CN1011733B - Flow controlling valve with pressure compensation - Google Patents
Flow controlling valve with pressure compensationInfo
- Publication number
- CN1011733B CN1011733B CN 89105618 CN89105618A CN1011733B CN 1011733 B CN1011733 B CN 1011733B CN 89105618 CN89105618 CN 89105618 CN 89105618 A CN89105618 A CN 89105618A CN 1011733 B CN1011733 B CN 1011733B
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- hole
- valve
- pressure
- flow control
- hydraulic
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- Operation Control Of Excavators (AREA)
Abstract
本发明涉及一种具有压力补偿功能的流量控制阀。其特征在于该阀内设有两个液压腔及连通两液压腔的节流孔；当压力油从第1通孔(35a)流入时，在两液压腔间产生压力差，滑阀左移，开闭开口(44a)打开，使第1通孔与第2通孔(36a)连通；当压力油从第2通孔流入时，滑阀右移，使控制小孔(45a)的开口面积减小，从而使压力油流量保持一定。该流量控制阀结构简单，使成本降低。
The invention relates to a flow control valve with pressure compensation function. It is characterized in that the valve is provided with two hydraulic chambers and an orifice connecting the two hydraulic chambers; when the pressure oil flows in from the first through hole (35a), a pressure difference is generated between the two hydraulic chambers, and the slide valve moves to the left. The opening and closing opening (44a) is opened, so that the first through hole communicates with the second through hole (36a); when the pressure oil flows in from the second through hole, the slide valve moves to the right, so that the opening area of the small control hole (45a) decreases. Small, so that the pressure oil flow can be kept constant. The flow control valve has a simple structure and reduces the cost.
Description
The present invention relates to a kind of flow control valve with pressure compensation.
Flow control valve is to control the flow that passes through with the regulating spool openings of sizes, to realize the speed controlling and the adjusting of operation mechanism.Major requirement to flow control valve is to obtain regime flow, takes pressure compensated method can reach this purpose.
For example, in various engineering machinery such as hydraulic actuated excavator, be equipped with hydraulic actuator, suitably drive these hydraulic actuators, can make this project machinery realize desired action.The action of above-mentioned hydraulic actuator is controlled by selector valve separately, and these selector valves are handled by operating stem.In recent years, the general employing to handle the preposition maneuverability pattern of pressure-driven selector valve, in simple terms, this maneuverability pattern is by pilot line, two control chambers of the symmetrical direction that is located at selector valve is received the hydraulic control circuit that constitutes like this on the pilot valve of operating handle control and is formed.
The selector valve that drives with control hydraulic actuated excavator running motor is the action that example illustrates this hydraulic control circuit device in the past below.When the manipulator with operating handle from middle position when a direction is pulled, from the pressure oil of the operating hydraulically operated pump output that is connected with pilot valve, flow into the pilot line of a corresponding side by pilot valve, to the manipulation chamber fuel feeding of the corresponding side of selector valve.Like this, selector valve is switched to operating position, flows into the main line of a side by selector valve from the pressure oil of Main Hydraulic Pump output, to the running motor fuel feeding, in running motor, made the main line of the pressure oil of merit by opposite side, flow back to fuel tank through the walking selector valve.Like this, running motor rotates, and hydraulic actuated excavator is advanced.
When stopping the walking of hydraulic actuated excavator, the manipulator can be withdrawn into the neutral position with operating handle, and at this moment pilot valve makes this pilot line be communicated with fuel tank the cut-out that is communicated with of the pilot line of operate pump and an above-mentioned side.Like this, the pressure oil in the manipulation chamber of selector valve one side flows back to fuel tank, and selector valve returns back to the neutral position, stops from the pressure oil supply of main pump to running motor, and above-mentioned main line is closed.At this moment, running motor does not stop immediately, because effect of inertia, motor is rotated further, and the result of this rotary action with the pressure oil suction of an above-mentioned side main line, exports the main line of above-mentioned opposite side to.Like this, the oil pressure in the pilot line of the opposite side that it is closed sharply raises, and this elevated pressure becomes retardation pressure, and running motor is stopped.
; in above-mentioned this existing loop apparatus; when operating handle when actuated position returns back to the neutral position; it is very fast that selector valve returns back to the answer speed in neutral position; thereby; the retardation pressure that produces in the main line of above-mentioned opposite side also rises very violently, act on walking when being about to stop the impact on the whole vehicle body of hydraulic actuated excavator also very big.Therefore, its shortcoming can cause the operating characteristics of hydraulic actuated excavator to reduce, and operator's sense of fatigue increases, and can damage the life-span of machinery in addition.This shortcoming is not limited only to above-mentioned hydraulic actuated excavator, also can produce on other the hydraulic actuator of engineering machinery, and particularly, the load inertia of its hydraulic actuator is big more, and then this shortcoming is obvious more.
In order to overcome above-mentioned shortcoming, can between pilot valve and selector valve, flow control valve be set, its control is flowed from the pressure oil of selector valve to pilot valve.The complex structure but existing flow control valve seems, cost is higher.
Therefore, the objective of the invention is to provide a kind of flow control valve with pressure compensation, this valve is installed in the shortcoming that can eliminate above-mentioned prior art in the oil hydraulic circuit, relax the impact of hydraulic actuator when stopping, improve operating characteristics, alleviate operator's sense of fatigue, improve the life-span, and this valve arrangement is simple, and cost is reduced.
Below for implementing the concrete installation drawing of each example of the present invention.
Fig. 1 is the profile of the hydraulic actuated excavator of one of typical engineering machinery of the hydraulic control circuit device that adopts flow control valve of the present invention.
Fig. 2 is the top view of hydraulic actuated excavator shown in Figure 1.
Fig. 3 is for using the hydraulic control circuit of flow control valve of the present invention, and it is applicable to the selector valve of the running motor of hydraulic actuated excavator shown in Figure 1.
Fig. 4 is the enlarged view of flow control valve shown in Figure 3.
Fig. 5 (a) (b) (c) is the coordinate diagram of hydraulic control circuit device action shown in Figure 3 with respect to the time.
Fig. 6 is an alternative embodiment of the invention, is the sectional drawing of a flow control valve.
Fig. 7 is the sectional drawing of known flow control valve.
Now as example preferred example of the present invention is described with regard to situation about using on the hydraulic actuated excavator.Generally, hydraulic actuated excavator as shown in Figures 1 and 2, have top rotating part 1 and base carrier 2, top rotating part 1 rotates by rotary hydraulic motor 3, base carrier 2 relies on walking oil hydraulic motor 5,7 drive left and right crawler belt 4 respectively, 6 walk, shear leg 8 is supported on the top rotating part 1 with freely rotating, on shear leg 8, support cantilever 9 with freely rotating, on cantilever 9, supporting bucket 10, shear leg 8 with freely rotating, cantilever 9, bucket 10 are respectively by shear leg oil hydraulic cylinder 12, and bucket oil hydraulic cylinder 13 drives.
The example of use flow control valve of the present invention as shown in Figure 3 on the driving selector valve of the running motor 5 of controlling this hydraulic actuated excavator.In Fig. 3, symbol 15 expression is installed in the oil hydraulic pump on the hydraulic actuated excavator, and this oil hydraulic pump 15 links to each other with running motor 5 by selector valve 16, and selector valve 16 is controlled from oil hydraulic pump 15 to running motor 5 pressure oil supply.Be provided with a pair of manipulation chamber 16a of symmetrical configuration in the left and right sides of selector valve 16,16b.Symbol 17 is a fuel tank.Selector valve 16 and a pair of main line 18a of running motor 5 usefulness, 18b links to each other, and between these main lines, safety valve 19 in cross-over connection.
As shown in the figure, the flow control valve 33a with pressure compensation of the present invention, 33b and pilot line 31a, 32a and pilot line 31b, 32b links to each other.
Referring now to Fig. 4 flow control valve 33a is described, the detailed structure of 33b, Fig. 4 has only represented the flow control valve 33a of a side, the structure of the flow control valve 33b of opposite side is identical therewith, so its figure all omits with explanation.
Flow control valve 33a has valve pocket 34a, valve body 37a, the 1st through hole 35a links to each other with pilot line 31a, the passage 30a of pilot line 31a and pilot valve 24 links, the 2nd through hole 36a links to each other with pilot line 32a, and the manipulation chamber 16a of pilot line 32a and selector valve 16 links to each other, and guiding valve 38a can be free to slide in the valve pocket 34a of valve body 37a, the 1st hydraulic pressure cavity 40a and the 2nd hydraulic pressure cavity 42a are arranged on guiding valve 38a, and hydraulic pressure cavity 40a is connected with the 1st through hole 35a by radial hole 39a; Hydraulic pressure cavity 42a is connected with the 2nd through hole 36a by radial hole 41a, between the 1st and the 2nd hydraulic pressure cavity 40a and 42a throttle orifice 43a is arranged, throttle orifice 43a is communicated with two hydraulic pressure cavity simultaneously, when pressure oil passes through throttle orifice 43a, between two hydraulic pressure cavity, produce pressure difference, make guiding valve produce displacement.When having pressure oil to flow into from the 1st through hole 35a, because pressure difference produces the displacement of guiding valve 38a, the switching opening 44a that formation communicates the 1st through hole 35a and the 2nd through hole 36a, simultaneously, when having pressure oil to flow into from the 2nd through hole 36a, ability adapts with the pressure difference that the displacement that is produced guiding valve 38a by above-mentioned pressure difference causes, opening area is reduced, formation is from the 2nd through hole 36a, through the 2nd hydraulic pressure cavity 42a, throttle orifice 43a, the 1st hydraulic pressure cavity 40a keeps the certain control aperture 45a of pressure oil flow that flows out from the 1st through hole 35a.
In illustrated example, throttle orifice 43a makes hole shape.In illustrated example, open and close opening 44a by the interior bore portion of the circular groove 46a that on the cylindrical of guiding valve 38a, makes with the valve pocket 34a that can only contact with the shoulder 47a of the 2nd through hole 36a one side of circular groove 46a, promptly the 1st shoulder 48a forms, like this, circular groove 46a is communicated with the 1st through hole 35a usually, at the 2nd through hole 36a place, when not having pressure oil to flow into the 1st through hole 35a, because shoulder 47a contacts with shoulder 48a, connection is cut off, have only because pressure oil flows into pressure official post guiding valve 38a that the 1st through hole 35a causes when producing displacement, shoulder 47a and shoulder 48a just leave, and become to interconnect.Control aperture 45a closes the interior bore portion of this radial hole 39a valve pocket 34a by the 1st radial hole 39a with being in part, and promptly the 2nd shoulder 49a constitutes.
Between the end face of guiding valve 38a and valve pocket 34a, be provided with the 1st and the 2nd and the spring 50a of positioned opposite, 51a, the elastic force of the 1st spring 50a is determined byer force, the elastic force of the 2nd spring 51a a little less than.
Secondly, the action of present embodiment can be illustrated with reference to the time diagram shown in Fig. 5 (a)-(c).
Now, when the manipulator at time t
1With operating handle 23 when pull in the left side of figure, the guiding valve 26a of pilot valve 24 moves, by the pressure oil of operating hydraulically operated pump 21 outputs, through passage 28, valve pocket 25a, passage 30a, pilot line 31a is to the I through hole 35a of flow control valve 33a fuel feeding, and this strand pressure oil is from I through hole 35a, through radial hole 39a, I hydraulic pressure cavity 40a, 43a flow into the 2nd hydraulic pressure cavity 42a, flow out to the 2nd through hole 36a from radial hole 41a again.At this moment, produce pressure difference between the 1st and the 2nd hydraulic pressure cavity 40a of throttle orifice 43a both sides and 42a, when this pressure difference acts on the elastic force of the force rate spring 51a on the guiding valve when big, the guiding valve 38a that is in the diagram neutral position will move to the left side of figure.Like this, shoulder 47a and the shoulder 48a of guiding valve 38a leave, and the circular groove 46a of guiding valve 38a is connected with the 2nd through hole 36a, flows into the pressure oil of the 1st through hole 35a, flow out to the 2nd through hole 36a through circular groove 46a.Because the elastic force of spring 51a select a little less than, above-mentioned guiding valve 38a to left movement, produce in the short time after pressure oil flows into the 1st through hole 35a, pressure oil is free-flow without any restriction from the 1st through hole 35a to the 2nd through hole 36a mobile.
Flow to the pressure oil of the 2nd through hole 36a, process pilot line 32a is to the manipulation chamber of selector valve 16 16a fuel feeding.Like this, shown in Fig. 5 (b), selector valve 16 is at time t
3Begin action, at time t
4Reach maximum displacement amount.Time t
4Certain hysteresis is arranged than the time under the loop apparatus situation that does not have flow control valve, about this hysteresis narration more later on.
When selector valve 16 when middle position is moved to the left, to running motor 5 fuel feeding, shown in Fig. 5 (c), the effective pressure of running motor 5 raises the pressure oil of oil hydraulic pump 15 through selector valve 16, main line 18b, and begins to rotate.And, at time t
4After, continue normal rotation, make hydraulic actuated excavator work.From time t
3To time t
4Between, the curve shape that above-mentioned effective pressure raises is different with the curve shape of the loop apparatus that does not have flow control valve, about this point also narration afterwards.
When reaching time t
5, if operating handle 23 is mediated, the valve pocket 25a of pilot valve 24 is communicated with operating oil tank 17.Therefore, the 1st through hole 35a, radial hole 39a, the 1st hydraulic pressure cavity 40a is communicated with fuel tank 17, the pressure height of pressure ratio the 1st hydraulic pressure cavity 40a of the 2nd hydraulic pressure cavity 42a.Like this, the pressure oil to the manipulation chamber of selector valve 16 16a supply flows to flow control valve 33a from the 2nd through hole 36a.This strand pressure oil, from radial hole 41a, the 2nd hydraulic pressure cavity 42a, by throttle orifice 43a, through the 1st hydraulic pressure cavity 40a, radial hole 39a, the 1st through hole 35a, pilot line 31a, pilot valve 24 flow into fuel tank 17.At this moment, the oil mass by throttle orifice 43a increases, if when the 1st and the 2nd hydraulic pressure cavity 40a of throttle orifice 43a both sides and elastic force that the pressure difference between the 42a acts on the force rate spring 50a on the guiding valve are big, guiding valve 38a moves right.Like this, the opening area A of the control aperture 45a that radial hole 39a and shoulder 49a form diminishes, and from the 1st hydraulic pressure cavity 40a, the pressure oil mass that flows out by this aperture is restricted.Like this, it is certain that the pressure difference between the 1st and the 2nd hydraulic pressure cavity 40a and the 42a keeps, also certain from the pressure oil that the 1st hydraulic pressure cavity 40a flows out.In this case, when the oil pressure that flows into the 2nd through hole 36a increases, because above-mentioned opening area A further reduces, it is certain that pressure difference keeps, on the contrary, and when the oil pressure that flows into the 2nd through hole 36a reduces, because it is big that above-mentioned opening area A becomes, and pressure difference also keeps necessarily, in other words, and through handling chamber 16a, pilot line 32a, from flow control valve 33a to pilot line 31a, pilot valve 24, the flow of the oil that fuel tank 17 flows out often is certain.Therefore such as Fig. 5 (b) shown in, even operating handle 23 returns back to the neutral position hastily, the answer speed of selector valve 16 also can lag behind, approximately will be than time t
7Also want much slow time t
8Just can return back to the neutral position.
As mentioned above, when the answer limited speed system of selector valve 16 position in the middle of it, main line 18a, 18b can not cut off hastily yet, and therefore, like that, the retardation pressure rising that produces in main line 18a has also become slowly shown in Fig. 5 (c).Like this, act on the impact on the whole of hydraulic actuated excavator vehicle body during parking and also relaxed widely, improved operating characteristics and mechanical life, operator's sense of fatigue has also lowered.
When below operating handle 23 being handled from middle position, action t lag time of selector valve 16
4And running motor 5
The curve shape that effective pressure raises describes.As mentioned above, when operating handle 23 is pulled the left side, at time t
3Selector valve 16 just begins to switch.In this case, on flow control valve 33a, produce the pressure loss hardly.When selector valve 16 begins to switch, at the manipulation chamber 16b of selector valve 16 and the pressure oil among the pilot line 32b, through flow control valve 33b, pilot line 31b, pilot valve 24 is discharged to fuel tank 17.At this moment, the 2nd through hole 36a that is equivalent to flow control valve 33a from the 2nd through hole 36b(of flow control valve 33b) flow to the 1st through hole 35a that the 1st through hole 35b(is equivalent to flow control valve 33a) pressure oil, as described in the flow control valve 33a, also be restricted.Like this, selector valve 16 reaches the time t of maximum displacement
4Also lag behind than the time under the situation that does not have flow control valve 33b.But, in this case, at the action elapsed time of selector valve 16 t
3Handle chamber 16b and be in the state that is connected with fuel tank 17, even since selector valve 16 from then on state mobile pressure oil is extruded from handling chamber 16b, distortion and the compressibility of oil own that this strand pressure oil is configured the high pressure hose of pipeline absorb, and be equivalent to the throttle orifice 43a of flow control valve 33a by the throttle orifice 43b(of flow control valve 33b) flow very little, the pressure difference of throttle orifice 43b both sides is also very little, thereby the degree of pressure oil restricted in flow system is little.Yet, though this confined degree reduces, but because of still existing of restriction itself, so the switch speed of selector valve 16 lags behind, like this, through main line 18b, the pressure of supplying with the pressure oil of running motor 5 raises and has become slowly, like that, the impact during running motor 5 startings has also just relaxed shown in Fig. 5 (c).
Like this, in this example, because flow control valve is to be placed on two pilot lines that connect pilot valve and selector valve, the impact in the time of therefore can relaxing the running motor parking with starting, and then can improve operating characteristics, life-span, and can alleviate operator's sense of fatigue.
In addition, in the present embodiment, owing to connected flow control valve with pressure compensation, when pressure oil flows into the 2nd through hole, even because the change of hydraulic actuator load causes the pressure surge of pressure oil, still can access certain flow, running motor can be realized more stable parking.
In addition, in illustrated example, when pressure oil flows into the 2nd through hole, because the restriction that pressure oil is flowed is by realizing that as throttling pore that produces pressure difference and control aperture their opening areas can be bigger, therefore can not produce the misgivings of the little hole plug that the dust in the pressure oil causes, and, because the existence of aperture, even oil viscosity increases during low temperature, the pressure loss during by aperture also can reduce, and reaches the pressure compensation that keeps certain.
According to present embodiment, with the valve pocket endoporus of guiding valve and the switching opening and the control aperture of its spool formation flow control valve, structure is very simple, and cost can reduce.
Fig. 6 is the sectional drawing of the flow control valve of another embodiment of the present invention.Among the figure, 50 expression flow control valves, this flow control valve 50 has replaced the flow control valve 33a with pressure compensation in the previous examples, and 33b is connected between pilot line 31a and the 32a and between 31b and the 32b.51 is pilot line 31a, the 1st through hole that 31b links to each other, and 52 are and pilot line 32a, the 2nd through hole that 32b links to each other.53 is spool, 54 springs for pushing spool 53, and 55a, 55b are the 1st and the 2nd hydraulic pressure cavity, and 56 are the throttle orifice with elongated hole shape at spool 53 tops, and 57 is at UNICOM the 1st and the 2nd hydraulic pressure cavity 55a, the hole between the 55b on the spool 53,58 is valve seat.
In oil hydraulic circuit shown in Figure 3, be provided with the flow control valve 33a that this flow control valve 50 replaces having pressure compensation, 33b, when operating handle 23 when pull on the left side, oil by operating hydraulically operated pump 21 outputs, through pilot valve 24, pilot line 31a is to the 1st through hole 51 fuel feeding of flow control valve 50.Because like this, spool 53 overcomes the elastic force of spring 54, is pushed to the below, and pressure oil is by the 1st through hole 51, the 1 hydraulic pressure cavity 55b, hole 57, the 2 hydraulic pressure cavity 55a, and the 2nd through hole 52 passes through pilot line 32a again, to the manipulation chamber of selector valve 16 16a fuel feeding.At this moment, on flow control valve 50, produce the pressure loss hardly.When selector valve 16 begins when mobile, handle the oil among the 16b of chamber, through pilot line 32b, flow control valve 50, pilot line 31b, pilot valve 24 flows back to fuel tank.At this moment, in flow control valve 50, because pressure oil passes through throttle orifice 56, it is slower that the switch speed of selector valve 16 is wanted, and the impact when making running motor 5 startings relaxes.
When operating handle 23 is returned back to the neutral position, when running motor 5 stops, handling chamber 16a, the oil of pilot line 32a flows to the 2nd through hole 52 of flow control valve 50, and the top of spool 53 is pressed on the valve seat 58.Thereby pressure oil only flows to the 2nd through hole 51, process pilot line 31a by throttle orifice 56, and pilot valve 24 is expelled to fuel tank 17.Like this, the oil return of pressure oil is subjected to the restriction of throttle orifice 56, and the answer speed of selector valve 16 becomes slow, and like this, the retardation pressure of main line 18a raises slowly, and the impact when running motor 5 stops can relax significantly.
Like this, in the present embodiment, because flow control valve is installed on two pilot lines that connect pilot valve and selector valve, the same with former example, reach in the time of also can and stopping when starting and relax the effect of impacting, and, because flow control valve is simple in structure, and cost is reduced more.
Fig. 7 is known flow control valve sectional drawing.Symbol 60 is represented the flow control valve of known band pressure compensation among the figure, its structure is different with the flow control valve 33a with pressure compensation shown in Figure 4, this flow control valve 60, on hydraulic control circuit device shown in Figure 3, replace flow control valve 33a and 33b, be connected between pilot line 31b and the 32b.Flow control valve 60 has the 1st and the 2nd through hole 61 and 62, the 1 through holes 61 to link to each other with 31b with pilot line 31a, and the 2nd through hole 61 links to each other with 32b with pilot line 32a.Be provided with the through hole 63 that links to each other with these through holes between the 1st and the 2nd through hole 61 and 62 respectively, 64, the one-way valve 65 that flows to the 2nd through hole 62 by an authorized pressure oil from the 1st through hole 61 with partly be connected with the guiding valve 66 of one-way valve parallel configuration and pressure compensation with aperture 67.Guiding valve 66 has major diameter part 66a and small diameter portion 66b at two ends, they are free to slide in the 1st and the 2nd hydraulic pressure cavity 68a and 68b respectively, and the 1st with the 2nd hydraulic pressure cavity 68a and 68b between form the intermediate cavity 70 be communicated with the 2nd through hole 62, and be connected with inner passage 69.External lateral portion at the 1st hydraulic pressure cavity 68a is equipped with spring 71, and this part is communicated with the 1st through hole 61 by passage 72.The inside part of the 1st hydraulic pressure cavity 68a is connected with inner passage 69 by passage 73 and 74 respectively with the 2nd hydraulic pressure cavity 68b.Aperture 67 is positioned at the connection part of inner passage 69 and the 1st through hole 61, and it is to form by the crescent-shaped slot of opening on the manual rod 67a, and dwang 67a can change the position of groove, thereby can adjust the opening area of aperture.
In this flow control valve 60, when pressure oil flowed into the 1st through hole 61, this strand pressure oil freely flowed to the 2nd through hole 62 by one-way valve 65.When pressure oil flowed into the 2nd through hole 62, this strand pressure oil was by intermediate cavity 70, and inner passage 69 reaches aperture 67 and flows to the 1st through hole.At this moment, pressure oil relies on by aperture 67, between inner passage 69 and the 1st through hole 61, produce pressure difference, this pressure difference is transferred to the 1st and the 2nd hydraulic pressure cavity 68a and 68b, with this pressure difference, guiding valve 66 moves right, and like this, the opening area of formed aperture 75 reduces between small diameter portion 66b and intermediate cavity 70 the 2nd through hole 62 open parts.Therefore, the flow that flows into the pressure oil of the 1st through hole 61 by the 2nd through hole 62 keeps certain.
Therefore, in hydraulic control circuit device shown in Figure 3,, also can obtain and the usefulness flow control valve 33a effect identical with 33b with this flow control valve 60 with pressure compensation.But this flow control valve arrangement is complicated, and cost is higher.
In above-mentioned each example, be that example is illustrated with the running motor selector valve of hydraulic actuated excavator, but obviously, be not limited only to this, in the selector valve of the various executive components of various engineering machinery, also all be suitable for.In addition, more than utilize on two pilot lines, flow control valve to be set all and to illustrate, still,, also can only be located on the side pilot line according to the variation of executive component or loading condition for example.
Above-mentioned each example is to be the example explanation to have two of symmetrical configuration selector valves of handling chambeies, still, also can use at one end to be provided with at those and handle the chamber, has only the spring selector valve of effect separately at the other end.
Claims (5)
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13559885U JPH0449688Y2 (en) | 1985-09-06 | 1985-09-06 | |
| JP135597/85 | 1985-09-06 | ||
| JP135598/85 | 1985-09-06 | ||
| JP1985135597U JPH032722Y2 (en) | 1985-09-06 | 1985-09-06 | |
| CN86106036.9A CN1007447B (en) | 1985-09-06 | 1986-09-06 | Hydraulic control circuit device for control reversing valve |
Related Parent Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN86106036 Division | 1986-09-06 | ||
| CN86106036.9A Division CN1007447B (en) | 1985-09-06 | 1986-09-06 | Hydraulic control circuit device for control reversing valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1039476A CN1039476A (en) | 1990-02-07 |
| CN1011733B true CN1011733B (en) | 1991-02-20 |
Family
ID=27178854
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 89105618 Expired CN1011733B (en) | 1985-09-06 | 1986-09-06 | Flow controlling valve with pressure compensation |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1011733B (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102536939B (en) * | 2012-01-04 | 2015-01-14 | 安徽博一流体传动股份有限公司 | Root overflow valve |
| JP5848721B2 (en) * | 2013-03-21 | 2016-01-27 | 川崎重工業株式会社 | Buffer valve |
| US9970571B2 (en) * | 2013-06-20 | 2018-05-15 | Shimadzu Corporation | Pressure control valve and control valve |
| CN106439145A (en) * | 2016-11-25 | 2017-02-22 | 合肥协力液压科技有限公司 | Hydraulic valve |
| SI3635282T1 (en) * | 2017-06-09 | 2022-05-31 | BUFFO, Salvatore | Safety valve for hydraulic systems |
| CN107883034A (en) * | 2017-10-11 | 2018-04-06 | 中国航发西安动力控制科技有限公司 | A kind of dual spring pressure difference slide valve assembly |
| CN108379711B (en) * | 2018-04-28 | 2024-05-14 | 佘小斌 | Water flow control device, condensed water collecting cup and breathing machine |
| CN108953648B (en) * | 2018-07-26 | 2019-10-08 | 新沂市佳富弘电子科技有限公司 | A kind of multi-function electromagnetic valve |
| CN109268551A (en) * | 2018-11-20 | 2019-01-25 | 中国船舶重工集团公司第七0四研究所 | Self-operated multi-stage throttle oil pressure regulating valve |
| CN113883116B (en) * | 2021-09-29 | 2025-07-18 | 三一汽车制造有限公司 | Oil drain valve, energy storage device, hydraulic system and working machine |
-
1986
- 1986-09-06 CN CN 89105618 patent/CN1011733B/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| CN1039476A (en) | 1990-02-07 |
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