CN201495029U - Electric hydraulic grab bucket with delayed unloading function - Google Patents
Electric hydraulic grab bucket with delayed unloading function Download PDFInfo
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- CN201495029U CN201495029U CN200920310331XU CN200920310331U CN201495029U CN 201495029 U CN201495029 U CN 201495029U CN 200920310331X U CN200920310331X U CN 200920310331XU CN 200920310331 U CN200920310331 U CN 200920310331U CN 201495029 U CN201495029 U CN 201495029U
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- hydraulic
- unloading
- grab bucket
- bucket
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Abstract
The utility model relates to a mechanical device for grabbing and unloading goods, in particular to an electric hydraulic grab bucket with a delayed unloading function, which comprises a grab bucket structure and an electric hydraulic device, wherein the electric hydraulic device comprises a hydraulic cylinder, a hydraulic pump, an electric motor and a control valve block, the electric motor connected with the hydraulic pump provides power for the hydraulic pump, and the hydraulic pump is connected with and drives the hydraulic cylinder. The utility model is characterized in that the control valve block comprises two unloading overflow valves, a control port of at least one unloading overflow valve is communicated with an orifice and an energy accumulator, and the other end of the orifice is connected with the hydraulic cylinder. The utility model has the advantages that the control technology of unloading and pressure maintaining is used when the grab bucket is opened or closed in place, the heat emission is minimum when the required work pressure of the grab bucket is ensured, and the optimal control mode of the hydraulic grab bucket is realized.
Description
Technical field
The utility model relates to a kind of mechanical equipment that unloads goods of grabbing, belong to hoisting crane: be used for industries such as harbour, harbour, steel mill, biomass power generation (garbage power, straw generating etc.), boats and ships, accumulating, be specifically related to a kind of electric hydraulic bucket with delayed unloading function.
Background technology
Electric hydraulic bucket is a kind of grab bucket of self-powered device, its structure such as Fig. 1.Present domestic existing electric hydraulic bucket, major part are to rely on the mode of electrical motor rotating to control the unlatching of grab bucket with closed.This mode is simple and reliable, need not control cable and use at home widely, is the main type of present electric hydraulic bucket, its representative type fluid control principle such as Fig. 2.Alternative electric hydraulic bucket is the solenoid control mode.
For the energy-conservation and heat-producing purpose of minimizing electric hydraulic bucket hydraulic efficiency pressure system, no matter adopt which kind of mode, after the complete closure of rock rake lobe, all adopted the control technology of off-load pressurize.Because the pressure of off-load pressurize size has direct relation with the extracting ability of grab bucket, therefore wishes to have bigger dwell pressure.But opening of rock rake lobe is a kind of dead work, and the extracting ability of grabbing bucket is not directly concerned, is for the energy-conservation and heat-producing purpose of minimizing electric hydraulic bucket hydraulic efficiency pressure system equally, under reliable premise, wishes the pressure minimum when grab bucket is opened.If possible, should adopt off-load pressurize technology as far as possible.
But above-mentioned hydraulic grab when adopting off-load holding pressure control mode when opening, the phenomenon that the pawl lobe is not opened can occur.Closed and open between the big more and pawl lobe own wt of difference of pressure when big more, this phenomenon is more obvious.Therefore in the electric hydraulic bucket of motor positive and inverse control, adopt control principle as shown in Figure 2, grab bucket is adopted the by pass valve overflow and is not adopted the control technology of off-load pressurize when the pawl lobe is opened.In the electric hydraulic bucket of some solenoid control, the use that when the rock rake lobe is opened, has off-load pressurize technology, but closed equate fully with the pressure unloading of opening.Even the phenomenon of after the complete closure of rock rake lobe, also can not open sometimes like this.
Summary of the invention
The purpose of this utility model is according to above-mentioned the deficiencies in the prior art part, a kind of electric hydraulic bucket with delayed unloading function is provided, this grab bucket makes it all can adopt the off-load control technology when closed and two motions of unlatching by cutoff port and energy storage are set in the control cock piece.
The utility model purpose realizes being finished by following technical scheme:
A kind of electric hydraulic bucket with delayed unloading function, be used for hoisting crane, this grab bucket comprises grab bucket structure and electro hydraulic gear, described electro hydraulic gear includes hydraulic actuating cylinder, Hydraulic Pump, electrical motor and control cock piece, described Hydraulic Pump relies on connected electrical motor that power is provided, and connect, drive described hydraulic actuating cylinder by the control cock piece, it is characterized in that: include two unloading overflow valves in the described control cock piece, wherein the control mouth of at least one unloading overflow valve is communicated with cutoff port and energy storage, and the described cutoff port other end is connected with hydraulic actuating cylinder.
The control mouth of described two unloading overflow valves is communicated with cutoff port and energy storage respectively.
The control mouth of described unloading overflow valve is provided with an interface, and described interface is connected by screw thread fit with described cutoff port.
The latus rectum of described cutoff port is 0.4mm-1.2mm.
The latus rectum of described cutoff port is 0.6mm-0.8mm.
The volume of described energy storage is not more than 0.63L.
The utility model has the advantages that: the unlatching of grab bucket, when closure puts in place, all used the control technology of off-load pressurize, when guaranteeing the needed operation pressure of grab bucket, heating is minimum.Eliminate the unreliable phenomenon of above-mentioned mode, realized the target of optimal hydraulic grab mode.
Description of drawings
Fig. 1 electric hydraulic bucket structural representation;
The original grab bucket fluid control of Fig. 2 principle schematic;
Fig. 3 grab bucket fluid control of the present utility model principle schematic.
The specific embodiment
The utility model feature and other correlated characteristic are described in further detail by embodiment below in conjunction with accompanying drawing, so that the understanding of technical personnel of the same trade:
As Figure 1-3, label is represented respectively: electrical motor 1, bidirectional hydraulic pump 2, control cock piece 3, hydraulic actuating cylinder 4, frame 5, pawl lobe 6, erecting by overhang 7, electric supply installation 8, oil sucting one-way valve V1, oil sucting one-way valve V2, unloading overflow valve CT1, by pass valve CT2, unloading overflow valve CT21, check valve CT3, check valve CT4, hydraulic control one-way valve CT5, hydraulic control one-way valve CT6, oil pipe P1, oil pipe P2, oil return pipe T, oil return oil filter F, cutoff port TH, energy storage AC; Pressure tap: MP1, MP2, MA, MB.
Electric hydraulic bucket is a kind of grab bucket of self-powered device, its structure such as Fig. 1.Electric hydraulic bucket mainly is made up of electrical motor 1, Hydraulic Pump 2, control cock piece 3, hydraulic actuating cylinder 4, frame 5, pawl lobe 6, erecting by overhang 7 and electric supply installation 8.General hydraulic actuating cylinder 4 equates with the quantity of pawl lobe 6, and minimum have two (two Hubei Province formulas), is generally 4-8 individual (multi-clove type).
Frame 5 is base paries of this grab bucket, and various equipments all are connected and fixed with frame 6.Pawl lobe 6 is work pieces, contacts with the material that grasps, and an end is fixed on the bottom of frame 5 with bearing pin, connects with hydraulic actuating cylinder 4 with a bearing pin in addition.Rely on stretching of hydraulic actuating cylinder 4 to drive and control 6 motions of pawl lobe, finish extracting and let-down material.The other end of hydraulic actuating cylinder 4 also is fixed on the top of frame 8 by a bearing pin, become the attachment point of hydraulic actuating cylinder 4.Erecting by overhang 7 is these grab buckets and the connector of hoisting crane, directly connects with suspension hook or steel rope on the hoisting crane.Electric supply installation 8 is power is obtained in this grab bucket from hoisting crane devices.
As shown in Figure 1,, because the weight of pawl lobe 6, can produce a cooresponding pressure P m, make the balanced of the application force and the pawl lobe 6 of hydraulic actuating cylinder 4 at the rod chamber of hydraulic actuating cylinder 4 when grab bucket during a midway location stop motion.Because pawl lobe 6 is the bearing pins with frame is that of the center of circle rotatablely moves, so the size of Pm is a variable relevant with the position of pawl lobe 6, general Pm value maximum when pawl lobe 6 is opened fully.
Above-mentioned pressure P m can record with compression indicator at the point of the MB among Fig. 2 or Fig. 3.But when grab bucket is fully closed, when promptly the piston rod of hydraulic actuating cylinder 4 stretches out fully, the weight that the direct contact force of piston and oil cylinder cover can balance pawl lobe, this moment, pressure P m may be zero.
Fig. 2 is present common grab bucket fluid control schematic diagram.V1, V2 are two oil sucting one-way valves, and bidirectional hydraulic pump 2 is connected with control cock piece 3 by it.CT1 is a unloading overflow valve, and CT2 is a by pass valve, and CT3, CT4 are check valve, and CT5, CT6 are hydraulic control one-way valve, and MP1, MP2, MA, MB are the pressure tap of cooresponding oil pipe P1, P2, A and B.CT1 to CT6 and corresponding pressure tap have been formed the control cock piece 3 among Fig. 1.The rod chamber of hydraulic actuating cylinder 4 and oil pipe B link, and rodless cavity and oil pipe A link.T be oil return pipe and and oil return oil filter F link.
When was just changeing at energized and control motor 1, bidirectional hydraulic pump 2 was from check valve V2 one side draught oil, by oil outlet pipe P1 fuel feeding in control valve body of check valve V1, pump.Pass through check valve CT3 and oil pipe A rodless cavity fuel feeding this moment to hydraulic actuating cylinder 4.Because there is charge oil pressure in the oil outlet pipe P1 of pump, and hydraulic control one-way valve CT6 is opened, this moment, the oil of hydraulic actuating cylinder 4 rod chambers can flow to oil return pipe T by hydraulic control one-way valve CT6 by oil pipe B, got back in the fuel tank through oil return oil filter F again.Realized the overhanging of hydraulic actuating cylinder 4 piston rods, driven the motion of pawl lobe, made grab bucket closed.The high output pressure of bidirectional hydraulic pump 2 was determined by unloading overflow valve CT1 when grab bucket was closed.When the pressure among the delivery side of pump pipe P1 reaches the pressure of unloading overflow valve CT1 setting, unloading overflow valve CT1 just produces overflow, and when oil pipe A reached setting pressure, unloading overflow valve CT1 can make the pump off-load, the pressure of oil pipe P1 is very low, has reduced the heating of hydraulic efficiency pressure system.
When electrical motor 1 counter-rotating, bidirectional hydraulic pump 2 is from check valve V1 one side draught oil, by oil outlet pipe P2 fuel feeding in control valve body of check valve V2, pump.The principle of control is identical when just changeing with motor basically.Realized the withdrawal of hydraulic actuating cylinder 4 piston rods, driven the rock rake lobe and open.Different is that CT2 is a by pass valve, does not enable the Hydraulic Pump off-load.Therefore after the pawl lobe was opened fully, the overflow meeting of by pass valve CT2 produced bigger heat.
Experimental results show that: in above-mentioned hydraulic control system, if change by pass valve CT2 into the unloading overflow valve the same with unloading overflow valve CT1, when grab bucket is in unloaded closure state fully (is that hydraulic actuating cylinder 4 piston rods all stretch out, the maximum close pressure PAmax that exists unloading overflow valve CT1 to set up among the oil pipe A) after, motor with reciprocating movement 1 immediately, the phenomenon that the pawl lobe is not opened can occur.Closed and open between difference of pressure big more or pawl lobe 6 own wts are big more, when there is internal leakage in hydraulic efficiency pressure system hardly, this phenomenon is more obvious.
Analyze above-mentioned phenomenon, its major cause is: what this hydraulic control system was used is fix-displacement pump, and when one timing of electrical motor 1 rotating speed, Q is constant for its flow system flow.When this flow Q opened motion in grab bucket, corresponding to the kinematic velocity V0 of a pawl lobe, flow Q was a balance, and this moment, by pass valve CT2 can overflow or off-load.But when the pawl lobe has just begun to open, the kinematic velocity V=0 of pawl lobe.Flow Q in the hydraulic efficiency pressure system must flow to the balance that oil pipe T reaches flow from by pass valve CT2 at this moment.If CT2 is a by pass valve, then be in overflow situation, establishing its oil pressure relief is PBmax.Hydraulic actuating cylinder 4 pulling force that the difference of the pressure P m that oil pressure relief PBmax and above-mentioned pawl lobe 6 weight produce produces are to the acceleration force of pawl lobe after the weight of hydraulic actuating cylinder 4 balance pawl lobes 6.Under the effect of this acceleration force, the pawl lobe quickens, and when reaching V0, no longer overflow of by pass valve CT2 enters the stable mode of operation of opening.Therefore, reach not overflow of by pass valve CT2, need a pawl lobe time for acceleration t.
When by pass valve CT2 changes unloading overflow valve CT21 into, almost, become unloading condition in the moment that unloading overflow valve CT21 overflow begins.This moment, the pressure of oil pipe P2 dropped to unloading overflow valve CT21 off-load value (being generally less than 1MPa), (K is the response pressure ratio of hydraulic control one-way valve CT5 and the response pressure of hydraulic control one-way valve CT5 needs PAmax/K, determine by structure, generally about 3), so the pressure of oil pipe P2 can't be opened hydraulic control one-way valve CT5, oil pipe A can not oil return, makes the pawl lobe stop motion.
Improve and to open pressure P Bmax, alleviate pawl lobe weight and equal to reduce Pm, all help the acceleration of pawl lobe, shorten pick-up time t.There is internal leakage in system, helps eliminating pressure P Amax or shortens unloading overflow valve CT21 and keep the time of unloading condition, and make system recovery arrive normal mode of operation easily.
As from the foregoing, after changing by pass valve CT2 into unloading overflow valve CT21, also need a time delay device to avoid above-mentioned unfavorable situation.As shown in Figure 3, increased energy storage AC and cutoff port TH in this scheme, in addition all the other each elements all with Fig. 2 in identical.
Cutoff port TH is one and has the hole of setting latus rectum that the one end is connecting the oil pipe B of hydraulic actuating cylinder 4, the control mouth of other end connection energy storage AC and unloading overflow valve CT21.Because the existence of cutoff port TH and energy storage AC, when cutoff port TH has hydraulic oil to flow, make that the pressure of off-load control mouth equals the pressure of energy storage AC and is not equal to the pressure that oil pipe B is hydraulic actuating cylinder 4 rod chambers among the unloading overflow valve CT21.The pressure that therefore will make the pressure of energy storage AC equal oil pipe B has a time difference, and promptly cutoff port TH and energy storage AC have constituted a time delay device.
If energy storage is necessarily filling the nitrogen pressure P
0Under volume be V
0, its volume is V when reaching unloading overflow valve CT21 minimum and keep pressure unloading PBmin
1, then the difference in volume of energy storage AC is Δ V=V under these two pressure
1-V
0When the oil pressure relief of unloading overflow valve CT21 setting was PBmax, PBmin kept the minimum pressure of off-load for it.PBmin=(1-ψ) PBmax, ψ is the pressure reduction rate, the structures shape by unloading overflow valve CT21 is generally 10-25%.
If cutoff port TH is from pressure reduction PBmax-P
0Average discharge when dropping to PBmax-PBmin is q.Then can calculate, unloading overflow valve CT21 from the shortest time that overflow situation changes to unloading condition is: t
1=Δ V/q.
Suitably select energy storage AC volume, fill the nitrogen pressure P
0(general P
0＞Pm) and the latus rectum of cutoff port TH, make t
1During＞t, just can avoid above-mentioned grab bucket to be in unloaded closure state fully fully after, the electrical motor pawl lobe that the occurs phenomenon of not opening of reversing immediately.
In like manner, when the similar insecure phenomenon of action appearred in closing direction, on the off-load control mouth of unloading overflow valve CT1, the delayed unloading control setup that equally also can increase an energy storage AC and a cutoff port TH composition solved, and is not giving unnecessary details at this.
Can be set to an element by cutoff port TH, its inside wears a hole, and outer wall is provided with outside thread; Cooresponding, at a unloading overflow valve CT21 control mouthful end interface with coupling negative thread is set, can replace the cutoff port TH of different latus rectums easily by screw thread fit.
Because the latus rectum of cutoff port TH and the cooperation of energy storage volume have determined the duration that off-load is delayed time.After the volume of having determined energy storage AC, the latus rectum that can change cutoff port reaches the purpose of various hydraulic grab optimum delay durations.General energy storage AC volume is selected 0.63L or littler of good for use.Because crossing conference, the volume of energy storage AC causes problems such as space hold and cost increase
Plugging fault appears in the latus rectum of cutoff port TH too small meeting easily.Therefore satisfying under the prerequisite of delay duration, the latus rectum of cutoff port TH should be controlled between the 0.4mm-1.2mm, and preferably is controlled between the 0.6mm-0.8mm.
The utility model has solved the problem that electric hydraulic bucket is unreliable in the closed work that produces with opening use unloading overflow valve on the both direction, do not open.Thereby overcome a large amount of heat-producing shortcomings of original electric hydraulic bucket hydraulic efficiency pressure system when opening fully, in the service life of saving the energy and having improved hydraulic efficiency pressure system, reduced fault rate.
Claims (6)
1. electric hydraulic bucket with delayed unloading function, be used for hoisting crane, this grab bucket comprises grab bucket structure and electro hydraulic gear, described electro hydraulic gear includes hydraulic actuating cylinder, Hydraulic Pump, electrical motor and control cock piece, described Hydraulic Pump relies on connected electrical motor that power is provided, and connect, drive described hydraulic actuating cylinder by the control cock piece, it is characterized in that: include two unloading overflow valves in the described control cock piece, wherein the control mouth of at least one unloading overflow valve is communicated with cutoff port and energy storage, and the described cutoff port other end is connected with hydraulic actuating cylinder.
2. a kind of electric hydraulic bucket with delayed unloading function according to claim 1 is characterized in that the control mouth of described two unloading overflow valves is communicated with cutoff port and energy storage respectively.
3. a kind of electric hydraulic bucket with delayed unloading function according to claim 2 is characterized in that the control mouth of described unloading overflow valve is provided with an interface, and described interface is connected by screw thread fit with described cutoff port.
4. according to claim 1,2 or 3 described a kind of electric hydraulic buckets with delayed unloading function, the latus rectum that it is characterized in that described cutoff port is 0.4mm-1.2mm.
5. a kind of electric hydraulic bucket with delayed unloading function according to claim 4, the latus rectum that it is characterized in that described cutoff port is 0.6mm-0.8mm.
6. a kind of electric hydraulic bucket with delayed unloading function according to claim 1 and 2 is characterized in that the volume of described energy storage is not more than 0.63L.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200920310331XU CN201495029U (en) | 2009-09-14 | 2009-09-14 | Electric hydraulic grab bucket with delayed unloading function |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200920310331XU CN201495029U (en) | 2009-09-14 | 2009-09-14 | Electric hydraulic grab bucket with delayed unloading function |
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| Publication Number | Publication Date |
|---|---|
| CN201495029U true CN201495029U (en) | 2010-06-02 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200920310331XU Expired - Lifetime CN201495029U (en) | 2009-09-14 | 2009-09-14 | Electric hydraulic grab bucket with delayed unloading function |
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| Country | Link |
|---|---|
| CN (1) | CN201495029U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102145854A (en) * | 2011-04-11 | 2011-08-10 | 杭州电子科技大学 | Electric four-clack hydraulic grab bucket |
| CN101665214B (en) * | 2009-09-14 | 2011-09-21 | 上海昂丰矿机科技有限公司 | Electric hydraulic bucket with delayed unloading function |
| CN105317760A (en) * | 2015-11-20 | 2016-02-10 | 连云港天明装备有限公司 | Start delay warning device for coal mine down-hole mine vehicle |
-
2009
- 2009-09-14 CN CN200920310331XU patent/CN201495029U/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101665214B (en) * | 2009-09-14 | 2011-09-21 | 上海昂丰矿机科技有限公司 | Electric hydraulic bucket with delayed unloading function |
| CN102145854A (en) * | 2011-04-11 | 2011-08-10 | 杭州电子科技大学 | Electric four-clack hydraulic grab bucket |
| CN102145854B (en) * | 2011-04-11 | 2013-01-23 | 杭州电子科技大学 | Electric four-clack hydraulic grab bucket |
| CN105317760A (en) * | 2015-11-20 | 2016-02-10 | 连云港天明装备有限公司 | Start delay warning device for coal mine down-hole mine vehicle |
| CN105317760B (en) * | 2015-11-20 | 2017-12-05 | 连云港天明装备有限公司 | Underground coal mine is mining vehicle start-up study warning device |
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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: 20100602 Effective date of abandoning: 20090914 |