CN201729582U - Closed hydraulic oil way of hoister - Google Patents
Closed hydraulic oil way of hoister Download PDFInfo
- Publication number
- CN201729582U CN201729582U CN2010201630195U CN201020163019U CN201729582U CN 201729582 U CN201729582 U CN 201729582U CN 2010201630195 U CN2010201630195 U CN 2010201630195U CN 201020163019 U CN201020163019 U CN 201020163019U CN 201729582 U CN201729582 U CN 201729582U
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- Prior art keywords
- hydraulic pump
- hydraulic
- pump
- braking liquid
- liquid press
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Abstract
The utility model relates to a closed hydraulic oil way of a hoister, which is characterized in that a brake hydraulic pump is additionally arranged on a mechanical connecting link of a diesel engine and a bidirectional hydraulic pump, a spindle of the brake hydraulic pump is connected with a spindle of the bidirectional hydraulic pump and a spindle of the diesel engine by the aid of mechanism drive, an oil inlet of the brake hydraulic pump is connected with an oil outlet of a hydraulic oil tank, a hydraulic oil is sucked from the hydraulic oil tank, and extracted oil of the brake hydraulic pump is connected to the hydraulic oil tank by the aid of an overflow valve. By measuring incremental speed of the diesel engine towed by the driving torque of the bidirectional hydraulic pump, the throttling functions of the brake hydraulic pump and the overflow valve are controlled, so that driven torque of the brake hydraulic pump balances the driving torque of the bidirectional hydraulic pump, and the closed hydraulic oil way has the function of stabilizing runaway overspeeding rotation of the hoister during descending and has a certain energy saving effect.
Description
Technical field
The utility model relates to the hydraulic circuit that all-hydraulic crane hook promotes and arm luffing winch rotating speed is controlled that adopts enclosed transmission hydraulic circuit.
Background technology
All-hydraulic hoisting winding is the acting of weight potential energy when down maneuver, can drive HM Hydraulic Motor and rotate.Adopt the hoisting winding hydraulic circuit of open type transmission, the heat energy that and speed that control weight transfer stable with balance cock, the throttling action of the potential energy that weight is transferred by balance cock become hydraulic oil passes in the whole hydraulic efficiency pressure system and dissipates.In closed oil circuit, bidirectional hydraulic pump and HM Hydraulic Motor are directly docked, constitute the mini system of an inner loop, the moment of torsion that the potential energy that weight is transferred produces winch can be by HM Hydraulic Motor to bidirectional hydraulic infusion oil, the bidirectional hydraulic pump driving diesel engine of changing from passive to active makes diesel engine that the trend of overspeed rotation out of control be arranged.In order to control descending speed reposefully, can adopt the method same with open-circuit system, add the throttling control descending speed of balance cock or other form in hot side, but do like this producing a large amount of heat energy, make the interior oil temperature of short circle too high.Also can use the speed of the reactive torque characteristic limitations decline of diesel engine, will make diesel engine overspeed rotation out of control in case surpass reactive torque, reduce the driving torque that the bidirectional hydraulic capacity of pump promptly reduces Hydraulic Pump if adopt, may influence the descending speed of winch.
Summary of the invention
Technical problem to be solved in the utility model is: a kind of closed hydraulic circuit of hoisting winding engine is provided, and the utility model can be controlled the descending speed of hoisting winding effectively, prevents the diesel engine overspeed rotation.
The technical scheme that the utility model adopted is: closed hydraulic circuit of hoisting winding engine comprises HM Hydraulic Motor and bidirectional hydraulic pump, and HM Hydraulic Motor and bidirectional hydraulic pump are formed the loop, and this closed hydraulic circuit also comprises the braking liquid press pump; Be connected to each other by mechanical transmission mechanism between the main shaft of bidirectional hydraulic pump, braking liquid press pump and diesel engine, the oil discharge outlet of braking liquid press pump is connected to hydraulic reservoir by a by pass valve, and the oil inlet of braking liquid press pump links to each other with the oil outlet of hydraulic reservoir; Be provided with tachogen on diesel engine, the input terminal of tachogen and control unit is connected, and by pass valve also is electrically connected with control unit, also is connected to rotational speed governor on the control unit.
It between bidirectional hydraulic pump, braking liquid press pump and the diesel engine coaxial connection or interconnected by auxiliary gear box.
When the braking liquid press pump adopted the technical scheme of quantitative hydraulic pump, by pass valve adopted electricity liquid ratio relief valve.
When the braking liquid press pump adopted the technical scheme of automatically controlled rate variable Hydraulic Pump, the control terminal of automatically controlled rate variable Hydraulic Pump was connected with the output port of control unit; By pass valve adopts unloading overflow valve.
The utility model is applicable to the control the when lifting of adopting the all-hydraulic hoisting crane that closed oil circuit drives and luffing winch carry out down maneuver.Preceence of the present utility model is and can controls the descending speed that closed oil circuit drives winch by actv., the heat that weight and arm decline potential energy produce can flow in the whole hydraulic efficiency pressure system and distribute, can be at inner overheated phenomenon, the energy that diesel engine consumption is minimum of producing of closed system; When carrying out weight, hoisting crane transfers and other action compound tense, to increase swinging radius horizontal sliding composite move is example: the energy that the luffing winch is transferred down maneuver can be used for the vertical motion of suspension hook automatically, and not enough difference is just by the equilibrium of torques of diesel engine energy output or braking liquid press pump; Winch can be saved the energy at the energy that hoists and also can the additive decrementation diesel engine during zero load descend.
Description of drawings
Fig. 1 is the structural representation of the utility model embodiment 1.
Fig. 2 is the structural representation of the utility model embodiment 2.
Among the figure: 1: diesel engine; 2: auxiliary gear box; 3: the bidirectional hydraulic pump; 4: HM Hydraulic Motor; 5: the braking liquid press pump; 6: by pass valve; 7: rotational speed governor; 8: control unit; 9: hydraulic reservoir; 10: tachogen; 11: automatically controlled rate variable Hydraulic Pump; 12: unloading overflow valve.
The specific embodiment
Further specify the utility model below in conjunction with accompanying drawing.
As shown in Figure 1, closed hydraulic circuit of hoisting winding engine comprises HM Hydraulic Motor 4 and bidirectional hydraulic pump 3, and the two forms the loop.Bidirectional hydraulic pump 3 drives winch HM Hydraulic Motor 4.This closed hydraulic circuit also comprises the braking liquid press pump.Be connected to each other by mechanical transmission mechanism between the main shaft of bidirectional hydraulic pump 3, braking liquid press pump 5 and diesel engine 1, the oil discharge outlet of braking liquid press pump 5 is connected to hydraulic reservoir 9 by a by pass valve 6, the oil inlet of braking liquid press pump 5 links to each other with the oil outlet of hydraulic reservoir 9, and braking liquid press pump 5 is drawn hydraulic oil from hydraulic reservoir 9.Be provided with tachogen 10 on diesel engine 1, tachogen 10 is connected with the input terminal of control unit 8, and by pass valve 6 also is electrically connected with control unit 8, also is connected to rotational speed governor 7 on the control unit 8.
Can coaxially connect between bidirectional hydraulic pump 3, braking liquid press pump 5 and the diesel engine 1, also can be connected to each other by auxiliary gear box 2.
The utility model has following two kinds of technical schemes for the oil circuit of braking liquid press pump 5 and by pass valve 6:
Embodiment 1:
As shown in Figure 1, braking liquid press pump 5 is a quantitative hydraulic pump, and by pass valve 6 adopts electricity liquid ratio relief valve, and oil pressure relief is directly proportional with the electric current of input electricity liquid ratio relief valve pressure control terminal.The oil discharge outlet of braking liquid press pump 5 is connected to hydraulic reservoir 9 by by pass valve 6, and the pressure control terminal of by pass valve 6 is connected with control unit 8 lead-out terminals.The hypervelocity increment of the rotating speed that control unit 8 is set according to the actual speed of diesel engine 1 and rotational speed governor 7 is to by pass valve 6 output commands.The actual speed that detects diesel engine 1 when control unit 8 has surpassed the rotating speed of having set, when the hypervelocity increment having occurred, and 8 pairs of electricity liquid ratio relief valve outgoing currents of control unit.The hypervelocity increment is big more, and big more to the electric current of by pass valve 6, the oil pressure relief of by pass valve 6 is high more, and it is just big more from dynamic torque that braking liquid press pump 5 produces, and vice versa.Braking liquid press pump 5 from dynamic torque effectively balance the driving torque of bidirectional hydraulic pump 3.When hoist action or light load descended, when perhaps carrying out composite move, as long as the increment that exceeds the speed limit does not appear in diesel engine 1, by pass valve 6 did not have the conducting of pressure, and braking liquid press pump 5 is in the empty stream mode of decompression, consumes very little energy.
Embodiment 2:
As shown in Figure 2, braking liquid press pump 5 adopts automatically controlled rate variable Hydraulic Pump 11, and the defeated port of the control terminal of automatically controlled rate variable Hydraulic Pump 11 and control unit 8 is electrically connected.By pass valve 6 adopts the common by pass valve 12 that has unloading function.The discharge capacity of automatically controlled rate variable Hydraulic Pump 11 is directly proportional with the electric current of its control terminal of input; The control terminal of automatically controlled rate variable Hydraulic Pump 11 is connected with the output port of control unit 8.When the actual speed that detects diesel engine 1 when control unit 8 had surpassed the rotating speed of having set and the hypervelocity increment occurred, 8 pairs of unloading overflow valve 12 output commands of control unit made unloading overflow valve 12 reach settling pressure; Simultaneously the control terminal of automatically controlled rate variable Hydraulic Pump 11 is exported control current, the hypervelocity increment is big more, control current is big more, the discharge capacity of automatically controlled rate variable Hydraulic Pump 11 is big more, the brake torque that produces is just big more, the moment of torsion of automatically controlled rate variable Hydraulic Pump 11 effectively balance the driving torque of bidirectional hydraulic pump 3.Vice versa.When increment did not appear exceeding the speed limit in diesel engine, unloading overflow valve 12 did not have the conducting of pressure, and automatically controlled rate variable Hydraulic Pump 11 is to minimum injection rate, consumed energy hardly.
Claims (4)
1. closed hydraulic circuit of hoisting winding engine, comprise HM Hydraulic Motor (4) and bidirectional hydraulic pump (3), the two forms the loop, it is characterized in that: this closed hydraulic circuit also comprises braking liquid press pump (5), be connected to each other by mechanical transmission mechanism between the main shaft of bidirectional hydraulic pump (3), braking liquid press pump (5) and diesel engine (1), the oil discharge outlet of braking liquid press pump (5) is connected to hydraulic reservoir (9) by a by pass valve (6), and the oil inlet of braking liquid press pump (5) links to each other with the oil outlet of hydraulic reservoir (9); Be provided with tachogen (10) on diesel engine (1), tachogen (10) is connected with the input terminal of control unit (8), and by pass valve (6) also is electrically connected with control unit (8), also is connected to rotational speed governor (7) on the control unit (8).
2. hydraulic circuit according to claim 1 is characterized in that: be coaxial connection or interconnected by auxiliary gear box (2) between bidirectional hydraulic pump (3), braking liquid press pump (5) and the diesel engine (1).
3. hydraulic circuit according to claim 1 and 2 is characterized in that: braking liquid press pump (5) adopts quantitative hydraulic pump, and by pass valve (6) adopts electricity liquid ratio relief valve, and the output port of the control terminal of by pass valve (6) and control unit (8) is electrically connected.
4. hydraulic circuit according to claim 1 and 2 is characterized in that: braking liquid press pump (5) adopts automatically controlled rate variable Hydraulic Pump (11), and the output port of the control terminal of automatically controlled rate variable Hydraulic Pump and control unit (8) is electrically connected; By pass valve (6) adopts unloading overflow valve (12).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201630195U CN201729582U (en) | 2010-04-13 | 2010-04-13 | Closed hydraulic oil way of hoister |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201630195U CN201729582U (en) | 2010-04-13 | 2010-04-13 | Closed hydraulic oil way of hoister |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201729582U true CN201729582U (en) | 2011-02-02 |
Family
ID=43520738
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010201630195U Expired - Lifetime CN201729582U (en) | 2010-04-13 | 2010-04-13 | Closed hydraulic oil way of hoister |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201729582U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101850937A (en) * | 2010-04-13 | 2010-10-06 | 中国第一冶金建设有限责任公司 | Closed hydraulic circuit of hoisting winding engine |
| CN102381652A (en) * | 2011-10-28 | 2012-03-21 | 中联重科股份有限公司 | Control device for winching mechanism and winching mechanism test platform |
| WO2013086882A1 (en) * | 2011-12-12 | 2013-06-20 | 中联重科股份有限公司 | Crane, and closed-type hoist negative power control system for use with crane |
| CN110775841A (en) * | 2019-11-01 | 2020-02-11 | 徐州重型机械有限公司 | Telescopic control system and engineering machinery |
-
2010
- 2010-04-13 CN CN2010201630195U patent/CN201729582U/en not_active Expired - Lifetime
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101850937A (en) * | 2010-04-13 | 2010-10-06 | 中国第一冶金建设有限责任公司 | Closed hydraulic circuit of hoisting winding engine |
| CN101850937B (en) * | 2010-04-13 | 2012-06-13 | 中国一冶集团有限公司 | Closed hydraulic circuit of hoisting winding engine |
| CN102381652A (en) * | 2011-10-28 | 2012-03-21 | 中联重科股份有限公司 | Control device for winching mechanism and winching mechanism test platform |
| CN102381652B (en) * | 2011-10-28 | 2013-03-20 | 中联重科股份有限公司 | Control device and method for winching mechanism and winching mechanism test platform |
| WO2013086882A1 (en) * | 2011-12-12 | 2013-06-20 | 中联重科股份有限公司 | Crane, and closed-type hoist negative power control system for use with crane |
| CN110775841A (en) * | 2019-11-01 | 2020-02-11 | 徐州重型机械有限公司 | Telescopic control system and engineering machinery |
| CN110775841B (en) * | 2019-11-01 | 2022-02-25 | 徐州重型机械有限公司 | Telescopic control system and engineering machinery |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20110202 Effective date of abandoning: 20120613 |