CN201771496U - Hydraulic tracting system for shearer driven by load sensitive pump - Google Patents
Hydraulic tracting system for shearer driven by load sensitive pump Download PDFInfo
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- CN201771496U CN201771496U CN2010205200035U CN201020520003U CN201771496U CN 201771496 U CN201771496 U CN 201771496U CN 2010205200035 U CN2010205200035 U CN 2010205200035U CN 201020520003 U CN201020520003 U CN 201020520003U CN 201771496 U CN201771496 U CN 201771496U
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Abstract
The utility model discloses a hydraulic tracting system for shearers driven by load sensitive pumps, which comprises a main circuit, a make-up circuit and a brake circuit.The hydraulic tracting system is characterized in that the main circuit is an enclosed circuit consisting of a main pump motor, a load sensitive pump driven by the main pump motor, a throttle valve, a piezoelectric relay, a high pressure safety valve, a three-position 4 channel magnetic exchange valve, a first traction motor and a second traction motor.According to the technical solution of the present utility model, speed regulation and reversing function of shearer traction systems are operated by the main circuit consisting of the load sensitive pump and the magnetic exchange valve instead of conventional plunger variable displacement pumps, thereby improving the efficiency of energy saving and automation degree.The structure of the hydraulic system is simplified. The fault rate and the cost thereof are also reduced, thus is adapted to the development trend of the stuntedness of shearer fuselages.
Description
Technical field
The utility model relates to a kind of trailer system of coal-winning machine running part.
Background technology
Coal-winning machine is a kind of large-scale coal mining equipment that is exclusively used in mining operation construction under the coal mine.The trailer system of hydraulic haulage shearer all adopts speed governing and the commutation function of plunger variable pump realization to traction motor both at home and abroad, this mode exists that energy saving of system efficient is low, automaticity is low, system architecture is complicated, poor reliability, and when load pressure reaches the highest safe pressure, system can not off-load, aggravated wearing and tearing and impacting with high pressure, reduced shortcomings such as system application life plunger variable pump.
The utility model content
The utility model is for avoiding above-mentioned existing in prior technology weak point, and a kind of good energy-conserving effect, automaticity height, simple in structure, coal-winning machine hydraulic haulage system that working service adopts load sensitive pump to drive easily are provided.
The utility model is to solve the problems of the technologies described above the technical scheme that is adopted to be:
The coal-winning machine hydraulic haulage system that the utility model adopts load sensitive pump to drive, system's setting includes major loop, feed circuit and brake circuit; Design feature of the present utility model is:
The closed circuit that load sensitive pump, choke valve, pressure switch, high-pressure safety valve, 3-position 4-way solenoid operated directional valve, first traction motor and second traction motor that described major loop drives by main pump motor, by main pump motor formed;
In the described brake circuit, first liquid braking device and second liquid braking device respectively with first traction motor and the corresponding setting of second traction motor; The oil pocket pressure oil of described first liquid braking device and second liquid braking device is to be the return flow line with the two-position three way magnetic valve opened.
The utility model adopts the design feature of the coal-winning machine hydraulic haulage system of load sensitive pump driving also to be:
At the heat exchange loop that the low-pressure side setting of major loop is composed in series by counterbalance valve, cooler and back pressure one way valve, the part high-temperature oil liquid of the low-pressure side of described major loop is back to fuel tank through counterbalance valve, cooler, back pressure one way valve.
Repairing one way valve and overflow valve that described feed circuit is arranged in the feed circuit by the repairing motor, by the motor-driven slippage pump of repairing, fuel tank, the coarse filter that is arranged on slippage pump inlet, the fine filter that is arranged on the slippage pump outlet, series connection are formed.
The output flow of load sensitive pump is complementary with the required hauling speed of work in the utility model system, and outlet pressure and load pressure adapt, and system does not have spill losses, only has very little difference pressuring loss; When system pressure reached the highest safe pressure of load sensitive pump, flow sharply descended, and the pressure switch action makes the spool of 3-position 4-way solenoid operated directional valve be in meta, the primary heat transport system off-load.Compared with prior art, the utility model beneficial effect is embodied in:
1, the utility model is implemented in the adjustment of hauling speed under the different operating mode demands by throttle valve opening.Required flow of flow system flow and pressure and load and pressure adapt to automatically, and system does not have spill losses.When load pressure surpassed the highest safe pressure of load sensitive pump, flow descended rapidly, has avoided the overload operation of system.
2, the utility model is by adopting the commutation function of solenoid operated directional valve realization to traction motor, and action response is fast, the automaticity height.And send electric signal by pressure switch during system overload, the electromagnetic switch valve core changes to meta, makes system unloaded, has reduced energy loss, has alleviated the wearing and tearing and the impacting with high pressure of load sensitive pump.
3, the utility model is used in combination by adopting load sensitive pump and solenoid operated directional valve, complex structure in the conventional hydraulic trailer system, variable pump and auxiliary hydraulic pressure element that cost is high have been replaced, as hydraulicchange-over valve etc., reduced system failure rate and equipment investment, and made that system's operation is more reliable.
Description of drawings
Accompanying drawing is the utility model structural representation.
Number in the figure: 1 main pump motor, 2 load sensitive pumps, 3 variable oil cylinders, 4 pressure-compensated valves, 5 flow compensation valves, 6 choke valves, 7 pressure switches, 8 high-pressure safety valves, 9 counterbalance valves, 10 coolers, 11.1 back pressure one way valve, 11.2 repairing one way valve, 12 3-position 4-way solenoid operated directional valves, 13.1 first traction motor, 13.2 second traction motor, 14.1 first liquid braking device, 14.2 second liquid braking device, 15 two-position three way magnetic valves, 16 fine filters, 17 slippage pumps, 18 repairing motors, 19 overflow valves, 20 coarse filters, 21 fuel tanks.
The specific embodiment
The setting of present embodiment system includes major loop, feed circuit and brake circuit; The closed circuit that load sensitive pump 2, choke valve 6, pressure switch 7, high-pressure safety valve 8,3-position 4-way solenoid operated directional valve 12, first traction motor 13.1 and second traction motor 13.2 that major loop drives by main pump motor 1, by main pump motor formed; In the brake circuit, first liquid braking device 14.1 and second liquid braking device 14.2 respectively with first traction motor 13.1 and the 13.2 corresponding settings of second traction motor; The oil pocket pressure oil of first liquid braking device 14.1 and second liquid braking device 14.2 is to be the return flow line with the two-position three way magnetic valve 15 opened.
In concrete the enforcement, low-pressure side at major loop, the heat exchange loop that setting is composed in series by counterbalance valve 9, cooler 10 and back pressure one way valve 11.1, the part high-temperature oil liquid of the low-pressure side of major loop is back to fuel tank 21 through counterbalance valve 9, cooler 10, back pressure one way valve 11.1; Repairing one way valve 11.2 and overflow valve 19 that feed circuit is arranged in the feed circuit by repairing motor 18, by the motor-driven slippage pump 17 of repairing, fuel tank 21, the coarse filter 20 that is arranged on slippage pump inlet, the fine filter 16 that is arranged on the slippage pump outlet, series connection are formed.
The course of work:
Start repairing motor 18, main pump motor 1 successively, and it is electric that the electromagnet 3YA of two-position three way magnetic valve 15 is got, and finishes the release of first liquid braking device 14.1 and 14.2 pairs first traction motors 13.1 of second liquid braking device and second traction motor 13.2.Low pressure fluid enters the major loop low-pressure side through fuel tank 21, coarse filter 20, slippage pump 17, fine filter 16, repairing one way valve 11.2, and system is carried out repairing, the operating pressure that overflow valve 19 is set up slippage pump 17.Major loop low-pressure side part high-temperature oil liquid is back to fuel tank 21 through counterbalance valve 9, cooler 10, back pressure one way valve 11.1 and carries out interchange of heat.
Left end electromagnet 1YA and right-hand member electromagnet 2YA to 3-position 4-way solenoid operated directional valve 12 carry out the gain and loss electric control, the hydraulic oil that load sensitive pump 2 is discharged enters first traction motor 13.1 and second traction motor 13.2 through 3-position 4-way solenoid operated directional valve 12, finishes shearer haulage commutation work.
Regulate choke valve 6 opening degrees, carry out the Flow-rate adjustment of required hauling speed under different operating modes, system carries out speed governing.Such as will improve load speed the time, choke valve 6 aperture areas increase, because this moment, flow did not also change, flow control valve 5 two ends pressure reduction reduce, this moment, flow control valve 5 spools moved to left, hydraulic oil liquid is through pressure-control valve 4 in variable oil cylinder 3 rodless cavities, flow control valve 5 flow to fuel tank 21, variable oil cylinder 3 piston rods are under spring action, load sensitive pump 2 swash plate angles are increased, thereby load sensitive pump 2 flows are increased, and correspondingly the flow through choke valve 6 increases, and flow control valve 5 two ends pressure reduction are increased, until reaching flow control valve 5 two ends pressure balance states, loading speed is improved.
When coal-winning machine was worked in the highest safe pressure working range that pressure-compensated valve is set, flow system flow and pressure adapted to the variation of load automatically.Adjustment process is as follows: such as when load pressure diminishes, under flow control valve 5 two ends pressure reduction increase effects, flow control valve 5 spools change to the work of position, a left side, high-voltage oil liquid is through flow control valve 5, pressure-control valve 4 entering variable oil cylinders 3 rodless cavities, load sensitive pump 2 swash plate angles are diminished, thereby load sensitive pump 2 flows are reduced, correspondingly reduce through choke valve 6 flows, system pressure reduces, choke valve 6 two ends pressure reduction reduce, until returning to flow control valve 5 two ends pressure balance states, the speed drawing that system sets up with choke valve 6.Otherwise, when load pressure increases, reduce under the effect at flow control valve 5 two ends pressure reduction, flow control valve 5 spools change to the work of right position, hydraulic oil liquid flow to fuel tank 21 through pressure-control valve 4, flow control valve 5 in variable oil cylinder 3 rodless cavities, variable oil cylinder 3 piston rods are under spring action, load sensitive pump 2 swash plate angles are increased, thereby load sensitive pump 2 flows are increased, correspondingly increase through choke valve 6 flows, system pressure increases, and choke valve 6 two ends pressure reduction increase, until returning to flow control valve 5 two ends pressure balance states.
When the highest safe pressure that the coal-winning machine load pressure reaches that pressure-compensated valve sets, high-voltage oil liquid moves down pressure-control valve 4 spools, high-voltage oil liquid is through pressure-control valve 4 rapid entering variable cylinder 3 rodless cavities, load sensitive pump 2 swash plate angles are reduced, thereby load sensitive pump 2 flows are sharply reduced, at this moment, pressure switch 7 place's pressure reach analog value, and send electric signal, 3-position 4-way solenoid operated directional valve 12 spools are changed to meta work, system unloaded reduces energy loss, and has reduced the wearing and tearing and the impacting with high pressure of load sensitive pump.
Under the high capacity operating mode, high-pressure safety valve 8 plays the high voltage protective effect.When system load surpasses the highest safe pressure, pressure switch 7 is malfunctioning, and when system failed timely off-load, high-pressure safety valve 10 was opened, and unnecessary high-voltage oil liquid is back to the system low-voltage side through high-pressure safety valve 10, realizes the protection to system.
When first traction motor 13.1 and the 13.2 need brakings of second traction motor, the electromagnet 3YA dead electricity of two-position three way magnetic valve 15, the oil pocket pressure oil of first liquid braking device 14.1 and second liquid braking device 14.2 is back to fuel tank 21 through two-position three way magnetic valve 15, by outside friction disc in the spring compression, with first traction motor 13.1 and 13.2 brakings of second traction motor.
Claims (3)
1. adopt the coal-winning machine hydraulic haulage system of load sensitive pump driving, system's setting includes major loop, feed circuit and brake circuit; It is characterized in that:
The closed circuit that load sensitive pump (2), choke valve (6), pressure switch (7), high-pressure safety valve (8), 3-position 4-way solenoid operated directional valve (12), first traction motor (13.1) and second traction motor (13.2) that described major loop drives by main pump motor (1), by main pump motor formed;
In the described brake circuit, first liquid braking device (14.1) and second liquid braking device (14.2) respectively with first traction motor (13.1) and the corresponding setting of second traction motor (13.2); The oil pocket pressure oil of described first liquid braking device (14.1) and second liquid braking device (14.2) is to be the return flow line with the two-position three way magnetic valve (15) opened.
2. the coal-winning machine hydraulic haulage system that employing load sensitive pump according to claim 1 drives, it is characterized in that the heat exchange loop that the low-pressure side setting at major loop is composed in series by counterbalance valve (9), cooler (10) and back pressure one way valve (11.1), the part high-temperature oil liquid of the low-pressure side of described major loop is back to fuel tank (21) through counterbalance valve (9), cooler (10), back pressure one way valve (11.1).
3. the coal-winning machine hydraulic haulage system that employing load sensitive pump according to claim 1 drives is characterized in that repairing one way valve (11.2) and overflow valve (19) that described feed circuit is arranged in the feed circuit by repairing motor (18), by the motor-driven slippage pump of repairing (17), fuel tank (21), the coarse filter (20) that is arranged on the slippage pump inlet, the fine filter (16) that is arranged on the slippage pump outlet, series connection are formed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205200035U CN201771496U (en) | 2010-09-03 | 2010-09-03 | Hydraulic tracting system for shearer driven by load sensitive pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205200035U CN201771496U (en) | 2010-09-03 | 2010-09-03 | Hydraulic tracting system for shearer driven by load sensitive pump |
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| Publication Number | Publication Date |
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| CN201771496U true CN201771496U (en) | 2011-03-23 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2010205200035U Expired - Fee Related CN201771496U (en) | 2010-09-03 | 2010-09-03 | Hydraulic tracting system for shearer driven by load sensitive pump |
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Cited By (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102278061A (en) * | 2011-07-07 | 2011-12-14 | 江苏谷登工程机械装备有限公司 | Hydraulic system for horizontal directional drilling machine power transmission device |
| CN102312881A (en) * | 2011-08-22 | 2012-01-11 | 三一重工股份有限公司 | Flushing circuit of closed hydraulic system |
| CN102756723A (en) * | 2012-07-31 | 2012-10-31 | 北京起重运输机械设计研究院 | Control system for hydraulic oil path |
| CN102837750A (en) * | 2012-01-11 | 2012-12-26 | 中国矿业大学 | Hydraulic driving moving platform of coal mine rescuing robot |
| CN102897159A (en) * | 2012-09-07 | 2013-01-30 | 徐州万邦道路工程装备服务股份公司 | Hydraulic brake system of spreading machine |
| CN102900436A (en) * | 2012-11-01 | 2013-01-30 | 中国矿业大学 | Cylinder stepping type thin seam coal mining machine |
| CN102927089A (en) * | 2012-11-16 | 2013-02-13 | 无锡汇虹机械制造有限公司 | Energy-saving control method of hydraulic system by using load sensitive technology |
| CN103114989A (en) * | 2013-01-28 | 2013-05-22 | 上海朝田实业有限公司 | Follow-up sensitive pump for energy-saving hydraulic pump station |
| CN104214150A (en) * | 2014-06-04 | 2014-12-17 | 上海中联重科桩工机械有限公司 | Double-winding hydraulic control system and engineering machine provided with same |
| CN104358722A (en) * | 2014-11-10 | 2015-02-18 | 武汉船用机械有限责任公司 | Hydraulic control system for ocean engineering crane |
| CN104373399A (en) * | 2014-11-03 | 2015-02-25 | 上海中联重科桩工机械有限公司 | Hydraulic system capable of achieving multi-torque output and rotary drilling rig |
| CN104500463A (en) * | 2014-11-28 | 2015-04-08 | 武汉船用机械有限责任公司 | Submersible-pump hydraulic control system |
| CN104675769A (en) * | 2015-03-11 | 2015-06-03 | 农业部南京农业机械化研究所 | Four-stage speed-regulating hydraulic control circuit of organic fertilizer turning machine |
| CN106567868A (en) * | 2015-10-10 | 2017-04-19 | 湖南希法工程机械有限公司 | Closed type hydraulic system and engineering machine |
| CN107524552A (en) * | 2017-08-30 | 2017-12-29 | 中国煤炭科工集团太原研究院有限公司 | A kind of cold-starting device of anti-explosion diesel engine vehicle |
| CN108105182A (en) * | 2016-11-24 | 2018-06-01 | 川崎重工业株式会社 | Oil pressure actuated systems |
| CN115450619A (en) * | 2022-08-03 | 2022-12-09 | 四川古叙科技咨询服务有限公司 | Slip suppression device and method for large-dip-angle thin seam floor-climbing coal mining machine |
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2010
- 2010-09-03 CN CN2010205200035U patent/CN201771496U/en not_active Expired - Fee Related
Cited By (23)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102278061A (en) * | 2011-07-07 | 2011-12-14 | 江苏谷登工程机械装备有限公司 | Hydraulic system for horizontal directional drilling machine power transmission device |
| CN102312881A (en) * | 2011-08-22 | 2012-01-11 | 三一重工股份有限公司 | Flushing circuit of closed hydraulic system |
| CN102312881B (en) * | 2011-08-22 | 2014-07-30 | 三一重工股份有限公司 | Flushing circuit of closed hydraulic system |
| CN102837750A (en) * | 2012-01-11 | 2012-12-26 | 中国矿业大学 | Hydraulic driving moving platform of coal mine rescuing robot |
| CN102756723A (en) * | 2012-07-31 | 2012-10-31 | 北京起重运输机械设计研究院 | Control system for hydraulic oil path |
| CN102897159A (en) * | 2012-09-07 | 2013-01-30 | 徐州万邦道路工程装备服务股份公司 | Hydraulic brake system of spreading machine |
| CN102900436A (en) * | 2012-11-01 | 2013-01-30 | 中国矿业大学 | Cylinder stepping type thin seam coal mining machine |
| CN102900436B (en) * | 2012-11-01 | 2014-10-29 | 中国矿业大学 | Cylinder stepping type thin seam coal mining machine |
| CN102927089A (en) * | 2012-11-16 | 2013-02-13 | 无锡汇虹机械制造有限公司 | Energy-saving control method of hydraulic system by using load sensitive technology |
| CN103114989A (en) * | 2013-01-28 | 2013-05-22 | 上海朝田实业有限公司 | Follow-up sensitive pump for energy-saving hydraulic pump station |
| CN104214150A (en) * | 2014-06-04 | 2014-12-17 | 上海中联重科桩工机械有限公司 | Double-winding hydraulic control system and engineering machine provided with same |
| CN104214150B (en) * | 2014-06-04 | 2016-03-23 | 上海中联重科桩工机械有限公司 | Double-hoist hydraulic control system and there is its engineering machinery |
| CN104373399A (en) * | 2014-11-03 | 2015-02-25 | 上海中联重科桩工机械有限公司 | Hydraulic system capable of achieving multi-torque output and rotary drilling rig |
| CN104373399B (en) * | 2014-11-03 | 2017-03-15 | 上海中联重科桩工机械有限公司 | Can achieve hydraulic system and the rotary drilling rig of many torque outputs |
| CN104358722A (en) * | 2014-11-10 | 2015-02-18 | 武汉船用机械有限责任公司 | Hydraulic control system for ocean engineering crane |
| CN104500463A (en) * | 2014-11-28 | 2015-04-08 | 武汉船用机械有限责任公司 | Submersible-pump hydraulic control system |
| CN104675769A (en) * | 2015-03-11 | 2015-06-03 | 农业部南京农业机械化研究所 | Four-stage speed-regulating hydraulic control circuit of organic fertilizer turning machine |
| CN104675769B (en) * | 2015-03-11 | 2017-04-26 | 农业部南京农业机械化研究所 | Four-stage speed-regulating hydraulic control circuit of organic fertilizer turning machine |
| CN106567868A (en) * | 2015-10-10 | 2017-04-19 | 湖南希法工程机械有限公司 | Closed type hydraulic system and engineering machine |
| CN108105182A (en) * | 2016-11-24 | 2018-06-01 | 川崎重工业株式会社 | Oil pressure actuated systems |
| CN108105182B (en) * | 2016-11-24 | 2020-01-17 | 川崎重工业株式会社 | Oil pressure driving system |
| CN107524552A (en) * | 2017-08-30 | 2017-12-29 | 中国煤炭科工集团太原研究院有限公司 | A kind of cold-starting device of anti-explosion diesel engine vehicle |
| CN115450619A (en) * | 2022-08-03 | 2022-12-09 | 四川古叙科技咨询服务有限公司 | Slip suppression device and method for large-dip-angle thin seam floor-climbing coal mining machine |
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| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20110323 Termination date: 20120903 |