CN2678983Y - Compensation feedback device of mechanical hydraulic governor - Google Patents
Compensation feedback device of mechanical hydraulic governor Download PDFInfo
- Publication number
- CN2678983Y CN2678983Y CN 200420028285 CN200420028285U CN2678983Y CN 2678983 Y CN2678983 Y CN 2678983Y CN 200420028285 CN200420028285 CN 200420028285 CN 200420028285 U CN200420028285 U CN 200420028285U CN 2678983 Y CN2678983 Y CN 2678983Y
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- compensating
- governor
- plunger
- feedback device
- damper piston
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Abstract
The utility model discloses a compensating feedback device of a mechanical hydraulic governor. The governor comprises an essential part of the governor, a speed setting part and a load control part. The essential part of the governor comprises an oil pump, a pressure accumulating chamber, a speed setting spring, a driving disk assemblage, a thrust bearing, a plunger, a rotating bush, a compensating feedback device and a power cylinder. The compensating feedback device comprises a buffer piston, a buffer spring, a compensating needle valve and a compensating bench. The compensating bench is directly connected to the plunger and integrated with the plunger. One side of the buffer piston is communicated with a control opening and leads below the compensating bench via an oil path. The other side of the buffer piston is communicated with the power cylinder and leads above the compensating bench via the oil path. Both sides of the buffer piston are communicated with each other via the compensating needle valve. The upper side and the lower side of the buffer piston are also provided with two by-pass oil paths. As the hydraulic feedback on both side of the buffer piston is directly acted above and below the compensating bench, namely on the plunger, the response is sensitive and the control precision is high.
Description
Technical field
The utility model relates to a kind of compensating feedback device of governor compensating feedback device, especially mechanical hydraulic-pressure type governor.
Background technology
Beginning of the sixties late 1950s, China railways department begins the self design diesel locomotive, introduced governor from the former Soviet Union at that time, after improving, mapping formed QJY series governor, be applied on easterly type, east wind 2 types, east wind 3 types and the Diesel Locomotive Model Beijing, its function only limits to control the rotating speed of diesel engine.Input and utilization along with the dong feng 4 locomotive, governor has been proposed new requirement, on the basis of QJY series governor, manufacture and design associating Type B governor by Dalian locomotive works and Tianjin Rolling Stock Machinery Plant, be used for the rotating speed and the power of dong feng 4 diesel locomotive control diesel engine.Enter the eighties, each main engine plants carries out the reinforcement of diesel engine energetically, improve relevant apparatus such as fuel oil, hoisting power significantly, because the hysteresis of governor product development can only be selected the serial governor of associating for use, all the time because of the limitation on its control principle, performance to diesel engine has produced adverse effect, and contradiction begins to occur.Enter the nineties, along with the raising of railway transportation to heavy duty, high speed development and reliability requirement, the especially appearance of east wind 4D visitor and east wind 11 locomotives, the declared power of homemade high-power locomotive diesel engine is to 5000 horsepowers, even 6000 horsepowers stride forward.Do not match because of there being corresponding novel governor, can only carry out necessary improvement on the associating governor, the result has released C3X type and D type associating governor, to apply urgent need.
The associating governor is the design-calculated product thirties, as shown in Figure 1, governor comprises the governor essential part, speed setting part and load control part, the governor essential part comprises oil pump, pressure accumulating chamber, join fast spring, the driving disk assembling, thrust baring, plunger, turnbarrel, compensating feedback device and power cylinder, the working process of the compensating feedback device of the associating governor of prior art is as follows: the associating governor is at first opened control mouth 15, pressure oil flows to or flows out power cylinder 11, power piston 5 actions drive compensating plunger 6 actions then, produce pressure and act on guiding valve 2, cause guiding valve 2 to follow plunger 1, up to closing control mouth 15.This process just causes the hysteresis of governor control, and this inadequate natural endowment has limited the improvement of its performance figure, makes it be difficult to be complementary with diesel engine newly developed.The effect of recoil spring 14 is that guiding valve 2 is equilibrated to neutral position, compensating needle valve 4 logical oil sumps, and its aperture size control slide 2 is followed the speed of plunger 1.
Because the inadequate natural endowment of principle of design, mainly there is following problem in the compensating feedback device of the associating governor of prior art:
A, instability: performance was difficult to keep after governor was adjusted, and especially the air receiver in the compensating feedback device is sewed seriously, needed frequent repairing.
B, idling position poor stability: the dong feng 4 diesel engine of locomotive has 30% idling position tourist bus.East wind 4D type, east wind 11 type locomotive diesel engine tourist buses are more serious, and what the tourist bus amplitude had reaches 30～40 rev/mins, and summer more very.
C, instantaneous speed change rate are bad: unloading causes the runaway governor action often, and driving takes place easily.
D, when playing machine rotating speed overshoot big: tooth bar is pulled out many, the diesel engine over-emitting black exhaust.
Summary of the invention
Technical problem to be solved in the utility model provides a kind of compensating feedback device of mechanical hydraulic-pressure type governor, adopts direct acting type, has improved the precision of governor control.
In order to solve the problems of the technologies described above, the technical solution adopted in the utility model is: a kind of compensating feedback device of mechanical hydraulic-pressure type governor, governor comprises governor essential part, speed setting part and load control part, the governor essential part comprises oil pump, pressure accumulating chamber, joins fast spring, driving disk assembling, thrust baring, plunger, turnbarrel, compensating feedback device and power cylinder, and the compensating feedback device comprises damper piston, recoil spring, compensating needle valve and compensation platform; The compensation platform directly is connected on the plunger, becomes one with plunger; One side of damper piston, logical by oil circuit with the control oral groove, lead to compensation platform below by oil circuit; The damper piston opposite side communicates with power cylinder by oil circuit, leads to compensation platform top by oil circuit; The damper piston both sides are linked up by compensating needle valve, also have two bleed off circuits in both sides up and down at damper piston.
The beneficial effects of the utility model are: because the oil pressure of damper piston both sides feedback acts directly on the upper and lower of compensation platform, promptly act directly on the plunger, so reflection is sensitive, and the control accuracy height.By alleviating and eliminating because the variation that the disturbance of the speed of driving engine or load brings the operation of stablizing driving engine and governor.
Description of drawings
Fig. 1 is the compensating feedback apparatus structure scheme drawing of the associating governor of prior art.
Fig. 2 is the compensating feedback apparatus structure scheme drawing of governor of the present utility model.
Among the figure, 1. plunger; 2. guiding valve; 3. compensation platform; 4. compensating needle valve; 5. power piston; 6. compensating plunger; 7. recoil spring; 8. damper piston; 9. compensating needle valve; 11. power cylinder; 12. fly iron; 13. join fast spring; 14. recoil spring; 15. control mouth; 16. BPO Bypass Orifice; 17,18,12,22. oil circuits; 19,20. bleed off circuits.
The specific embodiment
Be described in further detail below in conjunction with the compensating feedback device of the drawings and specific embodiments mechanical hydraulic-pressure type governor of the present utility model:
As shown in Figure 2, the compensating feedback device of governor of the present utility model comprises damper piston 8, recoil spring 7, compensating needle valve 9 and compensation platform 3.Compensation platform 3 directly is connected on the plunger 1, become one with it, there is oil circuit 17 to link up damper pistons 8 left sides from control mouth 15, damper piston 8 right sides have oil circuit 18 to communicate with power cylinder 11, damper piston 8 left sides have oil circuit 21 to lead to compensation platform 3 belows, damper piston 8 right sides have oil circuit 22 to lead to compensation platform 3 tops, and damper piston 8 left and right sides are linked up by compensating needle valve 9, and damper piston also has two bleed off circuits 19,20 up and down.After control mouth 15 was opened, pressure oil flow to or flows out the compensating feedback device, and the oil pressure feedback of damper piston 8 both sides can act directly on the upper and lower of plunger compensation platform 3 rapidly, so reflection is sensitive, and the control accuracy height.By alleviating and eliminating because the variation that the disturbance of the speed of driving engine or load brings the operation of stablizing driving engine and governor.In the compensating feedback device, act on the pressure reduction of plunger compensation platform between about in the of 3 and be perceived as the ccasual negative-feedback signal.Hydraulic oil flows to or flows out the compensating feedback device, force damper piston 8 to move by flow direction, damper piston 8 spring load is on one side increased, and the load of another side spring reduces, thereby produced a small difference of pressure on damper piston 8 both sides, higher with respect to the pressure that is compressed spring one end.Pressure is passed to the both sides of plunger compensation platform 3, has produced a power up or down, recenters to impel plunger 1, has adjusted oil mass up to correctly.
In case speed setting or load have big variation, damper piston 8 is just done significantly and is moved, open the BPO Bypass Orifice 16 of bleed off circuit 19,20 rapidly, the pressure reduction at damper piston 8 two ends is limited at maxim, hydraulic oil flows directly into or flows out power cylinder 11, so that the big variation of 5 pairs of speed settings of power piston or load is made actively, the fast speed response.
The oil duct that compensating needle valve 9 will cushion both sides is logical, and being provided with of compensating needle valve 9 apertures determined to compensate the speed that platform two ends pressure reduction descends, and governor can be complementary with the characteristic of driving engine.Along with pressure differential disappears, the external force that acts on the recoil spring 7 disappears, and makes damper piston 8 come back to its center.
The setting value that gathers way or increase load on given speed, its effect all is the same.In either case, fly iron 12 and all will close up,, engine speed is reduced, thereby the centnifugal force that brings reduces no matter be because joining fast spring 13 compressive forces increases.Fly closing up and converting moving down of plunger 1 to of iron 12, at this moment control mouth 15 is opened, pressure oil flows into the compensating feedback device, promoting damper piston 8 moves to power cylinder 11 directions, then, the pressure oil propulsion power piston 5 of discharging from assistant cylinder moves up, promptly to the direction motion that increases fuel feeding.Meanwhile, the pressure on damper piston 8 both sides has been passed to the both sides up and down of plunger compensation platform 3, and obviously the pressure below is big relatively, and this will produce a balancing force that makes progress on compensation platform 3.The size of balancing force is proportional to the displacement of damper piston 8, the rigidity of recoil spring 7, the rate travel of power piston 5 and the size of compensating needle valve 9 apertures.Balancing force upwards with fly the stack of iron 2 centnifugal forces, make its with join fast spring 13 compressive force balance, impel plunger 1 closing control mouth 15 before driving engine accelerates to set point fully.
Consequent effect is: in accelerator, when governor reaches smooth operation at the higher speed setpoint of expectation or when increasing needed fuel feeding position because of load, with regard to closing control mouth 15, make pressure oil no longer flow into power cylinder 11, thereby power piston 5 stop motions promptly do not provide excessive fuel oil.When driving engine continues when setting the rotating speed point and drive on boldly, the balancing force that acts on compensation platform 3 two ends will progressively reduce the compensation that flies iron 2 centnifugal forces to continuing to increase.By the effect of compensating needle valve 9, the power at compensation platform 3 two ends is with the speed of direct ratio and the lasting rate of acceleration of driving engine balance gradually.Fly the speed that iron 2 centnifugal forces increase if the speed that compensation platform 3 balancing forces reduce is equal to, when fly iron 2 centnifugal forces just with join fast spring 13 compressive forces when equating, the difference of pressure at compensation platform 3 two ends will be reduced to zero.This will make and the overshoot minimum of governor make governor can promptly rebulid stable mode of operation.Being provided with of compensating needle valve 9 apertures determined to compensate the speed that platform 3 two ends pressure reduction descend, and governor can be complementary with the characteristic of driving engine.Along with pressure differential disappears, act on the recoil spring 7 external force and disappear, make damper piston 8 come back to its center.
In case speed setting or load have big variation, damper piston 8 is just done significantly and is moved, open BPO Bypass Orifice 16 rapidly, the pressure reduction at damper piston 8 two ends is limited at maxim, hydraulic oil flows directly into power cylinder 11, so as power piston to the big variation of speed setting or load make actively, fast speed response.
Reduce speed setting value or reduce load on given speed, its effect is with top opposite.
Claims (1)
1, a kind of compensating feedback device of mechanical hydraulic-pressure type governor, governor comprises governor essential part, speed setting part and load control part, the governor essential part comprises oil pump, pressure accumulating chamber, joins fast spring, driving disk assembling, thrust baring, plunger, turnbarrel, compensating feedback device and power cylinder, it is characterized in that the compensating feedback device comprises damper piston (8), recoil spring (7), compensating needle valve (9) and compensation platform (3); Compensation platform (3) directly is connected on the plunger (1), becomes one with plunger (1); One side of damper piston (8) is linked up by oil circuit (17) and control mouthful (15), leads to compensation platform (3) below by oil circuit (21); Damper piston (8) opposite side communicates with power cylinder (11) by oil circuit (18), leads to compensation platform (3) top by oil circuit (22); Damper piston (8) both sides are linked up by compensating needle valve (9), also have two bleed off circuits (19,20) in both sides up and down at damper piston (8).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200420028285 CN2678983Y (en) | 2004-01-19 | 2004-01-19 | Compensation feedback device of mechanical hydraulic governor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200420028285 CN2678983Y (en) | 2004-01-19 | 2004-01-19 | Compensation feedback device of mechanical hydraulic governor |
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| Publication Number | Publication Date |
|---|---|
| CN2678983Y true CN2678983Y (en) | 2005-02-16 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200420028285 Expired - Fee Related CN2678983Y (en) | 2004-01-19 | 2004-01-19 | Compensation feedback device of mechanical hydraulic governor |
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| CN (1) | CN2678983Y (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102337973A (en) * | 2010-10-26 | 2012-02-01 | 重庆红江机械有限责任公司 | Dual-pulse speed regulator |
| CN105604705A (en) * | 2016-01-11 | 2016-05-25 | 重庆红江机械有限责任公司 | Dynamic displacement feedback adjusting type hydraulic speed regulator |
-
2004
- 2004-01-19 CN CN 200420028285 patent/CN2678983Y/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102337973A (en) * | 2010-10-26 | 2012-02-01 | 重庆红江机械有限责任公司 | Dual-pulse speed regulator |
| CN102337973B (en) * | 2010-10-26 | 2013-10-16 | 重庆红江机械有限责任公司 | Dual-pulse speed regulator |
| CN105604705A (en) * | 2016-01-11 | 2016-05-25 | 重庆红江机械有限责任公司 | Dynamic displacement feedback adjusting type hydraulic speed regulator |
| CN105604705B (en) * | 2016-01-11 | 2018-04-03 | 重庆红江机械有限责任公司 | Dynamic displacement feedback regulation formula hydrodynamic governor |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |