CN2040089U - Vibrationless luffing hydraulic system for door-base crane - Google Patents
Vibrationless luffing hydraulic system for door-base crane Download PDFInfo
- Publication number
- CN2040089U CN2040089U CN 88204349 CN88204349U CN2040089U CN 2040089 U CN2040089 U CN 2040089U CN 88204349 CN88204349 CN 88204349 CN 88204349 U CN88204349 U CN 88204349U CN 2040089 U CN2040089 U CN 2040089U
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- valve
- commutation
- reversing
- cushion
- oil
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Abstract
The utility model is mainly composed of a reversing buffering loop composed of a reversing buffering valve and a slide valve combined hydraulic lock, wherein, the reversing buffering valve controls the time of the reversing course of the slide valve combined hydraulic lock, changes the time of the value increasing course of the flow quantity of a main system, and has obvious damping and buffering effect in the whole course of reversing and amplitude change. The system has the advantages of few hydraulic elements, reasonable structural arrangement, convenient maintenance, low no-load pressure, convenient installation and dismounting of an assembly, etc. The utility model mainly solves the great technological problems of amplitude change and vibration of a portal crane, and is also applied to vibrationless amplitude changing mechanisms of single-stage cylinders of other large-sized hoisting machines and loading and unloading devices.
Description
The utility model belongs to the improvement of span winch (hereinafter to be referred as the door machine) luffing hydraulic efficiency pressure system.
At present, the luffing hydraulic efficiency pressure system of door machine is when work, and the luffing mechanism of whole hoisting crane exists very big vibration.Its hydraulic efficiency pressure system is made up of main oil pump 1, little oil pump 2, big by pass valve 3, little by pass valve 4, distributing box 6 and 7, oil cylinder 8 and 9, and total system is divided into main system loop and control system loop two parts.Main oil pump 1 fuel feeding is adopted in the main system loop, and little oil pump 2 fuel feeding are adopted in the control system loop.This hydraulic system structure complexity, Hydraulic Elements overlap, reliability is low, failure frequency is higher.Particularly during door machine luffing, this system does not solve reversing impact and brings very big vibration problem for whole luffing mechanism, causes the important meals structure of a machine often to ftracture.
The utility model is exactly for solving above-mentioned luffing vibration difficult problem design-calculated span winch friction luffing hydraulic efficiency pressure system and for realizing this system's purpose made commutation cushion valve.
Feature of the present utility model:
(1) it forms the main system loop by main oil pump 1, big by pass valve 3, spool valve combinations hydraulic lock 12, oil cylinder 8 and 9; Form commutation control buffer loop by commutate cushion valve 10 and electromagnetic valve 11 and spool valve combinations hydraulic lock 12.
(2) replace little oil pump 2 of original system and little by pass valve 4 with commutation cushion valve 10;
(3) replace original system low-voltage solenoid valve 5 with high-pressure solenoid valve 11;
(4) replace original system distributing box 6 and 7 with spool valve combinations hydraulic lock 12;
(5) match with spool valve combinations hydraulic lock 12 by commutation cushion valve 10 and realize that commutation cushions the friction luffing.
Accompanying drawing 1 is former door machine luffing hydraulic efficiency pressure system;
Accompanying drawing 2 is a door machine friction luffing hydraulic efficiency pressure system;
Accompanying drawing 3 is commutation cushion valve structure diagram.
The utility model was embodiment, now further specified the utility model with accompanying drawing in conjunction with the embodiments.
Constitute the main system loop by main oil pump 1, big by pass valve 3, spool valve combinations hydraulic lock 12, oil cylinder 9 and 8, constitute the control system loop by commutation cushion valve 10, high-pressure solenoid valve 11.
When main oil pump 1 during to main system loop fuel feeding.Because spool valve combinations hydraulic lock 12 mediates, oil circuit is dissengaged positions.Oil cylinder 9 and 8 attonitys, at this moment, main oil pump 1 is simultaneously to control system loop fuel feeding, to electromagnetic valve 11, because electromagnetic valve 11 mediates, this partly comes oily through electromagnetic valve 11 oil sump tanks by commutation cushion valve 10 through commutation cushion valve 10, simultaneously, the commutation cushion valve is opened the oil sump tank opening.All the other most next oil that make main oil pump 1 are through this direct oil sump tank, and total system is unloading condition.
When electromagnetic valve 11 was in the commutation control position, main oil pump 1 arrived electromagnetic valve 11 to the fuel feeding in control system loop through commutation cushion valve 10,12 commutations of control slide assembled hydraulic lock.In case commutation finishes, the commutation cushion valve just cuts out the opening of oil sump tank, and at this moment, all flows of main oil pump 1 to oil cylinder 9 and 8 fuel feeding, make system present the luffing mode of operation through spool valve combinations hydraulic lock 12.
Be to realize native system, the utility model is special a kind of commutation cushion valve.
The commutation cushion valve is equipped with valve liner 14, guiding valve 15, damper 16, spring 17, connector cover 18 in housing 13.Connector cover 18 is equipped with in housing 13 terminations, and connects locking by bolt 20, packing ring 19.Fuel feed hole 21 and fuel return hole 22 are arranged on the housing 13.Connector cover 18 has a circular groove 24 that has sealing member 23, and oil outlet 25 is arranged, and there is cavity 26 end.An import circular groove 27 is arranged on the valve liner 14, and have fuel feed hole 28 to communicate with it, other has an outer ring back leakage groove 29, and has fuel return hole 30 to communicate with it, and the circular groove 32 that sealing member 31 is housed is arranged between oil-feed circular groove 27 and oil return circular groove 29; The circular groove 34 that sealing member 33 is housed is arranged in a termination of valve liner 14; Oil return circular groove 35 in one is arranged in the valve liner 14, and it communicates with outer oil return circular groove 29 by fuel return hole 30.One end of guiding valve 15 has concave shaped cavity wall 36, and bottom surface 37 constitutes pressure chambers 38 within itself and the housing 13, and guiding valve 15 outside faces have annular groove 39, communicate with inner oilhole 41 by oilhole 40, and the other end has a concave shaped cavity wall 42, and damper 16 is housed.Pressure chamber 38 communicates with inner oilhole 41 by cutoff port 43.One cutoff port 44 is arranged on the damper 16.Fuel feed hole 21, fuel feed hole 28, circular groove 39, oilhole 40 constitute oil suction chamber 45 with inner oilhole 41.Connector cover termination cavity 26 forms oil pocket 46 with an end of valve liner 14 and guiding valve 15.Spring 17 is housed in going out oil pocket 46.
Why the utility model can make span winch friction luffing, is that it has tangible luffing commutation buffer action owing to the commutation cushion valve, the existing commutation cushioning principle of sketching the cushion valve that commutates:
When main system is come oily Q
0Enter oil suction chamber 45, arrive pressure chamber 38 through cutoff port 43 on the one hand.On the other hand through cutoff port 44 to going out oil pocket 46, this flow is Q
1To electromagnetic valve 11 fuel feeding, when electromagnetic valve 11 mediates, flow Q
1Oil sump tank; Pressure P at pressure chamber 38
1With the pressure P that goes out oil pocket 46
2Difference of pressure (the P that forms
1-P
2) effect under, guiding valve 15 overcomes the spring force of spring 17 and moves.Pressure chamber 38 spaces increase gradually, and the interior circular groove 35 that the circular groove 39 of guiding valve 15 is linked up valve liner 14 makes most flow Q of oil suction chamber 45
2=Q
0-Q
1, through oil outlet 22 oil sump tanks, make main system present unloading condition by inner groove 35.
When electromagnetic valve 11 commutates work, Q
1Flow make spool valve combinations hydraulic lock 12 carry out luffing commutation, so, dominant discharge Q
1The speed of controlled amount system reversing time.In case commutation finishes, pressure chamber levels off to " zero ", pressure chamber 38 and go out difference of pressure (P between the oil pocket 46
1-P
2) also level off to " zero ".Guiding valve 15 is under the effect of spring 17, and the opening that the interior circular groove 35 of guiding valve circular groove 38 and valve liner is formed is closed gradually, makes Q
2=0, this moment, pressure chamber dwindled gradually, and the fluid in it is through cutoff port 43, and cutoff port 44 is got back to out oil pocket 46.This moment, the main system flow increased to full flow gradually.This shows that the big I of the size of the spring force of controlling spring 15 and cutoff port 43, cutoff port 44 changes closes process time.General by t=0.1～0.2 second reversing time, shut t=0.3～0.5 second is comprehensively chosen.
Because the commutation cushion valve has been controlled the commutation process time of spool valve combinations hydraulic lock in whole luffing commutation process, changed the birth process time of main system flow again, thereby reached the purpose of friction luffing.
The door machine variable amplitude hydraulic system of making according to the utility model has Hydraulic Elements few (oil pump, 4 valves are only arranged), pipeline structure connection and reasonable arrangement. Maintain easily, fuel tank reduces 180 liters than original, and assembly is easy to loading and unloading, and unloaded pressure is low (only to have 2.6kgf/cm2), main is thoroughly to have solved door machine luffing to vibrate this great technical barrier.
It is used that the utility model is mainly a machine friction jib lubbing mechanism, also is applicable to other large scale hoisting machinery and handling facilities single-stage cylinder friction jib lubbing mechanism.
Claims (5)
1, span winch friction luffing hydraulic efficiency pressure system is made up of main system loop and commutation control buffer loop, it is characterized in that: form the main system loop by main oil pump 1, big by pass valve 3, spool valve combinations hydraulic lock 12, oil cylinder 9,8: form commutation control buffer loop by commutate cushion valve 10 and electromagnetic valve 11 and spool valve combinations hydraulic lock 12.
2, a kind of for realizing this system's purpose made commutation cushion valve, it is characterized in that: valve liner 14, guiding valve 15, damper 16, spring 17, connector cover 18 are housed in the housing 13.
3, according to the described commutation cushion valve of claim 2, it is characterized in that: cutoff port 43 is arranged on the guiding valve 15 and adorn to form oil suction chamber 45 between damper 16, two cutoff ports that have cutoff port 44.
4,, it is characterized in that valve liner 14 is separated into cavity pressure chamber 38 and goes out oil pocket 46 by guiding valve 15 according to the described commutation cushion valve of claim 2.
5, according to claim 2, described commutation cushion valve is characterized in that cutoff port 43, the size of cutoff port 44, by reversing time t=0.1～0.2 second and shut t=0.3～0.5 second comprehensively choose.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 88204349 CN2040089U (en) | 1988-04-11 | 1988-04-11 | Vibrationless luffing hydraulic system for door-base crane |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 88204349 CN2040089U (en) | 1988-04-11 | 1988-04-11 | Vibrationless luffing hydraulic system for door-base crane |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2040089U true CN2040089U (en) | 1989-06-28 |
Family
ID=4838971
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 88204349 Expired - Lifetime CN2040089U (en) | 1988-04-11 | 1988-04-11 | Vibrationless luffing hydraulic system for door-base crane |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2040089U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100371107C (en) * | 2005-08-08 | 2008-02-27 | 西安重型机械研究所 | Vibrating device hydraulic system |
| CN102502433A (en) * | 2011-10-08 | 2012-06-20 | 武汉船用机械有限责任公司 | Variable amplitude hydraulic system of dual-oil-cylinder variable amplitude crane |
| WO2013003998A1 (en) * | 2011-07-04 | 2013-01-10 | 长沙中联重工科技发展股份有限公司 | Hydraulic control loop circuit |
| CN105134091A (en) * | 2015-10-15 | 2015-12-09 | 海城市石油机械制造有限公司 | Lifting and lowering buffer control device for derrick of drilling machine and use method thereof |
-
1988
- 1988-04-11 CN CN 88204349 patent/CN2040089U/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100371107C (en) * | 2005-08-08 | 2008-02-27 | 西安重型机械研究所 | Vibrating device hydraulic system |
| WO2013003998A1 (en) * | 2011-07-04 | 2013-01-10 | 长沙中联重工科技发展股份有限公司 | Hydraulic control loop circuit |
| CN102502433A (en) * | 2011-10-08 | 2012-06-20 | 武汉船用机械有限责任公司 | Variable amplitude hydraulic system of dual-oil-cylinder variable amplitude crane |
| CN102502433B (en) * | 2011-10-08 | 2013-09-04 | 武汉船用机械有限责任公司 | Variable amplitude hydraulic system of dual-oil-cylinder variable amplitude crane |
| CN105134091A (en) * | 2015-10-15 | 2015-12-09 | 海城市石油机械制造有限公司 | Lifting and lowering buffer control device for derrick of drilling machine and use method thereof |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C15 | Extension of patent right duration from 15 to 20 years for appl. with date before 31.12.1992 and still valid on 11.12.2001 (patent law change 1993) | ||
| RN01 | Renewal of patent term | ||
| C17 | Cessation of patent right | ||
| CX01 | Expiry of patent term |