CN201747887U - Valve controlled speed-regulating double-cavity hydraulic coupler - Google Patents
Valve controlled speed-regulating double-cavity hydraulic coupler Download PDFInfo
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- CN201747887U CN201747887U CN2010202513451U CN201020251345U CN201747887U CN 201747887 U CN201747887 U CN 201747887U CN 2010202513451 U CN2010202513451 U CN 2010202513451U CN 201020251345 U CN201020251345 U CN 201020251345U CN 201747887 U CN201747887 U CN 201747887U
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Abstract
A valve controlled speed-regulating double-cavity hydraulic coupler comprises a box component, a rotation mechanism component and an oil recycle system component, wherein the rotation mechanism includes an input component comprising a double-impeller, and an output component comprising a double-turbo; an oil system includes an oil pump and an oil cooler, the oil flowing out from a conduit of the coupler is cooled and further connected to an oil inlet of the coupler through an electromagnetic direction valve by an oil feeding pump, the oil quantity in an oil pipe and a rotator is controlled by adding oil into the coupler or discharging the oil in an oil cylinder, and the flow rate is controlled by a flow control valve, thereby regulating the output speed. The valve controlled speed-regulating double-cavity hydraulic coupler has the advantages of high transmission power, easy-to-control property, convenient maintenance, good balance, reduced axial size, compact structure and long service life, and is suitable for hydraulic transmission occasions with demands of high power, high revolution and frequent speed change.
Description
Technical field
The utility model relates to a kind of two-chamber hydraulic couplers of two-chamber hydraulic couplers, particularly a kind of regulable speed type.
Technical background
Patent No. ZL200920059804.3 name is called the Chinese patent of " dual-chamber type fluid coupling " (notification number CN201448414 U, day for announcing 2010-05-05), discloses the applicant's a utility model patent.The coupler of this patent includes input assembly and output precision, and wherein input assembly comprises shaft coupling, and pump impeller A and pump impeller B connect cylindrical shell by one two pump impellers are coupled together; Output precision comprises turbine A and turbine B, forms a working room by turbine A and pump impeller A, forms a working room again by turbine B and pump impeller B, thereby forms two working rooms, and the pump housing is provided with oil filler plug, and temperature control apparatus also is housed.This patent is owing to have two active chambers, and the power that is transmitted is two times of single chamber type, can reach high rotating speed, and is high-power, and stationary performance is good.But it also is not a regulable speed type, and the control range of rotating speed is limited, is difficult to satisfy should transmitted power big, and speed governing is simple and easy again, the hydraudynamic drive requirement that regulation range is wide.
The model utility content
The purpose of this utility model is to avoid above-mentioned the deficiencies in the prior art part, and provides a kind of transmitted power big, and axial dimension is short, and speed governing is convenient, stepless, linear, and is simple in structure, energy-conservation, reliable, the valve controlled velocity modulation type two-chamber hydraulic couplers of long service life.
The purpose of this utility model can reach by following measure:
A kind of valve controlled velocity modulation type two-chamber hydraulic couplers is a kind of hydraudynamic drive machinery that is connected between motor and the working machine, includes box assembly, rotating machinery assembly and oil circulating system assembly; Described box assembly comprises bearing support, housing seat and case lid, described rotating machinery assembly, comprise input assembly that contains the double pump wheel and the output precision that contains two turbines, these assemblies are entangled and fix by housing seat, be equiped with the impeller of oneself in the wheel chamber of these pump impellers and turbine separately, described oil circulating system assembly comprises oil feed pump, Oil pump electrical machinery, oil pipe and supporting pipe fitting; Above-mentioned this input assembly comprises shell, input shaft, oil-feed dish, pump impeller A, connecting cylinder and pump impeller B, by this connecting cylinder pump impeller A and pump impeller B symmetry is connected, and the side of this pump impeller A and input shaft, oil-feed dish are installed in the rotating shaft of stretching out from motor; Above-mentioned this output precision comprises output shaft, turbine A, turbine B and turbine backing plate, then be installed in the rotating shaft of stretching out from working machine, it is characterized in that described oil circulating system assembly also includes, the oil inlet pipe that is communicated with the oil-feed dish, the conduit of the intracavity inter-connection by its catheter lumen and connecting cylinder, and the valve group that comprises solenoid directional control valve and flow control valve, and oil cooler, the oil pipe that picks out from fuel tank and oil feed pump, through solenoid directional control valve, be connected to oil inlet pipe; Through the oil-feed dish, lead to the active chamber of pump impeller A; Flow control valve is installed in connecting cylinder, and oil pipe connects to oil cooler from this conduit, is connected with the oil pipe of oil feed pump again.
Above-mentioned pump impeller A and pump impeller B, the shape in both wheel chambeies is identical with size, vertically is arranged in the both sides that connect cylindrical shell, is erected at respectively on input shaft and the output shaft; Described turbine A and turbine B, the shape in both wheel chambeies is identical with size, and vertically symmetry links together by the turbine backing plate, and between pump impeller A and pump impeller B, like this, form an active chamber, also form an active chamber by turbine B and pump impeller B by pump impeller A and turbine A.
Between above-mentioned pump impeller A and the end face of turbine A, have axial clearance, the gap is at 3mm～6mm; Between the end face of described turbine B and pump impeller B, have axial clearance, the gap is at 3mm～6mm; And be provided with oil-through hole between turbine A and the turbine B.
Above-mentioned at input shaft one end, be provided with input labyrinth bush and labyrinth thereof lid; At output shaft one end, be provided with output labyrinth bush and labyrinth thereof lid.
On the oil pipe of above-mentioned oil feed pump, be provided with a relief valve, given oil pressure relief is 0.63Mpa.
The utility model hydraulic couplers has following advantage:
1. transmitted power is big.The transmission capacity of two-chamber hydraulic couplers is 2 times of single chamber type; Have obvious energy-saving effect, power saving rate is 20%～40%, but motor starting under no load wherein can absorb and isolate torsional oscillation, reduces and impacts, and prevents dynamic overload.
2. be easy to realize automatic control, easy to operate, maintaining is simple.That this Coupler is controlled with solenoid directional control valve is oil-filled in the active chamber/or oil extraction, or by flow control valve regulate and control advance/go out the oil mass in the active chamber, only need change the total filling amount in the active chamber, and can realize speed governing, means are simple, convenient, stepless, linear.
3. balance is good.Two pump impellers and two turbines of Coupler I/O all are symmetrical arranged, and balance is installed, and has offset the axial force of rotating machinery assembly.
4. axial dimension reduces.The rotating machinery assembly of this Coupler, no bearing supporting, and support by the axle of motor and working machine, axial dimension has reduced more than 30%, highly reduces more than 20%, has also just reduced the oil-filled amount in the Coupler.By installing at the scene, the installation precision height has reduced the burden of maintaining.
5. compact structure is reliable, and the body deadweight reduces; Conduit is fixed, and its working life is consistent with revolving part, thereby the long service life of Coupler.
The utility model is done the narration of further indefiniteness below in conjunction with drawings and Examples.
Description of drawings
Fig. 1 is the structural representation of the utility model hydraulic couplers;
Fig. 2 is the schematic representation that concerns of the utility model hydraulic couplers body and oil circulating system;
Among each figure, the 1st, bearing support, the 2nd, oil inlet pipe, the 3rd, housing seat, the 4th, input shaft, the 5th, the labyrinth lid of input end, the 6th, input labyrinth bush, the 7th, oil inlet pipe, the 8th, pump impeller A, the 9th, turbine backing plate, the 10th, conduit, the 101st, catheter lumen, the 11st, shell, the 12nd, case lid, the 13rd, turbine A, the 14th, turbine B, the 15th, connecting cylinder, the 161st, filler opening flange, the 162nd, oil drain out flange, the 17th, pump impeller B, the 18th, output shaft, the 19th, output labyrinth bush, the 20th, the labyrinth lid of output terminal, the 211st, solenoid directional control valve, the 212nd, flow control valve, the 213rd, drip valve, the 22nd, oil feed pump, the 23rd, Oil pump electrical machinery, 25 expression oil systems, the 26th, motor, the body of 27 expression hydraulic couplerss, the 28th, working machine, the 29th, oil cooler.
Embodiment
As shown in drawings, make each mechanical part of the utility model hydraulic couplers, prepare electric accordingly, instrument.Because installation precision requires high, this Coupler needs on-the-spot the installation.At first, have good positioning motor 26 and working machine 28, and both shaft centre lines are on the same horizontal axis, and making it fixing, the body of Coupler is in them between the two.The utility model hydraulic couplers comprises box assembly, rotating machinery assembly and oil circulating system assembly, preceding two big assemblies are installed between motor and the working machine, and the rotating machinery assembly comprises input assembly and output precision, are installed in respectively in motor 26 and the working machine 28 extended rotating shafts.Described output precision comprises output shaft 18, turbine A 13, turbine B 14 and turbine backing plate 9, on one side be to have comprised input shaft 4, input labyrinth bush 6, oil-feed dish 7 with what connected, the input assembly of pump impeller A8 and shell 11, be hung on the mounting base of motor 26, on the axle that motor stretches out, use bolt; Another side is that pump impeller B 17 is packed in the output precision with connecting cylinder 15, loads onto output labyrinth bush 19, reinstalls on the axle that working machine 28 stretches out, and uses bolt; Like this, pump impeller A and pump impeller B by connecting cylinder 15 symmetry connections, be positioned at the both sides of input shaft and output shaft, turbine A and turbine B are installed between the two, turbine A and turbine B link together by turbine backing plate 9, are provided with oil-through hole between the two, form an active chamber by pump impeller A and turbine A, form another active chamber by turbine B and pump impeller B, the active chamber of two symmetries by input shaft 4 and output shaft 18, be positioned in the rotating shaft of motor 26 and working machine 28; Adjust between pump impeller A and the turbine end clearance between turbine B and the pump impeller B; Between 3mm～6mm, the gap departure is less than 0.10/1000; And adjust the relative jerk value of external diameter, and its deviation should be come the parallelism and the coaxality of calibration motor and working machine central axis with this less than 0.12/1000, thus the fixed electrical machinery base.
With connecting cylinder 15, pump impeller A and shell 11 connect, and carry out the installation of box assembly again; Housing seat 3 is inserted on the swivel assembly that the school has installed, load onto bearing support 1, and input labyrinth bush 6, output labyrinth bush 19, proofread and correct housing seat 3, make its radial clearance identical, install oil inlet pipe 2 and conduit 10 again, through filler opening flange 161 and oil drain out flange 162, be connected with oil system 25 respectively with oil cooler 29; The case lid 12 that closes tights a bolt; Install input labyrinth bush 5 then, and output labyrinth bush 20.
At last.The oil circulating system assembly is installed.Wherein oil feed pump 22, oil cooler 29 is installed in the base plane that is lower than Coupler, (failing) oil pipe (line) of being correlated with in the connection, load onto the upper and lower water pipe of oil cooler, the oil pipe output terminal of oil cooler 29, receive the filler opening flange 161 of Coupler, and the oil drain out flange 162 of cooler oil pipe input end and Coupler joins, and links conduit 10 again.
The utility model hydraulic couplers is by the oily circulating load of regulation and control oil system, and the storage of the interior working oil of Coupler, regulates the rotating speed and the power of working machine.Therefore, 15 li flow control valve 212 is installed, solenoid directional control valve 211 and relief valve 213 are installed on (failing) oil pipe (road) at connecting cylinder.And the dexterity of action and the accuracy of inspection solenoid directional control valve.
When using the utility model hydraulic couplers, at first, start Oil pump electrical machinery 23 and oil feed pump 22, connect solenoid directional control valve 211,, treat that the rotating speed of Coupler output terminal increases toward (failing) oil pipe (road) fuel feeding, refuel by spells, until reaching the highest test-run a machine rotating speed that working machine 28 is allowed; Connect solenoid directional control valve 211, the working oil that makes (failing) oil pipe (road) is toward fuel tank (being positioned at outside the figure not expression in the accompanying drawing) lining oil extraction, and the rotating speed of output terminal decreases, and oil extraction by spells, until the minimum speed that working machine allowed.By connecting solenoid directional control valve, toward the oiling of (fail) oil pipe (road) lining, perhaps oil extraction in the fuel tank is to reach the purpose of adjusting active chamber internal memory oil mass during debugging.
The cyclic process of working oil is that oil feed pump 22 goes out the oil pump in the fuel tank after motor 26 starts, through flow control valve 212, regulate oil drain quantity, flow to oil circulating system, after oil cooler 29 coolings, through filler opening flange 161, arrive the oil inlet pipe 2 of Coupler, through oil-feed dish 7, enter in the pump impeller A, working oil obtains quickening in pump impeller, flows to the outer rim of turbine A by the outer rim of pump impeller A, promotes turbine A rotation; Fluid flows to inner edge from turbine A outer rim, and the liquid of fluid can be converted into mechanical energy, through output shaft output, drives working machine; Wherein a part of fluid, by the oil-through hole of turbine A, flow to turbine B, flow to pump impeller B through turbine B, pump impeller B similarly quickens fluid, makes it to obtain the liquid energy; Swiftly flowing working oil flows to the outer rim of turbine B by pump impeller B outer rim, promotes turbine B rotation; When fluid flows to inner edge by turbine B outer rim, its liquid can be converted into mechanical energy, through output shaft output, thereby realizes the transmission of power.After the working solution of turbine A, turbine B slows down, flow back to pump impeller A again, pump impeller B quickens, the liquid energy of reentrying, so circulation constantly.Central a part of working solution, by the gap between pump impeller A and the turbine A, and the flow control valve 212 in connecting cylinder 15 inner chambers is flowed out in the gap between pump impeller B and the turbine B, flow to catheter lumen 101, flow out from conduit 10, through oil drain out flange 162, (failing) oil pipe (road) flows to 29 li of oil coolers again, cool off, flow back into Coupler afterwards again, through filler opening flange 161, to oil inlet pipe 2.This cyclic process, the temperature that makes working oil enter Coupler is lower than 75 ℃, and should be lower than 90 ℃ from the oily temperature that Coupler comes out.The cooling water pressure of cooler should be greater than 0.2Mpa.
By in oil system, refueling, the work oil mass of swivel assembly is increased, carry-over moment just increases, and output speed improves; Otherwise when the past fuel tank oil extraction of oil system, the work oil mass reduces, and carry-over moment just reduces, and output speed decreases.Like this,, reach the control output speed by adjusting to the oil mass in oil system and the swivel assembly, its control accuracy height, the linear relationship of controlled quentity controlled variable and rotating speed is good.Working pressure in the oil system requires oil pressure greater than 0.05Mpa, and relief valve 213 is installed on the oil feed pump, and given its oil pressure relief is 0.63Mpa.The utility model hydraulic couplers is applicable to the hydraudynamic drive of high rotating speed, high-power, speed governing frequently.
Claims (8)
1. a valve controlled velocity modulation type two-chamber hydraulic couplers is a kind of hydraudynamic drive machinery that is connected between motor (26) and the working machine (28), includes box assembly, rotating machinery assembly and oil circulating system assembly (25); Described box assembly comprises bearing support (1), housing seat (3) and case lid (12), described rotating machinery assembly, comprise input assembly that contains the double pump wheel and the output precision that contains two turbines, these assemblies are entangled and fix by housing seat (3), be equiped with the impeller of oneself in the wheel chamber of these pump impellers and turbine separately, described oil circulating system assembly (25) comprises oil feed pump (22), Oil pump electrical machinery, oil pipe and supporting pipe fitting; Above-mentioned this input assembly comprises shell (11), input shaft (4), oil-feed dish (7), pump impeller A (8), connecting cylinder (15) and pump impeller B (17), by this connecting cylinder (15) pump impeller A (8) is connected with pump impeller B (17) symmetry, the side of this pump impeller A (8) and input shaft (4), oil-feed dish (7) are installed in the rotating shaft of stretching out from motor (26); Above-mentioned this output precision comprises output shaft (18), turbine A (13), turbine B (14), with turbine backing plate (9), then be installed in the rotating shaft of stretching out from working machine (18), it is characterized in that, described oil circulating system assembly (25) also includes, the oil inlet pipe (4) that is communicated with oil-feed dish (7), by the conduit (10) of its catheter lumen (101) with the intracavity inter-connection of connecting cylinder (15), and comprise solenoid directional control valve (211), and the valve group of flow control valve (212), and oil cooler (29), the oil pipe that picks out from fuel tank and oil feed pump (22), through solenoid directional control valve (211), be connected to oil inlet pipe (4); Through oil-feed dish (7), the active chamber that leads to pump impeller A (8); In connecting cylinder (15) lining flow control valve (212) is installed, oil pipe connects to oil cooler (29) from this conduit (10), and the oil pipe with oil feed pump (22) is connected again.
2. valve controlled velocity modulation type two-chamber hydraulic couplers according to claim 1, it is characterized in that, described pump impeller A (8) and pump impeller B (13), the shape in both wheel chambeies is identical with size, vertically be arranged in the both sides that connect cylindrical shell (15), be erected at respectively on input shaft (4) and the output shaft (18); Described turbine A (13) and turbine B (14), the shape in both wheel chambeies is identical with size, link together by turbine backing plate (9) is vertically symmetrical, and be positioned between pump impeller A (8) and the pump impeller B (17), like this, form an active chamber by pump impeller A (8) and turbine A (13), also form an active chamber by turbine B (14) and pump impeller B (17).
3. valve controlled velocity modulation type two-chamber hydraulic couplers according to claim 1 and 2 is characterized in that, between the end face of described pump impeller A (8) and turbine A (13), has axial clearance, and the gap is at 3mm～6mm; Between the end face of described turbine B (14) and pump impeller B (17), have axial clearance, the gap is at 3mm～6mm; And be provided with oil-through hole between turbine A (13) and the turbine B (14).
4. valve controlled velocity modulation type two-chamber hydraulic couplers according to claim 1 and 2 is characterized in that, at input shaft (4) one ends, is provided with input labyrinth bush (6) and labyrinth thereof lid (5); At output shaft (18) one ends, be provided with output labyrinth bush (19) and labyrinth thereof lid (20).
5. valve controlled velocity modulation type two-chamber hydraulic couplers according to claim 3 is characterized in that, at input shaft (4) one ends, is provided with input labyrinth bush (6) and labyrinth thereof lid (5); At output shaft (18) one ends, be provided with output labyrinth bush (19) and labyrinth thereof lid (20).
6. valve controlled velocity modulation type two-chamber hydraulic couplers according to claim 1 and 2 is characterized in that, on the oil pipe of described oil feed pump (22), is provided with a relief valve (213), and given oil pressure relief is 0.63Mpa.
7. valve controlled velocity modulation type two-chamber hydraulic couplers according to claim 3 is characterized in that, on the oil pipe of described oil feed pump (22), is provided with a relief valve (213), and given oil pressure relief is 0.63Mpa.
8. valve controlled velocity modulation type two-chamber hydraulic couplers according to claim 4 is characterized in that, on the oil pipe of described oil feed pump (22), is provided with a relief valve (213), and given oil pressure relief is 0.63Mpa.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010202513451U CN201747887U (en) | 2010-07-08 | 2010-07-08 | Valve controlled speed-regulating double-cavity hydraulic coupler |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010202513451U CN201747887U (en) | 2010-07-08 | 2010-07-08 | Valve controlled speed-regulating double-cavity hydraulic coupler |
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| Publication Number | Publication Date |
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| CN201747887U true CN201747887U (en) | 2011-02-16 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010202513451U Expired - Fee Related CN201747887U (en) | 2010-07-08 | 2010-07-08 | Valve controlled speed-regulating double-cavity hydraulic coupler |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103591246A (en) * | 2013-10-22 | 2014-02-19 | 杭州前进齿轮箱集团股份有限公司 | Double-chamber torque-limiting type hydraulic coupling |
| CN103671803A (en) * | 2013-12-16 | 2014-03-26 | 天津钢铁集团有限公司 | Torque-limiting type hydraulic coupler |
| CN104006137A (en) * | 2014-05-21 | 2014-08-27 | 中煤张家口煤矿机械有限责任公司 | Open type valve-control liquid filling type liquid coupler |
| CN105020358A (en) * | 2015-08-06 | 2015-11-04 | 中交一航局安装工程有限公司 | Torque-limiting hydraulic coupler |
| CN106481775A (en) * | 2015-09-02 | 2017-03-08 | 熵零股份有限公司 | Energy adjustment system |
| CN106481776A (en) * | 2015-08-27 | 2017-03-08 | 熵零股份有限公司 | Hydraulic mechanism and its device |
| CN107091311A (en) * | 2016-02-17 | 2017-08-25 | 熵零技术逻辑工程院集团股份有限公司 | A kind of hydraulic mechanism |
-
2010
- 2010-07-08 CN CN2010202513451U patent/CN201747887U/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103591246A (en) * | 2013-10-22 | 2014-02-19 | 杭州前进齿轮箱集团股份有限公司 | Double-chamber torque-limiting type hydraulic coupling |
| CN103591246B (en) * | 2013-10-22 | 2016-05-18 | 杭州前进齿轮箱集团股份有限公司 | A kind of two-chamber load limiting type of constant filling fluid coupling |
| CN103671803A (en) * | 2013-12-16 | 2014-03-26 | 天津钢铁集团有限公司 | Torque-limiting type hydraulic coupler |
| CN103671803B (en) * | 2013-12-16 | 2016-07-06 | 天津钢铁集团有限公司 | A kind of torque-limiting hydraulic coupler |
| CN104006137A (en) * | 2014-05-21 | 2014-08-27 | 中煤张家口煤矿机械有限责任公司 | Open type valve-control liquid filling type liquid coupler |
| CN105020358A (en) * | 2015-08-06 | 2015-11-04 | 中交一航局安装工程有限公司 | Torque-limiting hydraulic coupler |
| CN106481776A (en) * | 2015-08-27 | 2017-03-08 | 熵零股份有限公司 | Hydraulic mechanism and its device |
| CN106481775A (en) * | 2015-09-02 | 2017-03-08 | 熵零股份有限公司 | Energy adjustment system |
| CN107091311A (en) * | 2016-02-17 | 2017-08-25 | 熵零技术逻辑工程院集团股份有限公司 | A kind of hydraulic mechanism |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20110216 Termination date: 20160708 |