CN105570215A - Constant-tension hydraulic valve group - Google Patents
Constant-tension hydraulic valve group Download PDFInfo
- Publication number
- CN105570215A CN105570215A CN201610153402.4A CN201610153402A CN105570215A CN 105570215 A CN105570215 A CN 105570215A CN 201610153402 A CN201610153402 A CN 201610153402A CN 105570215 A CN105570215 A CN 105570215A
- Authority
- CN
- China
- Prior art keywords
- valve
- identical tension
- relief valve
- tension
- setting value
- 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.)
- Granted
Links
- 230000008676 import Effects 0.000 claims description 13
- 239000003638 chemical reducing agent Substances 0.000 claims description 3
- 230000006837 decompression Effects 0.000 claims description 3
- 239000002828 fuel tank Substances 0.000 claims description 2
- 235000008331 Pinus X rigitaeda Nutrition 0.000 description 2
- 235000011613 Pinus brutia Nutrition 0.000 description 2
- 241000018646 Pinus brutia Species 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 238000010923 batch production Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/02—Driving gear
- B66D1/08—Driving gear incorporating fluid motors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/025—Pressure reducing valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a constant-tension hydraulic valve group. By the adoption of the constant-tension hydraulic valve group, the common winch lowering and hoisting function, the active constant-tension function and the passive constant-tension function can be achieved. According to the technical scheme, the constant-tension hydraulic valve group comprises a first overflow valve, a first ball valve, a second overflow valve, a proportional overflow valve, a uniform-pressure-drop valve, a balance valve and a second ball valve; the uniform-pressure-drop valve is arranged on an oil way of the high-pressure side of the motor externally connected; an outlet is connected with the balance valve; an outlet of the balance valve is formed in the high-pressure side of the motor externally connected, and a control opening is formed in the low-pressure side of the motor externally connected; an inlet of the first overflow valve is formed in the high-pressure side of the motor, a remote control opening is connected to an inlet of the second overflow valve, an outlet of the second overflow valve is connected with a control opening of the uniform-pressure-drop valve and an inlet of the proportional overflow valve in parallel, and an outlet of the proportional overflow valve is directly connected with an outside oil tank.
Description
Technical field
The present invention relates to the technology of Fluid Transmission and Control, particularly relate to a kind of new winch identical tension hydraulic valve bank.
Background technique
In existing identical tension hydraulic system, some pumping source adopts open type pump and only has passive identical tension function, and this identical tension only actually is a kind of pressure protect, does not possess initiatively identical tension function.Separately have and adopt enclosed pump discharge to increase Proportional valve, the delivery pressure of restrictive pump, but this mode to take pump more, each mechanism's needs at least 1 of identical tension that need overlap pump, cause economy not.
Summary of the invention
Below provide the brief overview of one or more aspect to provide the basic comprehension to these aspects.Detailed the combining of this not all aspect contemplated of general introduction is look at, and both not intended to be pointed out out the scope of key or decisive any or all aspect of elements nor delineate of all aspects.Its unique object is the sequence that some concepts that will provide one or more aspect in simplified form think the more detailed description provided after a while.
The object of the invention is to solve the problem, provide a kind of identical tension hydraulic valve bank, common winch draw-in and draw-off function, initiatively identical tension function and passive identical tension function can be realized.
Technological scheme of the present invention is: present invention is disclosed a kind of identical tension hydraulic valve bank, comprise the first relief valve, first ball valve, second relief valve, proportional pressure control valve, Fixed differential reducing valve, equilibrium valve, second ball valve, wherein Fixed differential reducing valve is arranged on the on high-tension side oil circuit of external motor, the outlet connecting balanced valve of Fixed differential reducing valve, the outlet of equilibrium valve is arranged on the high pressure side of external motor, the control mouth of equilibrium valve is arranged on the low voltage side of external motor, the import of the first relief valve is arranged on the high pressure side of external motor, the remote control mouth of the first relief valve is connected on the import of the second relief valve, the outlet of the second relief valve is connected in parallel the control mouth of Fixed differential reducing valve and the import of proportional pressure control valve, the outlet of proportional pressure control valve directly connects outside fuel tank.
According to an embodiment of identical tension hydraulic valve bank of the present invention, the first relief valve is long-range pressure adjustment relief valve, and the second relief valve is common relief valve.
According to an embodiment of identical tension hydraulic valve bank of the present invention, proportional pressure control valve is for arranging identical tension value.
According to an embodiment of identical tension hydraulic valve bank of the present invention, Fixed differential reducing valve is externally controlled type Fixed differential reducing valve.
According to an embodiment of identical tension hydraulic valve bank of the present invention, identical tension hydraulic valve bank is external speed reducer and winch also.
According to an embodiment of identical tension hydraulic valve bank of the present invention, when identical tension hydraulic valve bank is in the general mode not needing identical tension function, the first ball valve and the second ball valve are closed; When identical tension hydraulic valve bank have the initiative or passive identical tension pattern time, the first ball valve and the second ball valve are opened.
According to an embodiment of identical tension hydraulic valve bank of the present invention, when running active identical tension pattern, from the oil sources that the import access of Fixed differential reducing valve continues, and the identical tension value of Set scale relief valve, after wire rope unclamps, the outlet pressure decompression of Fixed differential reducing valve is setting value and the Fixed differential reducing valve spring pressure value sum of proportional pressure control valve, valve group carries out active rope closing until stop rope closing when tension force increases to setting value and the Fixed differential reducing valve spring pressure sum of proportional pressure control valve in wire rope, when tension force in wire rope continue to increase to cause motor high side pressure to be greater than the setting value sum of the setting value of proportional pressure control valve and the second relief valve time, wire rope is by anti-hauling-out, till in wire rope, tension force reaches the setting value of proportional pressure control valve and the setting value sum of the second relief valve.
According to an embodiment of identical tension hydraulic valve bank of the present invention, when running passive identical tension pattern, the identical tension value of Set scale relief valve, when tension force in wire rope increase to cause motor high side pressure to be greater than the setting value sum of the setting value of proportional pressure control valve and the second relief valve time, wire rope by anti-hauling-out, till in wire rope, tension force reaches the setting value of proportional pressure control valve and the setting value sum of the second relief valve.
The present invention contrasts prior art following beneficial effect: the realization of the identical tension function of hydraulic valve bank of the present invention mainly by means of a long-range pressure adjustment relief valve, common relief valve, one for arranging proportional pressure control valve and an externally controlled type Fixed differential reducing valve of identical tension value.Utilize above-mentioned assembly, multiple mechanism can be realized and share an oil sources and realize the different constant tensile control of each mechanism, realize the accurate telecontrol of identical tension, can be made into compact valve group batch production, realize initiatively and passive identical tension function.Also can connect various oil sources, constant voltage, load-sensitive etc., adapt to oil sources comparatively wide, also can connect various selector valve, multi-way valve, proportional reversing valve etc.
Accompanying drawing explanation
Fig. 1 shows the structural drawing of the preferred embodiment of identical tension hydraulic valve bank of the present invention.
Embodiment
After the detailed description of reading embodiment of the present disclosure in conjunction with the following drawings, above-mentioned feature and advantage of the present invention can be understood better.In the accompanying drawings, each assembly is not necessarily drawn in proportion, and the assembly with similar correlation properties or feature may have identical or close reference character.
Fig. 1 shows the structure of the preferred embodiment of identical tension hydraulic valve bank of the present invention.Refer to Fig. 1, externally controlled type Fixed differential reducing valve 5 is arranged on rope closing side oil circuit (high pressure side of motor 8), the outlet of externally controlled type Fixed differential reducing valve 5 connects equilibrium valve 6, and the outlet of equilibrium valve 6 connects the high pressure side of motor 8, and the control mouth of equilibrium valve 6 connects the low voltage side of motor 8.The import of long-range pressure adjustment relief valve 1 is connected on rope closing side (high pressure side of motor 8), the remote control mouth of long-range pressure adjustment relief valve 1 is connected on the import of common relief valve 3, the outlet of common relief valve 3 is connected in parallel the control mouth of externally controlled type Fixed differential reducing valve 5 and the import of proportional pressure control valve 4, the direct connected tank of outlet of proportional pressure control valve 4.
Motor 8, speed reducer 9 and winch 10 is all had outward in identical tension hydraulic valve bank.
In the present embodiment, initiatively identical tension is defined as: when tension force in winch cable initiatively tightens up until reach settings lower than during settings, when tension force in winch cable increases and is greater than settings, wire rope is gone until tension force reaches settings in wire rope by anti-hauling-out.
Passive identical tension is defined as: when tension force in winch cable can not initiatively tighten up lower than during settings, but when tension force in winch cable increases and is greater than settings, wire rope is gone until tension force reaches settings in wire rope by anti-hauling-out.
It is below the working procedure of identical tension hydraulic valve bank of the present invention.
When needs active identical tension function, from the oil sources that the import access of externally controlled type Fixed differential reducing valve 5 continues, and set identical tension value.When after wire rope pine, the outlet pressure decompression of externally controlled type Fixed differential reducing valve 5 carries out active rope closing for " the spring pressure value of the setting value+externally controlled type Fixed differential reducing valve 5 of proportional pressure control valve 4 ", and to wire rope, tension force increases to the identical tension value stopping rope closing of setting.When causing " motor high side pressure > proportional pressure control valve 4 setting value+common relief valve 3 setting value " when tension force in wire rope continues to increase to, wire rope by anti-hauling-out, till the tension force in wire rope reaches the identical tension value of setting.
When only needing passive identical tension function, at this moment the import access oil sources from externally controlled type Fixed differential reducing valve 5 is not needed, only need set identical tension value, when causing " motor high side pressure > proportional pressure control valve 4 setting value+common relief valve 3 setting value " when tension force in wire rope increases to, wire rope by anti-hauling-out, till the tension force in wire rope reaches set identical tension value.When wire rope pine, not initiatively rope closing.
Drive winch to be described for the external motor of identical tension valve group, when not needing identical tension function, when being namely operated in general mode, ball valve 2 and 7 is closed; When being operated in active or passive identical tension pattern, need ball valve 2 and 7 to open, now externally controlled type Fixed differential reducing valve 5 is when reduction valve use.
Select spring force to be 10bar with externally controlled type Fixed differential reducing valve 5, it is example that common relief valve 3 is set to 15bar, is described identical tension function.Proportional pressure control valve 4 is for arranging identical tension value in wire rope, and when supposing proportional pressure control valve 4 pressure setting to 60bar, now the oil pressure relief of long-range pressure adjustment relief valve 1 is (60+15) bar, is dragged when the pressure that namely in rope, tension force is corresponding reaches this value by counter.The pressure relief value of externally controlled type Fixed differential reducing valve 5 is (60+10) bar, and this value is the pressure that initiatively rope closing is corresponding.That is " pressure+5bar=hawser that the pulling force of hawser active receipts is corresponding is dragged corresponding pressure by counter ".
To sum up, the main points of the solution of the present invention are:
1. open system constant tensile control;
2. externally controlled type Fixed differential reducing valve is in conjunction with proportional pressure control valve, determines initiatively identical tension value;
3. long-range pressure adjustment relief valve is in conjunction with common relief valve and proportional pressure control valve, determines passive identical tension value;
4. identical tension valve group integrally, can be mass, and is applicable to all kinds of open type pump pumping source;
5. common relief valve pressure is set, the spring force of externally controlled type Fixed differential reducing valve must be greater than, to ensure that system can normally work.
Thering is provided previous description of the present disclosure is for making any person skilled in the art all can make or use the disclosure.To be all apparent for a person skilled in the art to various amendment of the present disclosure, and generic principles as defined herein can be applied to other variants and can not depart from spirit or scope of the present disclosure.Thus, the disclosure not intended to be is defined to example described herein and design, but the widest scope consistent with principle disclosed herein and novel features should be awarded.
Claims (8)
1. an identical tension hydraulic valve bank, it is characterized in that, comprise the first relief valve (1), first ball valve (2), second relief valve (3), proportional pressure control valve (4), Fixed differential reducing valve (5), equilibrium valve (6), second ball valve (7), wherein Fixed differential reducing valve (5) is arranged on the on high-tension side oil circuit of external motor (8), the outlet connecting balanced valve (6) of Fixed differential reducing valve (5), the outlet of equilibrium valve (6) is arranged on the high pressure side of external motor (8), the control mouth of equilibrium valve (6) is arranged on the low voltage side of external motor (8), the import of the first relief valve (1) is arranged on the high pressure side of external motor (8), the remote control mouth of the first relief valve (1) is connected on the import of the second relief valve (3), the outlet of the second relief valve (3) is connected in parallel the control mouth of Fixed differential reducing valve (5) and the import of proportional pressure control valve (4), the outlet of proportional pressure control valve (4) directly connects outside fuel tank.
2. identical tension hydraulic valve bank according to claim 1, is characterized in that, the first relief valve (1) is long-range pressure adjustment relief valve, and the second relief valve (3) is common relief valve.
3. identical tension hydraulic valve bank according to claim 2, is characterized in that, proportional pressure control valve (4) is for arranging identical tension value.
4. identical tension hydraulic valve bank according to claim 3, is characterized in that, Fixed differential reducing valve (5) is externally controlled type Fixed differential reducing valve.
5. identical tension hydraulic valve bank according to claim 4, is characterized in that, identical tension hydraulic valve bank is external speed reducer (9) and winch (10) also.
6. identical tension hydraulic valve bank according to claim 5, is characterized in that, when identical tension hydraulic valve bank is in the general mode not needing identical tension function, the first ball valve (2) and the second ball valve (7) are closed; When identical tension hydraulic valve bank have the initiative or passive identical tension pattern time, the first ball valve (2) and the second ball valve (7) are opened.
7. identical tension hydraulic valve bank according to claim 6, it is characterized in that, when running active identical tension pattern, from the oil sources that the import access of Fixed differential reducing valve (5) continues, and the identical tension value of Set scale relief valve (4), after wire rope unclamps, the outlet pressure decompression of Fixed differential reducing valve (5) is setting value and Fixed differential reducing valve (5) the spring pressure value sum of proportional pressure control valve (4), valve group carries out active rope closing until stop rope closing when tension force increases to setting value and Fixed differential reducing valve (5) the spring pressure sum of proportional pressure control valve (4) in wire rope, when tension force in wire rope continue to increase to cause motor (8) high side pressure to be greater than the setting value sum of the setting value of proportional pressure control valve (4) and the second relief valve (3) time, wire rope is by anti-hauling-out, till in wire rope, tension force reaches the setting value of proportional pressure control valve (4) and the setting value sum of the second relief valve (3).
8. identical tension hydraulic valve bank according to claim 7, it is characterized in that, when running passive identical tension pattern, the identical tension value of Set scale relief valve (4), when tension force in wire rope increase to cause motor (8) high side pressure to be greater than the setting value sum of the setting value of proportional pressure control valve (4) and the second relief valve (3) time, wire rope by anti-hauling-out, till in wire rope, tension force reaches the setting value of proportional pressure control valve (4) and the setting value sum of the second relief valve (3).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610153402.4A CN105570215B (en) | 2016-03-17 | 2016-03-17 | A kind of identical tension hydraulic valve bank |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610153402.4A CN105570215B (en) | 2016-03-17 | 2016-03-17 | A kind of identical tension hydraulic valve bank |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105570215A true CN105570215A (en) | 2016-05-11 |
| CN105570215B CN105570215B (en) | 2017-07-28 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610153402.4A Active CN105570215B (en) | 2016-03-17 | 2016-03-17 | A kind of identical tension hydraulic valve bank |
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| Country | Link |
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| CN (1) | CN105570215B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114060326A (en) * | 2021-12-02 | 2022-02-18 | 上海中车艾森迪海洋装备有限公司 | Constant tension winch hydraulic system |
| CN114314395A (en) * | 2021-12-28 | 2022-04-12 | 江苏政田重工股份有限公司 | Constant tension control system for steel wire rope of hydraulic winch |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56134663A (en) * | 1980-03-25 | 1981-10-21 | Kobe Steel Ltd | Hydraulic device for turning hydraulic crane or the like |
| JPS6153318B2 (en) * | 1978-04-19 | 1986-11-17 | Hitachi Ltd | |
| JP2003322103A (en) * | 2002-05-09 | 2003-11-14 | Sumitomo Heavy Industries Construction Crane Co Ltd | Elevating control device |
| EP1626183A1 (en) * | 2004-08-10 | 2006-02-15 | Walvoil S.p.A. | Inlet section for load sensing directional control valves |
| CN101723257A (en) * | 2009-12-31 | 2010-06-09 | 中国人民解放军国防科学技术大学 | Hydraulic driving system for active heave compensation crane |
| CN202322167U (en) * | 2011-10-18 | 2012-07-11 | 林龙海 | Hydraulic hoisting machine controlling system capable of realizing free releasing of constant tension |
| CN104925685A (en) * | 2015-06-30 | 2015-09-23 | 中国船舶重工集团公司第七一九研究所 | Winch hydraulic system controlling guide rope through stepless speed regulating constant tension |
| CN205423362U (en) * | 2016-03-17 | 2016-08-03 | 上海振华重工(集团)股份有限公司 | Permanent tension hydraulic pressure valves |
-
2016
- 2016-03-17 CN CN201610153402.4A patent/CN105570215B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6153318B2 (en) * | 1978-04-19 | 1986-11-17 | Hitachi Ltd | |
| JPS56134663A (en) * | 1980-03-25 | 1981-10-21 | Kobe Steel Ltd | Hydraulic device for turning hydraulic crane or the like |
| JP2003322103A (en) * | 2002-05-09 | 2003-11-14 | Sumitomo Heavy Industries Construction Crane Co Ltd | Elevating control device |
| EP1626183A1 (en) * | 2004-08-10 | 2006-02-15 | Walvoil S.p.A. | Inlet section for load sensing directional control valves |
| CN101723257A (en) * | 2009-12-31 | 2010-06-09 | 中国人民解放军国防科学技术大学 | Hydraulic driving system for active heave compensation crane |
| CN202322167U (en) * | 2011-10-18 | 2012-07-11 | 林龙海 | Hydraulic hoisting machine controlling system capable of realizing free releasing of constant tension |
| CN104925685A (en) * | 2015-06-30 | 2015-09-23 | 中国船舶重工集团公司第七一九研究所 | Winch hydraulic system controlling guide rope through stepless speed regulating constant tension |
| CN205423362U (en) * | 2016-03-17 | 2016-08-03 | 上海振华重工(集团)股份有限公司 | Permanent tension hydraulic pressure valves |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114060326A (en) * | 2021-12-02 | 2022-02-18 | 上海中车艾森迪海洋装备有限公司 | Constant tension winch hydraulic system |
| CN114060326B (en) * | 2021-12-02 | 2023-04-18 | 上海中车艾森迪海洋装备有限公司 | Constant tension winch hydraulic system |
| CN114314395A (en) * | 2021-12-28 | 2022-04-12 | 江苏政田重工股份有限公司 | Constant tension control system for steel wire rope of hydraulic winch |
| CN114314395B (en) * | 2021-12-28 | 2024-06-07 | 江苏政田重工股份有限公司 | Constant tension control system for hydraulic winch steel wire rope |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105570215B (en) | 2017-07-28 |
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