CN204041575U - A kind of constant-pressure control device for oil hydraulic pump - Google Patents
A kind of constant-pressure control device for oil hydraulic pump Download PDFInfo
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- CN204041575U CN204041575U CN201420487084.1U CN201420487084U CN204041575U CN 204041575 U CN204041575 U CN 204041575U CN 201420487084 U CN201420487084 U CN 201420487084U CN 204041575 U CN204041575 U CN 204041575U
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Abstract
The utility model discloses a kind of constant-pressure control device for oil hydraulic pump.Wherein, fine filter filler opening is communicated with oil hydraulic pump oil drain out, fine filter oil outlet is communicated with the rodless cavity of constant-pressure control valve P mouth, little variable piston simultaneously, constant-pressure control valve A mouth is communicated with damped valve P mouth, constant-pressure control valve T mouth is communicated with fuel tank with damped valve T mouth simultaneously, constant-pressure control valve is controlled mouth and is communicated with constant-pressure control valve P mouth by its inner fixing damping, and damped valve A mouth is communicated with the rodless cavity of large variable piston; Feedback rod is fixedly connected with little variable piston, during to make the proportional spring setting pressure of oil hydraulic pump oil drain out pressure higher than constant-pressure control valve, feedback rod can move to contact with damped valve spool and promote valve core movement to the P mouth of damped valve and be communicated with station with T mouth under the drive of little variable piston; When proportional spring setting pressure lower than constant-pressure control valve of the pressure of oil hydraulic pump oil drain out, feedback rod can be separated with damped valve spool.
Description
Technical field
The utility model relates to a kind of oil hydraulic pump constant-pressure control device, belongs to technical field of hydraulic.
Background technique
Oil hydraulic pump is as the core parts of hydraulic system, and the quality of its performance directly affects the overall performance of hydraulic system.Along with the development of hydraulics, hydraulic system working pressure is more and more higher, and output flow is increasing, and therefore, speed of response when transshipping for oil hydraulic pump answering system and stability it is also proposed more harsh requirement.In order to reduce oil hydraulic pump in its system overload situation applied, produce pressure overload infringement to oil hydraulic pump and hydraulic system element, the normal constant pressure control method that adopts carries out overload protection to oil hydraulic pump.
Traditional constant pressure control method generally adopts adjustable proportion amount of spring compression to have regulated the constant-pressure control valve of pressure regulation power, and hinder with a fixer and coordinate, the constant pressure control method of composition C type guide hydraulic half-bridge mode, the effect of the stability improving oil hydraulic pump constant pressure adjust process is played in fixer resistance.The program can realize hydraulic system overload protection by rational liquid resistance coupling, but the deficiency of depositing both ways: first, when oil hydraulic pump is in overload protection state, due to the existence of fixer resistance, part pilot control hydraulic oil leaks to fuel tank by fixer resistance, does not act on the piston cavity of variable piston completely and impels pump displacement to reduce, increasing with suppression system pressure, therefore, oil hydraulic pump for the speed of response that hydraulic system is transshipped be fixed liquid resistance weaken; Secondly, from the angle of pilot control system damping, in conventional c-guide hydraulic half-bridge control mode, the stability of oil hydraulic pump guide variable control system and rapidity restrict by fixing damping, namely when increasing fixing damping, constant pressure adjust process stability increases, and constant pressure adjust process is steady, but the speed of response of oil hydraulic pump guide variable control system is slack-off, constant pressure adjust process time is elongated, thus cause the infringement of oil hydraulic pump itself and system element, and reduce fixing damping, effect is contrary.Therefore the conventional constant voltage controlling method of this pump exists to be optimized and room for improvement.
Model utility content
The purpose of this utility model is to provide a kind of novel constant-pressure control device for oil hydraulic pump, thus overcomes all or part of defect of prior art.
For achieving the above object, technical solution adopted in the utility model is: the constant-pressure control device that the utility model is used for oil hydraulic pump comprises feedback rod, fine filter, constant-pressure control valve and damped valve, the filler opening of fine filter is communicated with the oil drain out of oil hydraulic pump, the oil outlet of fine filter simultaneously with the P mouth of constant-pressure control valve, the rodless cavity of the little variable piston of oil hydraulic pump is communicated with, the A mouth of constant-pressure control valve is communicated with the P mouth of damped valve, the T mouth of constant-pressure control valve is communicated with outside fuel tank with the T mouth of damped valve simultaneously, the control mouth of constant-pressure control valve is communicated with the P mouth of constant-pressure control valve by the fixing damping of its inside, the A mouth of damped valve is communicated with the rodless cavity of the large variable piston of oil hydraulic pump,
Feedback rod is fixedly connected with little variable piston, during to make proportional spring setting pressure higher than constant-pressure control valve of pressure when the oil drain out of oil hydraulic pump, feedback rod can move to and to contact with the spool of damped valve and to promote this valve core movement until the P mouth of this damped valve is communicated with T mouth under the drive of little variable piston; And when proportional spring setting pressure lower than constant-pressure control valve of the pressure of the oil drain out of oil hydraulic pump, feedback rod can be separated with the spool of described damped valve by little variable piston driving.
Compared with prior art, the utility model has the advantage of:
(1) compared with conventional c-guide hydraulic half-bridge constant pressure control method, the utility model device adopts variable-gain A type guide hydraulic half-bridge to carry out Isobarically Control.The initial stage that the utility model device regulates at overload protection, because of the effect of the valve core reseting spring of damped valve, damped valve is in station that P mouth is communicated with A mouth and has maximum slotted density, do not play throttling action, from the hydraulic oil of the oil drain out of oil hydraulic pump successively via the filler opening of fine filter, the oil outlet of fine filter, constant-pressure control valve P mouth, constant-pressure control valve A mouth, damped valve P mouth, damped valve A mouth flows into the rodless cavity of large variable piston, this control mode avoids the damping that is fixed of part guide hydraulic oil in conventional c-guide hydraulic half-bridge control mode and leaks to fuel tank, and cause speed of response be fixed damping weaken problem, therefore, this control mode speed of response is faster than traditional approach.
(2) the utility model device is in the overload protection middle and later periods, along with the rapid minimizing of hydraulic pressure pump delivery, feedback rod contacts gradually with the spool of damped valve, and making the area of passage between the P mouth of damped valve and A mouth be gradually reduced to fixed value, the area of passage between the P mouth of damped valve and T mouth increases gradually, the adaptive damping that between the P mouth of constant-pressure control valve and A mouth, variable area of passage is formed and the adaptive damping that between the P mouth of damped valve and T mouth, variable area of passage is formed form A type guide hydraulic half-bridge, large variable piston is controlled, therefore along with the continuous minimizing of hydraulic pressure pump delivery, feedback rod promotes the valve core movement of damped valve, orifice size between the P mouth of damped valve and T mouth constantly increases, the effect of bypass earial drainage is strengthened gradually, the fluid flowing into the rodless cavity of large variable piston constantly reduces, namely ride gain diminishes, the movement velocity of the swash plate of large variable piston and oil hydraulic pump is slack-off gradually, this can prevent the pressure of the oil drain out of oil hydraulic pump from producing pressure fluctuation because pilot control is unstable, therefore, the later stage stability of oil hydraulic pump pilot control system is stronger than traditional approach.
(3) constant-pressure control device of the present utility model is opened because damped valve is just fed bar when hydraulic pressure pump delivery is less and gets involved conciliation, the time of damped valve intervention accounts for the time less of constant pressure adjust process, regulating time can be ignored substantially in whole adjustment process, therefore regulating time is determined by the flow gain of constant-pressure control valve substantially, A type half-bridge stability can be determined by the P mouth of damped valve and T flow area of making a slip of the tongue, therefore, eliminate the stability of pilot control system in traditional control method and the rapidity problem that restriction is mutually set by fixing damping, make the setting of rapidity and stability independent and can be guaranteed simultaneously.
(4) feedback rod adopts the mode be fixedly connected with to be connected with little variable piston, and directly act on the spool of damped valve, the valve port opening of damped valve is controlled, avoids the use of sensor, therefore adopt the utility model device to carry out the mode of Isobarically Control safely, reliably.
Accompanying drawing explanation
Fig. 1 is the hydraulic schematic diagram utilizing constant-pressure control device of the present utility model to control oil hydraulic pump;
Wherein, the large variable piston of 1-, 2-oil hydraulic pump, the little variable piston of 3-, 4-feedback rod, 5-fine filter, 6-constant-pressure control valve, 7-damped valve, 8-fuel tank, 9-swash plate, the rodless cavity of the little variable piston of 10-, the rodless cavity of the large variable piston of 11-, the oil inlet and outlet of the rodless cavity of the large variable piston of 101-, the oil drain out of 201-oil hydraulic pump, the oil inlet and outlet of the rodless cavity of the little variable piston of 301-, the control mouth of 601-constant-pressure control valve, the A mouth of 602-constant-pressure control valve, the T mouth of 603-constant-pressure control valve, the P mouth of 604-constant-pressure control valve, the A mouth of 701-damped valve, the P mouth of 702-damped valve, the T mouth of 703-damped valve.
Embodiment
Below in conjunction with drawings and Examples, the utility model is described in further detail:
As shown in Figure 1, the constant-pressure control device that the utility model is used for oil hydraulic pump 2 comprises feedback rod 4, fine filter 5, constant-pressure control valve 6 and damped valve 7, and wherein, fine filter 5 plays a part to filter guide's hydraulic oil.The filler opening of fine filter 5 is communicated with the oil drain out 201 of oil hydraulic pump 2, the oil outlet of fine filter 5 is communicated with the rodless cavity 10 of the P mouth 604 of constant-pressure control valve, the little variable piston of oil hydraulic pump 2 simultaneously, the A mouth 602 of constant-pressure control valve is communicated with the P mouth 702 of damped valve, the T mouth 603 of constant-pressure control valve is communicated with outside fuel tank 8 with the T mouth 703 of damped valve simultaneously, the control mouth 601 of constant-pressure control valve is communicated with the P mouth 604 of constant-pressure control valve by its inner fixing damping, and the A mouth 701 of damped valve is communicated with the rodless cavity 11 of the large variable piston of oil hydraulic pump 2.Feedback rod 4 is fixedly connected with little variable piston 3, when making proportional spring setting pressure lower than constant-pressure control valve 6 of pressure when the oil drain out 201 of oil hydraulic pump, drives feedback rod 4 to leave the spool of damped valve 7 by the motion of little variable piston 3; And when proportional spring setting pressure higher than constant-pressure control valve 6 of the pressure of the oil drain out 201 of oil hydraulic pump, drive feedback rod 4 to move to by the motion of little variable piston 3 and to contact with the spool of damped valve 7 and to promote this valve core movement until the P mouth of this damped valve 7 is communicated with T mouth.
The utility model constant-pressure control device can control accordingly for the overload protection relieving state of the overload protection state of the normal working of oil hydraulic pump 2, oil hydraulic pump 2, oil hydraulic pump 2.Specific as follows:
Carry out in Isobarically Control process utilizing the utility model constant-pressure control device to oil hydraulic pump 2, when the pressure of the oil drain out 201 of oil hydraulic pump makes oil hydraulic pump 2 be in normal working lower than the proportional spring setting pressure of constant-pressure control valve 6, in the control mouth 601 of constant-pressure control valve, the active force of pressure to its spool of hydraulic oil is less than the active force of proportional spring to its spool of constant-pressure control valve 6, the station making constant-pressure control valve 6 be in its A mouth to be thus communicated with T mouth; And the valve core axis of damped valve 7 is only in P mouth and is communicated with station by the effect of the spring force of its Returnning spring with A mouth.Now, enter the rodless cavity 10 of little variable piston via fine filter 5 from the hydraulic oil of the oil drain out 201 of oil hydraulic pump, the hydraulic oil in the rodless cavity 11 of large variable piston simultaneously enters outside fuel tank 8 via the A mouth 701 of damped valve, the P mouth 702 of damped valve, the A mouth 602 of constant-pressure control valve, the T mouth 603 of constant-pressure control valve successively.Because the hydraulic oil in the rodless cavity 10 of the little variable piston of oil hydraulic pump 2 is from the oil drain out P201 of oil hydraulic pump, and the rodless cavity 11 of the large variable piston of oil hydraulic pump 2 is in unloading condition, pressure in the rodless cavity 10 of i.e. little variable piston is higher than the pressure in the rodless cavity 11 of large variable piston, therefore, the active force of the swash plate 9 of large variable piston 1 pair of oil hydraulic pump 2 is less than the active force of the swash plate 9 of little variable piston 3 pairs of oil hydraulic pumps 2, make the swash plate 9 of oil hydraulic pump 2 to the direction motion that discharge capacity increases, until oil hydraulic pump 2 is in maximum pump discharge state, now, the motion of little variable piston 3 drives feedback rod 4 to leave the spool of damped valve 7, feedback rod 4 is not contacted with the spool of damped valve 7.
The overload protection stage of oil hydraulic pump 2 is divided into three periods: be respectively the adjustment initial stage, regulate mid-term and regulate the later stage.
At the adjustment initial stage, the pressure of the oil drain out 201 of oil hydraulic pump enters the overload protection state of oil hydraulic pump 2 higher than the proportional spring setting pressure of constant-pressure control valve 6, the active force of proportional spring to its spool of constant-pressure control valve 6 is greater than at the active force of pressure to the spool of constant-pressure control valve 6 of the hydraulic oil at control mouth 601 place of constant-pressure control valve, the station that the Switch of working position that constant-pressure control valve 6 is communicated with T mouth by A mouth is communicated with to P mouth with A mouth, the valve core axis of damped valve 7 is still only in P mouth by the effect of the spring force of the Returnning spring of damped valve 7 and is communicated with station with A mouth and is in full-gear.Now, be divided into two-way from after oil outlet successively via the filler opening of fine filter 5, fine filter 5 of the hydraulic oil of the oil drain out 201 of oil hydraulic pump: wherein a road hydraulic oil is entered the rodless cavity 10 of little variable piston by the oil inlet and outlet 301 of the rodless cavity of little variable piston, another road hydraulic oil enters the rodless cavity 11 of large variable piston successively via the oil inlet and outlet 101 of the P mouth 702 of the A mouth 602 of the P mouth 604 of constant-pressure control valve, constant-pressure control valve, damped valve, the A mouth 701 of damped valve, the rodless cavity of large variable piston.Because the pressure in the rodless cavity 10 of little variable piston is substantially identical with the pressure in the rodless cavity 11 of large variable piston, and the size of little variable piston 3 is less than the size of large variable piston 1, therefore, the active force of the swash plate 9 of large variable piston 1 pair of oil hydraulic pump 2 is greater than swash plate 9 active force of little variable piston 3 pairs of oil hydraulic pumps 2, large variable piston 1 promotes the swash plate 9 of oil hydraulic pump 2 to the direction motion that discharge capacity reduces, and the discharge capacity of oil hydraulic pump 2 reduces to contain that the pressure of the oil drain out 201 of oil hydraulic pump raises.Now; although the discharge capacity of oil hydraulic pump 2 reduces; but feedback rod 4 does not still touch the spool of damped valve 7; therefore; this stage damped valve 7 does not have the effect of throttling and fixing damping shunting, and therefore maximum to the ride gain of large variable piston 1, this is reduced to rapidly less state by making the discharge capacity of oil hydraulic pump 2; thus the rising of quick suppression system pressure, protection oil hydraulic pump 2 and system element.
Regulating mid-term, swash plate 9 along with oil hydraulic pump 2 moves and then drives little variable piston 3 to move, feedback rod 4 moves to and contacts with the spool of damped valve 7 under the drive of little variable piston 3, and makes area of passage between the P mouth of damped valve 7 and A mouth be reduced to fixed value gradually; The flow direction of guide's hydraulic oil is consistent for early stage with adjustment; But along with between the P mouth of damped valve 7 and A mouth, area of passage diminishes gradually, throttling action is strengthened gradually, the ride gain of guide's oil circuit to large variable piston 1 diminishes because of throttling action, and the motion of large variable piston 1 and swash plate 9 slows down, and the stability of the Isobarically Control process of oil hydraulic pump 2 improves.
Phase after adjustment, feedback rod 4 continues to move under the drive of little variable piston 3 and the valve core movement promoting damped valve 7 to the P mouth of damped valve 7 is communicated with T mouth, owing to there is fixing damping hole between the P mouth 702 of damped valve and the A mouth 703 of damped valve, therefore area of passage no longer changes, and area of passage increases gradually between the P mouth of damped valve 7 and T mouth, make hydraulic oil from the oil drain out 201 of oil hydraulic pump successively via the filler opening of fine filter 5, the oil outlet of fine filter 5, the P mouth 604 of constant-pressure control valve, the A mouth 602 of constant-pressure control valve, two-way is divided into: wherein a road enters the rodless cavity 11 of large variable piston via the A mouth 701 of damped valve after the P mouth 702 of damped valve enters damped valve 7, another road enters outside fuel tank 8 through the T mouth 703 of damped valve.Therefore, for the oil inlet and outlet 101 of large variable piston, the adaptive damping that variable area of passage between the P mouth 604 of constant-pressure control valve and the A mouth 602 of constant-pressure control valve is formed, and the adaptive damping that the variable area of passage between the P mouth 702 of damped valve and the T mouth 703 of damped valve is formed forms A type guide hydraulic half-bridge.In the process that the spool promoting damped valve 7 at feedback rod 4 constantly moves, because the P mouth 702 of damped valve constantly increases with T mouth 703 area of passage of damped valve, damping between the P mouth 702 of damped valve and the T mouth 703 of damped valve is constantly reduced, the fluid being flowed into fuel tank 8 by the T mouth 703 of damped valve is increased gradually, so the fluid flowing into the rodless cavity 11 of the large variable piston of oil hydraulic pump 2 reduces gradually, the ride gain of large variable piston 1 is reduced further, the motion of the large variable piston 1 of oil hydraulic pump 2 and the swash plate 9 of oil hydraulic pump 2 stops gradually, the discharge capacity of oil hydraulic pump 2 is finally made to maintain a very little state, this discharge capacity only maintains the flow of T mouth 703 earial drainage to fuel tank 8 by damped valve and the internal leakage flow of oil hydraulic pump 2, thus thoroughly the pressure of the oil drain out 201 of containment oil hydraulic pump 2 raises, fluid pump 2 is finally made to be operated in pressure constant state thus.
In a word, the utility model constant-pressure control device is utilized to carry out in Isobarically Control process to oil hydraulic pump, at the adjustment initial stage in overload protection stage, pilot control gain is maximum, thus fast the discharge capacity of oil hydraulic pump 2 is reduced to less state, reduce system overload to the infringement of element in oil hydraulic pump 2 and system; Regulating mid-term, the discharge capacity of oil hydraulic pump 2 reduces further, and the gain of oil hydraulic pump pilot control also reduces, and pilot control system stability strengthens gradually; Phase after adjustment; the adaptive damping that variable area of passage between the P mouth 604 of constant-pressure control valve and the A mouth 602 of constant-pressure control valve is formed; and the adaptive damping that the variable area of passage between the P mouth 702 of damped valve and the T mouth 703 of damped valve is formed forms A type guide hydraulic half-bridge; the swash plate 9 of hydraulic control pump 2 finally reaches steady state, and namely above be variable-gain A type guide hydraulic half-bridge overload protection control procedure.Because this controlling method determines by regulating the initial stage the rapidity that oil hydraulic pump 2 controls, stability ensures by regulating mid-term and later stage, therefore relatively independent at the design aspect controlling rapidity and stability, avoid the problem that in traditional control method, rapidity and stability restrict by fixing damping.
When the pressure of the oil drain out 201 of oil hydraulic pump is got back to the proportional spring setting pressure lower than constant-pressure control valve 6 by the proportional spring setting pressure higher than constant-pressure control valve 6 thus is entered the overload protection relieving state of oil hydraulic pump 2, in the control mouth 601 of constant-pressure control valve, the active force of pressure to its spool of hydraulic oil is less than the active force of proportional spring to its spool of constant-pressure control valve 6, the station that the Switch of working position that constant-pressure control valve 6 is communicated with A mouth by P mouth is communicated with to A mouth with T mouth, damped valve 7 be still in its P mouth simultaneously with A mouth, the station that T mouth is communicated with, hydraulic oil in the rodless cavity 11 of large variable piston is divided into two-way after entering damped valve 7 via the A mouth 701 of damped valve: wherein a road is successively via the P mouth 702 of damped valve, the A mouth 602 of constant-pressure control valve, the T mouth 603 of constant-pressure control valve enters outside fuel tank 8, another road also enters outside fuel tank 8 via the T mouth 703 of damped valve, thus make the rodless cavity 11 of the large variable piston of oil hydraulic pump 2 be in unloading condition.Because the hydraulic oil in the rodless cavity 10 of the little variable piston of oil hydraulic pump 2 is from the oil drain out P201 of oil hydraulic pump, and the rodless cavity 11 of the large variable piston of oil hydraulic pump 2 is in unloading condition, pressure in the rodless cavity 10 of i.e. little variable piston is higher than the pressure in the rodless cavity 11 of large variable piston, therefore, the active force of the swash plate 9 of large variable piston 1 pair of oil hydraulic pump is less than the active force of the swash plate 9 of little variable piston 3 pairs of oil hydraulic pumps, the swash plate 9 of oil hydraulic pump is to the direction motion that discharge capacity increases, the motion of little variable piston 3 drives feedback rod 4 to leave the spool of damped valve 7, feedback rod 4 departs from the contact with the spool of damped valve 7 gradually, damped valve 7 by its P mouth simultaneously with A mouth, the station that the Switch of working position that T mouth is communicated with to only its P mouth is communicated with A mouth, the discharge capacity of oil hydraulic pump 2 gets back to maximum pump discharge state gradually, oil hydraulic pump 2 returns to normal working.
Claims (1)
1. the constant-pressure control device for oil hydraulic pump, it is characterized in that: comprise feedback rod (4), fine filter (5), constant-pressure control valve (6) and damped valve (7), the filler opening of fine filter (5) is communicated with the oil drain out (201) of oil hydraulic pump, the oil outlet of fine filter (5) simultaneously with the P mouth (604) of constant-pressure control valve, the rodless cavity (10) of the little variable piston of oil hydraulic pump is communicated with, the A mouth (602) of constant-pressure control valve is communicated with the P mouth (702) of damped valve, the T mouth (603) of constant-pressure control valve is communicated with outside fuel tank (8) with the T mouth (703) of damped valve simultaneously, the control mouth (601) of constant-pressure control valve is communicated with the P mouth (604) of constant-pressure control valve by the fixing damping of its inside, the A mouth (701) of damped valve is communicated with the rodless cavity (11) of the large variable piston of oil hydraulic pump, feedback rod (4) is fixedly connected with little variable piston (3), during to make proportional spring setting pressure higher than constant-pressure control valve (6) of pressure when the oil drain out (201) of oil hydraulic pump, feedback rod (4) can move to and to contact with the spool of damped valve (7) and to promote this valve core movement until the P mouth of this damped valve (7) is communicated with T mouth under the drive of little variable piston (3), and when proportional spring setting pressure lower than constant-pressure control valve (6) of the pressure of the oil drain out (201) of oil hydraulic pump, feedback rod (4) can be separated with the spool of described damped valve (7) by little variable piston driving.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420487084.1U CN204041575U (en) | 2014-08-27 | 2014-08-27 | A kind of constant-pressure control device for oil hydraulic pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420487084.1U CN204041575U (en) | 2014-08-27 | 2014-08-27 | A kind of constant-pressure control device for oil hydraulic pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204041575U true CN204041575U (en) | 2014-12-24 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420487084.1U Withdrawn - After Issue CN204041575U (en) | 2014-08-27 | 2014-08-27 | A kind of constant-pressure control device for oil hydraulic pump |
Country Status (1)
| Country | Link |
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| CN (1) | CN204041575U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104179734A (en) * | 2014-08-27 | 2014-12-03 | 浙江德泰机电工程有限公司 | Constant-pressure control device and method for hydraulic pump |
| CN111677623A (en) * | 2020-06-19 | 2020-09-18 | 中航力源液压股份有限公司 | Control valve device with override control for pressure difference between inlet and outlet of induction motor |
-
2014
- 2014-08-27 CN CN201420487084.1U patent/CN204041575U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104179734A (en) * | 2014-08-27 | 2014-12-03 | 浙江德泰机电工程有限公司 | Constant-pressure control device and method for hydraulic pump |
| CN111677623A (en) * | 2020-06-19 | 2020-09-18 | 中航力源液压股份有限公司 | Control valve device with override control for pressure difference between inlet and outlet of induction motor |
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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: 20141224 Effective date of abandoning: 20160629 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |