CN1821588A - Sleigh mounted electrohydraulic ratio regulating system - Google Patents
Sleigh mounted electrohydraulic ratio regulating system Download PDFInfo
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- CN1821588A CN1821588A CN 200610002237 CN200610002237A CN1821588A CN 1821588 A CN1821588 A CN 1821588A CN 200610002237 CN200610002237 CN 200610002237 CN 200610002237 A CN200610002237 A CN 200610002237A CN 1821588 A CN1821588 A CN 1821588A
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- velocity regulating
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- proportional velocity
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Abstract
The sleigh mounted electrohydraulic ratio regulating system includes one bidirectional variable capacity pump, one bidirectional variable capacity motor, and two sleigh mounted electrohydraulic ratio regulating valves with parallel controlling oil port and connected in the serial loop of the bidirectional variable capacity pump and the bidirectional variable capacity motor. The sleigh mounted electrohydraulic ratio regulating valve includes one main valve and one electrohydraulic ratio regulating valve connected in parallel, the main valve consists of one monoway valve and one hydraulic slide valve connected in parallel, and slide valve has oil passage between the oil inlet and the oil outlet opened while no pressure oil in the control oil port and closed while existing pressure oil in the control oil port. The present invention may be used in class II petroleum explosion preventing area, and has both volume speed regulation and electrohydraulic ratio throttle speed regulation capable of converting automatically.
Description
Technical field
The present invention relates to a kind of speed control system of oil well logging industry skid special use, refer in particular to the volumetric speed control that to realize in the oil hydraulic circuit and the sleigh mounted electrohydraulic ratio regulating system of two kinds of speed-regulating functions of electric-hydraulic proportion throttle grverning.
Background technique
Existing sledge is adorned the volume speed-modulating loop that the Hydraulic Adjustable Speed loop is made up of variable displacement pump, variable displacement motor, is the hydraulic schematic diagram in sledge dress Hydraulic Adjustable Speed loop in the prior art as shown in Figure 1.The changes in flow rate that this loop causes by variable displacement pump change discharge capacity changes the output speed of variable displacement motor, realizes the rotational speed regulation of sledge truck-mounted hoist.Be characterized in: Driving Scheme is succinct, and control is convenient accurately, and still, owing to be subjected to the restriction of loop characteristic, the adjusting of meticulous flow can not be realized in this loop, causes the motor can't proper functioning under the low speed operating mode.
Summary of the invention
In order to overcome the deficiency that motor in the existing loop can't proper functioning under the low speed operating mode, the invention provides a kind of sledge mounted electrohydraulic ratio series flow control valve.This valve can not only the self adaption volume speed-modulating loop, and can be converted to the electric-hydraulic proportion throttling speed control circuit by hydraulic control.
For solving the problems of the technologies described above, the invention provides a kind of sledge mounted electrohydraulic ratio series flow control valve, comprise: an electrohydraulic proportional velocity regulating valve and a main valve, described main valve is in parallel with described electrohydraulic proportional velocity regulating valve, described main valve is to be composed in parallel by an one-way valve and a guiding valve that surges, and the described guiding valve that surges is not when control port has pressure oil, and the oil circuit between the turnover valve port is communicated with, when control port had pressure oil, the oil circuit between the turnover valve port was obstructed.
Further, described electrohydraulic proportional velocity regulating valve is explosion-proof electrohydraulic proportional velocity regulating valve.
Further, described electrohydraulic proportional velocity regulating valve is that Fixed differential reducing valve of series connection is formed before the electro-hydraulic proportional throttle valve.
Further, described electro-hydraulic proportional throttle valve is explosion-proof electro-hydraulic proportional throttle valve.
For solving the problems of the technologies described above, the present invention also provides a kind of skid electro_hydraulic proportional speed control system, comprise two-way variable displacement pump, double-action variable displacement motor and be connected on two-way variable displacement pump respectively and loop that double-action variable displacement motor constitutes between two sledge mounted electrohydraulic ratio series flow control valves, the control port parallel connection of described two sledge mounted electrohydraulic ratio series flow control valves.
Further, described sledge mounted electrohydraulic ratio series flow control valve comprises: an electrohydraulic proportional velocity regulating valve and a main valve, described main valve is in parallel with described electrohydraulic proportional velocity regulating valve, described main valve is to be composed in parallel by an one-way valve and a guiding valve that surges, the described guiding valve that surges is not when control port has pressure oil, oil circuit between the turnover valve port is communicated with, and when control port had pressure oil, the oil circuit between the turnover valve port was obstructed.
Further, described electrohydraulic proportional velocity regulating valve is explosion-proof electrohydraulic proportional velocity regulating valve.
Further, described electrohydraulic proportional velocity regulating valve is that Fixed differential reducing valve of series connection is formed before the electro-hydraulic proportional throttle valve.
Further, described electro-hydraulic proportional throttle valve is explosion-proof electro-hydraulic proportional throttle valve.
The sledge mounted electrohydraulic ratio series flow control valve that the present invention proposes can satisfy the explosion-proof regional usage requirement of oil two classes, skid electro_hydraulic proportional speed control system has volumetric speed control and two kinds of speed-regulating functions of electric-hydraulic proportion throttle grverning and can change automatically, this system can realize the adjusting of meticulous flow, guarantees the normal smooth operation of motor in two kinds of flow control circuits.
Description of drawings
Fig. 1 is the hydraulic schematic diagram in sledge dress Hydraulic Adjustable Speed loop in the prior art;
Fig. 2 is the hydraulic schematic diagram of sledge mounted electrohydraulic ratio series flow control valve in the specific embodiment of the invention;
Fig. 3 is the hydraulic schematic diagram of sleigh mounted electrohydraulic ratio regulating system in the specific embodiment of the invention.
Embodiment
Below in conjunction with the drawings and specific embodiments the present invention is further introduced, but not as a limitation of the invention.
With reference to shown in Figure 2, be a kind of hydraulic schematic diagram of skid electrohydraulic proportional velocity regulating valve.This skid electrohydraulic proportional velocity regulating valve comprises: the guiding valve 4 that surges of Fixed differential reducing valve 1, an electro-hydraulic proportional throttle valve 2, an one-way valve 3 and a 2/2-way, wherein: surge guiding valve 4 when control port X does not have pilot pressure oil, oil circuit is communicated with between the turnover valve port, when control port X had pilot pressure oil, oil circuit was obstructed between the turnover valve port; Thereby electro-hydraulic proportional throttle valve 2 of the output terminal of Fixed differential reducing valve 1 series connection has been formed an electrohydraulic proportional velocity regulating valve; The one-way valve 3 and guiding valve 4 main valves that form in parallel that surge, main valve is in parallel with electrohydraulic proportional velocity regulating valve.The input hydraulic fluid port of Fixed differential reducing valve 1 is connected with a hydraulic fluid port of the guiding valve 4 that surges, and is set to skid electrohydraulic proportional velocity regulating valve pressure hydraulic fluid port P2; Fixed differential reducing valve 1, electro-hydraulic proportional throttle valve 2 is connected with another hydraulic fluid port of the guiding valve 4 that surges, is set to the pressure hydraulic fluid port P1 of skid electrohydraulic proportional velocity regulating valve.
The working principle of this skid electrohydraulic proportional velocity regulating valve is: because Fixed differential reducing valve 1 has guaranteed that the front and back pressure reduction of output of the restriction of the input of hydraulic fluid port P2 and electro-hydraulic proportional throttle valve 2 is definite value, and proportion electro-magnet is regulated output valve port size according to the size of electric current in the electro-hydraulic proportional throttle valve 2, thereby the just corresponding certain output flow of certain input current, different input signals changes, just corresponding different output flows change, thereby can utilize the size that changes electric current to regulate the pressure oil output speed.
Surge the control port X of guiding valve 4 when not having pilot pressure oil at 2/2-way, 2/2-way surge guiding valve 4 spool in position, form path between hydraulic fluid port P2 and the hydraulic fluid port P1, the pressure oil that is entered by hydraulic fluid port P2 flows to hydraulic fluid port P1 by the 2/2-way guiding valve 4 that surges, form free flow, realize the self adaption of volumetric speed control thus.When control port X has pilot pressure oil, the surge spool of guiding valve 4 of 2/2-way is positioned at position, a left side, obstructed by hydraulic fluid port P2 to the oil circuit of hydraulic fluid port P1, the pressure oil that enters through hydraulic fluid port P2 flows to the P1 mouth by explosion-proof electrohydraulic proportional velocity regulating valve, thereby controlled flow, realized the adjusting of meticulous flow in the electric-hydraulic proportion throttling speed control circuit.
It is pointed out that then this electrohydraulic proportional velocity regulating valve is explosion-proof electrohydraulic proportional velocity regulating valve if electro-hydraulic proportional throttle valve 2 is selected explosion-proof electro-hydraulic proportional throttle valve for use, be applicable to the usage requirement of satisfying the explosion-proof regional electrical apparatus element of oil two classes.
With reference to shown in Figure 3, two explosion-proof electrohydraulic proportional velocity regulating valve A of skid and B are connected on respectively between two loops of two-way variable displacement pump P and double-action variable displacement motor M formation, and the pressure control end X parallel connection of two explosion-proof electrohydraulic proportional velocity regulating valve A of skid and B has promptly constituted a sledge and has adorned explosion-proof electro_hydraulic proportional speed control system.This system can realize volumetric speed control and two kinds of speed-regulating functions of electric-hydraulic proportion throttle grverning.The working principle of this system is as follows:
When the control port X of explosion-proof electrohydraulic proportional velocity regulating valve A of skid and B does not have oil pressure, constitute a volume speed-modulating loop.If during two-way variable displacement pump P forward fuel feeding, pressure oil is entered in the main valve by the P1 hydraulic fluid port of the explosion-proof electrohydraulic proportional velocity regulating valve A of skid, guiding valve 4 and one-way valve 3 flow to hydraulic fluid port P2 by surging, among the input double-action variable displacement motor M, double-action variable displacement motor just changes, simultaneously, the pressure oil that is flowed out by double-action variable displacement motor M flows to two-way variable displacement pump P through the guiding valve that surges among the explosion-proof electrohydraulic proportional velocity regulating valve B of skid; If the reverse fuel feeding of two-way variable displacement pump P, pressure oil is entered in the main valve by the P1 hydraulic fluid port of the explosion-proof electrohydraulic proportional velocity regulating valve B of skid, guiding valve 4 and one-way valve 3 flow to hydraulic fluid port P2 by surging, among the input double-action variable displacement motor M, double-action variable displacement motor M counter-rotating, simultaneously, the pressure oil that is flowed out by double-action variable displacement motor M flows to two-way variable displacement pump P through the guiding valve 4 that surges among the explosion-proof electrohydraulic proportional velocity regulating valve A of skid.Owing to all can form free flow, and the discharge capacity of regulating the discharge capacity of two-way variable displacement pump P and double-action variable displacement motor M rotating speed of can regulate double-action variable displacement motor M all, realize the self adaption of volume speed-modulating loop thus from hydraulic fluid port P1 to P2 or hydraulic fluid port P2 to P1.
When the control port X of explosion-proof electrohydraulic proportional velocity regulating valve A of skid and B has oil pressure, the guiding valve 4 inner spools transposition of surging among explosion-proof electrohydraulic proportional velocity regulating valve A of skid and the B, the oil circuit of above-mentioned two valves of flowing through this moment is obstructed.If during two-way variable displacement pump P forward fuel feeding, pressure oil is entered in the main valve by the P1 hydraulic fluid port of the explosion-proof electrohydraulic proportional velocity regulating valve A of skid, flow to hydraulic fluid port P2 by one-way valve 3, form free flow, among the input double-action variable displacement motor M, double-action variable displacement motor M just changes, simultaneously, the pressure oil that is flowed out by double-action variable displacement motor M flows to the explosion-proof electrohydraulic proportional velocity regulating valve B of skid, this moment, the pressure oil that enters by the P2 hydraulic fluid port input of the explosion-proof electrohydraulic proportional velocity regulating valve B of skid can only flow to hydraulic fluid port P1 by explosion-proof electrohydraulic proportional velocity regulating valve, and then flowed to two-way variable displacement pump P; Thereby the formation control flow rate realizes the adjusting of meticulous flow in the electric-hydraulic proportion throttling speed control circuit; If during two-way variable displacement pump P counter-rotating, pressure oil is entered in the main valve by the P1 hydraulic fluid port of the explosion-proof electrohydraulic proportional velocity regulating valve B of skid, flow to hydraulic fluid port P2 by one-way valve 3, form free flow, among the input double-action variable displacement motor M, double-action variable displacement motor M just changes, simultaneously, the pressure oil that is flowed out by double-action variable displacement motor M flows to the explosion-proof electrohydraulic proportional velocity regulating valve A of skid, this moment, the pressure oil that enters by the P2 hydraulic fluid port input of the explosion-proof electrohydraulic proportional velocity regulating valve A of skid can only flow to hydraulic fluid port P1 by explosion-proof electrohydraulic proportional velocity regulating valve, and then flowed to two-way variable displacement pump P; Thereby the formation control flow rate realizes the adjusting of meticulous flow in the electric-hydraulic proportion throttling speed control circuit.
Claims (9)
1, a kind of sledge mounted electrohydraulic ratio series flow control valve, comprise: an electrohydraulic proportional velocity regulating valve, it is characterized in that, this series flow control valve also comprises a main valve, and described main valve is in parallel with described electrohydraulic proportional velocity regulating valve, and described main valve is to be composed in parallel by an one-way valve and a guiding valve that surges, the described guiding valve that surges is not when control port has pressure oil, oil circuit between the turnover valve port is communicated with, and when control port had pressure oil, the oil circuit between the turnover valve port was obstructed.
2, a kind of sledge mounted electrohydraulic ratio series flow control valve as claimed in claim 1 is characterized in that described electrohydraulic proportional velocity regulating valve is explosion-proof electrohydraulic proportional velocity regulating valve.
3, a kind of sledge mounted electrohydraulic ratio series flow control valve as claimed in claim 1 is characterized in that, described electrohydraulic proportional velocity regulating valve is that Fixed differential reducing valve of series connection is formed before the electro-hydraulic proportional throttle valve.
4, a kind of sledge mounted electrohydraulic ratio series flow control valve as claimed in claim 3 is characterized in that described electro-hydraulic proportional throttle valve is explosion-proof electro-hydraulic proportional throttle valve.
5, a kind of sleigh mounted electrohydraulic ratio regulating system, comprise two-way variable displacement pump, double-action variable displacement motor, it is characterized in that, this system also comprises two sledge mounted electrohydraulic ratio series flow control valves between the loop that is connected on two-way variable displacement pump and double-action variable displacement motor formation respectively, the control port parallel connection of described two sledge mounted electrohydraulic ratio series flow control valves.
6, a kind of sleigh mounted electrohydraulic ratio regulating system as claimed in claim 5, it is characterized in that, described sledge mounted electrohydraulic ratio series flow control valve comprises: an electrohydraulic proportional velocity regulating valve and a main valve, described main valve is in parallel with described electrohydraulic proportional velocity regulating valve, described main valve is to be composed in parallel by an one-way valve and a guiding valve that surges, and the described guiding valve that surges is not when control port has pressure oil, and the oil circuit between the turnover valve port is communicated with, when control port had pressure oil, the oil circuit between the turnover valve port was obstructed.
7, a kind of sleigh mounted electrohydraulic ratio regulating system as claimed in claim 6 is characterized in that, described electrohydraulic proportional velocity regulating valve is explosion-proof electrohydraulic proportional velocity regulating valve.
8, a kind of sleigh mounted electrohydraulic ratio regulating system as claimed in claim 6 is characterized in that, described electrohydraulic proportional velocity regulating valve is that Fixed differential reducing valve of series connection is formed before the electro-hydraulic proportional throttle valve.
9, a kind of sledge mounted electrohydraulic ratio series flow control valve as claimed in claim 8 is characterized in that described electro-hydraulic proportional throttle valve is explosion-proof electro-hydraulic proportional throttle valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006100022379A CN100374735C (en) | 2006-01-24 | 2006-01-24 | Sleigh mounted electrohydraulic ratio regulating system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006100022379A CN100374735C (en) | 2006-01-24 | 2006-01-24 | Sleigh mounted electrohydraulic ratio regulating system |
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| Publication Number | Publication Date |
|---|---|
| CN1821588A true CN1821588A (en) | 2006-08-23 |
| CN100374735C CN100374735C (en) | 2008-03-12 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNB2006100022379A Active CN100374735C (en) | 2006-01-24 | 2006-01-24 | Sleigh mounted electrohydraulic ratio regulating system |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101982660A (en) * | 2010-10-29 | 2011-03-02 | 江门市兴江转向器有限公司 | Flow control valve of hydraulic steering system |
| CN102852905A (en) * | 2012-07-25 | 2013-01-02 | 浙江工业大学 | Proportion speed regulation experiment system of air motor |
| CN102854805A (en) * | 2012-07-25 | 2013-01-02 | 浙江工业大学 | Proportional speed regulation system for pneumatic motor |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3042837C2 (en) * | 1980-11-13 | 1982-12-09 | Hydromatik Gmbh, 7900 Ulm | Control and regulating device in a hydrostatic transmission |
| DE3421958A1 (en) * | 1984-06-13 | 1985-12-19 | Hydromatik GmbH, 7915 Elchingen | SPEED CONTROL DEVICE FOR A HYDROSTATIC GEARBOX |
| CN2041374U (en) * | 1988-06-10 | 1989-07-19 | 北京起重机器厂 | Hydraulic lifting group valve |
| CN2186329Y (en) * | 1994-03-29 | 1994-12-28 | 洛阳矿山机械工程设计研究院 | Mechanical-hydraulic mixed speed regulating device |
| CN1147421C (en) * | 2001-08-13 | 2004-04-28 | 同济大学 | Novel forklift-walking speed-regulating device |
-
2006
- 2006-01-24 CN CNB2006100022379A patent/CN100374735C/en active Active
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101982660A (en) * | 2010-10-29 | 2011-03-02 | 江门市兴江转向器有限公司 | Flow control valve of hydraulic steering system |
| CN102852905A (en) * | 2012-07-25 | 2013-01-02 | 浙江工业大学 | Proportion speed regulation experiment system of air motor |
| CN102854805A (en) * | 2012-07-25 | 2013-01-02 | 浙江工业大学 | Proportional speed regulation system for pneumatic motor |
| CN102854805B (en) * | 2012-07-25 | 2014-11-12 | 浙江工业大学 | Proportional speed regulation system for pneumatic motor |
| CN102852905B (en) * | 2012-07-25 | 2015-01-28 | 浙江工业大学 | Proportion speed regulation experiment system of air motor |
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| Publication number | Publication date |
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| CN100374735C (en) | 2008-03-12 |
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