubrication, and another part oil enters two-position three way magnetic valve 16.When electromagnetic valve during in the I position, the oil that enters two-position three way magnetic valve is oil sump tanks 20 all, do not have oil in coupler rotor the chamber in, realize disengaging fully; When electromagnetic valve during in the II position, the oil that enters two position three-way valve is by two-position two-way solenoid valve 17 controls.When two-position two-way solenoid valve was logical, oil entered in the coupler rotor chamber by two-position two-way solenoid valve, and active chamber is oil-filled entirely, realized the function of combination; When two-position two-way solenoid valve closed, oil entered in the coupler rotor chamber by electromagnetic proportional valve 18 parts, and the active chamber part is oil-filled, played the effect of limit square.When the coupler part was oil-filled, its overload torque reduced, and as 30% when oil-filled, under the stuck situation of working machine, motor torque is about 90% of specified carry-over moment.The control of oil-way system can be adopted the interactive automatic control system of PLC Programmable Controller, also can adopt the three-way valve manual control system.The input end of working machine is equipped with tachometer (or moment instrument), when working machine transships, signal is transferred to control system, control system is sent instruction, the oil mass that control enters active chamber by electromagnetic proportional valve realizes that part is oil-filled, and the position of electromagnetic proportional valve is debugged setting in advance, thereby play the effect of limit square, realize the function of overload protection; Perhaps oil-filled by manual three-way valve control.
The utility model has the advantages that axial dimension is little, be difficult for producing vibrations, adopt the valve control oil-filled, realize clutch function, and overload protection function is arranged.
Claims (6)
1. clutch type hydraulic coupler, constitute by casing, bearings mechanism, input shaft, pump impeller, turbine, output shaft, oil-way system, control system, the input part that it is characterized in that described bearings mechanism adopts the supporting way of imbedding bearing type coupler input part to support, and output adopts respectively that the supporting way of supporting type coupler output supports.
2. clutch type hydraulic coupler according to claim 1, an end of input shaft (2) that it is characterized in that the input part of described bearings mechanism is supported on the input bearing (3) of the input shaft bearing (4) that is installed on the casing (14), and the other end is supported on by shell on the back (7) on the shell on the back bearing (15) on the output shaft bearing (9) that is installed on the casing (14); One end of the output shaft of output (10) is supported on the output bearing (12) of output shaft bearing one end that is installed on the casing (14), and the other end is supported on the output bearing (13) of the output shaft bearing the other end.
3. clutch type hydraulic coupler according to claim 1 is characterized in that described being installed in
Output shaft bearing (9) on the casing is a stepped shaft bearing support, and the front end of bearing support is installed with the bearing (13) of output shaft front end, and the bearing support rear end is installed with the bearing (12) of output shaft rear end, and the bearing (15) of shell on the back is installed at the ladder place.
4. clutch type hydraulic coupler according to claim 1 is characterized in that described oil-way system is a valve control oil-way system that comprises fuel tank, oil feed pump, filter, oil charge valve, pressure and temperature detection device.
5. according to claim 1 or 4 described clutch type hydraulic couplers, it is characterized in that the oil charge valve in the described oil-way system is the solenoid-operated proportional modulating valve that is combined into by a two-position three way magnetic valve (16), a two-position two-way solenoid valve (17), an electromagnetic proportional valve (18).
6. according to claim 1 or 4 described clutch type hydraulic couplers, it is characterized in that described control system comprises the automatic control system of the processing rear driving solenoid valve of the temperature of feedback, rotating speed, pressure signal being opened by the PLC programmable controller and by the three-way valve manual control system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2004201507852U CN2814025Y (en) | 2004-11-18 | 2004-11-18 | Disengaging hydraulic couplings |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2004201507852U CN2814025Y (en) | 2004-11-18 | 2004-11-18 | Disengaging hydraulic couplings |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2814025Y true CN2814025Y (en) | 2006-09-06 |
Family
ID=36949113
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2004201507852U Expired - Fee Related CN2814025Y (en) | 2004-11-18 | 2004-11-18 | Disengaging hydraulic couplings |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2814025Y (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100396968C (en) * | 2004-11-18 | 2008-06-25 | 大连交通大学 | Clutch type hydraulic coupler |
| CN101828049B (en) * | 2007-10-30 | 2014-11-05 | 株式会社小松制作所 | Pressure regulation device for fluid type power transmission device |
| CN104179924A (en) * | 2014-08-08 | 2014-12-03 | 洛阳雷斯达传动有限公司 | Hydraulic torque converter with flexible lock-out control function |
| CN109163066A (en) * | 2018-11-01 | 2019-01-08 | 象山杰尔德智能科技有限公司 | A kind of included clutch fluid torque-converter |
| EP3730796A1 (en) * | 2019-04-23 | 2020-10-28 | Sulzer Management AG | Centrifugal pump |
-
2004
- 2004-11-18 CN CNU2004201507852U patent/CN2814025Y/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100396968C (en) * | 2004-11-18 | 2008-06-25 | 大连交通大学 | Clutch type hydraulic coupler |
| CN101828049B (en) * | 2007-10-30 | 2014-11-05 | 株式会社小松制作所 | Pressure regulation device for fluid type power transmission device |
| CN104179924A (en) * | 2014-08-08 | 2014-12-03 | 洛阳雷斯达传动有限公司 | Hydraulic torque converter with flexible lock-out control function |
| CN109163066A (en) * | 2018-11-01 | 2019-01-08 | 象山杰尔德智能科技有限公司 | A kind of included clutch fluid torque-converter |
| CN109163066B (en) * | 2018-11-01 | 2020-07-31 | 宁波欧特传动技术有限公司 | Hydraulic torque converter with clutch |
| EP3730796A1 (en) * | 2019-04-23 | 2020-10-28 | Sulzer Management AG | Centrifugal pump |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |