CN205154782U - Novel move and carry quick -witted hydraulic control device - Google Patents
Novel move and carry quick -witted hydraulic control device Download PDFInfo
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- CN205154782U CN205154782U CN201520833424.6U CN201520833424U CN205154782U CN 205154782 U CN205154782 U CN 205154782U CN 201520833424 U CN201520833424 U CN 201520833424U CN 205154782 U CN205154782 U CN 205154782U
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- 238000004886 process control Methods 0.000 abstract description 2
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- 238000005265 energy consumption Methods 0.000 description 3
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- 229910001208 Crucible steel Inorganic materials 0.000 description 1
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Abstract
The utility model relates to a novel move and carry quick -witted hydraulic control device in the metallurgical industry continuous casting field, including electro -hydraulic reversing valve, speed regulation and position locking unit, acceleration rate the control unit, pneumatic cylinder unit, wherein, the stopper chamber of pneumatic cylinder unit and pole chamber loop through acceleration rate the control unit, speed regulation and position locking unit respectively to be connected with the electro -hydraulic reversing valve, electro -hydraulic reversing valve and main pressure pipeline with lead go back to the oil pipe way and be connected, utility model is under the prerequisite that need not to increase hydraulic power unit power and increase hydraulic pressure components and parts latus rectum, and pneumatic cylinder speed can obtain very big improvement, satisfies a quick operation requirement that moves the machine of carrying completely. When moving simultaneously to a plurality of pneumatic cylinders very much, the investment construction cost of its saving is more obvious, simultaneously according to the process control requirement, can realize the high low -speed automatic switch -over of pneumatic cylinder, the equipment that prevents assaults starting to produce when stopping, avoiding leading to the fact equipment to damage.
Description
Technical Field
The utility model relates to a move among the continuous cast steel field of metallurgical industry and carry quick-witted hydraulic control device.
Background
At present, in order to improve the production operation rate, domestic and foreign continuous casting machines are generally used for parallel production by adopting a multi-flow continuous casting machine, and a slab conveying device is adopted at the tail end of a billet discharging area of the continuous casting machine to merge multi-flow slabs and send the slabs to a production line of a subsequent process. The transfer machine is a slab transfer device which has simple structure, high operation efficiency and small failure rate and is widely applied to slab continuous casting machines.
Along with the improvement of the production operation rate of the continuous casting machine, the slab continuous casting machine with high drawing speed requires the transfer machine to have higher operation efficiency, namely, the hydraulic cylinder in the hydraulic system is required to have higher movement speed. In order to enable a hydraulic cylinder of a transfer machine to have a faster moving speed, the output flow of a hydraulic pump station of a hydraulic system is improved on the premise that the system pressure is not changed by the conventional known technology, and by adopting the known technology, the total capacity of the hydraulic pump station is increased and the drift diameter of a hydraulic component is increased so as to meet the requirement that the hydraulic cylinder has the faster moving speed. The known technical scheme has the problems of high investment cost in the early stage, high energy consumption in production and operation, high spare part cost in the later stage and the like.
Disclosure of Invention
In order to overcome the problems existing in the prior art, the utility model aims to provide a novel move and carry quick-witted hydraulic control device, under the prerequisite that need not to increase hydraulic power unit power and increase hydraulic components and parts latus rectum, pneumatic cylinder speed can obtain greatly improving to overcome the problem that exists among the prior art.
In order to achieve the above purpose, the technical scheme of the utility model is that:
a novel hydraulic control device of a transfer machine comprises an electro-hydraulic reversing valve 1, a speed adjusting and position locking unit 11, a speed increasing control unit 10 and a hydraulic cylinder unit 9; wherein,
a plug cavity and a rod cavity of the hydraulic cylinder unit 9 are respectively connected with the electro-hydraulic reversing valve 1 sequentially through the speed-increasing control unit 10 and the speed adjusting and position locking unit 11, and the electro-hydraulic reversing valve 1 is connected with a main pressure pipeline and a main oil return pipeline.
The hydraulic cylinder unit 9 is composed of a first hydraulic cylinder 901 and a second hydraulic cylinder 902;
the speed-increasing control unit 10 is composed of a first speed-increasing control unit 1001 and a second speed-increasing control unit 1002;
the first speed-increasing control unit 1001 includes a second choke 202, a first electromagnetic valve 501, a first check valve 601, a second check valve 602, a first load control valve 701, and a first overflow valve 801; wherein,
the main oil port B of the first check valve 601 is connected to the plug cavity of the first hydraulic cylinder 901 and the first speed regulating valve 401 of the speed regulating and position locking unit 11, respectively; a main oil port a of the first check valve 601 is connected with a pressure oil port P of the first electromagnetic valve 501 and an oil return port T of the first load control valve 701 respectively; a pressure port P of the first load control valve 701 is connected with a main port B of the second check valve 602 and a pressure port P of the first overflow valve 801 respectively, and then is connected with a rod cavity of the first hydraulic cylinder 901; an oil return port T of the first electromagnetic valve 501 is respectively connected with an oil drain port L of the first load control valve 701, a main oil port A of the second one-way valve 602 and an oil return port T of the first overflow valve 801, and then is connected with a main oil port B of the electro-hydraulic reversing valve 1; a control oil port X of the first load control valve 701 is connected with a main oil port A of the first electro-hydraulic directional control valve 1 through a second choke 202;
the second speed-increasing control unit 1002 comprises a third throttle 203, a second electromagnetic valve 502, a third check valve 603, a fourth check valve 604, a second load control valve 702 and a second overflow valve 802; wherein,
the main oil port B of the third check valve 603 is connected to the plug cavity of the second hydraulic cylinder 902 and the second speed adjustment valve 402 of the speed adjustment and position locking unit 11, respectively; a main oil port a of the third check valve 603 is connected with a pressure oil port P of the second solenoid valve 502 and an oil return port T of the second load control valve 702 respectively; a pressure port P of the second load control valve 702 is connected to a main port B of the fourth check valve 604 and a pressure port P of the second overflow valve 802, and then connected to a rod cavity of the second hydraulic cylinder 902; an oil return port T of the second electromagnetic valve 502 is respectively connected with an oil drainage port L of the second load control valve 702, a main oil port A of the fourth check valve 604 and an oil return port T of the second overflow valve 802, and then is connected with a main oil port B of the electro-hydraulic reversing valve 1; the control port X of the second load control valve 702 is connected with the main port a of the first electro-hydraulic directional valve 1 through the third choke 203.
The speed regulation and position locking unit 11 comprises a first speed regulation valve 401, a second speed regulator 402, a first pilot operated check valve 301, a second pilot operated check valve 302 and a first restrictor 201; wherein,
the first speed regulating valve 401 is connected with a main oil port B of the first hydraulic control one-way valve 301, the second speed regulating valve 402 is connected with a main oil port B of the second hydraulic control one-way valve 302, a main oil port A of the first hydraulic control one-way valve 301 and a main oil port A of the second hydraulic control one-way valve 302 are respectively connected with a main oil port A of the electro-hydraulic reversing valve 1, and control oil ports X of the first hydraulic control one-way valve 301 and the second hydraulic control one-way valve 302 are respectively connected with the main oil port B of the electro-hydraulic reversing valve 1 through the first restrictor 201.
Compared with the prior art, the utility model discloses possess following advantage:
1) the utility model discloses under the prerequisite that need not to increase hydraulic power unit power and increase hydraulic components and parts latus rectum, pneumatic cylinder speed can obtain very big improvement, satisfies completely to move the quick action requirement of carrying the machine. Especially, when a plurality of hydraulic cylinders act simultaneously, the investment and construction cost saved by the hydraulic cylinder is more obvious.
2) According to the process control requirements, the high-speed and low-speed switching of the hydraulic cylinder can be realized, the impact generated when the equipment is started and stopped is prevented, and the damage to the equipment is avoided.
3) The method has the characteristics of low investment and construction cost, low energy consumption in production and operation, low cost of spare parts in later period and the like.
4) The speed of the hydraulic cylinder of the transfer machine can not only quickly work to meet the action requirement of the transfer machine, but also can realize stable switching of high speed and low speed of the action of the transfer machine according to the process requirement.
5) Compared with the traditional mode of increasing the power of a hydraulic pump station of a hydraulic system and increasing the drift diameter of a hydraulic component, the novel hydraulic control device of the transfer machine has the advantages of low investment and construction cost, low energy consumption of production and operation, low cost of later-stage spare parts and the like.
Drawings
Fig. 1 is a schematic view of the hydraulic principle of the present invention.
The reference signs are:
1-an electro-hydraulic directional control valve, 201-a first choke, 202-a second choke, 203-a third choke, 301-a first pilot-operated check valve, 301-a second pilot-operated check valve, 401-a first speed regulating valve, 402-a second speed regulating valve, 501-a first solenoid valve, 502-a second solenoid valve, 601-a first check valve, 602-a second check valve, 603-a third check valve, 604-a fourth check valve, 701-a first load control valve, 702-a second load control valve, 801-a first overflow valve, 802-a second overflow valve, 9-a hydraulic cylinder unit, 901-a first hydraulic cylinder, 902-a second hydraulic cylinder, 10-a speed-increasing control unit, 1001-a first speed-increasing control unit, 1002-a second speed-increasing control unit, 11-a speed-regulating and position-locking unit, P '-a main pressure line, T' -a main return line, P-oil port pressure, T-an oil return port, the oil pump comprises an L-oil drainage port, an A-main oil port, a B-main oil port, an L-oil drainage port, an X-control oil port, an a-electromagnet and a B-electromagnet.
Detailed Description
The present invention will be described in detail with reference to the accompanying drawings and examples.
Referring to fig. 1, the utility model relates to a novel move and carry quick-witted hydraulic control device's concrete principle does:
the hydraulic control system comprises an electro-hydraulic reversing valve 1, a speed adjusting and position locking unit 11, a speed increasing control unit 10 and a hydraulic cylinder unit 9; wherein,
a plug cavity and a rod cavity of the hydraulic cylinder unit 9 are respectively connected with the electro-hydraulic reversing valve 1 sequentially through the speed-increasing control unit 10 and the speed adjusting and position locking unit 11, and the electro-hydraulic reversing valve 1 is connected with a main pressure pipeline and a main oil return pipeline.
The hydraulic cylinder unit 9 is composed of a first hydraulic cylinder 901 and a second hydraulic cylinder 902.
The speed-increasing control unit 10 is composed of a first speed-increasing control unit 1001 and a second speed-increasing control unit 1002, wherein,
the first speed-increasing control unit 1001 includes a second throttle 202, a first electromagnetic valve 501, a first check valve 601, a second check valve 602, a first load control valve 701, and a first overflow valve 801; wherein,
the main oil port B of the first check valve 601 is connected to the plug cavity of the first hydraulic cylinder 901 and the first speed regulating valve 401 of the speed regulating and position locking unit 11, respectively; a main oil port a of the first check valve 601 is connected with a pressure oil port P of the first electromagnetic valve 501 and an oil return port T of the first load control valve 701 respectively; a pressure port P of the first load control valve 701 is connected with a main port B of the second check valve 602 and a pressure port P of the first overflow valve 801 respectively, and then is connected with a rod cavity of the first hydraulic cylinder 901; an oil return port T of the first electromagnetic valve 501 is respectively connected with an oil drain port L of the first load control valve 701, a main oil port A of the second one-way valve 602 and an oil return port T of the first overflow valve 801, and then is connected with a main oil port B of the electro-hydraulic reversing valve 1; the control oil port X of the first load control valve 701 is connected with the main oil port a of the first electro-hydraulic directional control valve 1 through the second choke 202.
The second speed-increasing control unit 1002 comprises a third throttle 203, a second electromagnetic valve 502, a third check valve 603, a fourth check valve 604, a second load control valve 702 and a second overflow valve 802; wherein,
the main oil port B of the third check valve 603 is connected to the plug cavity of the second hydraulic cylinder 902 and the second speed regulating valve 402 of the speed regulating and position locking unit 11, respectively; a main oil port A of the third check valve 603 is respectively connected with a pressure oil port P of the second electromagnetic valve 502 and an oil return port T of the second load control valve 702; a pressure port P of the second load control valve 702 is connected to a main port B of the fourth check valve 604 and a pressure port P of the second overflow valve 802, and then connected to a rod cavity of the second hydraulic cylinder 902; an oil return port T of the second electromagnetic valve 502 is respectively connected with an oil drainage port L of the second load control valve 702, a main oil port A of the fourth check valve 604 and an oil return port T of the second overflow valve 802, and then is connected with a main oil port B of the electro-hydraulic reversing valve 1; the control port X of the second load control valve 702 is connected with the main port a of the first electro-hydraulic directional valve 1 through the third choke 203.
The speed regulation and position locking unit 11 comprises a first speed regulation valve 401, a second speed regulator 402, a first pilot operated check valve 301, a second pilot operated check valve 302 and a first restrictor 201; wherein,
the first speed regulating valve 401 is connected with a main oil port B of the first hydraulic control one-way valve 301, the second speed regulating valve 402 is connected with a main oil port B of the second hydraulic control one-way valve 302, a main oil port A of the first hydraulic control one-way valve 301 and a main oil port A of the second hydraulic control one-way valve 302 are respectively connected with a main oil port A of the electro-hydraulic reversing valve 1, and control oil ports X of the first hydraulic control one-way valve 301 and the second hydraulic control one-way valve 302 are respectively connected with the main oil port B of the electro-hydraulic reversing valve 1 through the first restrictor 201.
The electro-hydraulic directional valve 1 is used for controlling the action direction of the transfer machine.
The first hydraulic control check valve 301 and the second hydraulic control check valve 302 are used for locking the position of the hydraulic cylinder of the transfer machine.
The first speed regulating valve 401 and the second speed regulating valve 402 are used for regulating the speed of the hydraulic cylinder of the transfer machine, so that the working speed of the transfer machine can meet the process requirements.
The first restrictor 201 is used for controlling the time for opening the first hydraulic control one-way valve 301 and the second hydraulic control one-way valve 302, slowing down hydraulic impact and avoiding the shaking phenomenon during the action of equipment.
The second choke 202 and the third choke 203 are used for controlling the time for opening the first load control valve 701 and the second load control valve 702, and slowing down hydraulic shock, so that the on-off of oil in the rod cavity of the hydraulic cylinder unit 9 is controlled.
When the first load control valve 701 is used for extending the first hydraulic cylinder 901, hydraulic oil in a rod cavity of the first hydraulic cylinder 901 is supplemented to a plug cavity of the first hydraulic cylinder 901, so that the flow rate of the first hydraulic cylinder 901 is recycled, the speed of the first hydraulic cylinder 901 is greatly improved, when a control oil port X of the first load control valve 701 is communicated with pressure oil, the first load control valve 701 is opened, the oil flows to an oil port T through an oil port P, and otherwise, the first load control valve is closed; when the pressure at the oil port P of the first load control valve 701 exceeds the set pressure of the first load control valve 701, the first load control valve 701 will be opened, otherwise it will be closed, and at the same time it will be safe.
When the second load control valve 702 is used for extending the second hydraulic cylinder 902, the hydraulic oil in the rod cavity of the second hydraulic cylinder 902 is supplemented to the plug cavity of the second hydraulic cylinder 902, so that the flow of the second hydraulic cylinder 902 is recycled, the speed of the second hydraulic cylinder 902 is greatly improved, when the control oil port X of the second load control valve 702 is filled with pressure oil, the second load control valve 702 is opened, the oil flows to the oil port T through the oil port P, and otherwise, the second load control valve is closed; when the pressure at the port P of the second load control valve 702 exceeds the set pressure of the second load control valve 702, the second load control valve 702 will open, otherwise it will close, and at the same time it will act as a safety valve.
The first electromagnetic valve 501 is used for switching the high speed and the low speed of the first hydraulic cylinder 901, and by controlling the on-off of the electromagnet a of the first electromagnetic valve 501, the oil in the rod cavity of the first hydraulic cylinder 901 can be controlled to be discharged back to the oil tank, that is, the first hydraulic cylinder 901 runs at a low speed; the oil in the rod cavity of the first hydraulic cylinder 901 can also be controlled to be supplemented to the plug cavity of the first hydraulic cylinder 901, so that the flow rate of the first hydraulic cylinder 901 is recycled, the speed of the first hydraulic cylinder 901 is greatly increased, the speed increase rate is related to the annular area difference between the plug cavity and the rod cavity of the first hydraulic cylinder 901, and the larger the annular area difference is, the larger the speed increase is. When the first hydraulic cylinder 901 extends out, according to the process requirements, if the first hydraulic cylinder 901 is required to operate at a low speed, the electromagnet a of the first electromagnetic valve 501 is electrified, oil discharged from the rod cavity of the first hydraulic cylinder 901 flows back to the main oil return pipeline T' through the first load control valve 701 and the first electromagnetic valve 501 in sequence, so that the speed of the first hydraulic cylinder 901 is determined by the oil flow of the main oil port a of the electro-hydraulic directional valve 1, and the first hydraulic cylinder 901 extends out at a low speed; if the first hydraulic cylinder 901 needs to be extended quickly according to the process requirements, the electromagnet a of the first electromagnetic valve 501 is powered off, oil discharged from the rod cavity of the first hydraulic cylinder 901 sequentially passes through the first load control valve 701 and the first check valve 601 to be supplemented to the plug cavity of the first hydraulic cylinder 901, so that the speed of the first hydraulic cylinder 901 is determined by the sum of the oil flow of the main oil port a of the electro-hydraulic directional valve 1 and the oil flow discharged from the rod cavity of the first hydraulic cylinder 901, and the first hydraulic cylinder 901 is extended quickly.
The second electromagnetic valve 502 is used for switching between high speed and low speed of the second hydraulic cylinder 902, and by controlling the on-off of the electromagnet a of the second electromagnetic valve 502, the oil in the rod cavity of the second hydraulic cylinder 902 can be controlled to be discharged back to the oil tank, that is, the second hydraulic cylinder 902 runs at low speed; the oil in the rod cavity of the second hydraulic cylinder 902 can be controlled to be supplemented to the plug cavity of the second hydraulic cylinder 902, the flow recycling of the second hydraulic cylinder 902 is achieved, the speed of the second hydraulic cylinder 902 is greatly improved, the speed increasing rate is related to the annular area difference value between the plug cavity of the second hydraulic cylinder 902 and the rod cavity, and the larger the annular area difference value is, the larger the speed is. According to the process requirement, if the second hydraulic cylinder 902 is required to run at a low speed, the electromagnet a of the second electromagnetic valve 502 is electrified, oil discharged from the rod cavity of the second hydraulic cylinder 902 flows back to the main oil return pipeline T' through the second load control valve 702 and the second electromagnetic valve 502 in sequence, so that the speed of the second hydraulic cylinder 902 is determined by the oil flow of the main oil port a of the electro-hydraulic directional valve 1, and the second hydraulic cylinder 902 extends out at a low speed; if the second hydraulic cylinder 902 needs to extend rapidly according to the process requirement, the electromagnet a of the second solenoid valve 502 is de-energized, the oil discharged from the rod cavity of the second hydraulic cylinder 902 sequentially passes through the second load control valve 702 and the second make-up check valve 602 to be made up to the plug cavity of the second hydraulic cylinder 902, so the speed of the second hydraulic cylinder 902 is determined by the sum of the oil flow of the main oil port a of the electro-hydraulic directional valve 1 and the oil flow discharged from the rod cavity of the second hydraulic cylinder 902, and the second hydraulic cylinder 902 extends rapidly.
When the first overflow valve 801 is used for extending the first hydraulic cylinder 901, the rod cavity pipeline and elements of the first hydraulic cylinder 901 are prevented from being damaged due to pressure increase caused by different action areas of the first hydraulic cylinder 901.
When the second overflow valve 802 is used for extending the second hydraulic cylinder 902, it prevents the rod cavity pipeline and the components of the second hydraulic cylinder 902 from being damaged due to the increase of pressure caused by the difference of the action areas of the second hydraulic cylinder 902.
The utility model discloses require pneumatic cylinder unit 9 withdrawal during operation: electrifying an electromagnet a of the electro-hydraulic reversing valve 1; oil from a hydraulic pump station enters a main oil port B through a main pressure pipeline P 'and a pressure oil port P of the electro-hydraulic directional valve 1, respectively enters rod cavities of a first hydraulic cylinder 901 and a second hydraulic cylinder 902 through a second one-way valve 602 of a first speed-increasing control unit 1001 and a fourth one-way valve 604 of a second speed-increasing control unit 1002, the hydraulic cylinder unit 9 retracts, the oil discharged from a plug cavity of the hydraulic cylinder unit 9 enters a first speed regulating valve 401, a first hydraulic control one-way valve 301, a second speed regulating valve 402 and a second hydraulic control one-way valve 302 of a speed regulating and position locking unit 11 through the first speed-increasing control unit 1001 and the second speed control unit 1002 and flows back to the hydraulic pump station through a main oil port A of the electro-hydraulic directional valve, a main oil return port T and a main oil return pipe T', the normal retraction operation of the hydraulic cylinder unit 9 is realized by the first speed adjustment valve 401 and the second speed adjustment valve 402 which are adjusted in advance.
The utility model discloses at the time of requiring that pneumatic cylinder unit 9 stretches out the work at a slow speed: electromagnets a of the first electromagnetic valve 501 and the second electromagnetic valve 502 are electrified, and electromagnets b of the electro-hydraulic reversing valve 1 are electrified; pressure oil from a main pressure pipeline P' of the hydraulic station enters a main oil port A through a pressure oil port P of the electro-hydraulic directional valve 1, enters a first speed-increasing control unit 1001 and a second speed-increasing unit 1002 through a first hydraulic control one-way valve 301, a first speed-adjusting valve 401, a second hydraulic control one-way valve 302 and a second speed-adjusting valve 402 respectively, and then enters a plug cavity of a hydraulic cylinder unit 9 respectively, and the hydraulic cylinder unit 9 extends out; meanwhile, as the electromagnets a of the first electromagnetic valve 501 and the second electromagnetic valve 502 are electrified, oil discharged from the rod cavity of the first hydraulic cylinder 901 flows back to the main oil return pipeline T' through the first load control valve 701 and the first electromagnetic valve 501 in sequence, the speed of the first hydraulic cylinder 901 is determined by the oil flow of the main oil port A of the electro-hydraulic directional valve 1, and the first hydraulic cylinder 901 extends out slowly; the oil discharged from the rod cavity of the second hydraulic cylinder 902 flows back to the main oil return pipeline T' through the second load control valve 702 and the second electromagnetic valve 502 in sequence, the speed of the second hydraulic cylinder 902 is determined by the oil flow of the main oil port a of the electro-hydraulic directional valve 1, and the second hydraulic cylinder 902 extends out slowly; the slow extension operation of the hydraulic cylinder unit 9 is realized by the first speed adjustment valve 401 and the second speed adjustment valve 402 which are adjusted in advance.
The utility model discloses when requiring that pneumatic cylinder unit 9 stretches out the during operation fast: the electromagnets a of the first electromagnetic valve 501 and the second electromagnetic valve 502 are powered off, and the electromagnet b of the electro-hydraulic reversing valve 1 is powered on; pressure oil from a main pressure pipeline P' of the hydraulic station enters a main oil port A through a pressure oil port P of the electro-hydraulic directional valve 1, enters a first speed-increasing control unit 1001 and a second speed-increasing unit 1002 through a first hydraulic control one-way valve 301, a first speed-adjusting valve 401, a second hydraulic control one-way valve 302 and a second speed-adjusting valve 402 respectively, and then enters a plug cavity of a hydraulic cylinder unit 9 respectively, and the hydraulic cylinder unit 9 extends out; meanwhile, as the electromagnet a of the first electromagnetic valve 501 is powered off, oil discharged from the rod cavity of the first hydraulic cylinder 901 sequentially passes through the first load control valve 701 and the first check valve 601 to be supplemented to the plug cavity of the first hydraulic cylinder 901, the speed of the first hydraulic cylinder 901 is determined by the sum of the oil flow of the main oil port a of the electro-hydraulic directional valve 1 and the oil flow discharged from the rod cavity of the first hydraulic cylinder 901, and the first hydraulic cylinder 901 rapidly extends out; meanwhile, as the electromagnet a of the second solenoid valve 502 is de-energized, the oil discharged from the rod cavity of the second hydraulic cylinder 902 is sequentially supplemented to the plug cavity of the second hydraulic cylinder 902 through the second load control valve 702 and the second supplementing check valve 602, so that the speed of the second hydraulic cylinder 902 is determined by the sum of the oil flow rate of the main oil port a of the electro-hydraulic directional valve 1 and the oil flow rate discharged from the rod cavity of the second hydraulic cylinder 902, and the second hydraulic cylinder 902 is rapidly extended.
The switching between the slow extension and the fast extension of the hydraulic cylinder unit 9 is realized by electrically controlling the electromagnets a of the first electromagnetic valve 501 and the second electromagnetic valve 502, so that the large impact in production when the transfer machine is started or stopped is prevented, the safe operation of equipment is protected, and meanwhile, the automatic control can be realized.
In this embodiment, the description has been given by taking the first hydraulic cylinder 901 and the second hydraulic cylinder 902 as examples, and the utility model is particularly suitable for a hydraulic control system in which a plurality of hydraulic cylinders operate simultaneously. The operation program in which the plurality of hydraulic cylinders operate simultaneously is the same as the operation program in which the two hydraulic cylinders operate simultaneously in the present embodiment, and is not described here.
The components and structures of the present embodiments that are not described in detail are well known in the art and do not constitute essential structural elements or elements.
Claims (3)
1. The utility model provides a novel move and carry quick-witted hydraulic control device which characterized in that:
the hydraulic control system comprises an electro-hydraulic reversing valve (1), a speed adjusting and position locking unit (11), a speed increasing control unit (10) and a hydraulic cylinder unit (9); wherein,
a plug cavity and a rod cavity of the hydraulic cylinder unit (9) are respectively connected with the electro-hydraulic directional valve (1) through the speed-increasing control unit (10) and the speed adjusting and position locking unit (11) in sequence.
2. The hydraulic control apparatus for a transfer machine according to claim 1, wherein:
the hydraulic cylinder unit (9) is composed of a first hydraulic cylinder (901) and a second hydraulic cylinder (902);
the speed-increasing control unit (10) consists of a first speed-increasing control unit (1001) and a second speed-increasing control unit (1002);
the first speed-increasing control unit (1001) comprises a second throttle (202), a first electromagnetic valve (501), a first check valve (601), a second check valve (602), a first load control valve (701) and a first overflow valve (801); wherein,
a main oil port B of the first check valve (601) is respectively connected with a plug cavity of a first hydraulic cylinder (901) and a first speed regulating valve (401) of a speed regulating and position locking unit (11); a main oil port A of the first one-way valve (601) is respectively connected with a pressure oil port P of the first electromagnetic valve (501) and an oil return port T of the first load control valve (701); a pressure oil port P of the first load control valve (701) is respectively connected with a main oil port B of the second one-way valve (602) and a pressure oil port P of the first overflow valve (801), and then is connected with a rod cavity of the first hydraulic cylinder (901); an oil return port T of the first electromagnetic valve (501) is respectively connected with an oil drainage port L of the first load control valve (701), a main oil port A of the second one-way valve (602) and an oil return port T of the first overflow valve (801), and then is connected with a main oil port B of the electro-hydraulic reversing valve (1); a control oil port X of the first load control valve (701) is connected with a main oil port A of the first electro-hydraulic directional valve (1) through a second restrictor (202);
the second speed-increasing control unit (1002) comprises a third throttle (203), a second electromagnetic valve (502), a third one-way valve (603), a fourth one-way valve (604), a second load control valve (702) and a second overflow valve (802); wherein,
the main oil port B of the third one-way valve (603) is respectively connected with a plug cavity of a second hydraulic cylinder (902) and a second speed regulating valve (402) of a speed regulating and position locking unit (11); a main oil port A of the third one-way valve (603) is respectively connected with a pressure oil port P of the second electromagnetic valve (502) and an oil return port T of the second load control valve (702); a pressure oil port P of the second load control valve (702) is respectively connected with a main oil port B of the fourth check valve (604) and a pressure oil port P of the second overflow valve (802), and then is connected with a rod cavity of the second hydraulic cylinder (902); an oil return port T of the second electromagnetic valve (502) is respectively connected with an oil drainage port L of the second load control valve (702), a main oil port A of the fourth one-way valve (604) and an oil return port T of the second overflow valve (802), and then is connected with a main oil port B of the electro-hydraulic reversing valve (1); and a control oil port X of the second load control valve (702) is connected with a main oil port A of the first electro-hydraulic directional valve (1) through a third choke (203).
3. The hydraulic control apparatus for a transfer machine according to claim 1, wherein:
the speed regulation and position locking unit (11) comprises a first speed regulation valve (401), a second speed regulator (402), a first hydraulic control one-way valve (301), a second hydraulic control one-way valve (302) and a first throttle (201); wherein,
the hydraulic control system is characterized in that a first speed regulating valve (401) is connected with a main oil port B of a first hydraulic control one-way valve (301), a second speed regulating valve (402) is connected with a main oil port B of a second hydraulic control one-way valve (302), the main oil port A of the first hydraulic control one-way valve (301) and the main oil port A of the second hydraulic control one-way valve (302) are respectively connected with a main oil port A of an electro-hydraulic reversing valve (1), and control oil ports X of the first hydraulic control one-way valve (301) and the second hydraulic control one-way valve (302) are respectively connected with the main oil port B of the electro-hydraulic reversing valve (1) through a first throttling device (201).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520833424.6U CN205154782U (en) | 2015-10-26 | 2015-10-26 | Novel move and carry quick -witted hydraulic control device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520833424.6U CN205154782U (en) | 2015-10-26 | 2015-10-26 | Novel move and carry quick -witted hydraulic control device |
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| CN205154782U true CN205154782U (en) | 2016-04-13 |
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| CN201520833424.6U Expired - Fee Related CN205154782U (en) | 2015-10-26 | 2015-10-26 | Novel move and carry quick -witted hydraulic control device |
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| CN (1) | CN205154782U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105201934A (en) * | 2015-10-26 | 2015-12-30 | 中国重型机械研究院股份公司 | Novel hydraulic control system of transfer-machine |
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2015
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105201934A (en) * | 2015-10-26 | 2015-12-30 | 中国重型机械研究院股份公司 | Novel hydraulic control system of transfer-machine |
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| 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: 20160413 Termination date: 20171026 |